CN210307659U

CN210307659U - Hand tool

Info

Publication number: CN210307659U
Application number: CN201920199684.0U
Authority: CN
Inventors: 谢明健; 李佶; 钟红风; 张士松
Original assignee: Positec Power Tools Suzhou Co Ltd
Current assignee: Positec Power Tools Suzhou Co Ltd
Priority date: 2018-02-14
Filing date: 2019-02-14
Publication date: 2020-04-14
Anticipated expiration: 2029-02-14
Also published as: CN212497584U; CN212497586U; CN110153959A; CN212497583U; CN212497585U; CN212497582U; CN212706597U

Abstract

The utility model discloses a hand-held tool. The hand tool includes a motor, a drive shaft, a hammer impact mechanism, and a tool spindle. The drive shaft is rotated by the motor and rotates about the drive shaft axis. The hammer impact mechanism is provided with a hammer, and the hammer is sleeved outside the transmission shaft and can be driven to rotate by the transmission shaft. The tool spindle is connected with the transmission shaft, the tool spindle is movable relative to the transmission shaft, and the hammer impact mechanism further comprises a guide piece and an intermittent impact assembly which are arranged on the outer side of the hammer. When the ram is rotated, the intermittent impact assembly drives the ram to move linearly relative to the guide member along a predetermined path and to impact the tool spindle in at least one operating condition. According to the utility model discloses a hand tool utilizes clearance impact assembly, ram and the cooperation relation of guide, can guide the ram and make linear motion, and the ram can also strike the cutter main shaft to can realize the ascending removal of cutter main shaft axis, hand tool's structure sets up compactness and simple structure moreover, can conveniently carry.

Description

Hand tool

Technical Field

The utility model relates to an strike drilling technical field, particularly, especially, relate to a hand-held tool.

Background

In the field of percussion drilling technology, a rotary striking mechanism is driven by a motor as a driving source to provide rotation and striking to a gun drill, thereby intermittently transmitting a rotary striking force to a tip tool in order to perform an operation such as tightening a screw. In the related art, an active impact structure is mounted on a common gun drill to form an impact drill mode, and the overall length of the gun drill is too large and the structure is complex.

SUMMERY OF THE UTILITY MODEL

The utility model discloses aim at solving one of the technical problem that exists among the prior art at least. Therefore, the utility model provides a hand-held tool, hand-held tool has simple structure, advantage that work efficiency is high.

The utility model provides a technical scheme: a hand tool comprising a motor, a tool spindle, a drive shaft driven in rotation by the motor, and a hammer impact mechanism capable of providing axial impact to the tool spindle; the hammer impact mechanism comprises a hammer and a guide piece which can rotate relatively, and an energy storage mechanism which is abutted against the hammer, wherein a curved surface guide part is arranged on one of the hammer and the guide piece, a conversion piece is arranged on the other of the hammer and the guide piece, and when the hammer rotates relative to the guide piece, the curved surface guide part drives the hammer to move towards a first direction by overcoming the acting force of the energy storage mechanism through the conversion piece; the energy storage mechanism drives the hammer to move towards a second direction opposite to the first direction so as to impact the tool spindle; the hammer impact mechanism comprises an impact shaft which can drive one of the hammer and the guide piece to rotate; the transmission shaft is connected with the impact shaft in a non-rotatable manner.

Preferably, the transmission shaft is integrally provided with the impact shaft.

Preferably, the drive shaft is selectively rotatably connected to the ram.

Preferably, a first clutch member is arranged between the transmission shaft and the hammer, the first clutch member is movably arranged on one of the transmission shaft and the hammer, and the other of the transmission shaft and the hammer is provided with a first accommodating part; the first clutch piece is matched with the first accommodating part to realize the rotary connection between the transmission shaft and the hammer, and when the first clutch piece is separated from the first accommodating part, the transmission shaft and the hammer can rotate relatively.

Preferably, the tool spindle is provided integrally with the impact shaft.

Preferably, the tool spindle is selectively rotatably connected to the ram.

Preferably, a second clutch member is arranged between the tool spindle and the hammer, the second clutch member is movably arranged on one of the tool spindle and the hammer, and a second accommodating part is arranged on the other of the tool spindle and the hammer; the second clutch piece is matched with the second accommodating part to realize the rotary connection between the tool spindle and the hammer, and when the second clutch piece is separated from the second accommodating part, the tool spindle and the hammer can rotate relatively.

Preferably, the ram surrounds the tool spindle, the drive shaft and the percussion shaft in at least one plane.

Preferably, the guide member surrounds the ram in at least one plane.

Preferably, the hammer is provided with an impact surface facing the tool spindle, the impact surface being contactable with the tool spindle during impact, the impact surface being closer to the axis of rotation of the tool spindle than the curved guide.

Preferably, the guide is fitted around the outer side of the hammer, the curved guide is provided on an inner circumferential surface of the guide, and the conversion member is provided on an outer circumferential surface of the hammer.

Preferably, the ram has an end face facing the tool spindle, the impact face being closer to the free end of the tool spindle than the end face.

Preferably, the curved surface guide part comprises a plurality of climbing sections and falling sections corresponding to the climbing sections, and when the conversion part passes through the climbing sections, the conversion part drives the ram to move towards a first direction by overcoming the acting force of the energy storage mechanism; when the conversion piece passes through the falling section, the energy storage mechanism drives the hammer to move towards a second direction opposite to the first direction so as to impact the tool spindle; the number of the conversion pieces is consistent with that of the climbing sections.

Preferably, the energy storage mechanism is provided as an elastic member.

The utility model also provides another kind of technical scheme: a hand tool comprising a motor, a housing the motor, a tool spindle, a drive shaft driven for rotation by the motor, and a hammer impact mechanism capable of providing axial impact to the tool spindle; the hammer impact mechanism comprises a hammer and a guide piece which can rotate relatively, an impact shaft which is rotationally connected with the transmission shaft and an energy storage mechanism which is abutted against the hammer, wherein a curved surface guide part is arranged on one of the hammer and the guide piece, a conversion piece is arranged on the other of the hammer and the guide piece, one of the hammer and the guide piece is driven by the impact shaft to rotate relative to the other of the hammer and the guide piece, and the curved surface guide part drives the hammer to move towards a first direction along the central axis of the tool spindle by overcoming the acting force of the energy storage mechanism through the conversion piece; the energy storage mechanism drives the hammer to move along the central axis of the tool spindle in a second direction opposite to the first direction so as to impact the tool spindle; the ram is supported on the housing for linear movement.

Preferably, the guide is fitted around the outer side of the hammer, the guide is fixed to the housing in the impact mode, the hammer is driven by the impact shaft to rotate relative to the guide, and the hammer is supported on the inner peripheral surface of the guide so as to be linearly movable.

Preferably, the curved guide portion is provided on an inner periphery of the guide member, and the conversion member is provided on an outer peripheral surface of the hammer.

Additional aspects and advantages of the present invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.

The utility model also provides another technical scheme: a hand tool, comprising: a housing; a motor; a drive shaft driven by the motor and rotating about the drive shaft axis; the tool spindle is used for connecting a tool head and can be driven to rotate by the transmission shaft; the hammer impact mechanism is provided with a ram, and the ram is sleeved on the outer side of at least one of the transmission shaft and the tool spindle and can be driven to rotate by the transmission shaft; hammer impact mechanism still locates including the cover the guide in the ram outside, the cutter main shaft can be moved to the second position by the primary importance via the effect of an axial force, works as the cutter main shaft is in when the second position, the ram can by the transmission shaft drive is rotatory and can for the guide is according to the route motion of predetermineeing, thereby follows in at least one running state the axis striking of cutter main shaft the cutter main shaft, works as the cutter main shaft is in when the primary importance, the transmission shaft can't drive the ram is rotatory.

Preferably, the tool spindle includes a connecting end connected to the transmission shaft, and an output end connected to the tool head, and when the axial force applied to the tool spindle is directed from the output end to the connecting end, the tool spindle can be switched to the first position coupled to the transmission shaft.

Preferably, the tool spindle includes a connecting end connected to the transmission shaft, and an output end connected to the tool head, and when the axial force applied to the tool spindle is directed from the connecting end to the output end, the tool spindle is switched to the second position coupled to the transmission shaft.

Preferably, the hand tool further comprises a mode adjustment mechanism operable to switch between a first mode state in which the tool spindle is switchable between the first position and the second position relative to the drive shaft and a second mode state; when the tool spindle is located in the second mode state, the tool spindle is axially abutted to the mode adjusting mechanism to limit the tool spindle from being switched from the second position to the first position.

Preferably, the hand tool further comprises a mode adjustment mechanism operable to switch between a first mode state in which the guide is fixed to the housing and a second mode state in which the ram is movable along the guide in a predetermined path to strike the tool spindle when rotated; when the tool spindle is located in the second mode state, the guide piece is rotatably arranged on the shell, and the hammer does not impact the tool spindle.

Preferably, one end of the transmission shaft connected with the connecting end is a transmission end, one of the connecting end and the transmission end is provided with an axial hole, and the other end of the transmission shaft extends into the axial hole.

Preferably, splines are provided between the inner wall of the axial bore and the outer wall of the other of the end portions to provide an axially moveable but non-rotatable connection between the drive shaft and the tool spindle.

Preferably, the spline of the other end part forms a radial groove, the outer wall of the axial hole is provided with a radial hole, the handheld tool further comprises a steel ball for connecting the transmission shaft and the hammer, the radial hole corresponds to the radial groove in position, and the steel ball moves into the radial groove along the radial hole and is separated from the hammer; when the cutter spindle moves to the first position relative to the transmission shaft, the radial hole and the radial groove are staggered, and the steel ball moves in the reverse direction of the radial hole and is connected with the hammer.

Preferably, the hammer impact mechanism further comprises an intermittent impact assembly; when the transmission shaft drives the ram to rotate, the intermittent impact assembly forces the ram to move linearly relative to the guide member along a preset path and to impact the tool spindle in at least one operating state.

Preferably, the intermittent impact assembly includes an energy storage mechanism abutting against the hammer, and a conversion member and a curved surface guide portion provided between the guide member and the hammer.

Preferably, the conversion member is located on one of the guide member and the hammer, and the curved guide portion is located on the other of the guide member and the hammer.

Preferably, the conversion member is provided as a steel ball, and the curved guide portion is provided as a cam surface or a cam groove.

Preferably, the energy storage means is provided as a spring.

The utility model also provides another technical scheme: a hand tool, comprising: a motor having a rotational direction including a first direction and a second direction opposite to the first direction; a drive shaft driven to rotate by the motor; the tool spindle is used for connecting a tool head and movably connected with the transmission shaft; the hammer impact mechanism is provided with a hammer, the hammer is sleeved on the outer side of the transmission shaft or the cutter main shaft and can be driven to rotate by the transmission shaft, and the hammer impact mechanism further comprises a guide piece arranged on the outer side of the hammer; the hammer impact mechanism further comprises an intermittent impact assembly positioned between the hammer and the guide member, the intermittent impact assembly comprises a curved surface guide part positioned on one of the outer wall of the hammer or the inner wall of the guide member and a conversion member positioned on the other of the outer wall of the hammer and the inner wall of the guide member, the handheld tool further comprises an impact ring which is non-rotatably fixed on the shell, a first end tooth is arranged on the impact ring, a second end tooth capable of being meshed with the first end tooth is arranged on the guide member, when the motor rotates along the first direction, the first end tooth limits the guide member to rotate through the second end tooth meshed with the first end tooth, and the conversion member moves along the curved surface guide part according to a preset direction to enable the hammer to impact the tool spindle in at least one running state; when the motor rotates along the second direction, the second end tooth and the guide piece rotate relative to the first end tooth meshed with the second end tooth under the driving of the motor.

Preferably, the first end tooth comprises a plurality of first teeth, the first teeth comprise a guide section and a stop section, the guide section is connected with a free end of the stop section, the second end tooth comprises a plurality of second teeth, when the motor rotates along the first direction, the second teeth move to the guide section from the stop section, and the stop section abuts against the second teeth, so that the guide member cannot rotate; when the motor rotates in the second direction and the second tooth moves from the guide section to the stop section, the second tooth can move along the guide section, so that the guide piece rotates relative to the first end tooth.

Preferably, the guide section and the stopping section are sequentially arranged at intervals along the circumferential direction of the first end tooth, and the stopping section is parallel to the axis of the transmission shaft.

Preferably, when the second tooth moves from the stopping section to the guiding section, the side of the second tooth abutting against the stopping section is parallel to the stopping section.

Preferably, the impact ring is axially movable to effect engagement or disengagement of the first end teeth with the second end teeth, the guide is driven to rotate by the motor when the first end teeth are disengaged from the second end teeth, and the hand tool is in a non-impact mode.

Preferably, the hammer impact mechanism has a disengageable clutch mechanism arranged to transmit rotary motion.

Preferably, the clutch mechanism is arranged to be closed by a force transmitted via the tool spindle.

Preferably, the clutch mechanism is located between the transmission shaft and the hammer, and includes a clutch member disposed on one of the transmission shaft and the hammer, and an accommodating portion disposed on the other of the transmission shaft and the hammer, the clutch member is engaged with the accommodating portion when the mode adjusting mechanism is located at the first position, and the clutch member is separated from the accommodating portion when the mode adjusting mechanism is located at the second position.

Preferably, the clutch piece is arranged in a sphere or column shape, and the accommodating part is arranged as a groove body. Additional aspects and advantages of the present invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.

Drawings

The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:

fig. 1 is a schematic structural view of a hand tool according to an embodiment of the present invention;

fig. 2 is an exploded view of a portion of a hand tool according to an embodiment of the present invention;

fig. 3 is a schematic structural view of a mode adjustment mechanism of a hand tool according to an embodiment of the present invention;

fig. 4 is a schematic structural view of a mode adjustment mechanism of a hand tool according to an embodiment of the present invention;

fig. 5 is a schematic cross-sectional partial structure view of a hand tool according to an embodiment of the present invention;

FIG. 6 is an enlarged view of the structure at A in FIG. 5;

FIG. 7 is an enlarged view of the structure at B in FIG. 5;

FIG. 8 is an enlarged view of the structure at C in FIG. 5;

fig. 9 is a schematic cross-sectional partial structure view of a hand tool according to an embodiment of the present invention;

FIG. 10 is an enlarged view of the structure of FIG. 9 at D;

fig. 11 is a schematic structural view of a guide of a hand tool according to an embodiment of the present invention;

fig. 12 is a schematic cross-sectional view of a guide of a hand tool according to an embodiment of the present invention;

fig. 13 is a schematic cross-sectional partial structure view of a hand tool according to an embodiment of the present invention;

FIG. 14 is an enlarged view of the structure at E in FIG. 13;

FIG. 15 is an enlarged view of the structure of FIG. 13 at F;

fig. 16 is an exploded view of a portion of a hand tool according to an embodiment of the present invention;

fig. 17 is a schematic cross-sectional partial structure view of a hand tool according to an embodiment of the present invention;

fig. 18 is a schematic cross-sectional partial structure view of a hand tool according to an embodiment of the present invention;

fig. 19 is an exploded view of a portion of a hand tool according to an embodiment of the present invention;

fig. 20 is a partial schematic structural view of a hand tool according to an embodiment of the present invention;

fig. 21 is a schematic cross-sectional view of a hand tool according to an embodiment of the present invention;

FIG. 22 is an enlarged view of the structure of FIG. 21 at G;

fig. 23 is a schematic cross-sectional view of a hand tool according to an embodiment of the present invention;

FIG. 24 is an enlarged view of the structure at H in FIG. 23;

fig. 25 is a schematic cross-sectional partial structure view of a hand tool according to an embodiment of the present invention;

fig. 26 is a cross-sectional partial schematic view of a hand tool according to an embodiment of the present invention;

fig. 27 is a schematic cross-sectional view of a hand tool according to an embodiment of the present invention;

fig. 28 is a partial schematic structural view of a hand tool according to an embodiment of the present invention;

fig. 29 is a partial schematic structural view of a hand tool according to an embodiment of the present invention;

fig. 30 is a partial schematic structural view of a hand tool according to an embodiment of the present invention.

Fig. 31 is a partial cross-sectional view of a hand tool according to an embodiment of the present invention.

Reference numerals:

the hand-held tool 1 is provided with a handle,

the transmission shaft 10, the baffle 100, the through hole 110, the cavity 120, the transmission end 130, the flat square 140,

a hammer impact mechanism 20, a hammer 200, a housing portion 201, a groove body 201a, an insertion groove 202, a mounting groove 203,

the guide 210, the receiving groove 211, the first insection 212, the convex portion 212a, the tip 212a1, the striking surface 2001,

the operation of the clutch mechanism 220, clutch member 221,

an intermittent impact assembly 230, an energy storage mechanism 231, a conversion piece 232, a curved surface guide part 233,

a climbing section 233a, a falling section 233b,

a tool spindle 30, external threads 300, a first section 310, a second section 320, a third section 330, ribs 340, grooves 350, axial holes 360, splines 370, a connecting end 380, an output end 390,

the mode adjustment mechanism 40, the impact receiving portion 400, the first surface 401, the second surface 402, the third surface 403, the step surface 404, the press stop ring 410, the press stop portion 411, the fixing section 411a, the connecting section 411b, the fitting section 411c,

a mode adjustment knob 420, a flange 421, a channel 422,

the impact switch ring 430, the second tooth pattern 431, the guiding section 431a, the stopping section 431b, the matching block 432, the buffer 440,

the mode switching button 450, the guide block 451, the guide slope 451a,

chuck 50, threaded bore 500, motor 60, reset element 70, housing 80, reverse screw 90,

the impact ring 11a, the first end tooth 12a, the first tooth 121a, the guide section 121b, the stopper section 121c, the second end tooth 213a, and the second tooth 2131 a.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are exemplary only for the purpose of explaining the present invention, and should not be construed as limiting the present invention.

In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", and the like, indicate the orientation or positional relationship indicated based on the drawings, and are only for convenience of description and simplicity of description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore, should not be construed as limiting the present invention. Furthermore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.

In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood in specific cases to those skilled in the art.

Example 1

As shown in fig. 1 to 26, a hand tool 1 according to an embodiment of the present invention includes a motor 60, a transmission shaft 10, a hammer impact mechanism 20, and a tool spindle 30.

Specifically, as shown in fig. 2, 5, 9, 13, 17-18, 21, 23, and 25-26, the motor 60 may drive the transmission shaft 10 to rotate, and the transmission shaft 10 may rotate around the axis of the transmission shaft 10. The hammer impact mechanism 20 includes a hammer 200, the hammer 200 is sleeved outside the transmission shaft 10, and the hammer 200 can be driven to rotate by the transmission shaft 10. It is understood that the motor 60 is connected to the transmission shaft 10, and that "connected" as referred to herein may mean that the motor 60 is directly connected to the transmission shaft 10, for example, the output end of the motor 60 may be directly connected to the end of the transmission shaft 10, and "connected" may mean that the motor 60 is indirectly connected to the transmission shaft 10, for example, the motor 60 may be directly connected to an intermediate transmission assembly, and then directly connected to the transmission shaft 10 through the intermediate transmission assembly.

The motor 60 may drive the propeller shaft 10 to rotate, i.e., the motor 60 may drive the propeller shaft 10 to rotate about its central axis. The ram 200 may be externally fitted to the outer wall of the drive shaft 10, the ram 200 may be cooperatively connected to the drive shaft 10, and the drive shaft 10 may further drive the ram 200 to rotate around the axis of the drive shaft 10. It should be noted that "connection" mentioned herein may mean that the hammer 200 is directly connected to the drive shaft 10, or that the hammer 200 is indirectly connected to the drive shaft 10. As shown in fig. 5-9, the hand tool 1 further includes a tool spindle 30, one end of the tool spindle 30 is connected to the transmission shaft 10, the other end is used for connecting a tool head, and the tool spindle 30 is movable relative to the transmission shaft 10, and the tool spindle 30 is movably connected to the transmission shaft 10, for example, the tool spindle 30 is movable relative to the transmission shaft 10 along the axial direction of the transmission shaft 10 and is non-rotatably connected, that is, the tool spindle 30 is driven by the transmission shaft 10 to rotate. As shown in fig. 27, the ram 200 in the present embodiment may be sleeved outside the tool spindle 30, or a part of the ram may be sleeved outside the tool spindle 30, and a part of the ram may be sleeved outside the transmission shaft 10.

As shown in fig. 2, 5-13, the hammer impact mechanism 20 further includes a guide 210 provided outside the hammer 200, and an intermittent impact assembly 230. As the ram 200 rotates, the intermittent impact assembly 230 guides the ram 200 to move linearly relative to the guide 210 along a predetermined path and strike the tool spindle 30 in at least one operating condition. In other words, the hammer impact mechanism 20 includes the hammer 200, the guide 210, and the intermittent impact assembly 230, with the guide 210 externally fitted to the outer peripheral wall of the hammer 200. Preferably, in order to make the hammer 200 generate the required hammering force when hitting the tool spindle 30, the weight of the hammer 200 is 10% or more of the sum of the weights of the chuck 50 and the tool spindle 30, and in order to make the mass of the tool not too heavy and to make the entire machine compact, the weight of the hammer 200 is preferably 60% or less of the sum of the weights of the chuck 50 and the tool spindle 30. More preferably, the weight of the ram 200 is 35% or less of the sum of the weight of the collet 50 and the tool spindle 30.

As shown in fig. 25-26, the tool spindle 30 is fixedly connected to the chuck 50 by a screw connection, specifically, in the present embodiment, an external thread 300 is provided at an end of the tool spindle 30 close to the chuck 50, a threaded hole 500 is provided inside the chuck 50 to mate with the external thread 300, and the tool spindle 30 and the chuck 50 are connected to the threaded hole 500 through the external thread 300. It should be noted that the motor 60 can rotate the tool spindle 30 in either a first direction (forward direction) or a second direction (reverse direction) opposite to the first direction, and that a reverse screw 90 is provided between the chuck 50 and the tool spindle 30 in order to prevent the threaded connection between the tool spindle 30 and the chuck 50 from being disengaged during operation, where "reverse screw 90" means that the thread direction of the screw is opposite to the thread direction of the external thread 300. In this connection, since the hammering force of the hammer 200 to the tool bit 20 needs to be transmitted to the tool bit via the back screw 90, that is, the hammer 200 transmits the hammering force to the tool spindle 30, then to the back screw 90 via the tool spindle 30, and finally to the tool bit via the back screw 90, the loss of the hammering force transmitted to the tool bit via the hammer 200 is large.

Therefore, the present invention further provides another connection method of the tool spindle 30 and the chuck 50, referring to fig. 21, compared to the connection method between the tool spindle 30 and the chuck 50, the reverse screw 90 is eliminated in this connection method, the tool spindle 30 and the tool head are prevented from being separated during operation by coating the adhesive between the external thread 300 and the threaded hole 500, and meanwhile, the front portion of the tool spindle 30 has a protrusion (not shown) for abutting against the tool head, so that the impact can be directly transmitted to the tool head from the tool spindle 30, and the energy loss during the impact is reduced.

When the hammer 200 rotates, the intermittent impact assembly 230 may control a movement path of the hammer 200, and the movement path may both cause the hammer 200 to rotate around the circumferential direction of the drive shaft 10 and cause the hammer 200 to move along the axial direction of the drive shaft 10, so that the hammer 200 may strike the tool spindle 30, thereby completing the movement of the tool spindle 30 with respect to the drive shaft 10.

According to the utility model discloses hand tool 1, through setting up guide 210 and intermittent type impact assembly 230, utilize intermittent type to strike assembly 230, ram 200 and guide 210's cooperation relation, can guide ram 200 and make linear motion, and ram 200 can also strike cutter main shaft 30, thereby can realize the ascending removal of cutter main shaft 30 axis direction, when making cutter main shaft 30 drill on environmental component (like wall or plate), cutter main shaft 30 forms the impact force to environmental component, thereby can improve hand tool 1's drilling efficiency, moreover, the utility model discloses hand tool 1's of embodiment structure sets up compactness and simple structure, can conveniently carry.

As shown in fig. 2, 5, 7, and 9-12, according to some embodiments of the present invention, the intermittent impact assembly 230 includes an energy accumulating mechanism 231 abutting against the hammer 200, and a conversion member 232 and a curved surface guide 233 provided between the guide member 210 and the hammer 200. The intermittent impact assembly 230 further includes an energy accumulating mechanism 231, the conversion member 232 and the curved surface guide portion 233 are both located between the guide member 210 and the hammer 200, and one end of the energy accumulating mechanism 231 abuts against the hammer 200. Thus, by configuring the specific shape of the curved surface guide part 233 to guide the movement locus of the conversion member 232, the conversion member 232 can be interlocked with the hammer 200, and the hammer 200 is moved along the locus of the curved surface guide part 233 by the conversion member 232.

Further, as shown in fig. 13 and fig. 17 to 18, the transmission shaft 10 may be provided with a baffle 100, the baffle 100 is externally sleeved on the peripheral wall of the transmission shaft 10, the energy storage mechanism 231 is located between the hammer 200 and the baffle 100, and an end of the energy storage mechanism 231 away from the hammer 200 may be engaged with the baffle 100. When the ram 200 moves a certain distance toward the energy storage mechanism 231, the ram 200 and the stop plate 100 may compress the energy storage mechanism 231. Thereby, the energy accumulating mechanism 231 can exert an urging force on the hammer 200. Of course, other structures may be adopted for the axial limiting manner of the energy storage mechanism 231, and are not described herein again.

Energy storage mechanism 231's axial locating part is baffle 100 in this embodiment the utility model discloses in with baffle 100 and transmission shaft 10 design for fixed connection, the preferred interference fit that adopts can prevent the phenomenon of the cutter main shaft of instrument appearance under non-impact mode from making a round trip to drunkenness along the axis direction, improves the life-span of mechanism and user's operation experience.

The phenomenon of tool spindle axial float, here said, through research analysis, found the root cause that this phenomenon appears, based on this root cause, the utility model provides an above-mentioned technical scheme, baffle 100 and transmission shaft 10 fixed connection promptly, will specifically explain the root cause of tool spindle axial float below to and above-mentioned technical scheme can solve the fundamental principle of this problem.

The phenomenon of axial play of the tool spindle referred to herein is a phenomenon in which the tool spindle moves back and forth along the axial direction when the tool is operated in a non-impact mode, and it has been found through research and analysis that the axial play of the tool spindle is caused by the clutch 221 selectively connecting the hammer 200 and the transmission shaft 10 back and forth along the radial direction into and out of the receiving portion 201. Specifically, due to the clearance fit between the baffle 100 and the transmission shaft 10, the baffle 10 and the spring, i.e., the energy storage mechanism 231, and the hammer 200 are not rotated in the rotation direction when the transmission shaft 10 rotates. That is, in the non-impact mode, when the transmission shaft 10 rotates the tool spindle 30, the hammer 200 remains stationary in the rotational direction. During the non-impact mode, the operator slightly presses the tool spindle 30 to move the tool spindle 30 a little distance backward along the axial direction, so that the clutch member 221 is partially extruded along the radial direction, and when the rotating transmission shaft 10 drives the clutch member 221 to continue rotating, the clutch member 221 in the rotating state is extruded and contacts the inner wall of the stationary hammer 200, and the clutch member 221 is rebounded by the acting force, that is, the clutch member 221 is pushed back along the radial direction. The tool spindle 30 then continues to push the clutch element 221 out of the way due to the slight axial downward pressure and is then pushed back again, so that the clutch element 221 is moved back and forth in the radial direction repeatedly, which in turn causes the tool spindle 30 to move back and forth in the axial direction.

In order to solve the above problem, the utility model discloses be fixed connection with baffle 100 and transmission shaft 10 design, so that the instrument is at the in-process of non-impact mode operation, when transmission shaft 10 drove cutter main shaft 30 rotatory, transmission shaft 10 also can drive baffle 100 and rotate, and then can make the spring also be energy storage mechanism 231, and ram 200 rotates, and then make cutter main shaft 30 and ram 200 rotate together, and the speed is the same, there is not the relative velocity difference, cutter main shaft 30 receives slight axial downforce like this, from closing member 221 radially extrudes, when clutch 221 touches the inner wall of ram 200, just can not receive the effort, just can not rebound, and then solved the problem of clutch 221 along radial play back and forth, and then just also solved cutter main shaft 30 along the problem of axis direction play back and forth. Guide member

As shown in fig. 11 to 12, in some embodiments of the present invention, the curved surface guide portion 233 may be formed in a ring shape, and the curved surface guide portion 233 may be surrounded along a circumferential direction of the transmission shaft 10, specifically, the curved surface guide portion 233 may include a climbing section 233a and a falling section 233b, one end of the falling section 233b is connected with one end of the climbing section 233a, and the other end of the falling section 233b extends toward the other end of the climbing section 233 a. Further, the climbing section 233a may have a spiral line type, the falling section 233b may have a linear type, and the falling section 233b extends in the axial direction of the transmission shaft 10. Preferably, in order to ensure that the hammer 200 generates a sufficient impact force on the tool spindle 30 and the hand-held tool 1 is compact in size, the climbing height 233a in the axial direction is greater than 3mm and less than or equal to 15mm, preferably greater than or equal to 4mm and less than or equal to 8mm, and preferably 5 mm. Note that the "climbing height" refers to an axial distance between both ends of the climbing section 233a in the axial direction of the propeller shaft 10.

When the conversion member 232 is engaged with the climbing section 233a, the conversion member 232 rolls from one end of the climbing section 233a toward the other end of the climbing section 233a, the hammer 200 moves toward the baffle 100, and the hammer 200 and the baffle 100 can compress the energy storage mechanism 231; when the conversion member 232 is located at the other end of the ascending section 233a and rolls toward the falling section 233b, the energy storage mechanism 231 can push the hammer 200 to fall from one end of the falling section 233b close to the baffle 100 toward the other end of the falling section 233b close to the tool head, that is, the hammer 200 rapidly falls toward a direction away from the baffle 100 and close to the tool head, and a portion of the hammer 200 is close to and impacts a portion of the tool spindle 30 located outside the transmission shaft 10, so that the tool spindle 30 moves relative to the transmission shaft 10 along the axial direction of the transmission shaft 10, and the hammer 200 forms a hammering action on the tool spindle 30 and the tool head.

Further, as shown in fig. 7 and 15, an end surface of the hammer 200 near the energy accumulating mechanism 231 may be provided with a mounting groove 203, an end portion of the energy accumulating mechanism 231 may be located in the mounting groove 203, and the end portion of the energy accumulating mechanism 231 may abut against a bottom wall of the mounting groove 203. This can improve the stability of the assembly of the energy storage mechanism 231 and the hammer 200.

As shown in fig. 12, in some embodiments of the present invention, the curved guide portion 233 may include a plurality of segments, each segment including a climbing section 233a and a falling section 233 b. The conversion member 232 may be plural, and the plural conversion members 232 may be spaced apart in the circumferential direction of the hammer 200. In order to ensure the reasonableness of the overall design of the hand-held tool 1, the outer diameter of the middle hammer 200 is 15mm-50mm, preferably the outer diameter of the hammer 200 is 20mm-40mm, the climbing height is greater than 3mm and less than or equal to 15mm, preferably the climbing height is greater than or equal to 4mm and less than or equal to 8mm, and more preferably the climbing height is 5 mm. It will be appreciated that, in order to ensure that the transition piece 232 can climb smoothly, the number of segments is preferably 2 to 7, particularly advantageously 3 to 4, and the number of segments of the ascending segment 233a in this embodiment is preferably 3.

It should be noted that, as can be seen from the above description, the conversion member 232 and the curved guide portion 233 are located between the hammer 200 and the guide member 210, specifically, the conversion member 232 is located on one of the guide member 210 and the hammer 200, and the curved guide portion 233 is located on the other of the guide member 210 and the hammer 200. As shown in fig. 16-18, in other examples of the present invention, the transition piece 232 may be located on the guide piece 210 and the curved surface guide 233 is located on the hammer 200. For example, the guide member 210 may be provided with a receiving groove 211 on an inner circumferential wall thereof, a portion of the conversion member 232 may be located in the receiving groove 211, the hammer 200 may be provided with a curved surface guide 233 on an outer circumferential wall thereof, and another portion of the conversion member 232 may be engaged with the curved surface guide 233. As shown in fig. 16-18, in other examples of the present invention, the transition piece 232 may be located on the guide piece 210 and the curved surface guide 233 is located on the hammer 200. For example, the guide member 210 may be provided with a receiving groove 211 on an inner circumferential wall thereof, a portion of the conversion member 232 may be located in the receiving groove 211, the hammer 200 may be provided with a curved surface guide 233 on an outer circumferential wall thereof, and another portion of the conversion member 232 may be engaged with the curved surface guide 233. Thereby, the fitting relationship of the conversion member 232 and the curved surface guide portion 233 to the hammer 200 and the guide 210 can be realized, so that the relative movement of the hammer 200 with respect to the guide 210 can be realized by the fitting relationship between the conversion member 232 and the curved surface guide portion 233 and the relative movement between the conversion member 232 and the curved surface guide portion 233, and the hammer 200 can be moved with respect to the propeller shaft 10 in the axial direction of the propeller shaft 10. The movement locus of the conversion member 232 at the curved guide portion 233 is a predetermined path of the hammer 200.

As shown in fig. 2, 16 and 19, in some embodiments of the present invention, the converting element 232 may be configured as a steel ball, as shown in fig. 11-12, preferably, in order to ensure the strength of the steel ball, the diameter of the steel ball is greater than 4mm and less than or equal to 10mm, more preferably, the diameter of the steel ball is greater than or equal to 4mm and less than or equal to 6mm, and the diameter of the steel ball in this embodiment is 5 mm. The curved guide part 233 may be provided as a cam surface or a cam groove. Therefore, the cam surface or the cam groove can limit the moving track of the steel ball, the steel ball can move in the cam surface or the cam groove, the steel ball has a smooth outer surface, the relative moving friction force between the conversion piece 232 and the curved surface guide part 233 can be reduced, the moving smoothness of the conversion piece 232 in the curved surface guide part 233 is improved, the structural strength of the steel ball is high, the wear resistance is good, and the working performance of the intermittent impact assembly 230 can be guaranteed. It should be noted that the term "cam" as used herein may refer to the curved guide portion 233 protruding from the inner peripheral wall of the guide 210, or the curved guide portion 233 protruding from the outer peripheral wall of the hammer 200.

Further, the steel ball and the curved guide part 233 may be in point or line contact, and it can be understood that, in the process of the steel ball moving in the curved guide part 233, the steel ball and the curved guide part 233 are always in point or line contact, which is beneficial to reducing the friction between the steel ball and the curved guide part 233. For example, the radius of curvature of the cam surface may be substantially the same as or slightly larger than the radius of the steel ball, so that the degree of fit between the steel ball and the cam surface may be improved, and the assembly stability, wear resistance and life of the steel ball and the cam surface may be improved.

As shown in fig. 2, 16 and 19, in some embodiments of the present invention, the energy storage mechanism 231 may be configured as an elastic member, for example, the energy storage mechanism 231 may be a spring or an elastic rubber member, thereby simplifying the configuration and assembly of the energy storage mechanism 231 and reducing the manufacturing cost of the energy storage mechanism 231.

As shown in fig. 5, 8-10, 13 and 15, according to some embodiments of the present invention, the hammer impact mechanism 20 further has a disengageable clutch mechanism 220, the clutch mechanism 220 being configured to transmit rotational motion between the drive shaft 10 and the hammer 200. It is understood that the clutch mechanism 220 may be engaged with the hammer 200, and the clutch mechanism 220 may also be disengaged from the hammer 200, when the clutch mechanism 220 is engaged with the hammer 200, the rotational motion of the transmission shaft 10 may be transmitted to the hammer 200 through the clutch mechanism 220, thereby driving the hammer 200 to rotate; when the clutch mechanism 220 is disengaged from the hammer 200, i.e., the engagement relationship between the clutch mechanism 220 and the hammer 200 is released, the drive shaft 10 can rotate relative to the hammer 200, and the hammer 200 is stationary relative to the guide 210. Thus, the movement of the hammer 200 can be controlled by the clutch mechanism 220, thereby controlling whether the hammer 200 strikes the tool spindle 30, and thus the operation mode of the tool spindle 30 can be controlled.

Further, the clutch mechanism 220 may be configured to be closed by a force transmitted through the tool spindle 30, that is, when the tool bit abuts on a working condition (axially loaded), the clutch mechanism 220 can be automatically closed to realize an impact, and the hand tool 1 is in an impact state. Thus, whether or not there is a mating relationship between the clutch mechanism 220 and the hammer 200 can be controlled by the tool spindle 30, and the tool spindle 30 can apply an external force to the clutch mechanism 220 to change the relationship between the clutch mechanism 220 and the hammer 200. Therefore, the switching of the working state of the hand-held tool 1 can be conveniently changed, and an additional control structure is not needed.

Further, the clutch mechanism 220 is operable to shift between a closed state and a disengaged state, and when the clutch mechanism 220 is in the closed state, the hammer 200 is driven to rotate by the transmission shaft 10; when the clutch mechanism 220 is in the disengaged state, the hammer 200 cannot be driven by the transmission shaft 10. It is understood that the tool spindle 30 can control the operating state of the clutch mechanism 220 so that the clutch mechanism 220 can be engaged with the hammer 200 or disengaged from the hammer 200, and the clutch mechanism 220 can be switched between these two states by the tool spindle 30. When the clutch mechanism 220 is engaged with the hammer 200, the transmission shaft 10 can rotate the hammer 200, and when the clutch mechanism 220 is disengaged from the hammer 200, the hammer 200 cannot be driven by the transmission shaft 10. Thus, the movement of the hammer 200 can be controlled by the clutch mechanism 220, so that the hand tool 1 can automatically realize the impact function or enter the impact state when working under load.

As shown in fig. 5, 8-10, 13 and 15, in some examples of the present invention, the clutch mechanism 220 includes a clutch member 221 provided on one of the transmission shaft 10 and the hammer 200, and a receiving portion 201 provided on the other of the transmission shaft 10 and the hammer 200, wherein the clutch member 221 is engaged with the receiving portion 201 in a shape matching manner when the clutch mechanism 220 is in an engaged state, and the clutch member 221 is disengaged from the receiving portion 201 when the clutch mechanism 220 is in a disengaged state.

It is understood that the clutch mechanism 220 includes a clutch member 221 and a receiving portion 201, and one of the transmission shaft 10 and the hammer 200 is provided with the clutch member 221 and the other is provided with the receiving portion 201. When the clutch mechanism 220 is in the engaged state, the clutch member 221 is engaged with the housing portion 201, and when the clutch mechanism 220 is in the disengaged state, the clutch member 221 is disengaged from the housing portion 201. Thus, the operating state of the clutch mechanism 220 can be switched by the fitting relationship between the clutch member 221 and the housing portion 201.

As shown in fig. 5, 8-10, 13 and 15, in some examples of the present invention, the clutch member 221 may be provided in a spherical or cylindrical shape, and the receiving portion 201 may be provided as a groove 201 a. The ball or the column has a smooth outer surface having a small friction force during the movement, thereby facilitating the state switching of the clutch member 221. The accommodation portion 201 is provided as the groove 201a, which is convenient to be installed and to be engaged with the clutch member 221. For example, a part of the inner circumferential wall of the hammer 200 is recessed toward the radially outer side of the hammer 200 to form a housing 201. Further, the bottom wall of the groove body 201a may be formed into a curved surface, and the curved surface may be recessed toward the radially outer side of the hammer 200. Therefore, the groove body 201a can wrap part of the clutch member 221, so that the matching stability of the clutch member 221 and the groove body 201a can be improved.

According to some embodiments of the present invention, the tool spindle 30 is axially movable but non-rotatably connected relative to the drive shaft 10. In other words, the tool spindle 30 is relatively stationary with the drive shaft 10 or rotates together with the drive shaft 10 when rotating in the circumferential direction of the drive shaft 10, the tool spindle 30 being movable relative to the drive shaft 10 in the axial direction of the drive shaft 10. Therefore, the transmission shaft 10 can drive the tool spindle 30 to rotate along the circumferential direction of the transmission shaft 10, and the tool spindle 30 can also complete sliding in the axial direction of the transmission shaft 10.

For example, as shown in fig. 5, how the tool spindle 30 is moved axially relative to the drive shaft 10 to effect the engagement or disengagement of the clutch mechanism 220 and how the tool spindle 30 is connected axially movably but not rotatably relative to the drive shaft 10 will be described in detail below with reference to the drawings. The tool spindle 30 is movable from a first position into a second position by the action of an axial force, the ram 200 being rotationally drivable by the drive shaft 10 and being movable relative to the guide 210 along a predetermined path when the tool spindle 30 is in the second position, so as to strike the tool spindle 30 along its axis in at least one operating state; when the tool spindle 30 is in the first position, the drive shaft 10 cannot drive the ram 200 to rotate. The cutter main shaft 30 comprises a connecting end connected with the transmission shaft 10 and an output end connected with the tool head, one side of the transmission shaft 10 close to the connecting end is provided with a cavity 120 with an axial opening, the cavity 120 can extend along the axial direction of the transmission shaft 10, the connecting end of the cutter main shaft 30 extends into the cavity 120 from the opening, the inner wall of the cavity 120 is matched with the outer wall of the connecting end of the cutter main shaft 30 through a spline 370 extending along the axial direction, so that the cutter main shaft 30 can move axially relative to the transmission shaft 10 and can rotate together with the transmission shaft 10. Specifically, as shown in fig. 2, the outer wall of the tool spindle 30 and the inner wall of the cavity 120 are provided with ribs 340, and radially recessed grooves 350 are formed between adjacent ribs 340 on the tool spindle 30, so that the inner wall of the cavity 120 can be fitted with the grooves 350.

With continued reference to fig. 5, 8-10, 13 and 15, a radial hole 110 is formed on a sidewall of the cavity 120, the radial hole 110 penetrates through the sidewall of the cavity 120 in the radial direction of the transmission shaft 10, the clutch member 221 is located in the radial hole 110 and can move in the radial hole 110, and the receiving portion 201 may be formed on an inner circumferential wall of the hammer 200. When the clutch mechanism 220 is in the engaged state, that is, referring to fig. 13 and 15, when the tool spindle 30 moves to the first position, the radial hole 110 corresponds to the position of the groove 350 described above, and the clutch member 221 moves in a direction away from the accommodating portion 201 of the hammer 200 and closer to the groove 350 along the radial hole 110, so that the clutch member 221 is disengaged from the hammer 200; referring to fig. 9 and 10, when the tool spindle moves to the second position, the groove 350 no longer corresponds to the position of the radial hole 110, that is, there is no room for the clutch 221 to be accommodated at the position of the tool spindle 30 corresponding to the radial hole, the tool spindle 30 presses the clutch 221 during the movement to move the clutch 221 along the radial hole 110 toward the hammer accommodating portion 221, so that a portion of the clutch is located in the radial hole 110, and another portion is located in the accommodating portion 201, and the hammer 200 rotates under the action of the clutch 221 and can rotate together with the transmission shaft 10. It should be noted that, in other embodiments of the present invention, the cavity 120 may be located at the connecting end of the tool spindle 30, and the end of the transmission shaft 10 connected to the tool spindle 30 extends into the cavity 120, and such an embodiment will be described in detail later in this specification.

As shown in fig. 5, 9 and 13, according to some embodiments of the present invention, the tool spindle 30 is provided with an impact receiving portion 400 coupled to the hammer 200. It is understood that the tool spindle 30 may be provided with an impact receiving portion 400, and the hammer 200 may strike the impact receiving portion 400, whereby the hammer 200 may drive the tool spindle 30 to move by striking the impact receiving portion 400, so that the tool spindle 30 may move the tool head relative to the transmission shaft 10 in the axial direction of the transmission shaft 10.

Further, as shown in fig. 2, the impact receiving portion 400 may be formed in a ring shape, the impact receiving portion 400 is fixed to the outer circumferential wall of the tool spindle 30, the impact receiving portion 400 is located outside the drive shaft 10, the impact receiving portion 400 is connected to the tool spindle 30, for example, the impact receiving portion 400 may be engaged with the tool spindle 30, and the impact receiving portion 400 may be welded to the tool spindle 30. Thereby, when the hammer 200 strikes the tool spindle 30, the contact area between the impact receiving portion 400 and the hammer 200 can be enlarged, so that the stability of the striking force applied from the hammer 200 to the impact receiving portion 400 can be improved.

Example 2

As shown in fig. 1 to 30, a hand tool 1 according to an embodiment of the present invention includes a housing 80, a motor 60, a transmission shaft 10, a tool spindle 30, and a hammer impact mechanism 20.

As shown in fig. 1, 5, 13, 21, 23, 25-27, the drive shaft 10 can be driven by a motor 60 to rotate, and the drive shaft 10 can rotate around its axis. The tool spindle 30 is used for connecting a tool head, and the tool spindle 30 can be driven to rotate by the drive shaft 10. The hammer impact mechanism 20 has a hammer 200, and the hammer 200 is sleeved on the outer side of at least one of the transmission shaft 10 and the tool spindle 30 and can be driven to rotate by the transmission shaft 10. In other words, the hammer 200 may be mounted externally to the drive shaft 10 as shown in fig. 1, 5, 13, 21, 23, 25-26, or the hammer 200 may be mounted externally to the tool spindle 30 as shown in fig. 27, or the hammer 200 may be mounted externally to both the drive shaft 10 and the tool spindle 30, and the drive shaft 10 may directly or indirectly drive the hammer 200 to rotate.

As shown in fig. 1, 5, 13, 21, 23, and 25 to 27, the hammer impact mechanism 20 further includes a guide 210, and the guide 210 is fitted to the outer side of the hammer 200. The tool spindle 30 is switchable from the first position to the second position by the action of an axial force, in other words, there is an external force acting on the tool spindle 30 in the direction of the axis of the tool spindle 30, so that the tool spindle 30 can be switched from the first position to the second position. When the tool spindle 30 is in the second position, the hammer 200 can be driven in rotation by the drive shaft 10 and can be moved relative to the guide 210 in a predetermined path so as to strike the tool spindle 30 along the axis of the tool spindle 30 in at least one operating state, and when the tool spindle 30 is in the first position, the drive shaft 10 cannot drive the hammer 200 in rotation.

According to the utility model discloses hand tool 1, through applying along its ascending effort of axis direction to cutter main shaft 30, thereby can switch cutter main shaft 30's position, and then can control the relation between ram 200 and the transmission shaft 10, and further guide ram 200 through intermittent type impact subassembly 230 and make linear motion, and ram 200 can also strike cutter main shaft 30, thereby can realize the ascending removal of cutter main shaft 30 axis direction, when making cutter main shaft 30 drill on environmental component (like wall or plate), cutter main shaft 30 forms the impact force to environmental component, thereby can improve hand tool 1's drilling efficiency, moreover, the utility model discloses hand tool 1's of embodiment structure sets up compactness and simple structure, conveniently carries.

As shown in fig. 25-27, according to some embodiments of the present invention, the tool spindle 30 has a connecting end 380 and an output end 390 at its two ends, the connecting end 380 is connected to the transmission shaft 10, and the output end 390 is connected to the tool head. When the direction of the axial force experienced by tool spindle 30 is from output end 390 to connection end 380, in other words, when the direction of the force experienced by tool spindle 30 is from output end 390 to connection end 380 of tool spindle 30, tool spindle 30 can be switched to the mated second position relative to drive shaft 10. When the direction of the force experienced by tool spindle 30 is in the direction from connecting end 380 to output end 390 of tool spindle 30, tool spindle 30 switches to the mated first position relative to drive shaft 10. Accordingly, the position state of the tool spindle 30 can be switched by the direction of the external force applied to the tool spindle 30, and the operation state of the hand tool 1 can be switched.

As shown in fig. 1, 5, 13, 21, 23, 25-27, in some embodiments of the present invention, the hand tool 1 further includes a mode adjusting mechanism 40, the mode adjusting mechanism 40 is operable to switch between a first mode state and a second mode state, in the first mode state, the tool spindle 30 can be switched between a first position and a second position relative to the transmission shaft 10, that is, when the mode adjusting mechanism 40 is in the first mode state, the hand tool 1 can generate an axial impact under the action of an axial load, which is hereinafter referred to as "impact mode"; in the second mode state, the tool spindle 30 axially abuts against the mode adjustment mechanism 40 to restrict the tool spindle 30 from being switched from the first position to the second position, that is, in the second mode state of the mode adjustment mechanism 40, no impact is generated in the hand tool 1 regardless of whether the tool spindle 30 is subjected to an axial load, and this mode is hereinafter referred to as "non-impact mode".

Further, as shown in fig. 1, 5, 13, 21, 23, 25-27, the hand tool 1 further comprises a mode adjustment mechanism 40, the mode adjustment mechanism 40 being operable to transition between a first mode state and a second mode state. When the mode adjustment mechanism 40 is in the first mode state, the guide 210 is fixed to the housing 80, that is, the guide 210 is stationary relative to the housing 80, and the hammer 200 can move along the guide 210 along a preset path to strike the tool spindle 30 when rotating; when the mode adjustment mechanism 40 is in the second mode state, the guide 210 is rotatably disposed on the housing 80, i.e., the guide 210 is movable relative to the housing 80, and the hammer 200 does not impact the tool spindle 30. Therefore, the operating state of the guide member 210 can be controlled by controlling the state of the mode adjusting mechanism 40, so that the fitting relationship between the hammer 200 and the guide member 210 can be controlled, and the operating state of the hammer 200 can be controlled, thereby realizing switching of the operating state of the hand tool 1.

As shown in fig. 19 to 20, in some embodiments of the present invention, the mode adjustment mechanism 40 includes a first insection 212 disposed on the guide member 210, an impact switch member having a second insection 431, the impact switch member being axially movable but non-rotatably fixed in the housing 80 of the hand tool 1, specifically, the impact switch member is an impact switch ring 430, and the impact switch ring 430 is movably sleeved on the hammer 200. Wherein, when the mode adjustment mechanism 40 is in the first mode state, the first insections 212 are engaged with the second insections 431; when mode adjustment mechanism 40 is in the second mode state, first insection 212 is spaced apart from second insection 431.

It is understood that the impact switch ring 430 is externally sleeved on the hammer 200, the impact switch ring 430 and the hammer 200 can move relatively, the impact switch ring 430 is provided with a second insection 431, the guide member 210 is provided with a first insection 212, the first insection 212 and the second insection 431 can be connected in a matching way, so that the guide member 210 and the impact switch ring 430 can be connected, at the moment, the impact switch ring 430 can limit the movement of the guide member 210, the guide member 210 and the impact switch ring 430 are relatively static, and the hammer 200 can move linearly according to a preset path relative to the guide member 210 and impact the tool spindle 30 in at least one operation state.

The position of the impact switch ring 430 can be switched so that the first insections 212 are spaced apart from the second insections 431, and the guide 210 is movable relative to the impact switch ring 430, and the guide 210 can rotate together with the hammer 200 under the driving of the intermittent impact assembly 230, and the hammer 200 and the guide 210 are relatively stationary. Therefore, the position relation and the assembly relation of the guide 210 and the impact switching ring 430 can be adjusted by adjusting the matching relation of the first insections 212 and the second insections 431, so that the motion state of the guide 210 can be controlled, the motion state of the tool spindle 30 can be further improved, and the working mode of the hand-held tool 1 can be controlled.

Further, as shown in fig. 19, 21-26, the mode adjustment mechanism 40 further includes a buffer member 440, one end of the buffer member 440 abuts against the impact switch ring 430 to always push the impact switch ring 430 to move toward the guide member 210. Thus, the buffer 440 may always push the impact switch ring 430 close to the guide 210, so that the first insections 212 may be engaged with the second insections 431.

Further, as shown in fig. 19 to 24, the mode adjusting mechanism 40 further includes a mode switching button 450, the mode switching button 450 is rotatably sleeved on the impact switching ring 430, the mode switching button 450 is rotatable relative to the impact switching ring 430, an inner peripheral wall of the mode switching button 450 is provided with a guiding block 451, an outer peripheral wall of the impact switching ring 430 is provided with a matching block 432 matched with the guiding block 451, the mode switching button 450 is rotated, wherein when the guiding block 451 and the matching block 432 axially abut against each other, the guiding block 451 presses the impact switching ring 430 to compress the buffer 440 to move away from the guiding element 210, and the first insections 212 are spaced apart from the second insections 431; when the guide block 451 is misaligned with the engagement block 432, the impact switch ring 430 moves closer to the guide 210 by the buffer 440, and the first insections 212 are engaged with the second insections 431.

It is understood that the positional relationship between the mode switching knob 450 and the impact switching ring 430 can be switched by rotating the mode switching knob 450 or the impact switching ring 430 to change the engagement state between the guide block 451 and the engagement block 432. Thus, the fitting relationship between the first insection 212 and the second insection 431 can be controlled by switching the fitting relationship between the guide block 451 and the fitting block 432. Further, as shown in fig. 20, the guide block 451 has a guide slope 451a to guide the fitting block 432. Thereby, the fitting relationship between the guide block 451 and the fitting block 432 can be switched easily.

In other embodiments of the present invention, the mode adjustment mechanism 40 may also adopt other structures, and specifically, referring to fig. 2-5, 9 and 13, the mode adjustment mechanism 40 includes a retaining ring 410 and a mode adjustment knob 420. The retaining ring 410 is sleeved on the transmission shaft 10, and specifically sleeved on the above-mentioned impact receiving portion 400, and the retaining ring 410 is rotatable but not axially movable relative to the transmission shaft 10, and the mode adjusting button 420 is rotatably sleeved on the retaining ring 410. The retaining ring 410 is provided with a retaining portion 411, the inner peripheral wall of the mode adjusting button 420 is provided with a channel 422 through which the retaining portion 411 passes, and the channel 422 extends along the axial direction of the transmission shaft 10.

When the mode adjustment mechanism 40 is in the first mode state, the stopping portion 411 stops against the mode adjustment button 420; when the mode adjustment mechanism 40 is in the second mode state, the abutting portion 411 corresponds to the channel 422, and the tool spindle 30 can drive the press ring to move along the axial direction of the tool spindle. Thus, the relative positional relationship between the stopper 411 of the stopper ring 410 and the mode adjustment knob 420 can be adjusted to adjust the movement state of the hammer 200, thereby adjusting the operation mode of the tool spindle 30. Specifically, as shown in fig. 3 to 4, the mode adjustment knob 420 further includes a flange 421 disposed on an inner peripheral wall of the mode adjustment knob 420, the flange 421 is annular and extends in a circumferential direction of the retaining ring 410, and the channel 422 penetrates the flange 421 in an axial direction of the retaining ring 410. Therefore, the flange 421 can form the channel 422, and the flange 421 can also stop against the stop portion 411.

As shown in fig. 3-4, in some embodiments of the present invention, the abutting portion 411 includes a fixing section 411a, a connecting section 411b, and a fitting section 411 c. The fixing section 411a extends from the retaining ring 410, one end of the connecting section 411b is connected with the fixing section 411a, one end of the matching section 411c is connected with the other end of the connecting section 411b, the matching section 411c is suitable for passing through the channel 422, and the fixing section 411a and the connecting section 411b are spaced along the axial direction of the retaining ring 410. Further, the connecting portion 411b is smoothly connected with the fixing portion 411 a; alternatively, the connecting section 411b and the matching section 411c are smoothly connected.

As shown in fig. 2 and 6, in some embodiments of the present invention, the outer peripheral wall of the impact receiving portion 400 has a step surface 404, and the press ring 410 is pressed against the step surface 404. Thus, the stepped surface 404 may limit the movement of the retaining ring 410, avoiding the retaining ring 410 from impacting the receptacle 400.

As shown in fig. 25-27, in some embodiments of the present invention, the end of the shaft 10 connected to the connecting end 380 is the driving end 130, one of the connecting end 380 and the driving end 130 is provided with an axial hole 360, and the other end extends into the axial hole 360. For example, the end face of the drive end 130 of the drive shaft 10 may be provided with an axial hole 360, the axial hole 360 extending along the axial direction of the drive shaft 10, the axial hole 360 being open to the connecting end 380 of the tool spindle 30, and the end of the connecting end 380 of the tool spindle 30 may protrude into the axial hole 360. For another example, the connecting end 380 of the tool spindle 30 may be provided with an axial hole 360, the axial hole 360 extends along the axial direction of the tool spindle 30, the axial hole 360 is open toward the driving end 130 of the transmission shaft 10, and the end of the driving end 130 of the transmission shaft 10 may extend into the axial hole 360. The connection manner in which the connecting end of the tool spindle 30 is provided with the opening to facilitate the insertion of the transmission shaft 10 has been described in the above embodiment 1, and will not be described again. The connection mode in which the opening is provided on the drive end surface of the drive shaft 10 will be described in detail below.

As shown in fig. 25-27, the inner wall of the axial bore 360 and the outer wall of the other end portion are provided with splines 370 for enabling torque transmission between the drive shaft 10 and the tool spindle 30. Therefore, the stability of connection between the transmission shaft 10 and the tool spindle 30 can be improved, and not only the rotation in the circumferential direction of the tool spindle 30 and the transmission shaft 10 can be transmitted, but also the relative movement in the axial direction between the tool spindle 30 and the transmission shaft 10 can be made.

Further, as shown in fig. 13, 25-27, a radial groove may be formed between the splines 370 on the other end portion that extends into the axial hole 360, the outer wall of the axial hole 360 is provided with a radial hole 110, the radial hole 110 corresponds in position to the radial groove when the tool spindle 30 is in the first position, and the steel ball may fall at least partially into the radial groove and disengage from the hammer; when the tool spindle 30 is subjected to an axial force from the output end 390 to the connection end 380, that is, when the tool spindle 30 is located at the second position, the radial hole 110 no longer corresponds to the radial groove, and the steel ball moves along the radial hole 110 and is connected to the ram 200, so that the transmission shaft can drive the ram 200 to rotate. Therefore, the matching relationship between the hammer 200 and the tool spindle 30 or the transmission shaft 10 can be controlled by controlling the relative position relationship between the steel ball and the radial groove, so that the motion state of the hammer 200 can be controlled, and the working state of the tool spindle 30 can be controlled, and the switching of the working modes of the handheld tool 1 can be realized.

As shown in fig. 1, 5, 13, 21, 23, 25-27, according to some embodiments of the present invention, hammer impact mechanism 20 further includes an intermittent impact assembly 230. When the drive shaft 10 drives the ram 200 to rotate, the intermittent impact assembly 230 forces the ram 200 to move linearly relative to the guide 210 along a predetermined path and strike the tool spindle 30 in at least one operating condition. It is understood that the intermittent impact assembly 230 may cooperate with the ram 200 and that the intermittent impact assembly 230 may also cooperate with the guide 210. When the hammer 200 is driven to rotate by the transmission shaft 10, the intermittent impact assembly 230 may change a movement path of the hammer 200, and the movement path may cause the hammer 200 to rotate around the circumferential direction of the transmission shaft 10 and may cause the hammer 200 to move along the axial direction of the transmission shaft 10, so that the hammer 200 may strike the tool spindle 30, thereby completing the sliding of the tool spindle 30 with respect to the transmission shaft 10.

As shown in fig. 2, 5, 7, and 9-12, according to some embodiments of the present invention, the intermittent impact assembly 230 includes an energy accumulating mechanism 231 abutting against the hammer 200, and a conversion member 232 and a curved surface guide 233 provided between the guide member 210 and the hammer 200. It is understood that the intermittent impact assembly 230 includes the energy charging mechanism 231, the conversion member 232, and the curved surface guide portion 233, the conversion member 232 and the curved surface guide portion 233 are both located between the guide member 210 and the hammer 200, and one end of the energy charging mechanism 231 abuts against the hammer 200. Thus, by configuring the specific shape of the curved surface guide part 233 to guide the movement track of the conversion part 232, the conversion part 232 can be linked with the hammer 200, the hammer 200 can drive the conversion part 232 to rotate along the circumferential direction of the transmission shaft 10, and the conversion part 232 can drive the hammer 200 to move along the track of the curved surface guide part 233.

Further, as shown in fig. 13 and fig. 17 to 18, the transmission shaft 10 may be provided with a baffle 100, the baffle 100 is externally sleeved on the peripheral wall of the transmission shaft 10, the energy storage mechanism 231 is located between the hammer 200 and the baffle 100, and an end of the energy storage mechanism 231 away from the hammer 200 may be engaged with the baffle 100. When the ram 200 moves a certain distance toward the energy storage mechanism 231, the ram 200 and the stop plate 100 may compress the energy storage mechanism 231. Thereby, the energy accumulating mechanism 231 can exert an urging force on the hammer 200.

As shown in fig. 11 to 12, in some embodiments of the present invention, the curved surface guide portion 233 may be formed in a ring shape, the curved surface guide portion 233 may be surrounded along a circumferential direction of the transmission shaft 10, the curved surface guide portion 233 may include a climbing section 233a and a falling section 233b, one end of the falling section 233b is connected with one end of the climbing section 233a, and the other end of the falling section 233b extends toward the other end of the climbing section 233 a. Further, the climbing section 233a may have a spiral line type. The falling section 233b may be linear, and the falling section 233b extends in the axial direction of the drive shaft 10. At least a portion of the conversion member 232 may be engaged with the curved guide part 233. Preferably, in order to ensure that the hammer generates sufficient impact force on the tool spindle 30 and the hand-held tool 1 is compact, the climbing height 233a in the axial direction is greater than 3mm and less than or equal to 20mm, preferably, the climbing height is between 4mm and 15mm, and preferably, the climbing height is 10 mm.

When the conversion member 232 is engaged with the climbing section 233a, the conversion member 232 rolls from one end of the climbing section 233a toward the other end of the climbing section 233a, the hammer 200 moves toward the baffle 100, and the hammer 200 and the baffle 100 can compress the energy storage mechanism 231; when the conversion member 232 is located at the other end of the ascending section 233a and rolls toward the falling section 233b, the energy storage mechanism 231 may push the hammer 200 to fall from one end of the falling section 233b close to the barrier 100 toward the other end of the falling section 233b close to the tool head, that is, the hammer 200 moves toward a direction away from the barrier 100 and close to the tool head, a portion of the hammer 200 approaches and strikes a portion of the tool spindle 30 located outside the transmission shaft 10, so that the tool spindle 30 moves relative to the transmission shaft 10 along the axial direction of the transmission shaft 10, and the hammer 200 forms a hammering action on the tool spindle 30 and the tool head.

As shown in fig. 12, in some embodiments of the present invention, the curved guide portion 233 may include a plurality of segments, each segment including a climbing section 233a and a falling section 233 b. The conversion member 232 may be plural, and the plural conversion members 232 may be spaced apart in the circumferential direction of the hammer 200. In the embodiment, the outer diameter of the hammer 200 is 20mm-40mm, the slope height is greater than 3mm and less than or equal to 15mm, preferably, the climbing height is greater than or equal to 4mm and less than or equal to 8mm, and more preferably, the climbing height is 5 mm. It is to be understood that, in order to ensure smooth climbing of the transition member 232, the number of segments is preferably 2 to 7, particularly preferably 3 to 4, and the number of segments of the climbing section 233a is preferably 3 in this embodiment.

The mounting positions and the mounting relationship of the conversion member 232 and the curved guide 233 to the hammer 200 and the guide 210 are not particularly limited. In some embodiments of the present invention, the converting element 232 is located on one of the guide element 210 and the ram 200, and the curved surface guiding element 233 is located on the other of the guide element 210 and the ram 200. Thereby, the fitting relationship of the conversion member 232 and the curved surface guide portion 233 to the hammer 200 and the guide 210 can be realized, so that the relative movement of the hammer 200 with respect to the guide 210 can be realized by the fitting relationship between the conversion member 232 and the curved surface guide portion 233 and the relative movement between the conversion member 232 and the curved surface guide portion 233, and the hammer 200 can be moved with respect to the propeller shaft 10 in the axial direction of the propeller shaft 10. The movement locus of the conversion member 232 at the curved guide portion 233 is a predetermined path of the hammer 200.

As shown in fig. 9-12, in some examples of the invention, the transition piece 232 may be located on the ram 200 and the curved guide 233 is located on the guide 210. For example, as shown in fig. 2, 5, 7, and 11-12, an outer circumferential wall of the hammer 200 may be provided with an insertion groove 202, a portion of the conversion member 232 may be located in the insertion groove 202, an inner circumferential wall of the guide member 210 may be provided with a curved guide portion 233, and another portion of the conversion member 232 may be engaged with the curved guide portion 233.

As shown in fig. 16-18, in other examples of the present invention, the transition piece 232 may be located on the guide piece 210 and the curved surface guide 233 is located on the hammer 200. For example, the guide member 210 may be provided with a receiving groove 211 on an inner circumferential wall thereof, a portion of the conversion member 232 may be located in the receiving groove 211, the hammer 200 may be provided with a curved surface guide 233 on an outer circumferential wall thereof, and another portion of the conversion member 232 may be engaged with the curved surface guide 233.

As shown in fig. 2, 16 and 19, in some embodiments of the present invention, the converting element 232 may be configured as a steel ball, as shown in fig. 11-12, preferably, in order to ensure the strength of the steel ball, the diameter of the steel ball is greater than 4mm and less than or equal to 10mm, advantageously, the diameter of the steel ball is greater than or equal to 4mm and less than or equal to 6mm, and the diameter of the steel ball in this embodiment is 5 mm. The curved guide part 233 may be provided as a cam surface or a cam groove. Therefore, the cam surface or the cam groove can limit the moving track of the steel ball, the steel ball can move in the cam surface or the cam groove, the steel ball has a smooth outer surface, the relative moving friction force between the conversion piece 232 and the curved surface guide part 233 can be reduced, the moving smoothness of the conversion piece 232 in the curved surface guide part 233 is improved, the structural strength of the steel ball is high, the wear resistance is good, and the working performance of the intermittent impact assembly 230 can be guaranteed. It should be noted that the term "cam" as used herein may refer to the curved guide portion 233 protruding from the inner peripheral wall of the guide 210, or the curved guide portion 233 protruding from the outer peripheral wall of the hammer 200.

As shown in fig. 2, 16 and 19, in some embodiments of the present invention, the energy storage mechanism 231 may be configured as an elastic member, for example, the energy storage mechanism 231 may be a spring or an elastic rubber member. This simplifies the installation and assembly of the energy storage mechanism 231 and reduces the manufacturing cost of the energy storage mechanism 231. Further, the energy accumulating means 231 may be formed in a ring shape, and the energy accumulating means 231 may be externally fitted to the outer peripheral wall of the transmission shaft 10. Thus, the assembly of the energy accumulating mechanism 231 is facilitated, and the force of the energy accumulating mechanism 231 against the hammer 200 can be made uniform.

Example 3

As shown in fig. 1 to 30, a hand tool 1 according to an embodiment of the present invention includes a motor 60, a transmission shaft 10, a hammer impact mechanism 20, and a tool spindle 30.

Specifically, as shown in fig. 1, 2 and 5, the transmission shaft 10 is driven by the motor 60 to rotate and rotates around the axis of the transmission shaft 10, in other words, the motor 60 drives the transmission shaft 10 to rotate, and the transmission shaft 10 rotates around the axis of the transmission shaft 10. It is understood that the motor 60 is connected to the transmission shaft 10, and it should be noted that the term "connected" as used herein may mean that the motor 60 is directly connected to the transmission shaft 10, for example, the output end of the motor 60 may be directly connected to the end of the transmission shaft 10, and "connected" may mean that the motor 60 is indirectly connected to the transmission shaft 10, for example, the motor 60 may be directly connected to an intermediate transmission assembly, and then directly connected to the transmission shaft 10 through the intermediate transmission assembly.

The tool spindle 30 is connected axially displaceable but rotationally fixed relative to the drive shaft 10, in other words the tool spindle 30 is stationary relative to the drive shaft 10 in the circumferential direction of the drive shaft 10, and the tool spindle 30 is displaceable relative to the drive shaft 10 in the axial direction of the drive shaft 10. The transmission shaft 10 can drive the tool spindle 30 to rotate along the circumferential direction of the transmission shaft 10, and the tool spindle 30 can also complete sliding in the axial direction of the transmission shaft 10.

As shown in fig. 2, 5-13, the hammer impact mechanism 20 has a hammer 200, and the hammer 200 is sleeved outside the transmission shaft 10 and can be driven to rotate by the transmission shaft 10. It is understood that the hammer impact mechanism 20 includes a hammer 200, the hammer 200 may be externally sleeved on the peripheral wall of the transmission shaft 10, the hammer 200 may be cooperatively connected with the transmission shaft 10, and the transmission shaft 10 may further drive the hammer 200 to rotate around the axis of the transmission shaft 10. It should be noted that "connection" mentioned herein may mean that the hammer 200 is directly connected to the drive shaft 10, or that the hammer 200 is indirectly connected to the drive shaft 10.

As shown in fig. 5, 8-10, 13 and 15, according to some embodiments of the present invention, the hammer impact mechanism 20 further has a disengageable clutch mechanism 220, the clutch mechanism 220 being configured to transmit rotational motion between the drive shaft 10 and the hammer 200. It can be understood that the clutch mechanism 220 can enable the transmission shaft 10 to be matched with the hammer 200, the clutch mechanism 220 can also enable the transmission shaft 10 to be separated from the hammer 200, when the clutch mechanism 220 enables the transmission shaft 10 to be matched with the hammer 200, the rotation motion of the transmission shaft 10 can be transmitted to the hammer 200 through the clutch mechanism 220, so as to drive the hammer 200 to rotate; when the clutch mechanism 220 disengages the two, the engagement relationship between the clutch mechanism 220 and the hammer 200 is released, the drive shaft 10 rotates relative to the hammer 200, and the hammer 200 is stationary relative to the guide 210. Thus, the movement of the hammer 200 can be controlled by the clutch mechanism 220, thereby controlling whether or not the hammer 200 strikes the tool spindle 30, and the operating state of the hand tool 1 can be changed. In some embodiments of the present invention, the clutch mechanism 220 is configured to be closed by a force transmitted via the tool spindle 30. It can be understood that whether the clutch mechanism 220 and the hammer 200 are in a matching relationship or not can be controlled by the tool spindle 30, and the tool spindle 30 can apply an external force to the clutch mechanism 220 to change the relationship between the clutch mechanism 220 and the hammer 200, for example, when the tool head or the tool spindle 30 abuts on a working condition (i.e. when the tool spindle 30 is subjected to an axial load), the clutch mechanism 220 is closed, and the hand-held tool 1 is switched to an impact state. Therefore, when the tool bit abuts against the working condition while the hand tool 1 is in the working state, the hand tool 1 can be automatically switched to the impact state, and hereinafter, this mode is referred to as "impact mode".

It should be noted that, in actual work, not all working conditions are suitable for the handheld tool 1 to work under the impact condition, and many times, the operator wants to keep the handheld tool 1 in the working condition, and the tool head or the tool spindle 30 can still be in the non-impact working condition when being subjected to the load from the working conditions, and this working mode is hereinafter referred to as "non-impact working mode".

Thus, in order to allow the hand tool 1 to accommodate a variety of operating conditions, the hand tool 1 further comprises a mode adjustment mechanism 40, as shown in fig. 2-6, 13-15 and 19-30, the mode adjustment mechanism 40 being operable to switch between a first mode state and a second mode state, when the mode adjustment mechanism 40 is in the first mode state (i.e., the position shown in fig. 5-6, 9-10, 21-22, and 25), the hammer 200 can be driven to rotate by the drive shaft 10 to move linearly along a predetermined path, and strikes the tool spindle 30 in at least one operating state, in other words, the drive shaft 10 can cooperate with the ram 200, the drive shaft 10 can power the ram 200, so that the hammer 200 moves along a preset path and the hammer 200 can strike the tool spindle 30 during the movement; when the mode adjustment mechanism 40 is in the second mode state (the position shown in fig. 13-15, 23-24, and 26), the drive shaft 10 cannot drive the hammer 200 to rotate, and the hammer 200 has no impact on the tool spindle 30.

According to the utility model discloses hand tool 1, through setting up mode adjustment mechanism 40, and the cooperation relation between state change transmission shaft 10 and the ram 200 through switching mode adjustment mechanism 40, thereby can control whether ram 200 has the striking effect to tool spindle 30, and then can realize the switching of 1 impact mode of hand tool and non-impact mode, thereby can improve hand tool 1's performance, make hand tool 1's structure set up compactly, simply, the function is diversified, and can conveniently carry simultaneously.

It is understood that the clutch mechanism 220 includes a clutch member 221 and a receiving portion 201, and one of the transmission shaft 10 and the hammer 200 is provided with the clutch member 221 and the other is provided with the receiving portion 201. When the clutch mechanism 220 is in the closed state, the clutch member 221 is engaged with the housing portion 201, and when the clutch mechanism 220 is in the disengaged state, the clutch member 221 is disengaged from the housing portion 201. Thus, the operating state of the clutch mechanism 220 can be switched by the fitting relationship between the clutch member 221 and the housing portion 201.

For example, as shown in fig. 5, the tool spindle 30 is switchable between a first position and a second position relative to the drive shaft 10 via the action of an axial force, when the tool spindle 30 is in the second position, the ram 200 is rotatably driven by the drive shaft 10 and is movable relative to the guide 210 along a predetermined path so as to strike the tool spindle 30 along its axis in at least one operating state; when the tool spindle 30 is in the first position, the drive shaft 10 cannot drive the ram 200 to rotate. The cutter spindle 30 comprises a connecting end connected with the transmission shaft 10 and an output end connected with the tool head, one side of the transmission shaft 10 close to the connecting end is provided with a cavity 120 with an axial opening, the cavity 120 can extend along the axial direction of the transmission shaft 10, the connecting end of the cutter spindle 30 extends into the cavity 120 from the opening, the inner wall of the cavity 120 is matched with the outer wall of the connecting end of the cutter spindle 30 through a spline 370 extending along the axial direction, so that the cutter spindle 30 can move axially relative to the transmission shaft 10 and can rotate together with the transmission shaft 10. Specifically, as shown in fig. 2, the outer wall of the tool spindle 30 and the inner wall of the cavity 120 are provided with ribs 340, and a radially recessed groove 350 is formed between adjacent ribs 340 on the tool spindle 30, so that the inner wall of the cavity 120 can be matched with the groove 350.

With continued reference to fig. 5, 8-10, 13 and 15, a radial hole 110 is formed on a sidewall of the cavity 120, the radial hole 110 penetrates through the sidewall of the cavity 120 in the radial direction of the transmission shaft 10, the clutch member 221 is located in the radial hole 110 and can move in the radial hole 110, and the receiving portion 201 may be formed on an inner circumferential wall of the hammer 200. Referring to fig. 13 and 15, when the clutch mechanism 220 is in the disengaged state, that is, when the tool spindle 30 moves to the second position, the radial hole 110 corresponds to the position of the groove 350, and the clutch member 221 moves in a direction away from the receiving portion 201 of the hammer 200 and close to the groove 350 along the radial hole 110, so that the clutch member 221 is disengaged from the hammer 200; referring to fig. 9 and 10, when the clutch mechanism 220 is in the closed state, that is, the tool spindle moves to the second position, the groove 350 no longer corresponds to the position of the radial hole 110, that is, there is no room for the clutch 221 to be received at the position on the tool spindle 30 corresponding to the radial hole, the tool spindle 30 presses the clutch 221 during the movement to move the clutch 221 along the radial hole 110 toward the receiving portion 221 of the hammer, so that a portion of the clutch 221 is located in the radial hole 110, and another portion is located in the receiving portion 201, and the hammer 200 rotates under the action of the clutch 221 and can rotate together with the transmission shaft 10. It should be noted that, in other embodiments of the present invention, the cavity 120 may also be located at the connecting end of the tool spindle 30, and the end of the transmission shaft 10 connected to the tool spindle 30 extends into the cavity 120.

As shown in fig. 2, 5, 7, and 9-12, according to some embodiments of the present invention, the intermittent impact assembly 230 includes an energy accumulating mechanism 231 abutting against the hammer 200, and a conversion member 232 and a curved surface guide 233 provided between the guide member 210 and the hammer 200. The intermittent impact assembly 230 further includes an energy accumulating mechanism 231, the conversion member 232 and the curved surface guide portion 233 are both located between the guide member 210 and the hammer 200, and one end of the energy accumulating mechanism 231 abuts against the hammer 200. Thus, by configuring the specific shape of the curved guide part 233 to guide the movement locus of the conversion member 232, the conversion member 232 can be interlocked with the hammer 200, and the hammer 200 moves along the locus of the curved guide part 233 by the conversion member 232.

Further, as shown in fig. 13 and fig. 17 to 18, the transmission shaft 10 may be provided with a baffle 100, the baffle 100 is externally sleeved on the peripheral wall of the transmission shaft 10, the energy storage mechanism 231 is located between the hammer 200 and the baffle 100, and an end of the energy storage mechanism 231 away from the hammer 200 may be engaged with the baffle 100. When the ram 200 moves a certain distance toward the energy storage mechanism 231, the ram 200 and the stop plate 100 may compress the energy storage mechanism 231. Thereby, the energy accumulating mechanism 231 can exert an urging force on the hammer 200. Of course, other structures can be adopted for the axial limiting mode of the energy storage mechanism, and the description is omitted here.

As shown in fig. 11 to 12, in some embodiments of the present invention, the curved surface guide portion 233 may be formed in a ring shape, and the curved surface guide portion 233 may be surrounded along a circumferential direction of the transmission shaft 10, specifically, the curved surface guide portion 233 may include a climbing section 233a and a falling section 233b, one end of the falling section 233b is connected to one end of the climbing section 233a, and the other end of the falling section 233b extends toward the other end of the climbing section 233 a. Further, the climbing section 233a may have a spiral line type, the falling section 233b may have a linear type, and the falling section 233b extends in the axial direction of the transmission shaft 10. Preferably, in order to ensure that the hammer generates sufficient impact force on the tool spindle 30 and the hand-held tool 1 is compact in size, the climbing height 233a in the axial direction is greater than 3mm and less than or equal to 15mm, preferably greater than or equal to 4mm and less than or equal to 8mm, and preferably 5 mm.

As shown in fig. 5, 9 and 13, according to some embodiments of the present invention, the tool spindle 30 is provided with an impact receiving portion 400 coupled to the hammer 200. It is understood that the tool spindle 30 may be provided with an impact receiving portion 400, and the hammer 200 may strike the impact receiving portion 400, whereby the hammer 200 may drive the tool spindle 30 to move by striking the impact receiving portion 400, so that the tool spindle 30 may be moved relative to the drive shaft 10 in the axial direction of the drive shaft 10.

As shown in fig. 12, in some embodiments of the present invention, the curved guide portion 233 may include a plurality of segments, each segment including a climbing section 233a and a falling section 233 b. The conversion member 232 may be plural, and the plural conversion members 232 may be spaced apart in the circumferential direction of the hammer 200. In order to ensure the reasonableness of the overall design of the hand-held tool, the outer diameter of the middle hammer 200 is 15mm-50mm, preferably the outer diameter of the hammer is 20mm-40mm, the slope height is greater than 3mm and less than or equal to 15mm, preferably the climbing height is greater than or equal to 4mm and less than or equal to 8mm, and more preferably the climbing height is 5 mm. It will be appreciated that, in order to ensure that the transition piece 232 can climb smoothly, the number of segments is preferably 2 to 7, particularly advantageously 3 to 4, and the number of segments of the ascending segment 233a in this embodiment is preferably 3.

The specific form of mode switching by the mode adjustment mechanism 40 of the hand tool 1 will be described below in conjunction with the specific structure of the hand tool 1.

As shown in fig. 19 to 20, in some embodiments of the present invention, the mode adjustment mechanism 40 includes a first insection 212 disposed on the guiding element 210, an impact switch element having a second insection 431, the impact switch element is axially movable but non-rotatably fixed in the housing of the hand tool 1, the impact switch element is an impact switch ring 430, and the impact switch ring 430 is movably sleeved on the hammer 200. Wherein, when the mode adjustment mechanism 40 is in the first mode state, the first insections 212 are engaged with the second insections 431; when mode adjustment mechanism 40 is in the second mode state, first insection 212 is spaced apart from second insection 431.

In other embodiments of the present invention, the mode adjustment mechanism 40 may also adopt other structures, specifically, referring to fig. 2-5, 9 and 13, the mode adjustment mechanism 40 includes a retaining ring 410 and a mode adjustment knob 420. The retaining ring 410 is sleeved on the transmission shaft 10, and specifically sleeved on the above-mentioned impact receiving portion 400, and the retaining ring 410 is rotatable but not axially movable relative to the transmission shaft 10, and the mode adjusting button 420 is rotatably sleeved on the retaining ring 410. The retaining ring 410 is provided with a retaining portion 411, the inner peripheral wall of the mode adjusting button 420 is provided with a channel 422 through which the retaining portion 411 passes, and the channel 422 extends along the axial direction of the transmission shaft 10.

As shown in fig. 2 and 6, in some embodiments of the present invention, the outer peripheral wall of the impact receiving portion 400 has a step surface 404, and the press ring 410 is pressed against the step surface 404. Thus, the stepped surface 404 may limit the movement of the stopper ring 410, preventing the stopper ring 410 from being detached from the impact receiving part 400.

Example 4

As shown in fig. 1 to 30, a hand tool 1 according to an embodiment of the present invention includes a motor 60, a transmission shaft 10, a tool spindle 30, a hammer impact mechanism 20, and an impact switch ring 430.

Specifically, the rotation direction of the motor 60 includes a first direction and a second direction, and one of the first direction and the second direction may be a clockwise direction and the other may be a counterclockwise direction. The motor 60 may drive the drive shaft 10 to rotate. The tool spindle 30 is connected to the drive shaft 10, the tool spindle 30 being movable relative to the drive shaft 10, for example the tool spindle 30 being movable relative to the drive shaft 10. The hammer impact mechanism 20 includes a hammer 200 and a guide member 210, the hammer 200 is sleeved outside the transmission shaft 10, and the transmission shaft 10 can drive the hammer 200 to rotate. According to the utility model discloses hand tool 1, through setting up guide 210 and intermittent type impact assembly 230, utilize intermittent type to strike assembly 230, ram 200 and guide 210's cooperation relation, can guide ram 200 and make linear motion, and ram 200 can also strike cutter main shaft 30, thereby can realize the ascending removal of cutter main shaft 30 axis direction, when making cutter main shaft 30 drill on environmental component (like wall or plate), cutter main shaft 30 forms the impact force to environmental component, thereby can improve hand tool 1's drilling efficiency, moreover, the utility model discloses hand tool 1's of embodiment structure sets up compactness and simple structure, can conveniently carry.

As shown in fig. 2, 5, 7, and 9 to 12, the intermittent impact assembly 230 includes an energy accumulating mechanism 231 abutting against the hammer 200, and a conversion member 232 and a curved surface guide portion 233 provided between the guide member 210 and the hammer 200. The intermittent impact assembly 230 further includes an energy accumulating mechanism 231, the conversion member 232 and the curved surface guide portion 233 are both located between the guide member 210 and the hammer 200, and one end of the energy accumulating mechanism 231 abuts against the hammer 200. Thus, by configuring the specific shape of the curved guide part 233 to guide the movement locus of the conversion member 232, the conversion member 232 can be interlocked with the hammer 200, and the hammer 200 moves along the locus of the curved guide part 233 by the conversion member 232.

As shown in fig. 11 and 12, in the present invention, the ascending section 233a and the falling section 233b are disposed inside the guiding element 210, when the motor 60 rotates forward, in the "impact mode", the hammer 200 impacts the tool spindle 30 to realize a hammering action, but when the motor 60 rotates backward, the converting element 232 needs to cross the falling section 233b and move to the ascending section 233b, but in order to ensure the impact effect of the hammer 200, the falling sections 233b are substantially coaxial and parallel, so when the converting element 232 rotates axially, the converting element 232 cannot cross the falling section 233b, which causes the motor to "stall", or even burn.

Therefore, referring to fig. 28-30, the hand tool 1 further comprises an impact ring 11a fixed to the housing 80 in a non-rotatable manner, the impact ring 11a is provided with a first end tooth 12a, the guide member 210 is provided with a second end tooth 213a capable of meshing with the first end tooth 12a, when the motor 60 rotates in the first direction, the first end tooth 12a limits the rotation of the guide member 213 through the second end tooth 213a meshing therewith, and the conversion member 232 moves along the curved guide portion in the predetermined direction to make the hammer 200 strike the tool spindle 30 in at least one operating state; when the motor 60 rotates in the second direction, the second end tooth 213a and the guide member 213 rotate relative to the first end tooth 12a engaged therewith under the driving of the motor 60, that is, the second end tooth 213a of the guide member 213 performs a climbing motion relative to the first end tooth 12 a. The first end tooth 12a comprises a plurality of first teeth 121a, the first teeth 121a comprise a guide section 121b and a stop section 121c, the guide section 121b is connected with the free end of the stop section 121c, the second end tooth 213a comprises a plurality of second teeth 2131a, when the motor 60 rotates along the first direction, the second teeth 2131a move from the stop section 121c to the guide section 121b, and the stop section 121c abuts against the second teeth 2131a, so that the guide member 210 cannot rotate; when the motor 60 rotates in the second direction and the second tooth 2131a moves from the guide segment 121b to the stop segment 121c, the second tooth 2131a can move along the guide segment 121b, so that the guide 213 rotates relative to the first end tooth 12 a. The guide section 121b and the stopping section 121c are sequentially arranged at intervals along the circumferential direction of the first end tooth 12a, and the stopping section 121c is parallel to the axis of the transmission shaft 10. When the second tooth 2131a moves from the stopping section 121c to the guiding section 121b, the side of the second tooth 2131a abutting against the stopping section 121c is parallel to the stopping section 121 c. The impact ring 11a is axially movable to engage or disengage the first end tooth 12a with or from the second end tooth 213a, and when the first end tooth 12a is disengaged from the second end tooth 213a, the guide 210 is rotated by the motor and the tool is in a non-impact mode. It is understood that, when the impact ring 11a is axially movable in the present embodiment, the impact ring 11a in the present embodiment has not only the function of "anti-stalling", but also the function realized by the impact switch ring 430 described in the other embodiments of the present invention, in other words, in the embodiments described above, by setting the tooth pattern shapes of the first tooth pattern 212 and the second tooth pattern 431 of the embodiments described above to the tooth pattern shapes of the first tooth 121a and the second tooth 2131a of the embodiments described above, the mode switching mechanism 40 in the embodiments described above has not only the mode switching function, but also the anti-stalling function in the impact mode.

As shown in fig. 5, 8-10, 13 and 15, according to some embodiments of the present invention, the hammer impact mechanism 20 further has a disengageable clutch mechanism 220, the clutch mechanism 220 being configured to transmit rotational motion between the drive shaft 10 and the hammer 200. It can be understood that the clutch mechanism 220 can enable the transmission shaft 10 to be matched with the hammer 200, the clutch mechanism 220 can also enable the transmission shaft 10 to be separated from the hammer 200, when the clutch mechanism 220 enables the transmission shaft 10 to be matched with the hammer 200, the rotation motion of the transmission shaft 10 can be transmitted to the hammer 200 through the clutch mechanism 220, so as to drive the hammer 200 to rotate; when the clutch mechanism 220 disengages the two, the engagement relationship between the clutch mechanism 220 and the hammer 200 is released, the drive shaft 10 rotates relative to the hammer 200, and the hammer 200 is stationary relative to the guide 210. Thus, the movement of the hammer 200 can be controlled by the clutch mechanism 220, thereby controlling whether or not the hammer 200 strikes the tool spindle 30, and the operating state of the hand tool 1 can be changed. In some embodiments of the present invention, the clutch mechanism 220 is configured to be closed by a force transmitted via the tool spindle 30. It can be understood that whether the clutch mechanism 220 and the hammer 200 are in a matching relationship or not can be controlled by the tool spindle 30, and the tool spindle 30 can apply an external force to the clutch mechanism 220 to change the relationship between the clutch mechanism 220 and the hammer 200, for example, when the tool head or the tool spindle 30 abuts on a working condition (i.e. when the tool spindle 30 is subjected to an axial load), the clutch mechanism 220 is closed, and the hand-held tool 1 is switched to an impact state.

As shown in fig. 5, the tool spindle 30 is switchable between a first position and a second position relative to the drive shaft 10 by the action of an axial force, when the tool spindle 30 is in the second position, the ram 200 is rotatably driven by the drive shaft 10 and is movable relative to the guide 210 along a predetermined path so as to strike the tool spindle 30 along the axis of the tool spindle 30 in at least one operating state; when the tool spindle 30 is in the first position, the drive shaft 10 cannot drive the ram 200 to rotate. The cutter spindle 30 comprises a connecting end connected with the transmission shaft 10 and an output end connected with the tool head, one side of the transmission shaft 10 close to the connecting end is provided with a cavity 120 with an axial opening, the cavity 120 can extend along the axial direction of the transmission shaft 10, the connecting end of the cutter spindle 30 extends into the cavity 120 from the opening, the inner wall of the cavity 120 is matched with the outer wall of the connecting end of the cutter spindle 30 through a spline 370 extending along the axial direction, so that the cutter spindle 30 can move axially relative to the transmission shaft 10 and can rotate together with the transmission shaft 10. Specifically, as shown in fig. 2, the outer wall of the tool spindle 30 and the inner wall of the cavity 120 are provided with ribs 340, and a radially recessed groove 350 is formed between adjacent ribs 340 on the tool spindle 30, so that the inner wall of the cavity 120 can be matched with the groove 350.

With continued reference to fig. 5, 8-10, 13 and 15, a radial hole 110 is formed on a sidewall of the cavity 120, the radial hole 110 penetrates through the sidewall of the cavity 120 in the radial direction of the transmission shaft 10, the clutch member 221 is located in the radial hole 110 and can move in the radial hole 110, and the receiving portion 201 may be formed on an inner circumferential wall of the hammer 200. Referring to fig. 13 and 15, when the clutch mechanism 220 is in the disengaged state, that is, when the tool spindle 30 moves to the second position, the radial hole 110 corresponds to the position of the groove 350, and the clutch member 221 moves in a direction away from the receiving portion 201 of the hammer 200 and close to the groove 350 along the radial hole 110, so that the clutch member 221 is disengaged from the hammer 200; referring to fig. 9 and 10, when the clutch mechanism 220 is in the closed state, that is, when the tool spindle 30 moves to the second position, the groove 350 no longer corresponds to the position of the radial hole 110, that is, there is no room for the clutch 221 to be received at the position of the tool spindle 30 corresponding to the radial hole 110, the tool spindle 30 presses the clutch 221 during the movement to move the clutch 221 along the radial hole 110 toward the receiving portion 221 of the hammer, so that a portion of the clutch 221 is located in the radial hole 110, and another portion is located in the receiving portion 201, and the hammer 200 rotates under the action of the clutch 221 and can rotate together with the transmission shaft 10. It should be noted that, in other embodiments of the present invention, the cavity 120 may also be located at the connecting end of the tool spindle 30, and the end of the transmission shaft 10 connected to the tool spindle 30 extends into the cavity 120.

Example 5

The hand tool 1 according to various embodiments of the present invention is described in detail below with reference to fig. 1-27. It is to be understood that the following description is illustrative only and is not intended as a specific limitation on the invention.

As shown in fig. 1 to 15, a hand tool 1 according to an embodiment of the present invention includes a motor 60, a drive shaft 10, a tool spindle 30, a reset member 70, a hammer impact mechanism 20, an impact receiving portion 400, a retaining ring 410, and a mode adjustment knob 420.

Specifically, the motor 60 is connected to the transmission shaft 10, and the motor 60 can drive the transmission shaft 10 to rotate along the axial direction of the transmission shaft 10, and the transmission shaft 10 rotates around the axial line of the transmission shaft 10. The transmission shaft 10 can be formed into a cylinder with an open end, that is, the transmission shaft 10 can be formed into a cavity 120 with an open end, the cavity 120 can extend along the axial direction of the transmission shaft 10, the tool spindle 30 can extend into the transmission shaft 10 from the open end of the cavity 120, the other end of the transmission shaft 10 can be formed into a flat square 140, and torque transmission is performed between the flat square 140 and the motor 60, the resetting piece 70 is located in the cavity 120, one end of the resetting piece 70 is axially abutted against the tool spindle 30, and the other end of the resetting piece 70 is abutted against the bottom wall of the cavity 120 far away from the open end. Reset element 70 may normally urge tool spindle 30 from the bottom wall of cavity 120 toward the open end of cavity 120.

As shown in fig. 2, an end of the tool spindle 30 near the drive shaft 10 may include a first section 310, a second section 320, and a third section 330, the first section 310 being connected to an end of the second section 320, and an end of the second section 320 being connected to the third section 330. The axis of the first section 310 coincides with the axis of the third section 330, the third section 330 completely extends into the cavity 120 of the transmission shaft 10, a part of the first section 310 can extend into the cavity 120, the other part of the first section 310 is positioned outside the cavity 120, the cross-sectional radius of the third section 330 is smaller than that of the first section 310, and the peripheral wall of the second section 320 is an arc surface. The outer peripheral wall of the third section 330 is provided with a plurality of ribs 340, the plurality of ribs 340 are arranged at intervals along the circumferential direction of the third section 330, any one rib 340 extends along the axial direction of the third section 330, and any two adjacent ribs 340 can be configured into a groove 350.

The inner peripheral wall of the transmission shaft 10 corresponding to the cavity 120 may be provided with a plurality of protrusions, the plurality of protrusions are arranged at intervals along the circumferential direction of the transmission shaft 10, and any one of the protrusions extends along the axial direction of the transmission shaft 10. Any two adjacent projections can be configured into a matching groove, any one rib 340 corresponds to one matching groove, and each rib 340 can extend into the corresponding matching groove. When the transmission shaft 10 rotates, the rib 340 may abut against at least one of the two protrusions corresponding to the mating groove, so as to drive the tool spindle 30 to rotate along the circumferential direction of the transmission shaft 10. The tool spindle 30 is movable relative to the drive shaft 10 in the axial direction of the drive shaft 10, and the tool spindle 30 can perform sliding movement in the axial direction of the drive shaft 10.

As shown in fig. 5, 8-10, 13, and 15, the hammer impact mechanism 20 includes a hammer 200, a guide 210, a clutch mechanism 220, and an intermittent impact assembly 230. The clutch mechanism 220 includes a clutch member 221 and a receiving portion 201, and the intermittent impact assembly 230 includes an energy storage mechanism 231, a conversion member 232 and a curved surface guide portion 233.

As shown in fig. 5, 8-10, 13 and 15, the hammer 200 is housed around the outer peripheral wall of the drive shaft 10, the hammer 200 is located near an end of the drive shaft 10 remote from the reset member 70, and the inner peripheral wall of the hammer 200 is spaced from the outer peripheral wall of the drive shaft 10. A portion of the driving shaft 10 that is fitted over the hammer 200 may be provided with a radial hole 110, the radial hole 110 penetrating the driving shaft 10 in a radial direction of the driving shaft 10, the clutch member 221 may be located in the radial hole 110, and the clutch member 221 may be movable in the radial hole 110. The inner circumferential wall of the hammer 200 may be provided with a receiving portion 201, the receiving portion 201 may penetrate the hammer 200 in the axial direction of the transmission shaft 10, the receiving portion 201 may be provided as a groove 201a, a part of the inner circumferential wall of the hammer 200 may be recessed outward in the radial direction of the hammer 200 to construct the groove 201a, and the clutch member 221 may be provided as a steel ball. The diameter of the steel ball is more than or equal to 3mm and less than or equal to 8 mm. The bottom wall of the groove 201a may be formed into an arc-shaped face, which may be recessed toward the radially outer side of the hammer 200.

When the clutch mechanism 220 is in a closed state, the steel ball moves to a position between the transmission shaft 10 and the hammer 200, namely, one part of the steel ball is located in the radial hole 110, and the other part of the steel ball is located in the groove body 201a, the part of the steel ball located in the groove body 201a can be matched and abutted against the groove body 201a, and when the steel ball rotates along with the transmission shaft 10, the steel ball can drive the hammer 200 to rotate along the circumferential direction of the transmission shaft 10. When the clutch mechanism 220 is in the disengaged state, when the steel ball moves between the drive shaft 10 and the tool spindle 30, i.e., a portion of the steel ball is located in the radial hole 110 and another portion of the steel ball is located in the groove 350, the drive shaft 10 is spaced apart from the hammer 200, and the hammer 200 is in a stationary state.

The position of the steel ball can be switched by the positional relationship of the tool spindle 30 with respect to the drive shaft 10. When the tool head is in a working state and bears an axial abutting force from a working condition, that is, when the tool spindle 30 moves towards a direction close to the reset piece 70, the reset piece 70 is compressed, the first section 310 of the tool spindle 30 is opposite to the through hole 110, the first section 310 extrudes the steel ball, the steel ball moves from the groove 350 to the groove body 201a along the radial direction of the through hole 110, one part of the steel ball is matched with the through hole 110, the other part of the steel ball is matched with the groove body 201a, so that the transmission shaft 10 and the hammer 200 rotate, the clutch mechanism 220 is in a meshing state, and the hand-held tool 1 is in the above-mentioned impact state; when the axial force from the working condition disappears, the tool spindle 30 moves towards the direction close to the tool head under the action of the reset piece 70, the tool spindle 30 moves from the first section 310 to the third section 330 relative to the through hole 110, so that the first section 310 does not extrude the steel ball any more, the steel ball moves into the groove 350 along the through hole 110 under the action of the hammer 200 and is separated from the groove body 201a, the transmission shaft 10 cannot drive the hammer 200 to rotate, and the clutch mechanism 220 is in a separated state. Referring to fig. 15, in the present embodiment, when the clutch mechanism 220 is in the disengaged state, the steel ball remains at least partially within the through hole 110 to facilitate the switching of the clutch mechanism 220 between the engaged state and the disengaged state.

As shown in fig. 5, 8 to 10, 13 and 15, the guide member 210 is externally fitted to the outer circumferential wall of the hammer 200, the curved guide portion 233 is formed on the inner circumferential wall of the guide member 210, the curved guide portion 233 may be formed in a ring shape, and the curved guide portion 233 may be surrounded in the circumferential direction of the propeller shaft 10. The curved guide part 233 may include a plurality of segments, each of which corresponds to one of the conversion members 232. Each segment includes a climbing segment 233a and a falling segment 233 b. The climbing section 233a may be a spiral line type, and the falling section 233b may be a straight line type. The conversion member 232 may be provided as a steel ball.

Referring to fig. 16 to 18, unlike the embodiment shown in fig. 1 to 15, in another embodiment of the present invention, a receiving groove 211 may be formed on an inner peripheral wall of the guide member 210, a portion of the conversion member 232 may be located in the receiving groove 211, the conversion member 232 may be connected (e.g., snapped) to the guide member 210, a curved surface guide 233 may be formed on an outer peripheral wall of the hammer 200, and another portion of the conversion member 232 may be engaged with the curved surface guide 233.

As shown in fig. 5, 7-10, 13, 15, the end surface of the hammer 200 facing the reset member 70 may be provided with a mounting groove 203. The transmission shaft 10 may be provided with a baffle 100, the baffle 100 is sleeved on the outer circumferential wall of the transmission shaft 10, the baffle 100 is connected with the transmission shaft 10, and the baffle 100 is opposite to the mounting groove 203. The energy storage mechanism 231 is located between the ram 200 and the baffle 100, one end of the energy storage mechanism 231 can extend into the mounting groove 203, the end of the energy storage mechanism 231 can abut against the bottom wall of the mounting groove 203, and the other end of the energy storage mechanism 231 can abut against the baffle 100. The energy storage mechanism 231 may be provided as a ring spring, which may be sleeved outside the transmission shaft 10.

As shown in fig. 2, 5, 1, 9-10 and 13, an insertion groove 202 may be formed on an outer circumferential wall of the hammer 200, a portion of the conversion member 232 may be located in the insertion groove 202, such that the conversion member 232 is connected to the hammer 200, and a portion of the conversion member 232 located outside the insertion groove 202 may be engaged with the curved guide 233, such that the conversion member 232 may move along the curved guide 233, such that the hammer 200 moves along a path of the curved guide 233 by the rotational force of the transmission shaft 10.

When the conversion member 232 is engaged with the climbing section 233a, the conversion member 232 rolls from the other end of the climbing section 233a toward one end of the climbing section 233a, the hammer 200 moves toward the baffle 100, and the hammer 200 and the baffle 100 can compress the energy storage mechanism 231; when the transition piece 232 is located at one end of the ascending section 233a and rolls toward the falling section 233b, the energy accumulating mechanism 231 may always push the hammer 200 to fall from one end of the falling section 233b toward the other end of the falling section 233b, and the hammer 200 moves in a direction away from the barrier 100.

As shown in fig. 5, 9 and 13, the tool spindle 30 may be provided with an impact receiving portion 400, the impact receiving portion 400 may be fixedly connected to the tool spindle 30, the impact receiving portion 400 may be formed in a ring shape, the impact receiving portion 400 may be sleeved on the first section 310 of the tool spindle 30, the impact receiving portion 400 is located outside the transmission shaft 10, and the impact receiving portion 400 is connected (e.g., clamped or welded) to the tool spindle 30. When the hammer 200 moves a distance in a direction away from the shield plate 100, the hammer 200 can contact the impact receiving portion 400, and due to the urging action of the energy accumulating mechanism 231, the hammer 200 can have an impact action effect on the impact receiving portion 400, so that the tool spindle 30 can move in a direction away from the reset piece 70 along the axial direction of the transmission shaft 10.

Since the environmental component (e.g. wall surface or flat plate) drilled by the handheld tool 1 has a load effect on the tool spindle 30, the tool spindle 30 moves toward the direction close to the reset member 70, and the process is repeated, so that the tool spindle 30 can rotate along the circumferential direction of the transmission shaft 10 under the driving action of the transmission shaft 10, and the tool spindle 30 can move along the axial direction of the transmission shaft 10 under the impact action of the ram 200 and the external force action of the environmental component.

In the above, it was described that the hand tool 1 is capable of performing a hammering function when the hand tool 1 is in an operating state, i.e. the tool head is under the action of an axial force. However, in practice, some operators do not need the hammering function, and therefore, the handheld tool of the present invention further has the mode adjusting mechanism 40.

As shown in fig. 6, the outer circumferential wall of the shock-receiving portion 400 may include a first surface 401, a second surface 402, and a third surface 403, the first surface 401 being connected to one end of the second surface 402, the other end of the second surface 402 being connected to the third surface 403, the first surface 401 being coincident with an extending direction of the third surface 403, the first surface 401 being spaced apart from the third surface 403 in a radial direction of the shock-receiving portion 400, the first surface 401 being located radially outward of the third surface 403. The first surface 401, the second surface 402 and the third surface 403 are configured as a step surface 404. The retaining ring 410 is sleeved on the impact receiving portion 400 corresponding to the third surface 403, and the impact receiving portion 400 corresponding to the first surface 401 may axially define the retaining ring 410 on the third surface 403.

As shown in fig. 3-6, the mode adjustment knob 420 is rotatably sleeved on the retaining ring 410. The retaining ring 410 is provided with a retaining portion 411, the inner peripheral wall of the mode adjusting button 420 is provided with a flange 421, the flange 421 is annular and extends along the circumferential direction of the retaining ring 410, the flange 421 can form a channel 422, the channel 422 penetrates through the flange 421 along the axial direction of the retaining ring 410, and the retaining portion 411 can pass through the channel 422.

As shown in fig. 3 to 4, the abutting portion 411 includes a fixing section 411a, a connecting section 411b, and a fitting section 411 c. The fixing section 411a extends from the retaining ring 410, one end of the connecting section 411b is connected with the fixing section 411a, one end of the matching section 411c is connected with the other end of the connecting section 411b, the matching section 411c is suitable for passing through the channel 422, and the fixing section 411a and the connecting section 411b are spaced along the axial direction of the retaining ring 410. The connecting portion 411b and the fixing portion 411a are connected to each other, and the connecting portion 411b and the matching portion 411c are connected to each other.

When the stopping portion 411 stops against the mode adjusting button 420, the stopping ring 410 is stationary relative to the mode adjusting button 420, the stopping ring 410 further stops against the impact receiving portion 400 corresponding to the first surface 401, the impact receiving portion 400 is stationary, the impact receiving portion 400 further limits movement of the tool spindle 30, external force applied by an environmental component to the tool spindle 30 cannot drive the tool spindle 30 to move, the clutch member 221 is located between the tool spindle 30 and the transmission shaft 10, the hammer 200 is spaced apart from the transmission shaft 10, the motor 60 drives the transmission shaft 10 to rotate, the transmission shaft 10 further drives the tool spindle 30 to rotate, and the tool spindle 30 only rotates.

When the stopping portion 411 is located in the channel 422, the stopping portion 411 can move in the channel 422, the external force applied by the environmental component to the tool spindle 30 drives the tool spindle 30 to move toward the reset piece 70, and further drives the clutch piece 221 to be disposed between the transmission shaft 10 and the hammer 200, the transmission shaft 10 can drive the hammer 200 to rotate, the hammer 200 can move along the axial direction of the transmission shaft 10 under the matching action of the conversion piece 232 and the curved surface guide portion 233 and strike the impact receiving portion 400, the impact receiving portion 400 can further drive the pressure stopping ring 410 to move in the inner ring of the mode adjusting button 420, and the tool spindle 30 has both movement in the axial direction and rotation in the circumferential direction.

The mode adjustment mechanism 40 may have other configurations in other embodiments of the present invention.

Unlike the embodiment shown in fig. 1-15, in the embodiment shown in fig. 19-26, the mode adjustment mechanism 40 includes a shock switching ring 430, a buffer 440, and a mode switching knob 450. Specifically, the guide 210 has a first insection 212, the mode adjustment mechanism 40 includes an impact switch ring 430, the impact switch ring 430 is movably sleeved outside the hammer 200, and the impact switch ring 430 has a second insection 431 matching the first insection 212. One end of the buffer 440 abuts against the impact switching ring 430 to always push the impact switching ring 430 to move toward the guide 210. The mode switch knob 450 is rotatably sleeved on the impact switch ring 430, the mode switch knob 450 is rotatable relative to the impact switch ring 430, the inner peripheral wall of the mode switch knob 450 is provided with a guide block 451, the outer peripheral wall of the impact switch ring 430 is provided with a matching block 432 matched with the guide block 451, and the impact switch ring 430 is axially movable but non-rotatably fixed on the housing.

A rotation mode switching button 450 in which the first insection 212 is spaced apart from the second insection 431 when the guide block 451 abuts against the fitting block 432, and at this time, the guide 210 is movable with respect to the impact switching ring 430, and the guide 210 is rotated together with the hammer 200 by the intermittent impact assembly 230, and the hammer 200 and the guide 210 are relatively stationary, so that the hammer 200 does not collide with the tool spindle 30; by continuing to rotate the mode switching knob 450, when the guide block 451 is misaligned with the mating block 432, the first insection 212 is engaged with the second insection 431, so that the guide 210 can be connected to the impact switching ring 430, at this time, the impact switching ring 430 can limit the movement of the guide 210, the guide 210 and the impact switching ring 430 are relatively stationary, and the hammer 200 can linearly move along a predetermined path with respect to the guide 210 and strike the tool spindle 30 in at least one operating state. In this embodiment, the axial movement of the impact switch ring 430 is realized by rotating the mode switch 450, in other embodiments, in order to realize the axial movement of the impact switch ring, a toggle button connected to the impact switch ring 430 may be further provided, and the axial movement of the impact switch ring 450 is directly driven by toggling the toggle button to perform the axial movement.

As shown in fig. 20, the first insection 212 includes a convex portion 212 a. The second thread 431 includes a guiding section 431a and a stopping section 431b, the guiding section 431a may include a straight section and an inclined section, one end of the inclined section is connected with a free end of the stopping section 431b, and the other end of the inclined section is connected with one end of the straight section. The stopping section 431b extends along the axial direction of the impact switch ring 430, and the straight section is perpendicular to the stopping section 431 b. The abutting sections 431b may be multiple, the multiple abutting sections 431b may be arranged at intervals along the circumferential direction of the guide 210, a guide section 431a is arranged between any two adjacent abutting sections 431b, and both ends of any one guide section 431a are respectively connected with two adjacent abutting sections 431 b. There may be a plurality of protrusions 212a, and the plurality of protrusions 212a correspond to the plurality of stopping sections 431b one to one. The protrusion 212a may be formed in a triangular shape. The free end of the boss 212a may be formed as a pointed end 212a 1.

When the motor 60 rotates forward, there are two situations, one of which is: the guiding block 451 abuts against the matching block 432, the first insection 212 is spaced apart from the second insection 431, at this time, the guiding element 210 is movable relative to the impact switching ring 430, the guiding element 210 can rotate along with the hammer 200 under the driving of the intermittent impact assembly 230, and the hammer 200 and the guiding element 210 are relatively stationary; another case is: when the guide block 451 is offset from the mating block 432, the protrusion 212a abuts against the abutting section 431b, the first insection 212 and the second insection 431 are relatively stationary, so that the guide 210 and the impact switch ring 430 can be connected, at this time, the impact switch ring 430 can limit the movement of the guide 210, the guide 210 and the impact switch ring 430 are relatively stationary, and the hammer 200 can linearly move along a preset path relative to the guide 210 and strike the tool spindle 30 in at least one operation state. When the motor 60 is reversely rotated, the protrusion 212a may slide along the guide section 431a, relative rotation may be made between the first insection 212 and the second insection 431, the guide 210 may rotate relative to the impact switching ring 430, and the guide 210 may rotate along with the hammer 200.

In the related art, when the first insection 212 is connected to the second insection 431 in a contacting manner, the guide 210 and the impact switching ring 430 are relatively stationary, and when the motor 60 rotates reversely, the conversion member 232 abuts against the falling section 233b, which may hinder the rotation of the motor 60, thereby deteriorating the performance of the guide 210 and the motor 60, and affecting the service life of the hand tool 1. Compare correlation technique, the utility model discloses handheld tool 1 consideration of embodiment is more, has fine security performance.

In contrast to the embodiment shown in fig. 20, in the embodiment shown in fig. 28-30, the hand tool 1 further includes an impact ring 11a fixed to the housing 80 in a non-rotatable manner, the impact ring 11a is provided with a first end tooth 12a, the guide member 210 is provided with a second end tooth 213a capable of meshing with the first end tooth 12a, when the motor 60 rotates in the first direction, the first end tooth 12a limits the rotation of the guide member 213 via the second end tooth 213a meshing therewith, and the conversion member 232 moves in a predetermined direction along the curved guide portion to cause the hammer 200 to strike the tool spindle 30 in at least one operating state; when the motor 60 rotates in the second direction, the second end tooth 213a and the guide member 213 rotate relative to the first end tooth 12a engaged therewith under the driving of the motor 60, that is, the second end tooth 213a of the guide member 213 performs a climbing motion relative to the first end tooth 12 a. The first end tooth 12a comprises a plurality of first teeth 121a, the first teeth 121a comprise a guide section 121b and a stop section 121c, the guide section 121b is connected with the free end of the stop section 121c, the second end tooth 213a comprises a plurality of second teeth 2131a, when the motor 60 rotates along the first direction, the second teeth 2131a move from the stop section 121c to the guide section 121b, and the stop section 121c abuts against the second teeth 2131a, so that the guide member 210 cannot rotate; when the motor 60 rotates in the second direction and the second tooth 2131a moves from the guide segment 121b to the stop segment 121c, the second tooth 2131a can move along the guide segment 121b, so that the guide 213 rotates relative to the first end tooth 12 a. The guide section 121b and the stopping section 121c are sequentially arranged at intervals along the circumferential direction of the first end tooth 12a, and the stopping section 121c is parallel to the axis of the transmission shaft 10. When the second tooth 2131a moves from the stopping section 121c to the guiding section 121b, the side of the second tooth 2131a abutting against the stopping section 121c is parallel to the stopping section 121 c. The impact ring 11a is axially movable to engage or disengage the first end tooth 12a with or from the second end tooth 213a, and when the first end tooth 12a is disengaged from the second end tooth 213a, the guide 210 is rotated by the motor and the tool is in a non-impact mode. It is understood that, in the present embodiment, when the impact ring 11a is axially movable, the impact ring 11a in the present embodiment not only has the function of "anti-rotation blocking", but also has the function of the impact switch ring 430 described in the other embodiments of the present invention.

Referring to fig. 31, the present invention provides another embodiment, in which the hammer 200 is sleeved outside the transmission shaft 10, the clutch 221 is used to selectively rotatably connect the transmission shaft 10 and the hammer 200, the hammer 200 rotates relative to the guide 210 to axially move the hammer 200, and the compression spring, i.e. the energy storage mechanism, stores energy, after the hammer 200 climbs the slope, and rapidly moves toward the free end of the tool spindle 30 along the axis of the tool spindle 30 under the action of the energy storage mechanism, thereby achieving axial impact on the tool spindle 30. During the impact of the hammer 200 against the tool spindle 30, the end face of the hammer 200 facing the free end of the tool spindle 30 has a surface which comes into contact with the tool spindle 30, and this surface is referred to as the "impact surface" of the hammer 200. In this embodiment, the striking surface 2001 on the hammer 200 is outwardly convex with respect to the other surface on the end surface of the hammer 200 on the side facing the free end of the tool spindle 30, that is, on the end surface of the hammer 200 on the side facing the free end of the tool spindle 30, it is a stepped end surface, and the striking surface 2001 which is in striking contact with the tool spindle 30 is higher than the other end surface, that is, the striking surface 2001 is closer to the free end of the tool spindle 30 than the other end surface. The advantage of the impact surface being higher than the other end surfaces is that a higher impact efficiency and a better impact effect can be obtained than if the impact surface were lower than the other end surfaces. The higher impact efficiency and better impact results are mainly reflected in that the loss of impact energy during the impact is reduced. The free end of the tool spindle 30 is here the end of the tool spindle 30 which is closer to the working head, i.e. the end of the tool spindle which is further away from the motor.

In this embodiment, in which the hammer 200 is located on the inner circumferential side of the guide 210 and the curved guide portion 233 is provided between the hammer 200 and the guide 210, the striking surface 2001 on the hammer 200 can be made closer to the axis of the tool spindle 30, and thus higher impact efficiency, i.e., less energy loss during impact, can be obtained, as compared to a case where the hammers are distributed on the outer circumferential side of the guide.

In addition, the diameter range of the striking surface on the hammer can be matched with the diameter of the tool spindle, so that the impact effect can be improved to a certain extent, namely, the energy loss in the striking process can be reduced. In this embodiment, the range of diameters of the striking face 2001 of the hammer 200 may be selected to be in the range of 6-25 mm. The fact that the diameter of the impact surface on the hammer is matched with that of the tool spindle means that the part of the end surface, which is contacted with the impact surface, of the tool spindle during the impact process of the impact surface on the hammer and the tool spindle can be called as an impacted surface, and the diameter of the impact surface on the hammer is consistent with that of the impacted surface on the tool spindle as much as possible, so that the impact surface on the hammer is matched with the impacted surface on the tool spindle.

If the hammer 200 is directly abutted against the driving shaft 10, the hammer 200 may generate barbs on the inner surface due to contact friction during the long-term engagement of the hammer 200 with the clutch 221 to transmit torque during the axial movement of the hammer 200 relative to the driving shaft 10, thereby affecting the axial movement of the hammer 200, particularly reducing the impact energy output from the hammer 200 to the tool spindle 30. In order to solve the above problem, in this embodiment, the following technical solutions are provided: the hammer 200 is linearly supported on the inner circumferential surface of the guide 210, and further, the hammer 200 may be in clearance fit with the drive shaft 10. Specifically, a gap is provided between the inner surface of the hammer 200 and the outer surface of the transmission shaft 10, for example, a single-side gap may be 0.1 mm to 0.2 mm. Of course, the specific value of the small gap is not limited to the above examples, and the present application is not limited thereto.

In the present embodiment, the hammer 200 is linearly supported on the inner circumferential surface of the guide 210, and the guide 210 is fixed to the housing of the hand tool, or the hammer 200 is supported by the housing.

In other embodiments, the hammer may be supported in a linear motion in the housing of the hand tool when the hammer is located outside the guide, i.e., the hammer surrounds the guide, in which embodiment the guide located inside the hammer may be rotated, the hammer moves only in a linear motion and does not rotate, the curved guide may be disposed on the inner circumferential side of the hammer, and the conversion member, i.e., the steel ball, may be disposed on the outer circumferential surface of the guide, such that rotation of the guide drives axial movement of the hammer through the curved guide and the conversion member, thereby causing the hammer to impact the tool spindle under the action of the energy storage mechanism.

The utility model discloses in, the cutter main shaft is as being strikeed the piece, and the quality is lower, and the energy loss of striking in-process is less, but cutter main shaft quality is less, makes the little technical scheme of cutter main shaft quality reduce the diameter of cutter main shaft exactly, has also reduced the volume of cutter main shaft, will influence the intensity of cutter main shaft to a certain extent like this, can keep as high as intensity as possible under the condition of quality in order to make the cutter main shaft in size, the utility model provides a technical scheme. Referring to fig. 31, in the present embodiment, the tool spindle 30 is mainly used for rotatably connecting with the transmission shaft 10, and thus the rotary connection is also the place where the strength is most required. In this embodiment, the connection mode between the tool spindle 30 and the transmission shaft 10 is a hexagonal shape, that is, the tool spindle 30 is an external hexagonal cylinder, the transmission shaft 10 has an internal hexagonal aperture, and the external hexagonal of the tool spindle 30 is matched with the internal hexagonal aperture of the transmission shaft 10 to realize the rotary connection. In the present embodiment, the inner hexagonal aperture of the transmission shaft 10 is disposed on the side close to the free end of the tool spindle 30, and correspondingly, the outer hexagonal cylinder of the tool spindle 30 is disposed on the side close to the free end of the tool spindle corresponding to the inner hexagonal aperture. The advantages of such an arrangement are: the attachment mechanism with the high strength requirement is located near the middle or forward of the tool spindle 30 to reduce the chance of a tool spindle strength failure. Forward in this context means close to the free end of the tool spindle.

It should be noted that the utility model discloses an among the hand-held type instrument, the hand-held type instrument includes drive mechanism, hammer impact mechanism, the cutter main shaft, wherein, drive mechanism includes the transmission shaft of rotatory output behind motor and gear reduction mechanism, the cutter main shaft is by transmission shaft rotary drive, and the cutter main shaft can the rotary drive working head to realize the rotatory operation of hand-held type instrument, moreover, the impact of hammer impact mechanism still need be accepted to the cutter main shaft, and then can transmit the axial impact for the working head. The hammer impact mechanism comprises an impact shaft, the impact shaft can drive one of the hammer and the guide piece to rotate, and the rotation driving of the impact shaft can be directly or indirectly realized by the transmission shaft. The impact shaft can drive one of the hammer and the guide to rotate, and the hammer can rotate relative to the guide under the drive of the impact shaft, so that the hammer and the guide can rotate relative to each other, and the hammer can climb the slope relative to the guide, so that the hammer can impact the tool spindle under the drive of the energy storage mechanism. In various embodiments, the ram may rotate and the guide may not rotate, or the ram may not rotate and the guide may rotate, and in either embodiment, the impact shaft drives the rotating element to move, thereby achieving relative rotation between the two.

The utility model discloses in, the cutter main shaft, the transmission shaft, the jump bit has the function of corresponding ground the utility model discloses in, three axles that have the above-mentioned function that corresponds are indispensable, but, in other embodiments, the cutter main shaft also can act as the jump bit, that is to say, has a axle and has two functions: the working head can be driven to rotate, and the hammer can be driven to rotate relative to the guide piece. In other embodiments, the drive shaft may also act as an impact shaft, that is, the drive shaft can drive both the rotation of the tool spindle and the rotation of either the ram or the guide.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "an illustrative embodiment," "an example," "a specific example," or "some examples" or the like mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

While embodiments of the present invention have been shown and described, it will be understood by those of ordinary skill in the art that: various changes, modifications, substitutions and alterations can be made to the embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A hand tool comprising a motor, a tool spindle, a drive shaft driven in rotation by the motor, and a hammer impact mechanism capable of providing axial impact to the tool spindle;

the hammer impact mechanism comprises a hammer and a guide piece which can rotate relatively, and an energy storage mechanism which is abutted against the hammer, wherein a curved surface guide part is arranged on one of the hammer and the guide piece, a conversion piece is arranged on the other of the hammer and the guide piece, and when the hammer rotates relative to the guide piece, the curved surface guide part drives the hammer to move towards a first direction by overcoming the acting force of the energy storage mechanism through the conversion piece; the energy storage mechanism drives the hammer to move towards a second direction opposite to the first direction so as to impact the tool spindle;

the method is characterized in that: the hammer impact mechanism comprises an impact shaft which can drive one of the hammer and the guide piece to rotate;

the transmission shaft is connected with the impact shaft in a non-rotatable manner.

2. The hand tool of claim 1, wherein: the transmission shaft and the impact shaft are integrally arranged.

3. The hand-held tool of claim 2, wherein: the drive shaft is selectively rotatably coupled to the ram.

4. The hand tool of claim 3, wherein: a first clutch piece is arranged between the transmission shaft and the hammer, the first clutch piece is movably arranged on one of the transmission shaft and the hammer, and a first accommodating part is arranged on the other one of the transmission shaft and the hammer; the first clutch piece is matched with the first accommodating part to realize the rotary connection between the transmission shaft and the hammer, and when the first clutch piece is separated from the first accommodating part, the transmission shaft and the hammer can rotate relatively.

5. The hand tool of claim 1, wherein: the tool spindle and the impact shaft are integrally arranged.

6. The hand tool of claim 5, wherein: the tool spindle is selectively rotatably coupled to the ram.

7. The hand tool of claim 6, wherein: a second clutch piece is arranged between the tool spindle and the hammer, the second clutch piece is movably arranged on one of the tool spindle and the hammer, and a second accommodating part is arranged on the other one of the tool spindle and the hammer; the second clutch piece is matched with the second accommodating part to realize the rotary connection between the tool spindle and the hammer, and when the second clutch piece is separated from the second accommodating part, the tool spindle and the hammer can rotate relatively.

8. The hand tool of claim 1, wherein: the ram surrounds the tool spindle, the drive shaft and the impact shaft in at least one plane.

9. The hand tool of claim 8, wherein: the guide surrounds the ram in at least one plane.

10. The hand tool of claim 1, wherein: the ram is provided with an impact surface facing the tool spindle, the impact surface being contactable with the tool spindle during impact, the impact surface being closer to the axis of rotation of the tool spindle than the curved surface guide.

11. The hand-held tool of claim 10, wherein: the guide is sleeved on the outer side of the hammer, the curved surface guide part is arranged on the inner circumferential surface of the guide, and the conversion part is arranged on the outer circumferential surface of the hammer.

12. The hand-held tool of claim 10, wherein: the ram has an end face facing the tool spindle, the impact face being closer to a free end of the tool spindle than the end face.

13. The hand tool of claim 1, wherein: the curved surface guide part comprises a plurality of climbing sections and falling sections corresponding to the climbing sections, and when the conversion part passes through the climbing sections, the conversion part drives the ram to move towards a first direction by overcoming the acting force of the energy storage mechanism; when the conversion piece passes through the falling section, the energy storage mechanism drives the hammer to move towards a second direction opposite to the first direction so as to impact the tool spindle; the number of the conversion pieces is consistent with that of the climbing sections.

14. The hand tool of claim 1, wherein: the energy storage mechanism is arranged as an elastic piece.

15. A hand tool comprising a motor, a housing the motor, a tool spindle, a drive shaft driven for rotation by the motor, and a hammer impact mechanism capable of providing axial impact to the tool spindle;

the method is characterized in that: the hammer impact mechanism comprises a hammer and a guide piece which can rotate relatively, an impact shaft which is rotationally connected with the transmission shaft and an energy storage mechanism which is abutted against the hammer, wherein a curved surface guide part is arranged on one of the hammer and the guide piece, a conversion piece is arranged on the other of the hammer and the guide piece, one of the hammer and the guide piece is driven by the impact shaft to rotate relative to the other of the hammer and the guide piece, and the curved surface guide part drives the hammer to move towards a first direction along the central axis of the tool spindle by overcoming the acting force of the energy storage mechanism through the conversion piece; the energy storage mechanism drives the hammer to move along the central axis of the tool spindle in a second direction opposite to the first direction so as to impact the tool spindle;

the ram is supported on the housing for linear movement.

16. The hand-held tool of claim 15, wherein: the guide piece is sleeved on the outer side of the hammer, the guide piece is fixedly arranged relative to the shell in an impact mode, the hammer is driven by the impact shaft to rotate relative to the guide piece, and the hammer is supported on the inner circumferential surface of the guide piece in a linear motion mode.

17. The hand-held tool of claim 16, wherein: the curved surface guide portion is provided on an inner periphery of the guide member, and the conversion member is provided on an outer peripheral surface of the hammer.

18. The hand-held tool of claim 15, wherein: the transmission shaft and the impact shaft are integrally arranged.