Handheld tool

Abstract

The present invention discloses a hand-held tool. The hand-held tool includes a motor, a transmission shaft, a hammer impact mechanism, and a tool spindle. The transmission shaft is driven by the motor to rotate and rotate about the axis of the transmission shaft. The hammer impact mechanism has a ram, and the ram is sleeved outside the transmission shaft and can be driven by the transmission shaft to rotate. The tool spindle is connected to the transmission shaft, and the tool spindle is movable relative to the transmission shaft. The hammer impact mechanism further includes a guide member and an intermittent impact assembly disposed outside the ram. When the ram rotates, the intermittent impact assembly drives the ram to linearly move relative to the guide member along a preset path and impacts the tool spindle in at least one operating state. According to the hand-held tool of the present invention, by using the cooperation relationship between the clearance impact assembly, the ram, and the guide member, the ram can be guided to linearly move, and the ram can also impact the tool spindle, so that the movement in the axial direction of the tool spindle can be achieved, and the structure of the hand-held tool is compact and simple, which is convenient to carry.

Description

Technical Field

[0001] The present invention relates to the technical field of impact drilling, and more particularly, to a handheld tool. Background Art

[0002] In the technical field of impact drilling, a rotary impact mechanism is driven by an electric motor as a driving source to provide rotation and impact to a gun drill, so as to intermittently transmit a rotary impact force to a tip tool to perform operations such as tightening a screw. In the related art, an active impact structure is installed on an ordinary gun drill to form an impact drill mode, which usually causes the overall length of the gun drill to be too large and the structure to be complex. Summary of the Invention

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention provides a handheld tool, which has the advantages of simple structure and high working efficiency.

[0004] The present invention provides a technical solution: a handheld tool, including a motor, a tool spindle, a transmission shaft driven by the motor to rotate, and a hammer impact mechanism capable of providing axial impact to the tool spindle; the hammer impact mechanism includes a ram and a guide member that can rotate relative to each other, and an energy storage mechanism in contact with the ram, wherein a curved surface guiding portion is provided on one of the ram and the guide member, and a conversion member is provided on the other of the ram and the guide member. When the ram rotates relative to the guide member, the curved surface guiding portion drives the ram to move in a first direction against the acting force of the energy storage mechanism through the conversion member; the energy storage mechanism drives the ram to move in a second direction opposite to the first direction so as to impact the tool spindle; the hammer impact mechanism includes an impact shaft, and the impact shaft can drive one of the ram and the guide member to rotate; the transmission shaft is non-rotatably connected to the impact shaft.

[0005] Preferably, the transmission shaft and the impact shaft are integrally provided.

[0006] Preferably, the transmission shaft is selectively rotatably connected to the ram.

[0007] Preferably, a first clutch member is provided between the transmission shaft and the ram, the first clutch member is movably provided on one of the transmission shaft and the ram, and a first receiving portion is provided on the other of the transmission shaft and the ram; the cooperation between the first clutch member and the first receiving portion can realize the rotational connection between the transmission shaft and the ram, and when the first clutch member is separated from the first receiving portion, the transmission shaft and the ram can rotate relative to each other.

[0008] Preferably, the tool spindle and the impact shaft are integrally provided.

[0009] Preferably, the tool spindle is selectively rotatably connected to the ram.

[0010] Preferably, a second clutch member is provided between the tool spindle and the ram. The second clutch member is movably disposed on one of the tool spindle and the ram, and a second receiving portion is provided on the other of the tool spindle and the ram. The cooperation between the second clutch member and the second receiving portion can achieve the rotational connection between the tool spindle and the ram. When the second clutch member is separated from the second receiving portion, the tool spindle and the ram can rotate relative to each other.

[0011] Preferably, the ram surrounds the tool spindle, the transmission shaft, and the impact shaft on at least one plane.

[0012] Preferably, the guide member surrounds the ram on at least one plane.

[0013] Preferably, the ram is provided with an impact surface facing the tool spindle. The impact surface can contact the tool spindle during the impact process, and the impact surface is closer to the rotation axis of the tool spindle than the curved surface guiding portion.

[0014] Preferably, the guide member is sleeved on the outer side of the ram, the curved surface guiding portion is provided on the inner circumferential surface of the guide member, and the conversion member is provided on the outer circumferential surface of the ram.

[0015] Preferably, the ram has an end face facing the tool spindle, and the impact surface is closer to the free end of the tool spindle than the end face.

[0016] Preferably, the curved surface guiding portion includes a plurality of climbing segments and corresponding dropping segments. When the conversion member passes through the climbing segments, the conversion member drives the ram to move in a first direction against the acting force of the energy storage mechanism. When the conversion member passes through the dropping segments, the energy storage mechanism drives the ram to move in a second direction opposite to the first direction so as to impact the tool spindle. The number of the conversion members is the same as the number of the climbing segments.

[0017] Preferably, the energy storage mechanism is arranged as an elastic member.

[0018] The present invention also provides another technical solution: a handheld tool, comprising a motor, a housing for accommodating the motor, a tool spindle, a transmission shaft driven to rotate by the motor, and a hammer impact mechanism capable of providing an axial impact to the tool spindle; the hammer impact mechanism comprises a relatively rotatable hammer and a guide member, an impact shaft rotationally connected to the transmission shaft, and an energy storage mechanism abutting against the hammer, one of the hammer and the guide member is provided with a curved guide portion, and the other of the hammer and the guide member is provided with a conversion member, in an impact mode, one of the hammer and the guide member is driven by the impact shaft to rotate relative to the other, the curved guide portion drives the hammer through the conversion member to overcome the force of the energy storage mechanism and move in a first direction along the central axis of the tool spindle; the energy storage mechanism drives the hammer to move in a second direction opposite to the first direction along the central axis of the tool spindle to impact the tool spindle; the hammer is supported on the housing for linear motion.

[0019] Preferably, the guide member is sleeved on the outside of the hammer. In the impact mode, the guide member is fixed relative to the shell. The hammer is driven by the impact shaft to rotate relative to the guide member. The hammer is supported on the inner circumference of the guide member for linear motion.

[0020] Preferably, the curved guide portion is arranged on the inner circumference of the guide member, and the adapter is arranged on the outer circumference of the hammer.

[0021] Preferably, the transmission shaft and the impact shaft are integrally arranged.

[0022] Additional aspects and advantages of the technical solution in the present invention will be partially given in the following description, and partially will become apparent from the following description, or will be understood through the practice of the present invention.

[0023] The present invention also provides another technical solution: a hand-held tool, comprising: a housing; a motor; a transmission shaft, driven by the motor and rotating around the axis of the transmission shaft; a tool spindle, the tool spindle is used to connect a tool head, and the tool spindle can be driven to rotate by the transmission shaft; a hammer impact mechanism, the hammer impact mechanism has a hammer, the hammer is sleeved on the outside of at least one of the transmission shaft and the tool spindle and can be driven to rotate by the transmission shaft; the hammer impact mechanism also includes a guide member sleeved on the outside of the hammer, the tool spindle can be moved from a first position to a second position by an axial force, when the tool spindle is in the second position, the hammer can be driven to rotate by the transmission shaft and can move relative to the guide member according to a preset path, thereby striking the tool spindle along the axis of the tool spindle in at least one operating state, when the tool spindle is in the first position, the transmission shaft cannot drive the hammer to rotate.

[0024] Preferably, the tool spindle includes a connection end connected to the transmission shaft and an output end connected to the tool head. When the direction of the axial force borne by the tool spindle is from the output end to the connection end, the tool spindle can switch to the first position mating with the transmission shaft.

[0025] Preferably, the tool spindle includes a connection end connected to the transmission shaft and an output end connected to the tool head. When the direction of the axial force borne by the tool spindle is from the connection end to the output end, the tool spindle switches to the second position mating with the transmission shaft.

[0026] Preferably, the hand-held tool further includes a mode adjustment mechanism, which can be operably switched between a first mode state and a second mode state. When in the first mode state, the tool spindle can switch between the first position and the second position state relative to the transmission shaft; when in the second mode state, the tool spindle axially abuts against the mode adjustment mechanism to limit the tool spindle from switching from the second position to the first position.

[0027] Preferably, the hand-held tool further includes a mode adjustment mechanism, which can be operably switched between a first mode state and a second mode state. When in the first mode state, the guide member is fixed to the housing, and when the ram rotates, it can move along the guide member along a preset path to strike the tool spindle; when in the second mode state, the guide member is rotatably arranged on the housing, and the ram has no impact on the tool spindle.

[0028] Preferably, one end of the transmission shaft connected to the connection end is a transmission end, and one of the connection end and the transmission end is provided with an axial hole, and the other end extends into the axial hole.

[0029] Preferably, splines are provided between the inner wall of the axial hole and the outer wall of the other end to achieve an axially movable but non-rotatable relative connection between the transmission shaft and the tool spindle.

[0030] Preferably, the splines at the other end form a radial groove, and a radial hole is provided on the outer wall of the axial hole. The hand-held tool further includes a steel ball for connecting the transmission shaft and the ram. The radial hole corresponds to the radial groove in position. The steel ball moves into the radial groove along the radial hole and disengages from the ram; when the tool spindle moves relative to the transmission shaft to the first position, the radial hole and the radial groove are out of alignment in position, and the steel ball moves in the reverse direction of the radial hole and connects with the ram.

[0031] Preferably, the hammer impact mechanism further includes an intermittent impact assembly; when the drive shaft drives the ram to rotate, the intermittent impact assembly forces the ram to linearly move relative to the guide member along a preset path and strike the tool spindle in at least one operating state.

[0032] Preferably, the intermittent impact assembly includes an energy storage mechanism abutting against the ram, and a conversion member and a curved surface guiding portion disposed between the guide member and the ram.

[0033] Preferably, the conversion member is located on one of the guide member and the ram, and the curved surface guiding portion is located on the other of the guide member and the ram.

[0034] Preferably, the conversion member is arranged as a steel ball, and the curved surface guiding portion is arranged as a cam surface or a cam groove.

[0035] Preferably, the energy storage mechanism is arranged as an elastic member.

[0036] In the present invention, additional aspects and advantages of this technical solution will be partly given in the following description, partly will become obvious from the following description, or will be understood through the practice of the present invention.

[0037] The present invention also provides another technical solution: a hand-held tool, including: a motor, the rotation direction of the motor includes a first direction and a second direction opposite to the first direction; a drive shaft driven to rotate by the motor; a tool spindle for connecting a tool head, the tool spindle is movably connected to the drive shaft; a hammer impact mechanism having a ram sleeved outside the drive shaft or the tool spindle and capable of being driven to rotate by the drive shaft, the hammer impact mechanism further includes a guide member disposed outside the ram; the hammer impact mechanism further includes an intermittent impact assembly located between the ram and the guide member, the intermittent impact assembly includes a curved surface guiding portion located on one of the outer wall of the ram or the inner wall of the guide member, and a conversion member located on the other of them, the hand-held tool further includes an impact ring fixedly and non-rotatably disposed on the housing, the impact ring is provided with first end teeth, and the guide member is provided with second end teeth capable of meshing with the first end teeth. When the motor rotates in the first direction, the first end teeth limit the rotation of the guide member through the second end teeth meshing with them, and the conversion member moves along the curved surface guiding portion in a preset direction to make the ram strike the tool spindle in at least one operating state; when the motor rotates in the second direction, the second end teeth and the guide member rotate relative to the first end teeth meshing with them under the drive of the motor.

[0038] Preferably, the first end teeth include a plurality of first teeth, each first tooth including a guiding section and a stopping section, the guiding section being connected to the free end of the stopping section. The second end teeth are composed of a plurality of second teeth. When the motor rotates in the first direction, the second teeth move from the stopping section to the guiding section, and the stopping section abuts against the second teeth, so that the guiding member cannot rotate. When the motor rotates in the second direction, when the second teeth move from the guiding section to the stopping section, the second teeth can move along the guiding section, so that the guiding member rotates relative to the first end teeth.

[0039] Preferably, the guiding section and the stopping section are arranged at intervals in sequence along the circumferential direction of the first end teeth, and the stopping section is parallel to the axis of the transmission shaft.

[0040] Preferably, when the second teeth move from the stopping section to the guiding section, the side of the second teeth abutting against the stopping section is parallel to the stopping section.

[0041] Preferably, the impact ring can move axially to realize the engagement or separation of the first end teeth and the second end teeth. When the first end teeth and the second end teeth are separated, the guiding member rotates under the drive of the motor, and the hand tool is in a non-impact mode.

[0042] Preferably, the hammer impact mechanism has a disengaging clutch mechanism, and the clutch mechanism is configured to transmit rotational motion.

[0043] Preferably, the clutch mechanism is configured to be closed by a force transmitted through the tool spindle.

[0044] Preferably, the clutch mechanism is located between the transmission shaft and the ram, and includes a clutch member provided on one of the transmission shaft and the ram, and a receiving portion provided on the other of the transmission shaft and the ram. When the mode adjustment mechanism is in the first position, the clutch member engages with the receiving portion. When the mode adjustment mechanism is in the second position, the clutch member is separated from the receiving portion.

[0045] Preferably, the clutch member is provided in a spherical or columnar shape, and the receiving portion is provided in a groove shape. In the present invention, additional aspects and advantages of this technical solution will be partially given in the following description, partially become obvious from the following description, or be understood through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0046] The above and / or additional aspects and advantages of the present invention will become obvious and easy to understand from the description of the embodiments in conjunction with the following drawings, in which:

[0047] Figure 1 It is a schematic structural diagram of a hand-held tool according to an embodiment of the present invention;

[0048] Figure 2 It is an exploded view of a partial structure of a hand-held tool according to an embodiment of the present invention;

[0049] Figure 3 It is a schematic structural diagram of a mode adjustment mechanism of a hand-held tool according to an embodiment of the present invention;

[0050] Figure 4 It is a schematic structural diagram of a mode adjustment mechanism of a hand-held tool according to an embodiment of the present invention;

[0051] Figure 5 It is a schematic diagram of a partial cross-sectional structure of a hand-held tool according to an embodiment of the present invention;

[0052] Figure 6 It is Figure 5 An enlarged view of the structure at position A in

[0053] Figure 7 It is Figure 5 An enlarged view of the structure at position B in

[0054] Figure 8 It is Figure 5 An enlarged view of the structure at position C in

[0055] Fig. 9 It is a schematic diagram of a partial cross-sectional structure of a hand-held tool according to an embodiment of the present invention;

[0056] Fig.10 It is Fig. 9 An enlarged view of the structure at position D in

[0057] Fig.11 It is a schematic structural diagram of a guide member of a hand-held tool according to an embodiment of the present invention;

[0058] Fig.12 It is a cross-sectional structural diagram of a guide member of a hand-held tool according to an embodiment of the present invention;

[0059] Fig.13 It is a schematic diagram of a partial cross-sectional structure of a hand-held tool according to an embodiment of the present invention;

[0060] Fig.14 It is Fig.13 An enlarged view of the structure at position E in

[0061] Fig.15 It is Fig.13 An enlarged view of the structure at position F in

[0062] Fig.16 It is an exploded view of a partial structure of a hand-held tool according to an embodiment of the present invention;

[0063] Fig.17 Partial cross-sectional structure diagram of a hand-held tool according to an embodiment of the present invention;

[0064] Fig.18 Partial cross-sectional structure diagram of a hand-held tool according to an embodiment of the present invention;

[0065] Fig.19 Exploded view of the partial structure of a hand-held tool according to an embodiment of the present invention;

[0066] Fig. 20 Partial structure diagram of a hand-held tool according to an embodiment of the present invention;

[0067] Fig.21 Cross-sectional structure diagram of a hand-held tool according to an embodiment of the present invention;

[0068] Fig. 22 is Fig.21 Enlarged view of the structure at G in;

[0069] Fig.23 Cross-sectional structure diagram of a hand-held tool according to an embodiment of the present invention;

[0070] Fig.24 is Fig.23 Enlarged view of the structure at H in;

[0071] Fig.25 Partial cross-sectional structure diagram of a hand-held tool according to an embodiment of the present invention;

[0072] Fig.26 Partial cross-sectional structure diagram of a hand-held tool according to an embodiment of the present invention;

[0073] Fig. 27 Cross-sectional structure diagram of a hand-held tool according to an embodiment of the present invention;

[0074] Fig.28 Partial structure diagram of a hand-held tool according to an embodiment of the present invention;

[0075] Fig.29 Partial structure diagram of a hand-held tool according to an embodiment of the present invention;

[0076] Fig.30 Partial structure diagram of a hand-held tool according to an embodiment of the present invention.

[0077] Fig.31 Partial cross-sectional view of a hand-held tool according to an embodiment of the present invention.

[0078] Reference numerals:

[0079] Hand-held tool 1,

[0080] Drive shaft 10, baffle 100, through hole 110, cavity 120, drive end 130, flat square 140,

[0081] Hammer impact mechanism 20, ram 200, receiving portion 201, groove body 201a, embedding groove 202, mounting groove 203,

[0082] Guide member 210, receiving groove 211, first tooth pattern 212, protruding portion 212a, tip 212a1, impact surface 2001,

[0083] Clutch mechanism 220, clutch member 221,

[0084] Intermittent impact assembly 230, energy storage mechanism 231, conversion member 232, curved surface guiding portion 233,

[0085] Climbing section 233a, falling section 233b,

[0086] Tool spindle 30, external thread 300, first section 310, second section 320, third section 330, rib 340, groove 350, axial

[0087] Hole 360, spline 370, connection end 380, output end 390,

[0088] Mode adjustment mechanism 40, impact receiving portion 400, first surface 401, second surface 402, third surface 403, step surface 404,

[0089] Pressure retaining ring 410, abutting portion 411, fixed section 411a, connection section 411b, mating section 411c,

[0090] Mode adjustment knob 420, flange 421, channel 422,

[0091] Impact switching ring 430, second tooth pattern 431, guiding section 431a, abutting section 431b, mating block 432, buffer member 440,

[0092] Mode switching knob 450, guiding block 451, guiding inclined surface 451a,

[0093] Chuck 50, threaded hole 500, motor 60, reset member 70, housing 80, reverse screw 90,

[0094] Impact ring 11a, first end tooth 12a, first tooth 121a, guiding section 121b, stopping section 121c, second end tooth 213a, second tooth 2131a. Detailed implementation manner

[0095] Embodiments of the present invention will be described in detail below. Examples of the embodiments are shown in the accompanying drawings, where like or similar reference numerals denote like or similar elements or elements having like or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary only for explaining the present invention and should not be construed as limiting the present invention.

[0096] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings. They are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present invention. In addition, features defined as "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present invention, unless otherwise stated, the meaning of "plurality" is two or more.

[0097] In the description of the present invention, it should be noted that, unless otherwise clearly defined and limited, the terms "mounted", "connected", and "coupled" should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or an integral connection; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the communication inside two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0098] Embodiment 1

[0099] As Figure 1-Figure 26 shown, a hand tool 1 according to an embodiment of the present invention includes a motor 60, a drive shaft 10, a hammer impact mechanism 20, and a tool spindle 30.

[0100] Specifically, as Figure 2 , Figure 5 , Fig. 9 , Fig.13 , Figure 17-Figure 18 , Fig.21 , Fig.23 and Figure 25-26As shown, the motor 60 can drive the transmission shaft 10 to rotate, and the transmission shaft 10 can rotate about the axis of the transmission shaft 10. The hammer impact mechanism 20 includes a ram 200. The ram 200 is sleeved outside the transmission shaft 10, and the ram 200 can be driven to rotate by the transmission shaft 10. It can be understood that the motor 60 is connected to the transmission shaft 10. The "connection" mentioned here can mean that the motor 60 is directly connected to the transmission shaft 10. For example, the output end of the motor 60 can be directly connected to the end of the transmission shaft 10. The "connection" can also mean that the motor 60 is indirectly connected to the transmission shaft 10. For example, the motor 60 can be directly connected to an intermediate transmission component and then directly connected to the transmission shaft 10 through the intermediate transmission component.

[0101] The motor 60 can drive the transmission shaft 10 to rotate, that is, the motor 60 can drive the transmission shaft 10 to rotate about its central axis. The ram 200 can be sleeved outside the outer wall of the transmission shaft 10. The ram 200 can be connected to the transmission shaft 10 in a cooperative manner. The transmission shaft 10 can further drive the ram 200 to rotate about the axis of the transmission shaft 10. It should be noted that the "connection" mentioned here can mean that the ram 200 is directly connected to the transmission shaft 10 or that the ram 200 is indirectly connected to the transmission shaft 10. As Figure 5-Figure 9 shown, the hand tool 1 further includes a tool spindle 30. One end of the tool spindle 30 is connected to the transmission shaft 10, and the other end is used to connect to a tool head. And the tool spindle 30 is movable relative to the transmission shaft 10. The tool spindle 30 is movably connected to the transmission shaft 10. For example, the tool spindle 30 can move along the axis direction of the transmission shaft 10 relative to the transmission shaft 10 and is connected in a non-rotatable manner relative to each other, that is, the tool spindle 30 is driven to rotate by the transmission shaft 10. It should be noted that, as Fig. 27 shown, the ram 200 in this embodiment can also be sleeved outside the tool spindle 30 or a part of it is sleeved outside the tool spindle 30 and a part of it is sleeved outside the transmission shaft 10.

[0102] As Figure 2 、 Figure 5-Figure 13As shown, the hammer impact mechanism 20 further includes a guide member 210 disposed outside the ram 200 and an intermittent impact assembly 230. When the ram 200 rotates, the intermittent impact assembly 230 guides the ram 200 to move linearly relative to the guide member 210 along a preset path and strike the tool spindle 30 in at least one operating state. In other words, the hammer impact mechanism 20 includes a ram 200, a guide member 210, and an intermittent impact assembly 230. The guide member 210 is sleeved on the outer peripheral wall of the ram 200. Preferably, in order to enable the ram 200 to generate the required hammering force when striking the tool spindle 30, the weight of the ram 200 is greater than or equal to 10% of the sum of the weights of the chuck 50 and the tool spindle 30. In order to prevent the tool from being too heavy and to make the overall structure of the machine compact, preferably, the weight of the ram 200 is less than or equal to 60% of the sum of the weights of the chuck 50 and the tool spindle 30. More preferably, the weight of the ram 200 is less than or equal to 35% of the sum of the weights of the chuck 50 and the tool spindle 30.

[0103] As Figure 25-26 shown, the tool spindle 30 is fixedly connected to the chuck 50 by means of a threaded connection. Specifically, in this embodiment, an external thread 300 is provided at one end of the tool spindle 30 close to the chuck 50, and a threaded hole 500 mating with the external thread 300 is provided inside the chuck 50. The tool spindle 30 and the chuck 50 are connected by the external thread 300 and the threaded hole 500. It should be noted that the motor 60 drives the tool spindle 30 to rotate both in the first direction (forward) and in the second direction (reverse) opposite to the first direction. In order to prevent the threaded connection between the tool spindle 30 and the chuck 50 from coming loose during operation, a reverse screw 90 is further provided between the chuck 50 and the tool spindle 30. Here, the "reverse screw 90" means that the thread direction on the screw is opposite to the thread direction of the above-mentioned external thread 300. In this connection method, since the hammering force of the ram 200 on the tool head 20 needs to be transmitted to the tool head via the reverse screw 90, that is, the ram 200 transmits the hammering force to the tool spindle 30, then through the tool spindle 30 to the reverse screw 90, and finally through the reverse screw 90 to transmit the hammering force to the tool head. Therefore, the hammering force transmitted to the tool head by the ram 200 is greatly lost.

[0104] Therefore, the present invention also provides another connection method between the tool spindle 30 and the chuck 50. Refer to Fig.21 , compared with the above connection method between the tool spindle 30 and the chuck 50, the reverse screw 90 is cancelled in this connection method. An adhesive is applied between the external thread 300 and the threaded hole 500 to prevent the tool spindle 30 and the tool head from coming loose during operation. At the same time, a protruding portion (not marked in the figure) is provided at the front of the tool spindle 30 for abutting against the tool head, so that the impact can be directly transmitted from the tool spindle 30 to the tool head, reducing the energy loss during impact.

[0105] When the ram 200 rotates, the intermittent impact assembly 230 can control the movement path of the ram 200, and the movement path can enable the ram 200 to rotate circumferentially around the transmission shaft 10 and also enable the ram 200 to move along the axial direction of the transmission shaft 10, so that the ram 200 can strike the tool spindle 30, thereby completing the movement of the tool spindle 30 relative to the transmission shaft 10.

[0106] For the hand tool 1 according to the embodiment of the present invention, by providing the guide member 210 and the intermittent impact assembly 230, and utilizing the cooperation relationship among the intermittent impact assembly 230, the ram 200 and the guide member 210, the ram 200 can be guided to perform a linear motion, and the ram 200 can also strike the tool spindle 30, so that the movement in the axial direction of the tool spindle 30 can be realized. When the tool spindle 30 drills holes in environmental components (such as walls or panels), the tool spindle 30 forms an impact force on the environmental components, thereby improving the drilling efficiency of the hand tool 1. Moreover, the structure of the hand tool 1 according to the embodiment of the present invention is compact and simple in structure, and can be conveniently carried.

[0107] As Figure 2 、 Figure 5 、 Figure 7 and Figure 9-12 shown, according to some embodiments of the present invention, the intermittent impact assembly 230 includes an energy storage mechanism 231 in contact with the ram 200, and a conversion member 232 and a curved surface guiding portion 233 disposed between the guide member 210 and the ram 200. The intermittent impact assembly 230 further includes the energy storage mechanism 231. Both the conversion member 232 and the curved surface guiding portion 233 are located between the guide member 210 and the ram 200, and one end of the energy storage mechanism 231 is in contact with the ram 200. Thus, by constructing the specific shape of the curved surface guiding portion 233, the movement trajectory of the conversion member 232 can be guided, and the conversion member 232 can be linked with the ram 200, and the ram 200 moves along the trajectory of the curved surface guiding portion 233 under the action of the conversion member 232.

[0108] Further, as Fig.13 and Figure 17-Figure 18 shown, a baffle 100 can be provided on the transmission shaft 10. The baffle 100 is sleeved on the outer peripheral wall of the transmission shaft 10. The energy storage mechanism 231 is located between the ram 200 and the baffle 100, and the end of the energy storage mechanism 231 away from the ram 200 can cooperate with the baffle 100. When the ram 200 moves a certain distance towards the energy storage mechanism 231, the ram 200 and the baffle 100 can compress the energy storage mechanism 231. Thus, the energy storage mechanism 231 can form a driving force on the ram 200. Of course, other structures can also be adopted for the axial limiting manner of the energy storage mechanism 231, which will not be elaborated here.

[0109] The axial limiting member of the energy storage mechanism 231 is a baffle 100 in this embodiment. In the present invention, the baffle 100 and the transmission shaft 10 are designed to be fixedly connected, preferably by interference fit, which can prevent the phenomenon that the tool spindle moves back and forth along the axial direction during non-impact mode, improving the service life of the mechanism and the user's operation experience.

[0110] Regarding the phenomenon of axial movement of the tool spindle mentioned here, through research and analysis, the root cause of this phenomenon has been found. Based on this root cause, the above technical solution is proposed in the present invention, that is, the baffle 100 and the transmission shaft 10 are fixedly connected. Next, the root cause of the axial movement of the tool spindle and the basic principle of how the above technical solution can solve this problem will be specifically described.

[0111] The phenomenon of axial movement of the tool spindle mentioned here refers to the phenomenon that the tool spindle moves back and forth along the axial direction when the tool is operating in non-impact mode. Through research and analysis, it is found that the axial movement of the tool spindle is caused by the clutch member 221 that selectively connects the ram 200 and the transmission shaft 10 moving back and forth in the radial direction in and out of the receiving portion 201. Specifically, since there is a clearance fit between the baffle 100 and the transmission shaft 10, when the transmission shaft 10 rotates, the baffle 10, the spring, that is, the energy storage mechanism 231, and the ram 200 do not rotate in the rotational direction. That is to say, in non-impact mode, when the transmission shaft 10 drives the tool spindle 30 to rotate, the ram 200 remains stationary in the rotational direction. During the non-impact mode movement, the operator slightly presses down on the tool spindle 30, causing the tool spindle 30 to move backward a little distance along the axial direction, and then causing the clutch member 221 to be partially extruded radially. When the rotating transmission shaft 10 drives the clutch member 221 to continue rotating, when the rotating clutch member 221 hits the inner wall of the stationary ram 200 during the extrusion process, it will be rebounded by the acting force, that is, the clutch member 221 will be pushed back radially again. Then the tool spindle 30 will continue to squeeze out the clutch member 221 due to the slight axial downward pressure and then be pushed back, and this back-and-forth repetition will cause the clutch member 221 to move back and forth in the radial direction, thereby causing the tool spindle 30 to move back and forth axially.

[0112] To solve the above problems, in the present invention, the baffle 100 and the transmission shaft 10 are designed to be fixedly connected. When the tool operates in a non-impact mode, when the transmission shaft 10 drives the tool spindle 30 to rotate, the transmission shaft 10 will also drive the baffle 100 to rotate, which will further cause the spring, that is, the energy storage mechanism 231, and the ram 200 to rotate. As a result, the tool spindle 30 and the ram 200 rotate together at the same speed without a relative speed difference. In this way, the tool spindle 30 is subjected to a slight axial downward pressure, squeezing the clutch member 221 radially outwards. When the clutch member 221 touches the inner wall of the ram 200, it will not be subjected to a force and will not bounce back, thus solving the problem of the clutch member 221 moving back and forth radially, and further solving the problem of the tool spindle 30 moving back and forth along the axial direction. Guide member

[0113] As Figure 11-Figure 12 shown, in some embodiments of the present invention, the curved surface guiding portion 233 can be formed in a ring shape. The curved surface guiding portion 233 can surround the transmission shaft 10 in the circumferential direction. Specifically, the curved surface guiding portion 233 can include a climbing section 233a and a dropping section 233b. One end of the dropping section 233b is connected to one end of the climbing section 233a, and the other end of the dropping section 233b extends towards the other end of the climbing section 233a. Further, the climbing section 233a can be in a spiral shape, and the dropping section 233b can be in a straight line shape, and the dropping section 233b extends along the axis direction of the transmission shaft 10. Preferably, in order to ensure that the ram 200 forms sufficient impact force on the tool spindle 30 and the volume of the hand-held tool 1 is compact, the climbing height of the climbing section 233a in the axial direction is greater than 3 mm and less than or equal to 15 mm. Preferably, the climbing height is greater than or equal to 4 mm and less than or equal to 8 mm. Preferably, the climbing height is 5 mm. It should be noted that the "climbing height" refers to the axial distance between the two ends of the climbing section 233a in the axis direction of the transmission shaft 10.

[0114] When the conversion member 232 cooperates with the climbing section 233a, the conversion member 232 rolls from one end of the climbing section 233a towards the other end of the climbing section 233a, and the ram 200 moves towards the baffle 100. The ram 200 and the baffle 100 can compress the energy storage mechanism 231; when the conversion member 232 is at the other end of the climbing section 233a and rolls towards the dropping section 233b, the energy storage mechanism 231 can push the ram 200 to drop from the end of the dropping section 233b close to the baffle 100 towards the end of the dropping section 233b close to the tool head, that is, the ram 200 drops rapidly towards the direction away from the baffle 100 and close to the tool head. A part of the ram 200 approaches and impacts the part 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 axis direction of the transmission shaft 10, and the ram 200 forms a hammering on the tool spindle 30 and the tool head.

[0115] Furthermore, as Figure 7 and Fig.15 shown, an installation groove 203 may be provided on the end face of the ram 200 close to the energy storage mechanism 231. The end of the energy storage mechanism 231 may be located within the installation groove 203, and the end of the energy storage mechanism 231 may abut against the bottom wall of the installation groove 203. Thereby, the assembly stability between the energy storage mechanism 231 and the ram 200 can be improved.

[0116] As Fig.12 shown, in some embodiments of the present invention, the curved surface guiding portion 233 may include multiple segments, and each segment includes a climbing section 233a and a falling section 233b. There may be multiple conversion members 232, and the multiple conversion members 232 may be spaced apart along the circumferential direction of the ram 200. In this embodiment, in order to ensure the rationality of the overall design of the hand tool 1, the outer diameter of the ram 200 is between 15 mm and 50 mm. Preferably, the outer diameter of the ram 200 is between 20 mm and 40 mm, the climbing height is greater than 3 mm and less than or equal to 15 mm. Preferably, the climbing height is greater than or equal to 4 mm and less than or equal to 8 mm. More preferably, the climbing height is 5 mm. It can be understood that, in order to ensure that the conversion member 232 can climb smoothly, preferably, the number of segments is 2 to 7, and particularly preferably, the number of segments is 3 - 4. In this embodiment, the number of segments of the climbing section 233a is preferably 3.

[0117] It should be noted that, as can be seen from the above introduction, the conversion member 232 and the curved surface guiding portion 233 are located between the ram 200 and the guiding member 210. Specifically, the conversion member 232 is located at one of the guiding member 210 and the ram 200, and the curved surface guiding portion 233 is located at the other of the guiding member 210 and the ram 200. As Figure 16-18 shown, in some other examples of the present invention, the conversion member 232 may be located on the guiding member 210, and the curved surface guiding portion 233 is located on the ram 200. For example, a receiving groove 211 is provided on the inner peripheral wall of the guiding member 210. A part of the conversion member 232 may be located within the receiving groove 211, and a curved surface guiding portion 233 may be provided on the outer peripheral wall of the ram 200. Another part of the conversion member 232 may cooperate with the curved surface guiding portion 233. As Figure 16-18As shown, in some other examples of the present invention, the conversion member 232 can be located on the guide member 210, and the curved surface guiding portion 233 is located on the ram 200. For example, a receiving groove 211 is provided on the inner peripheral wall of the guide member 210, a part of the conversion member 232 can be located in the receiving groove 211, a curved surface guiding portion 233 can be provided on the outer peripheral wall of the ram 200, and another part of the conversion member 232 can cooperate with the curved surface guiding portion 233. Thus, the assembly relationship between the conversion member 232, the curved surface guiding portion 233 and the ram 200, the guide member 210 can be realized. Therefore, by using the cooperation relationship between the conversion member 232 and the curved surface guiding portion 233 and the relative movement between the conversion member 232 and the curved surface guiding portion 233, the relative movement of the ram 200 relative to the guide member 210 can be realized, and the ram 200 can move relative to the transmission shaft 10 along the axis direction of the transmission shaft 10. The movement locus of the conversion member 232 on the curved surface guiding portion 233 is the preset path of the ram 200.

[0118] As Figure 2 , Fig.16 and Fig.19 shown, in some embodiments of the present invention, the conversion member 232 can be set as a steel ball, as Figure 11-Figure 12 shown. Preferably, in order to ensure the strength of the steel ball, the diameter of the steel ball is greater than 4 mm and less than or equal to 10 mm. More preferably, the diameter of the steel ball is greater than or equal to 4 mm and less than or equal to 6 mm. In this embodiment, the diameter of the steel ball is 5 mm. The curved surface guiding portion 233 can be set as a cam surface or a cam groove. Thus, the cam surface or the cam groove can define the movement locus of the steel ball, and the steel ball can move inside the cam surface or the cam groove. The steel ball has a smooth outer surface, which can not only reduce the relative movement friction between the conversion member 232 and the curved surface guiding portion 233, improve the movement smoothness of the conversion member 232 inside the curved surface guiding portion 233, but also the steel ball has high structural strength and good wear resistance, so as to ensure the working performance of the intermittent impact assembly 230. It should be noted that the "cam" mentioned here can refer to that the curved surface guiding portion 233 protrudes from the inner peripheral wall of the guide member 210, or the curved surface guiding portion 233 protrudes from the outer peripheral wall of the ram 200.

[0119] Furthermore, the steel ball and the curved surface guiding portion 233 can be in point or line contact. It can be understood that during the movement of the steel ball inside the curved surface guiding portion 233, the contact between the steel ball and the curved surface guiding portion 233 is always a point or a line contact, which is beneficial to reducing the friction between the steel ball and the curved surface guiding portion 233. For example, the curvature radius of the cam surface can be basically the same as or slightly larger than the radius of the steel ball, so as to improve the cooperation degree between the steel ball and the cam surface, and further improve the assembly stability, wear resistance and service life of the steel ball and the cam surface.

[0120] As Figure 2 , Fig.16 and Fig.19 As shown, in some embodiments of the present invention, the energy storage mechanism 231 may be arranged as an elastic member. For example, the energy storage mechanism 231 may be a spring or an elastic rubber member. Thereby, the arrangement and assembly of the energy storage mechanism 231 can be simplified, and the manufacturing cost of the energy storage mechanism 231 can also be reduced.

[0121] As Figure 5 , Figure 8-Figure 10 , Fig.13 and Fig.15 As shown, according to some embodiments of the present invention, the hammer impact mechanism 20 further has a detachable clutch mechanism 220, and the clutch mechanism 220 is arranged to transmit the rotational movement between the transmission shaft 10 and the ram 200. It can be understood that the clutch mechanism 220 can cooperate with the ram 200, and the clutch mechanism 220 can also be disengaged from the ram 200. When the clutch mechanism 220 cooperates with the ram 200, the rotational movement of the transmission shaft 10 can be transmitted to the ram 200 through the clutch mechanism 220, thereby driving the ram 200 to rotate; when the clutch mechanism 220 is disengaged from the ram 200, that is, the cooperation relationship between the clutch mechanism 220 and the ram 200 is released, the transmission shaft 10 can rotate relative to the ram 200, and the ram 200 is stationary relative to the guide member 210. Thereby, the movement of the ram 200 can be controlled through the clutch mechanism 220, so as to control whether the ram 200 impacts the tool spindle 30, and further the working mode of the tool spindle 30 can be controlled.

[0122] Furthermore, the clutch mechanism 220 may be arranged to be closed by a force transmitted through the tool spindle 30, that is, when the tool head abuts against the working condition (with an axial load), the clutch mechanism 220 can automatically close to achieve impact, and the hand-held tool 1 is in an impact state. Therefore, whether there is a cooperation relationship between the clutch mechanism 220 and the ram 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 ram 200. Thereby, the switching of the working state of the hand-held tool 1 can be conveniently changed, and no additional control structure is required.

[0123] Further, the clutch mechanism 220 is operable to switch between a closed state and a disengaged state. When the clutch mechanism 220 is in the closed state, the ram 200 is driven to rotate by the transmission shaft 10. When the clutch mechanism 220 is in the disengaged state, the ram 200 cannot be driven by the transmission shaft 10. It can be understood that the tool spindle 30 can control the working state of the clutch mechanism 220, so that the clutch mechanism 220 can engage with or disengage from the ram 200. The clutch mechanism 220 can be switched between these two states under the action of the tool spindle 30. When the clutch mechanism 220 engages with the ram 200, the transmission shaft 10 can drive the ram 200 to rotate. When the clutch mechanism 220 disengages from the ram 200, the ram 200 cannot be driven by the transmission shaft 10. Thus, the movement of the ram 200 can be controlled by the clutch mechanism 220, so that the handheld tool 1 can automatically achieve the impact function or enter the impact state when working under load.

[0124] As Figure 5 , Figure 8-Figure 10 , Fig.13 and Fig.15 shown, 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 ram 200, and a receiving portion 201 provided on the other of the transmission shaft 10 and the ram 200. When the clutch mechanism 220 is in the engaged state, the clutch member 221 meshes with the receiving portion 201 in a shape-matching manner. When the clutch mechanism 220 is in the disengaged state, the clutch member 221 is separated from the receiving portion 201.

[0125] It can be understood that the clutch mechanism 220 includes a clutch member 221 and a receiving portion 201. One of the transmission shaft 10 and the ram 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 cooperates with the receiving portion 201. When the clutch mechanism 220 is in the disengaged state, the clutch member 221 is separated from the receiving portion 201. Thus, the working state of the clutch mechanism 220 can be switched by the assembly relationship between the clutch member 221 and the receiving portion 201.

[0126] As Figure 5 , Figure 8-Figure 10 , Fig.13 and Fig.15As shown, in some examples of the present invention, the clutch member 221 can be configured as a spherical or cylindrical shape, and the receiving portion 201 can be configured as a groove 201a. Both the spherical and cylindrical shapes have a smooth outer surface, and the smooth outer surface has a relatively small frictional force during movement, thus facilitating the state switching of the clutch member 221. Configuring the receiving portion 201 as the groove 201a is not only convenient for setting but also convenient for cooperating with the clutch member 221. For example, a part of the inner peripheral wall of the ram 200 is recessed toward the radially outer side of the ram 200 to form the receiving portion 201. Further, the bottom wall of the groove 201a can be formed as an arc surface, and the arc surface can be recessed toward the radially outer side of the ram 200. Thus, the groove 201a can wrap part of the clutch member 221, thereby improving the cooperation stability between the clutch member 221 and the groove 201a.

[0127] According to some embodiments of the present invention, the tool spindle 30 is axially movable relative to the drive shaft 10 but is non-rotatably connected. In other words, in the circumferential direction of the drive shaft 10, the tool spindle 30 and the drive shaft 10 are relatively stationary or rotate together when rotating, and in the axial direction of the drive shaft 10, the tool spindle 30 is movable relative to the drive shaft 10. Thus, the drive shaft 10 can drive the tool spindle 30 to rotate along the circumferential direction of the drive shaft 10, and the tool spindle 30 can also complete sliding in the axial direction of the drive shaft 10.

[0128] For example, as Figure 5 shown, the following will specifically describe in conjunction with the drawings how the clutch mechanism 220 is closed or disengaged when the tool spindle 30 axially moves relative to the drive shaft 10 and how the tool spindle 30 is axially movable but non-rotatably connected to the drive shaft 10. The tool spindle 30 can be moved from a first position to a second position under the action of an axial force. When the tool spindle 30 is in the second position, the ram 200 can be driven to rotate by the drive shaft 10 and can move relative to the guide member 210 along a preset path, so as to impact 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 tool spindle 30 includes a connection end connected to the drive shaft 10 and an output end connected to the tool head. A cavity 120 with an axial opening is provided on one side of the drive shaft 10 close to the connection end. The cavity 120 can extend along the axial direction of the drive shaft 10. The connection end of the tool spindle 30 extends into the cavity 120 from the opening. The inner wall of the cavity 120 and the outer wall of the connection end of the tool spindle 30 are engaged by splines 370 extending axially, so that the tool spindle 30 can axially move relative to the drive shaft 10 and can rotate together with the drive shaft 10. Specifically, as Figure 2As shown, ribbed protrusions 340 are provided on the outer wall of the tool spindle 30 and the inner wall of the cavity 120, and a radially recessed groove 350 is formed between adjacent ribbed protrusions 340 on the tool spindle 30, so that the inner wall of the cavity 120 can cooperate with the groove 350.

[0129] Continue to refer to Figure 5 、 Figure 8-Figure 10 、 Fig.13 and Fig.15 , a radial hole 110 is provided on the side wall of the cavity 120. The radial hole 110 penetrates the side wall 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 within the radial hole 110. The above-mentioned receiving portion 201 may be provided on the inner peripheral wall of the ram 200. When the clutch mechanism 220 is in the engaged state, that is, refer to Fig.13 and Fig.15 , when the tool spindle 30 moves to the first position, the radial hole 110 corresponds to the position of the above-mentioned groove 350, and the clutch member 221 moves along the radial hole 110 in a direction away from the receiving portion 201 of the ram 200 and closer to the groove 350, so that the clutch member 221 is disengaged from the ram 200; refer to Fig. 9 and Fig.10 , when the tool spindle moves to the second position, the groove 350 no longer corresponds to the position of the above-mentioned radial hole 110, that is, there is no longer a space for receiving the clutch member 221 at the position on the tool spindle 30 corresponding to the radial hole. During the movement of the tool spindle 30, the clutch member 221 is squeezed so that the clutch member 221 moves along the radial hole 110 in a direction closer to the receiving portion 221 of the ram, so that a part of the clutch member is located in the radial hole 110, and at the same time, another part is located in the receiving portion 201. The ram 200 can rotate and rotate together with the transmission shaft 10 under the action of the clutch member 221. It should be noted that in other embodiments of the present invention, the above-mentioned cavity 120 may also be located at the connection end of the tool spindle 30, and one end of the transmission shaft 10 connected to the tool spindle 30 extends into the cavity 120. This embodiment will be described in detail later in this specification.

[0130] As Figure 5 、 Fig. 9 and Fig.13 shown, according to some embodiments of the present invention, an impact receiving portion 400 is provided on the tool spindle 30 for mating with the ram 200. It can be understood that an impact receiving portion 400 may be provided on the tool spindle 30, and the ram 200 can impact the impact receiving portion 400. Thus, the ram 200 can drive the tool spindle 30 to move by impacting the impact receiving portion 400, so that the tool spindle 30 can drive the tool head to move relative to the transmission shaft 10 along the axis direction of the transmission shaft 10.

[0131] Furthermore, as Figure 2As shown, the impact receiving portion 400 can be formed in a ring shape. The impact receiving portion 400 is fixed to the outer peripheral wall of the tool spindle 30. The impact receiving portion 400 is located outside the transmission shaft 10. The impact receiving portion 400 is connected to the tool spindle 30. For example, the impact receiving portion 400 can be snap-fitted to the tool spindle 30, or the impact receiving portion 400 can be welded to the tool spindle 30. Thus, when the ram 200 impacts the tool spindle 30, the contact area between the impact receiving portion 400 and the ram 200 can be enlarged, thereby improving the stability of the impact force exerted by the ram 200 on the impact receiving portion 400.

[0132] Embodiment 2

[0133] As Figure 1-Figure 30 shown, the hand-held 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.

[0134] As Figure 1 、 Figure 5 、 Fig.13 、 Fig.21 、 Fig.23 、 Figure 25-27 shown, the transmission shaft 10 can be driven to rotate by the motor 60, and the transmission shaft 10 can rotate about its axis. The tool spindle 30 is used to connect the tool head, and the tool spindle 30 can be driven to rotate by the transmission shaft 10. The hammer impact mechanism 20 has a ram 200. The ram 200 is sleeved on the outside 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, as Figure 1 、 Figure 5 、 Fig.13 、 Fig.21 、 Fig.23 、 Figure 25-26 shown, the ram 200 can be sleeved on the outside of the transmission shaft 10, or, as Fig. 27 shown, the ram 200 can be sleeved on the outside of the tool spindle 30, or the ram 200 can be sleeved on the outside of both the transmission shaft 10 and the tool spindle 30. The transmission shaft 10 can directly or indirectly drive the ram 200 to rotate.

[0135] As Figure 1 、 Figure 5 、 Fig.13 、 Fig.21 、 Fig.23 、 Figure 25-27As shown, the hammer impact mechanism 20 further includes a guide member 210 which is sleeved outside the ram 200. The tool spindle 30 can be switched from a first position to a second position under the action of an axial force. In other words, there is an external force acting on the tool spindle 30 along the axis direction 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 ram 200 can be driven by the transmission shaft 10 to rotate and can move relative to the guide member 210 along a preset path, so as to impact 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 transmission shaft 10 cannot drive the ram 200 to rotate.

[0136] For the hand tool 1 according to an embodiment of the present invention, by applying a force along the axis direction of the tool spindle 30, the position of the tool spindle 30 can be switched, and then the relationship between the ram 200 and the transmission shaft 10 can be controlled. Further, the ram 200 is guided by the intermittent impact assembly 230 to perform a linear motion, and the ram 200 can also impact the tool spindle 30, so as to realize the movement in the axis direction of the tool spindle 30. When the tool spindle 30 drills on an environmental component (such as a wall or a panel), the tool spindle 30 forms an impact force on the environmental component, thereby improving the drilling efficiency of the hand tool 1. Moreover, the structure of the hand tool 1 according to the embodiment of the present invention is compact and simple in structure, and is convenient to carry.

[0137] As Figure 25-27 shown, according to some embodiments of the present invention, both ends of the tool spindle 30 are a connection end 380 and an output end 390 respectively. The connection 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 borne by the tool spindle 30 is from the output end 390 to the connection end 380, in other words, when the direction of the force borne by the tool spindle 30 is from the output end 390 to the connection end 380 of the tool spindle 30, the tool spindle 30 can be switched to the second position where it is mated with the transmission shaft 10. When the direction of the force borne by the tool spindle 30 is from the connection end 380 to the output end 390 of the tool spindle 30, the tool spindle 30 is switched to the first position where it is mated with the transmission shaft 10. Thus, the position state of the tool spindle 30 can be switched by the acting direction of the external force applied to the tool spindle 30, and then the working state of the hand tool 1 can be switched.

[0138] As Figure 1 、 Figure 5 、 Fig.13 、 Fig.21 、 Fig.23 、 Figure 25-27As shown, in some embodiments of the present invention, the hand-held tool 1 further includes a mode adjustment mechanism 40. The mode adjustment mechanism 40 is operable to switch between a first mode state and a second mode state. When in the first mode state, the tool spindle 30 is capable of switching between a first position and a second position relative to the drive shaft 10. That is, when the mode adjustment mechanism 40 is in the first mode state, the hand-held tool 1 can generate an axial impact under the action of an axial load. Hereinafter, this mode is abbreviated as the "impact mode". When in the second mode state, the tool spindle 30 axially abuts against the mode adjustment mechanism 40 to limit the tool spindle 30 from switching from the first position to the second position. That is, when the mode adjustment mechanism 40 is in the second mode state, regardless of whether the tool spindle 30 is under the action of an axial load, no impact is generated on the hand-held tool 1. Hereinafter, this mode is abbreviated as the "non-impact mode".

[0139] Further, as Figure 1 , Figure 5 , Fig.13 , Fig.21 , Fig.23 , Figure 25-27 As shown, the hand-held tool 1 further includes a mode adjustment mechanism 40. The mode adjustment mechanism 40 is 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, the guide member 210 is fixed to the housing 80, that is, the guide member 210 is stationary relative to the housing 80, and the ram 200 can move along the guide member 210 in a preset path when rotating to impact the tool spindle 30. When the mode adjustment mechanism 40 is in the second mode state, the guide member 210 is rotatably provided in the housing 80, that is, the guide member 210 is movable relative to the housing 80, and the ram 200 does not impact the tool spindle 30. Thus, by controlling the state of the mode adjustment mechanism 40, the operating state of the guide member 210 can be controlled, thereby the cooperation relationship between the ram 200 and the guide member 210 can be controlled, and further the working state of the ram 200 can be controlled to realize the switching of the working state of the hand-held tool 1.

[0140] As Figure 19-20 shown, in some embodiments of the present invention, the mode adjustment mechanism 40 includes a first tooth pattern 212 provided on the guide member 210, and an impact switching member provided with a second tooth pattern 431. The impact switching member is axially movable but non-rotatably fixed in the housing 80 of the hand-held tool 1. Specifically, the impact switching member is an impact switching ring 430, and the impact switching ring 430 is movably sleeved outside the ram 200. Among them, when the mode adjustment mechanism 40 is in the first mode state, the first tooth pattern 212 meshes with the second tooth pattern 431. When the mode adjustment mechanism 40 is in the second mode state, the first tooth pattern 212 is spaced apart from the second tooth pattern 431.

[0141] It can be understood that the impact switching ring 430 is sleeved on the hammer 200, and the impact switching ring 430 and the hammer 200 can move relative to each other. The impact switching ring 430 is provided with a second tooth pattern 431, and the guide member 210 is provided with a first tooth pattern 212. The first tooth pattern 212 and the second tooth pattern 431 can be matched and connected together, so that the guide member 210 and the impact switching ring 430 can be connected. At this time, the impact switching ring 430 can limit the movement of the guide member 210, and the guide member 210 and the impact switching ring 430 are relatively stationary. The hammer 200 can make linear motion relative to the guide member 210 along a preset path and impact the tool spindle 30 in at least one operating state.

[0142] The first tooth pattern 212 and the second tooth pattern 431 can also be spaced apart by switching the position of the impact switching ring 430. At this time, the guide member 210 is movable relative to the impact switching ring 430. The guide member 210 can rotate along with the hammer 200 under the drive of the intermittent impact assembly 230, and the hammer 200 and the guide member 210 are relatively stationary. Therefore, the positional relationship and assembly relationship between the guide member 210 and the impact switching ring 430 can be adjusted by adjusting the matching relationship between the first tooth pattern 212 and the second tooth pattern 431, so as to control the motion state of the guide member 210, and further improve the motion state of the tool spindle 30, so as to achieve the control of the working mode of the handheld tool 1.

[0143] Furthermore, if Fig.19 , Figure 21-26 As shown, the mode adjustment mechanism 40 further includes a buffer 440, one end of which abuts against the impact switching ring 430 to constantly push the impact switching ring 430 to move toward the guide member 210. Thus, the buffer 440 can constantly push the impact switching ring 430 to approach the guide member 210, so that the first tooth pattern 212 can be matched with the second tooth pattern 431.

[0144] Furthermore, if Figure 19-Figure 24 As shown, the mode adjustment mechanism 40 also includes a mode switching button 450, which is rotatably mounted on the impact switching ring 430. The mode switching button 450 is rotatable relative to the impact switching ring 430. The inner circumferential wall of the mode switching button 450 is provided with a guide block 451, and the outer circumferential wall of the impact switching ring 430 is provided with a matching block 432 matched with the guide block 451. The mode switching button 450 is rotated, wherein when the guide block 451 and the matching block 432 are axially abutted against each other, the guide block 451 pushes the impact switching ring 430 to compress the buffer 440 to move away from the guide member 210, and the first tooth pattern 212 is spaced apart from the second tooth pattern 431; when the guide block 451 and the matching block 432 are offset, the impact switching ring 430 moves toward the direction close to the guide member 210 under the action of the buffer 440, and the first tooth pattern 212 is meshed with the second tooth pattern 431.

[0145] It can be understood that the positional relationship between the mode switching button 450 and the impact switching ring 430 can be switched by rotating the mode switching button 450 or the impact switching ring 430, so as to change the mating state between the guiding block 451 and the mating block 432. Thus, by switching the mating relationship between the guiding block 451 and the mating block 432, the mating relationship between the first tooth pattern 212 and the second tooth pattern 431 can be controlled. Further, as Fig. 20 shown, the guiding block 451 has a guiding inclined surface 451a to guide the mating block 432. Thus, the mating relationship between the guiding block 451 and the mating block 432 can be conveniently switched.

[0146] In other embodiments of the present invention, the mode adjustment mechanism 40 can also adopt other structures. Specifically, refer to Figure 2-Figure 5 、 Fig. 9 and Fig.13 , the mode adjustment mechanism 40 includes a pressure retaining ring 410 and a mode adjustment button 420. The pressure retaining ring 410 is sleeved on the transmission shaft 10, specifically sleeved on the above-mentioned impact receiving portion 400, and the pressure retaining ring 410 is rotatable relative to the transmission shaft 10 but not axially movable, and the mode adjustment button 420 is rotatably sleeved on the pressure retaining ring 410. The pressure retaining ring 410 is provided with a retaining portion 411, and the inner peripheral wall of the mode adjustment button 420 is provided with a channel 422 adapted for the retaining portion 411 to pass through, and the channel 422 extends along the axis direction of the transmission shaft 10.

[0147] Among them, when the mode adjustment mechanism 40 is in the first mode state, the retaining portion 411 abuts against the mode adjustment button 420; when the mode adjustment mechanism 40 is in the second mode state, the retaining portion 411 corresponds to the position of the channel 422, and the tool spindle 30 can drive the pressure retaining ring to move axially along the tool spindle. Thus, by adjusting the relative positional relationship between the retaining portion 411 of the pressure retaining ring 410 and the mode adjustment button 420, the movement state of the impact hammer 200 can be adjusted, so that the working mode of the tool spindle 30 can be adjusted. Specifically, as Figure 3-Figure 4 shown, the mode adjustment button 420 further includes a flange 421 provided on the inner peripheral wall of the mode adjustment button 420. The flange 421 is annular and extends along the circumferential direction of the pressure retaining ring 410, and the channel 422 penetrates through the flange 421 along the axis direction of the pressure retaining ring 410. Thus, the flange 421 can construct the channel 422, and the flange 421 can also abut against the retaining portion 411.

[0148] As Figure 3-Figure 4As shown, in some embodiments of the present invention, the abutting portion 411 includes a fixing section 411a, a connecting section 411b, and a mating section 411c. The fixing section 411a extends from the pressure stopping ring 410. One end of the connecting section 411b is connected to the fixing section 411a, and one end of the mating section 411c is connected to the other end of the connecting section 411b. The mating section 411c is adapted to pass through the channel 422. The fixing section 411a and the connecting section 411b are spaced apart along the axis direction of the pressure stopping ring 410. Further, the part where the connecting section 411b is connected to the fixing section 411a has a smooth transition; or, the part where the connecting section 411b is connected to the mating section 411c has a smooth transition.

[0149] As Figure 2 and Figure 6 shown, in some embodiments of the present invention, the outer peripheral wall of the impact receiving portion 400 has a stepped surface 404, and the pressure stopping ring 410 abuts against the stepped surface 404. Thus, the stepped surface 404 can define the movement of the pressure stopping ring 410 and prevent the pressure stopping ring 410 from coming off the impact receiving portion 400.

[0150] As Figure 25-27 shown, in some embodiments of the present invention, one end of the transmission shaft 10 connected to the connection end 380 is the transmission end 130. One of the connection end 380 and the transmission 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 transmission end 130 of the transmission shaft 10 may be provided with an axial hole 360. The axial hole 360 extends along the axis direction of the transmission shaft 10 and opens towards the connection end 380 of the tool spindle 30. The end of the connection end 380 of the tool spindle 30 may extend into the axial hole 360. Again, the connection end 380 of the tool spindle 30 may be provided with an axial hole 360. The axial hole 360 extends along the axis direction of the tool spindle 30 and opens towards the transmission end 130 of the transmission shaft 10. The end of the transmission end 130 of the transmission shaft 10 may extend into the axial hole 360. For the connection method of providing an opening on the connection end of the tool spindle 30 to facilitate the insertion of the transmission shaft 10, it has been introduced in the above-mentioned Embodiment 1 and will not be elaborated here. The connection method of providing an opening on the transmission end face of the transmission shaft 10 will be described in detail below.

[0151] As Figure 25-27 shown, splines 370 for realizing torque transmission between the transmission shaft 10 and the tool spindle 30 are provided on the inner wall of the axial hole 360 and the outer wall of the other end. Thus, the connection stability between the transmission shaft 10 and the tool spindle 30 can be improved, and not only can the rotation in the circumferential direction between the tool spindle 30 and the transmission shaft 10 be transmitted, but also the relative movement between the tool spindle 30 and the transmission shaft 10 in the axial direction can be achieved.

[0152] Furthermore, as Fig.13 , Figure 25-27 As shown, radial grooves can be formed between the splines 370 on the other end extending into the axial hole 360. The outer wall of the axial hole 360 is provided with a radial hole 110. When the tool spindle 30 is in the first position, the radial hole 110 corresponds to the position of the radial groove, and the steel ball can at least partially fall into the radial groove and disengage from the ram. 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 in 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 connects with the ram 200 so that the transmission shaft can drive the ram 200 to rotate. Thus, by controlling the relative positional relationship between the steel ball and the radial groove, the mating relationship between the ram 200 and the tool spindle 30 or the transmission shaft 10 can be controlled, thereby controlling the movement state of the ram 200, and further controlling the working state of the tool spindle 30 to achieve the switching of the working mode of the hand tool 1.

[0153] As Figure 1 , Figure 5 , Fig.13 , Fig.21 , Fig.23 , Figure 25-27 As shown, according to some embodiments of the present invention, the hammer impact mechanism 20 further includes an intermittent impact assembly 230. When the transmission 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 preset path and impacts the tool spindle 30 in at least one operating state. It can be understood that the intermittent impact assembly 230 can cooperate with the ram 200, and the intermittent impact assembly 230 can also cooperate with the guide 210. When the transmission shaft 10 drives the ram 200 to rotate, the intermittent impact assembly 230 can change the movement path of the ram 200, and this movement path can both make the ram 200 rotate around the circumferential direction of the transmission shaft 10 and make the ram 200 move along the axial direction of the transmission shaft 10, so that the ram 200 can impact the tool spindle 30, and then complete the sliding of the tool spindle 30 relative to the transmission shaft 10.

[0154] As Figure 2 , Figure 5 , Figure 7 and Figure 9-12As shown, according to some embodiments of the present invention, the intermittent impact assembly 230 includes an energy storage mechanism 231 in contact with the ram 200, as well as a conversion member 232 and a curved surface guiding portion 233 disposed between the guiding member 210 and the ram 200. It can be understood that the intermittent impact assembly 230 includes an energy storage mechanism 231, a conversion member 232, and a curved surface guiding portion 233. Both the conversion member 232 and the curved surface guiding portion 233 are located between the guiding member 210 and the ram 200, and one end of the energy storage mechanism 231 is in contact with the ram 200. Thus, by constructing the specific shape of the curved surface guiding portion 233, the movement trajectory of the conversion member 232 can be guided. The conversion member 232 can be linked with the ram 200. The ram 200 can drive the conversion member 232 to rotate along the circumferential direction of the transmission shaft 10, and the conversion member 232 can drive the ram 200 to move along the trajectory of the curved surface guiding portion 233.

[0155] Further, as Fig.13 and Figure 17-Figure 18 shown, a baffle 100 can be provided on the transmission shaft 10. The baffle 100 is sleeved on the outer peripheral wall of the transmission shaft 10. The energy storage mechanism 231 is located between the ram 200 and the baffle 100, and the end of the energy storage mechanism 231 away from the ram 200 can cooperate with the baffle 100. When the ram 200 moves a certain distance towards the energy storage mechanism 231, the ram 200 and the baffle 100 can compress the energy storage mechanism 231. Thus, the energy storage mechanism 231 can form a driving force on the ram 200.

[0156] As Figure 11-Figure 12 shown, in some embodiments of the present invention, the curved surface guiding portion 233 can be formed in a ring shape. The curved surface guiding portion 233 can surround along the circumferential direction of the transmission shaft 10. The curved surface guiding portion 233 can 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 towards the other end of the climbing section 233a. Further, the climbing section 233a can be in a spiral shape. The falling section 233b can be in a straight line shape and extend along the axial direction of the transmission shaft 10. At least part of the conversion member 232 can cooperate with the curved surface guiding portion 233. Preferably, in order to ensure that the ram forms sufficient impact force on the tool spindle 30 and the volume of the hand-held tool 1 is compact, the climbing height of the climbing section 233a in the axial direction is greater than 3 mm and less than or equal to 20 mm. Preferably, the climbing height is between 4 mm and 15 mm. Preferably, the climbing height is 10 mm.

[0157] When the conversion member 232 cooperates with the climbing section 233a, the conversion member 232 rolls from one end of the climbing section 233a towards the other end of the climbing section 233a, and the ram 200 moves towards the baffle 100. The ram 200 and the baffle 100 can compress the energy storage mechanism 231; when the conversion member 232 is at the other end of the climbing section 233a and rolls towards the dropping section 233b, the energy storage mechanism 231 can push the ram 200 to drop from the end of the dropping section 233b close to the baffle 100 towards the end of the dropping section 233b close to the tool head, that is, the ram 200 moves in a direction away from the baffle 100 and close to the tool head. A part of the ram 200 approaches and impacts the part of the tool spindle 30 outside the transmission shaft 10, so that the tool spindle 30 moves relative to the transmission shaft 10 along the axis direction of the transmission shaft 10, and the ram 200 forms a hammering on the tool spindle 30 and the tool head.

[0158] Further, as Figure 7 , Fig.15 shown, an installation groove 203 can be provided on the end face of the ram 200 close to the energy storage mechanism 231. The end of the energy storage mechanism 231 can be located in the installation groove 203, and the end of the energy storage mechanism 231 can abut against the bottom wall of the installation groove 203. Thereby, the assembly stability between the energy storage mechanism 231 and the ram 200 can be improved.

[0159] As Fig.12 shown, in some embodiments of the present invention, the curved surface guiding portion 233 can include multiple segments, and each segment includes a climbing section 233a and a dropping section 233b. The conversion members 232 can be multiple, and the multiple conversion members 232 can be spaced apart along the circumferential direction of the ram 200. In this embodiment, the outer diameter of the ram 200 is between 20 mm and 40 mm, the slope height is greater than 3 mm and less than or equal to 15 mm. Preferably, the climbing height is greater than or equal to 4 mm and less than or equal to 8 mm. More preferably, the climbing height is 5 mm. It can be understood that, in order to ensure the smooth climbing of the conversion member 232, preferably, the number of segments is 2 to 7, and particularly advantageously the number of segments is 3 - 4. In this embodiment, the number of segments of the climbing section 233a is preferably 3.

[0160] It should be noted that the assembly positions and relationships of the conversion member 232 and the curved surface guiding portion 233 on the ram 200 and the guiding member 210 are not specifically limited. In some embodiments of the present invention, the conversion member 232 is located on one of the guiding member 210 and the ram 200, and the curved surface guiding portion 233 is located on the other of the guiding member 210 and the ram 200. Thus, the assembly relationship between the conversion member 232, the curved surface guiding portion 233, the ram 200, and the guiding member 210 can be achieved. Therefore, by utilizing the cooperation relationship between the conversion member 232 and the curved surface guiding portion 233 and the relative movement between the conversion member 232 and the curved surface guiding portion 233, the relative movement of the ram 200 relative to the guiding member 210 can be achieved, and the ram 200 can move relative to the transmission shaft 10 along the axis direction of the transmission shaft 10. The movement locus of the conversion member 232 on the curved surface guiding portion 233 is the preset path of the ram 200.

[0161] As Figure 9-12 shown, in some examples of the present invention, the conversion member 232 can be located on the ram 200, and the curved surface guiding portion 233 is located on the guiding member 210. For example, as Figure 2 , Figure 5 , Figure 7 and Figure 11-Figure 12 shown, an embedding groove 202 can be provided on the outer peripheral wall of the ram 200, a part of the conversion member 232 can be located in the embedding groove 202, a curved surface guiding portion 233 is provided on the inner peripheral wall of the guiding member 210, and another part of the conversion member 232 can cooperate with the curved surface guiding portion 233.

[0162] As Figure 16-18 shown, in some other examples of the present invention, the conversion member 232 can be located on the guiding member 210, and the curved surface guiding portion 233 is located on the ram 200. For example, a receiving groove 211 is provided on the inner peripheral wall of the guiding member 210, a part of the conversion member 232 can be located in the receiving groove 211, a curved surface guiding portion 233 can be provided on the outer peripheral wall of the ram 200, and another part of the conversion member 232 can cooperate with the curved surface guiding portion 233.

[0163] As Figure 2 , Fig.16 and Fig.19 shown, in some embodiments of the present invention, the conversion member 232 can be set as a steel ball, as Figure 11-Figure 12As shown, preferably, in order to ensure the strength of the steel ball, the diameter of the steel ball is greater than 4 mm and less than or equal to 10 mm. Advantageously, the diameter of the steel ball is greater than or equal to 4 mm and less than or equal to 6 mm. In this embodiment, the diameter of the steel ball is 5 mm. The curved surface guiding portion 233 can be arranged as a cam surface or a cam groove. Thus, the cam surface or the cam groove can define the moving track of the steel ball, and the steel ball can move within the cam surface or the cam groove. The steel ball has a smooth outer surface, which can not only reduce the relative movement friction between the conversion member 232 and the curved surface guiding portion 233, improve the smoothness of the movement of the conversion member 232 within the curved surface guiding portion 233, but also the steel ball has a large structural strength and good wear resistance, thereby ensuring the working performance of the intermittent impact assembly 230. It should be noted that the "cam" mentioned here can refer to that the curved surface guiding portion 233 protrudes from the inner peripheral wall of the guiding member 210, or the curved surface guiding portion 233 protrudes from the outer peripheral wall of the ram 200.

[0164] Furthermore, the steel ball and the curved surface guiding portion 233 can be in point or line contact. It can be understood that during the movement of the steel ball within the curved surface guiding portion 233, the contact between the steel ball and the curved surface guiding portion 233 is always a point or a line contact, which is beneficial to reducing the friction between the steel ball and the curved surface guiding portion 233. For example, the radius of curvature of the cam surface can be basically the same as or slightly larger than the radius of the steel ball, so as to improve the matching degree between the steel ball and the cam surface, and further improve the assembly stability, wear resistance and service life of the steel ball and the cam surface.

[0165] As Figure 2 、 Fig.16 and Fig.19 shown, in some embodiments of the present invention, the energy storage mechanism 231 can be arranged as an elastic member. For example, the energy storage mechanism 231 can be a spring or an elastic rubber member. Thus, the setting and assembly of the energy storage mechanism 231 can be simplified, and the manufacturing cost of the energy storage mechanism 231 can also be reduced. Further, the energy storage mechanism 231 can be formed into a ring shape, and the energy storage mechanism 231 can be sleeved on the outer peripheral wall of the transmission shaft 10. Thus, it is convenient for the assembly of the energy storage mechanism 231, and can evenly apply the acting force of the energy storage mechanism 231 on the ram 200.

[0166] Embodiment 3

[0167] As Figure 1-Figure 30 shown, the hand-held 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.

[0168] Specifically, as Figure 1 、 Figure 2 and Figure 5As shown, the drive shaft 10 is driven by the motor 60 to rotate and rotate about the axis of the drive shaft 10. In other words, the motor 60 drives the drive shaft 10 to rotate, and the drive shaft 10 rotates about its own axis. It can be understood that the motor 60 is connected to the drive shaft 10. It should be noted that the "connection" mentioned here can mean that the motor 60 is directly connected to the drive shaft 10. For example, the output end of the motor 60 can be directly connected to the end of the drive shaft 10. The "connection" can also mean that the motor 60 is indirectly connected to the drive shaft 10. For example, the motor 60 can be directly connected to an intermediate transmission component and then directly connected to the drive shaft 10 through the intermediate transmission component.

[0169] The tool spindle 30 is connected to the drive shaft 10 so as to be axially movable but non-rotatable relative to the drive shaft 10. In other words, in the circumferential direction of the drive shaft 10, the tool spindle 30 is relatively stationary with respect to the drive shaft 10. In the axial direction of the drive shaft 10, the tool spindle 30 can move relative to the drive shaft 10. The drive shaft 10 can drive the tool spindle 30 to rotate along the circumferential direction of the drive shaft 10, and the tool spindle 30 can also complete sliding in the axial direction of the drive shaft 10.

[0170] As Figure 2 、 Figure 5-Figure 13 shown, the hammer impact mechanism 20 has a ram 200. The ram 200 is sleeved outside the drive shaft 10 and can be driven by the drive shaft 10 to rotate. It can be understood that the hammer impact mechanism 20 includes the ram 200. The ram 200 can be sleeved on the outer peripheral wall of the drive shaft 10. The ram 200 can be connected to the drive shaft 10 in a mating manner. The drive shaft 10 can further drive the ram 200 to rotate about the axis of the drive shaft 10. It should be noted that the "connection" mentioned here can mean that the ram 200 is directly connected to the drive shaft 10 or that the ram 200 is indirectly connected to the drive shaft 10.

[0171] As Figure 5 、 Figure 8-Figure 10 、 Fig.13 And Fig.15As shown, according to some embodiments of the present invention, the hammer impact mechanism 20 further has a detachable clutch mechanism 220, and the clutch mechanism 220 is arranged to transmit the rotational movement between the drive shaft 10 and the ram 200. It can be understood that the clutch mechanism 220 can cooperate the drive shaft 10 with the ram 200, and the clutch mechanism 220 can also disengage the drive shaft 10 from the ram 200. When the clutch mechanism 220 cooperates the drive shaft 10 with the ram 200, the rotational movement of the drive shaft 10 can be transmitted to the ram 200 through the clutch mechanism 220, thereby driving the ram 200 to rotate; when the clutch mechanism 220 disengages the two, the cooperation relationship between the clutch mechanism 220 and the ram 200 is released, the drive shaft 10 rotates relative to the ram 200, and the ram 200 is stationary relative to the guide member 210. Thus, the movement of the ram 200 can be controlled by the clutch mechanism 220, so as to control whether the ram 200 impacts the tool spindle 30, and further the working state of the hand-held tool 1 can be changed. In some embodiments of the present invention, the clutch mechanism 220 is arranged to be closed by a force transmitted through the tool spindle 30. It can be understood that whether there is a cooperation relationship between the clutch mechanism 220 and the ram 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 ram 200. For example, when the tool head or the tool spindle 30 abuts against the working condition (that is, when the tool spindle 30 is subject to an axial load), the clutch mechanism 220 is closed, and the hand-held tool 1 switches to the impact state. Therefore, when the hand-held tool 1 is in the working state and the tool head abuts against the working condition, the hand-held tool 1 can automatically switch to the impact state. Hereinafter, this mode is simply referred to as the "impact mode".

[0172] It should be noted that in actual work, not all working conditions are suitable for the hand-held tool 1 to work in the impact state. Many times, the operator hopes that when the hand-held tool 1 is in the working state and the tool head or the tool spindle 30 is subject to a load from the working condition, it can still be in the non-impact working state. Hereinafter, this working mode is simply referred to as the "non-impact working mode".

[0173] Therefore, in order to enable the hand-held tool 1 to adapt to various working conditions, the hand-held tool 1 further includes a mode adjustment mechanism 40, which can be as Figure 2-Figure 6 、 Figure 13-Figure 15 and Figure 19-Figure 30 shown. The mode adjustment mechanism 40 can be operably switched between a first mode state and a second mode state. When the mode adjustment mechanism 40 is in the first mode state (that is, as Figure 5-Figure 6 、 Figure 9-10 、 Figure 21-22 and Fig.25When the ram 200 is at the position shown (), the ram 200 can be driven by the drive shaft 10 to rotate and thus move linearly along a preset path, and in at least one operating state, the ram 200 impacts the tool spindle 30. In other words, the drive shaft 10 can cooperate with the ram 200, and the drive shaft 10 can provide power for the ram 200 to make the ram 200 move along the preset path, and the ram 200 can impact the tool spindle 30 during the movement; when the mode adjustment mechanism 40 is in the second mode state (such as Figure 13-Figure 15 , Figure 23-Figure 24 and Fig.26 the positions shown), the drive shaft 10 cannot drive the ram 200 to rotate, and the ram 200 does not impact the tool spindle 30.

[0174] For the hand-held tool 1 according to the embodiment of the present invention, by providing the mode adjustment mechanism 40 and changing the cooperation relationship between the drive shaft 10 and the ram 200 by switching the state of the mode adjustment mechanism 40, it is possible to control whether the ram 200 has an impact effect on the tool spindle 30, and further, the switching between the impact mode and the non-impact mode of the hand-held tool 1 can be realized, so that the performance of the hand-held tool 1 can be improved, the structure of the hand-held tool 1 is compact, simple, the functions are diversified, and at the same time, it is convenient to carry.

[0175] Such as Figure 5 , Figure 8-Figure 10 , Fig.13 and Fig.15 shown, in some examples of the present invention, the clutch mechanism 220 includes a clutch member 221 provided on one of the drive shaft 10 and the ram 200, and a receiving portion 201 provided on the other of the drive shaft 10 and the ram 200. When the clutch mechanism 220 is in the engaged state, the clutch member 221 meshes with the receiving portion 201 in a shape-matching manner. When the clutch mechanism 220 is in the disengaged state, the clutch member 221 is separated from the receiving portion 201.

[0176] It can be understood that the clutch mechanism 220 includes a clutch member 221 and a receiving portion 201. One of the drive shaft 10 and the ram 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 cooperates with the receiving portion 201. When the clutch mechanism 220 is in the disengaged state, the clutch member 221 is separated from the receiving portion 201. Thus, the working state of the clutch mechanism 220 can be switched through the assembly relationship between the clutch member 221 and the receiving portion 201.

[0177] Such as Figure 5 , Figure 8-Figure 10 , Fig.13 and Fig.15As shown, in some examples of the present invention, the clutch member 221 can be set to a spherical or cylindrical shape, and the receiving portion 201 can be set to a groove body 201a. Both the spherical and cylindrical shapes have a smooth outer surface, and the smooth outer surface has a relatively small frictional force during the movement process, thereby facilitating the state switching of the clutch member 221. Setting the receiving portion 201 as the groove body 201a is not only convenient for setting but also convenient for cooperating with the clutch member 221. For example, a part of the inner peripheral wall of the ram 200 is recessed toward the radially outer side of the ram 200 to form the receiving portion 201. Further, the bottom wall of the groove body 201a can be formed as an arc surface, and the arc surface can be recessed toward the radially outer side of the ram 200. Thus, the groove body 201a can wrap part of the clutch member 221, thereby improving the cooperation stability between the clutch member 221 and the groove body 201a.

[0178] According to some embodiments of the present invention, the tool spindle 30 is axially movable relative to the drive shaft 10 but is non-rotatably connected. In other words, in the circumferential direction of the drive shaft 10, the tool spindle 30 and the drive shaft 10 are relatively stationary or rotate together when rotating, and in the axial direction of the drive shaft 10, the tool spindle 30 is movable relative to the drive shaft 10. Thus, the drive shaft 10 can drive the tool spindle 30 to rotate along the circumferential direction of the drive shaft 10, and the tool spindle 30 can also complete the sliding in the axial direction of the drive shaft 10.

[0179] For example, as Figure 5 shown, the tool spindle 30 can be switched between a first position and a second position relative to the drive shaft 10 under the action of an axial force. When the tool spindle 30 is in the second position, the ram 200 can be driven by the drive shaft 10 to rotate and can move relative to the guide member 210 along a preset path, so as to impact 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 tool spindle 30 includes a connection end connected to the drive shaft 10 and an output end connected to the tool head. A cavity 120 with an axial opening is provided on one side of the drive shaft 10 close to the connection end. The cavity 120 can extend along the axial direction of the drive shaft 10. The connection end of the tool spindle 30 extends into the cavity 120 from the opening. The inner wall of the cavity 120 and the outer wall of the connection end of the tool spindle 30 are matched by splines 370 extending axially, so that the tool spindle 30 can move axially relative to the drive shaft 10 and can rotate together with the drive shaft 10. Specifically, as Figure 2 shown, ribs 340 are provided on the outer wall of the tool spindle 30 and the inner wall of the cavity 120, and grooves 350 that are radially recessed are formed between adjacent ribs 340 on the tool spindle 30, so that the inner wall of the cavity 120 can be matched with the grooves 350.

[0180] Continue to refer to Figure 5 、 Figure 8-Figure 10 、 Fig.13 and Fig.15 , a radial hole 110 is provided on the side wall of the cavity 120. The radial hole 110 penetrates the side wall 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 within the radial hole 110. The above-mentioned receiving portion 201 may be provided on the inner peripheral wall of the ram 200. Refer to Fig.13 and Fig.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 above-mentioned groove 350. The clutch member 221 moves along the radial hole 110 in a direction away from the receiving portion 201 of the ram 200 and closer to the groove 350, so that the clutch member 221 is disengaged from the ram 200; Refer to Fig. 9 and Fig.10 , when the clutch mechanism 220 is in the closed state, that is, when the tool spindle moves to the second position, the groove 350 no longer corresponds to the position of the above-mentioned radial hole 110, that is, there is no longer a space for receiving the clutch member 221 at the position on the tool spindle 30 corresponding to the radial hole. During the movement of the tool spindle 30, the clutch member 221 is squeezed so that the clutch member 221 moves along the radial hole 110 in a direction closer to the receiving portion 221 of the ram. A part of the clutch member 221 is located in the radial hole 110, and at the same time, another part is located in the receiving portion 201. The ram 200 can rotate and rotate together with the transmission shaft 10 under the action of the clutch member 221. It should be noted that in other embodiments of the present invention, the above-mentioned cavity 120 may also be located at the connection end of the tool spindle 30, and one end of the transmission shaft 10 connected to the tool spindle 30 extends into the cavity 120.

[0181] Such as Figure 2 、 Figure 5 、 Figure 7 and Figure 9-12 shown, according to some embodiments of the present invention, the intermittent impact assembly 230 includes an energy storage mechanism 231 in contact with the ram 200, and a conversion member 232 and a curved surface guiding portion 233 provided between the guiding member 210 and the ram 200. The intermittent impact assembly 230 further includes an energy storage mechanism 231. The conversion member 232 and the curved surface guiding portion 233 are both located between the guiding member 210 and the ram 200, and one end of the energy storage mechanism 231 is in contact with the ram 200. Thus, by constructing the specific shape of the curved surface guiding portion 233, the movement trajectory of the conversion member 232 can be guided, and the conversion member 232 can be linked with the ram 200. The ram 200 moves along the trajectory of the curved surface guiding portion 233 under the action of the conversion member 232.

[0182] Furthermore, as Fig.13 and Figure 17-Figure 18As shown, a baffle 100 may be provided on the transmission shaft 10. The baffle 100 is sleeved on the outer peripheral wall of the transmission shaft 10. The energy storage mechanism 231 is located between the ram 200 and the baffle 100. One end of the energy storage mechanism 231 away from the ram 200 can cooperate with the baffle 100. After the ram 200 moves a certain distance towards the energy storage mechanism 231, the ram 200 and the baffle 100 can compress the energy storage mechanism 231. Thus, the energy storage mechanism 231 can form a driving force on the ram 200. Of course, other structures can also be adopted for the axial limiting manner of the energy storage mechanism, which will not be elaborated here.

[0183] As Figure 11-Figure 12 shown, in some embodiments of the present invention, the curved surface guiding portion 233 may be formed in a ring shape. The curved surface guiding portion 233 can surround along the circumferential direction of the transmission shaft 10. Specifically, the curved surface guiding 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 towards the other end of the climbing section 233a. Further, the climbing section 233a may be in a spiral shape, and the falling section 233b may be in a straight line shape, and the falling section 233b extends along the axial direction of the transmission shaft 10. Preferably, in order to ensure that the ram forms sufficient impact force on the tool spindle 30 and the volume of the hand tool 1 is compact, the climbing height of the climbing section 233a in the axial direction is greater than 3 mm and less than or equal to 15 mm. Preferably, the climbing height is greater than or equal to 4 mm and less than or equal to 8 mm. Preferably, the climbing height is 5 mm.

[0184] When the conversion member 232 cooperates with the climbing section 233a, the conversion member 232 rolls from one end of the climbing section 233a towards the other end of the climbing section 233a, and the ram 200 moves towards the baffle 100. The ram 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 climbing section 233a and rolls towards the falling section 233b, the energy storage mechanism 231 can push the ram 200 to fall from one end of the falling section 233b close to the baffle 100 towards the other end of the falling section 233b close to the tool head, that is, the ram 200 rapidly falls towards the direction away from the baffle 100 and close to the tool head. A part of the ram 200 approaches and impacts the part 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 ram 200 forms a hammering on the tool spindle 30 and the tool head.

[0185] As Figure 5 、 Fig. 9 and Fig.13As shown, according to some embodiments of the present invention, an impact receiving portion 400 adapted to mate with the ram 200 is provided on the tool spindle 30. It can be understood that the impact receiving portion 400 may be provided on the tool spindle 30, and the ram 200 may impact the impact receiving portion 400. Thus, the ram 200 can drive the tool spindle 30 to move by impacting the impact receiving portion 400, so that the tool spindle 30 can move relative to the transmission shaft 10 along the axial direction of the transmission shaft 10.

[0186] Furthermore, as Figure 7 , Fig.15 shown, an installation groove 203 may be provided on the end face of the ram 200 close to the energy storage mechanism 231. The end of the energy storage mechanism 231 may be located within the installation groove 203, and the end of the energy storage mechanism 231 may abut against the bottom wall of the installation groove 203. Thereby, the assembly stability between the energy storage mechanism 231 and the ram 200 can be improved.

[0187] As Fig.12 shown, in some embodiments of the present invention, the curved surface guiding portion 233 may include multiple segments, and each segment includes a climbing section 233a and a dropping section 233b. There may be multiple conversion members 232, and the multiple conversion members 232 may be spaced apart along the circumferential direction of the ram 200. In this embodiment, in order to ensure the rationality of the overall design of the hand tool, the outer diameter of the ram 200 is between 15 mm and 50 mm. Preferably, the outer diameter of the ram is between 20 mm and 40 mm, the slope height is greater than 3 mm and less than or equal to 15 mm. Preferably, the climbing height is greater than or equal to 4 mm and less than or equal to 8 mm. More preferably, the climbing height is 5 mm. It can be understood that, in order to ensure that the conversion member 232 can climb smoothly, preferably, the number of segments is 2 to 7, and particularly advantageously, the number of segments is 3 - 4. In this embodiment, the number of segments of the climbing section 233a is preferably 3.

[0188] It should be noted that, as can be seen from the above introduction, the conversion member 232 and the curved surface guiding portion 233 are located between the ram 200 and the guiding member 210. Specifically, the conversion member 232 is located on one of the guiding member 210 and the ram 200, and the curved surface guiding portion 233 is located on the other of the guiding member 210 and the ram 200. As Figure 16-18 shown, in some other examples of the present invention, the conversion member 232 may be located on the guiding member 210, and the curved surface guiding portion 233 may be located on the ram 200. For example, a receiving groove 211 is provided on the inner peripheral wall of the guiding member 210, a part of the conversion member 232 may be located within the receiving groove 211, a curved surface guiding portion 233 may be provided on the outer peripheral wall of the ram 200, and another part of the conversion member 232 may cooperate with the curved surface guiding portion 233. As Figure 16-18As shown, in some other examples of the present invention, the conversion member 232 may be located on the guide member 210, and the curved surface guiding portion 233 is located on the ram 200. For example, a receiving groove 211 is provided on the inner peripheral wall of the guide member 210. A part of the conversion member 232 may be located in the receiving groove 211. A curved surface guiding portion 233 may be provided on the outer peripheral wall of the ram 200, and another part of the conversion member 232 may cooperate with the curved surface guiding portion 233. Thus, the assembly relationship between the conversion member 232, the curved surface guiding portion 233, the ram 200, and the guide member 210 can be realized. Therefore, by using the cooperation relationship between the conversion member 232 and the curved surface guiding portion 233 and the relative movement between the conversion member 232 and the curved surface guiding portion 233, the relative movement of the ram 200 relative to the guide member 210 can be realized, and the ram 200 can move relative to the transmission shaft 10 along the axis direction of the transmission shaft 10. The movement track of the conversion member 232 on the curved surface guiding portion 233 is the preset path of the ram 200.

[0189] As Figure 2 , Fig.16 and Fig.19 shown, in some embodiments of the present invention, the conversion member 232 may be set as a steel ball. As Figure 11-Figure 12 shown, preferably, in order to ensure the strength of the steel ball, the diameter of the steel ball is greater than 4 mm and less than or equal to 10 mm. More preferably, the diameter of the steel ball is greater than or equal to 4 mm and less than or equal to 6 mm. In this embodiment, the diameter of the steel ball is 5 mm. The curved surface guiding portion 233 may be set as a cam surface or a cam groove. Thus, the cam surface or the cam groove can define the movement track of the steel ball, and the steel ball can move inside the cam surface or the cam groove. The steel ball has a smooth outer surface, which can not only reduce the relative movement friction between the conversion member 232 and the curved surface guiding portion 233 and improve the movement smoothness of the conversion member 232 inside the curved surface guiding portion 233, but also has a large structural strength and good wear resistance of the steel ball, thereby ensuring the working performance of the intermittent impact assembly 230. It should be noted that the "cam" mentioned here may refer to that the curved surface guiding portion 233 protrudes from the inner peripheral wall of the guide member 210, or the curved surface guiding portion 233 protrudes from the outer peripheral wall of the ram 200.

[0190] Furthermore, the steel ball and the curved surface guiding portion 233 may be in point or line contact. It can be understood that during the movement of the steel ball inside the curved surface guiding portion 233, the contact between the steel ball and the curved surface guiding portion 233 is always a point or a line contact, which is beneficial to reducing the friction between the steel ball and the curved surface guiding portion 233. For example, the curvature radius of the cam surface may be basically the same as or slightly larger than the radius of the steel ball, so as to improve the cooperation degree between the steel ball and the cam surface, and further improve the assembly stability, wear resistance and service life of the steel ball and the cam surface.

[0191] The following will introduce the specific form of mode switching of the mode adjustment mechanism 40 of the handheld tool 1 in combination with the specific structure of the handheld tool 1.

[0192] As Figure 19-20 shown, in some embodiments of the present invention, the mode adjustment mechanism 40 includes a first tooth pattern 212 provided on the guide member 210, an impact switching member provided with a second tooth pattern 431. The impact switching member is fixedly arranged in the housing of the handheld tool 1 and can move axially but not rotate. Specifically, the impact switching member is an impact switching ring 430, and the impact switching ring 430 is movably sleeved on the ram 200. Among them, when the mode adjustment mechanism 40 is in the first mode state, the first tooth pattern 212 meshes with the second tooth pattern 431; when the mode adjustment mechanism 40 is in the second mode state, the first tooth pattern 212 is spaced apart from the second tooth pattern 431.

[0193] It can be understood that the impact switching ring 430 is sleeved on the ram 200, and the impact switching ring 430 and the ram 200 can move relative to each other. The impact switching ring 430 is provided with a second tooth pattern 431, and the guide member 210 is provided with a first tooth pattern 212. The first tooth pattern 212 and the second tooth pattern 431 can be cooperatively connected, so that the guide member 210 and the impact switching ring 430 can be connected. At this time, the impact switching ring 430 can limit the movement of the guide member 210, the guide member 210 and the impact switching ring 430 are relatively stationary, and the ram 200 can linearly move relative to the guide member 210 along a preset path and strike the tool spindle 30 in at least one operating state.

[0194] It is also possible to switch the position of the impact switching ring 430 so that the first tooth pattern 212 is spaced apart from the second tooth pattern 431. At this time, the guide member 210 is movable relative to the impact switching ring 430. Driven by the intermittent impact assembly 230, the guide member 210 can rotate together with the ram 200, and the ram 200 and the guide member 210 are relatively stationary. Thus, by adjusting the cooperation relationship between the first tooth pattern 212 and the second tooth pattern 431, the positional relationship and assembly relationship between the guide member 210 and the impact switching ring 430 can be adjusted, so that the movement state of the guide member 210 can be controlled, and further the movement state of the tool spindle 30 can be improved, so as to control the working mode of the handheld tool 1.

[0195] Furthermore, as Fig.19 、 Figure 21-26 shown, the mode adjustment mechanism 40 further includes a buffer member 440. One end of the buffer member 440 abuts against the impact switching ring 430 to constantly push the impact switching ring 430 to move towards the guide member 210. Thus, the buffer member 440 can constantly push the impact switching ring 430 close to the guide member 210, so that the first tooth pattern 212 and the second tooth pattern 431 can be cooperated.

[0196] Furthermore, if Figure 19-Figure 24 As shown, the mode adjustment mechanism 40 also includes a mode switching button 450, which is rotatably mounted on the impact switching ring 430. The mode switching button 450 is rotatable relative to the impact switching ring 430. The inner circumferential wall of the mode switching button 450 is provided with a guide block 451, and the outer circumferential wall of the impact switching ring 430 is provided with a matching block 432 matched with the guide block 451. The mode switching button 450 is rotated, wherein when the guide block 451 and the matching block 432 are axially abutted against each other, the guide block 451 pushes the impact switching ring 430 to compress the buffer 440 to move away from the guide member 210, and the first tooth pattern 212 is spaced apart from the second tooth pattern 431; when the guide block 451 and the matching block 432 are offset, the impact switching ring 430 moves toward the direction close to the guide member 210 under the action of the buffer 440, and the first tooth pattern 212 is meshed with the second tooth pattern 431.

[0197] It is understandable that the positional relationship between the mode switch button 450 and the impact switch ring 430 can be switched by rotating the mode switch button 450 or the impact switch ring 430 to change the matching state between the guide block 451 and the matching block 432. Thus, the matching relationship between the first tooth pattern 212 and the second tooth pattern 431 can be controlled by switching the matching relationship between the guide block 451 and the matching block 432. Fig. 20 As shown, the guide block 451 has a guide slope 451a to guide the matching block 432. Thus, the matching relationship between the guide block 451 and the matching block 432 can be conveniently switched.

[0198] In other embodiments of the present invention, the mode adjustment mechanism 40 may also adopt other structures. For details, see Figure 2-Figure 5 , Fig. 9 and Fig.13 The mode adjustment mechanism 40 includes a pressure stop ring 410 and a mode adjustment button 420. The pressure stop ring 410 is sleeved on the transmission shaft 10, specifically sleeved on the impact receiving portion 400, and the pressure stop ring 410 is rotatable but not axially movable relative to the transmission shaft 10, and the mode adjustment button 420 is rotatably sleeved on the pressure stop ring 410. The pressure stop ring 410 is provided with a stop portion 411, and the inner peripheral wall of the mode adjustment button 420 is provided with a channel 422 suitable for the stop portion 411 to pass through, and the channel 422 extends along the axial direction of the transmission shaft 10.

[0199] Among them, when the mode adjustment mechanism 40 is in the first mode state, the abutting portion 411 abuts against the mode adjustment knob 420; when the mode adjustment mechanism 40 is in the second mode state, the abutting portion 411 corresponds to the position of the channel 422, and the tool spindle 30 can drive the pressure retaining ring to move along the axial direction of the tool spindle. Thus, by adjusting the relative position relationship between the abutting portion 411 of the pressure retaining ring 410 and the mode adjustment knob 420, the movement state of the ram 200 can be adjusted, and thus the working mode of the tool spindle 30 can be adjusted. Specifically, as Figure 3-Figure 4 shown, the mode adjustment knob 420 further includes a flange 421 provided on the inner peripheral wall of the mode adjustment knob 420. The flange 421 is annular and extends along the circumferential direction of the pressure retaining ring 410, and the channel 422 penetrates through the flange 421 along the axial direction of the pressure retaining ring 410. Thus, the flange 421 can construct the channel 422, and the flange 421 can also abut against the abutting portion 411.

[0200] As Figure 3-Figure 4 shown, in some embodiments of the present invention, the abutting portion 411 includes a fixed section 411a, a connecting section 411b, and a mating section 411c. The fixed section 411a extends from the pressure retaining ring 410, one end of the connecting section 411b is connected to the fixed section 411a, one end of the mating section 411c is connected to the other end of the connecting section 411b, the mating section 411c is adapted to pass through the channel 422, and the fixed section 411a and the connecting section 411b are spaced apart along the axial direction of the pressure retaining ring 410. Further, the portion where the connecting section 411b is connected to the fixed section 411a is smoothly transitioned; or, the portion where the connecting section 411b is connected to the mating section 411c is smoothly transitioned.

[0201] As Figure 2 and Figure 6 shown, in some embodiments of the present invention, the outer peripheral wall of the impact receiving portion 400 has a stepped surface 404, and the pressure retaining ring 410 abuts against the stepped surface 404. Thus, the stepped surface 404 can limit the movement of the pressure retaining ring 410 and prevent the pressure retaining ring 410 from detaching from the impact receiving portion 400.

[0202] Embodiment 4

[0203] As Figure 1-Figure 30 shown, the handheld 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 switching ring 430.

[0204] Specifically, the rotation direction of the motor 60 includes a first direction and a second direction. One of the first direction and the second direction may be the clockwise direction, and the other is the counterclockwise direction. The motor 60 can drive the transmission shaft 10 to rotate. The tool spindle 30 is connected to the transmission shaft 10, and the tool spindle 30 is movable relative to the transmission shaft 10. For example, the tool spindle 30 can move relative to the transmission shaft 10. The hammer impact mechanism 20 includes a ram 200 and a guide member 210. The ram 200 is sleeved outside the transmission shaft 10, and the transmission shaft 10 can drive the ram 200 to rotate. According to the handheld tool 1 of the embodiment of the present invention, by providing the guide member 210 and the intermittent impact assembly 230, and utilizing the cooperation relationship among the intermittent impact assembly 230, the ram 200 and the guide member 210, the ram 200 can be guided to perform a linear motion, and the ram 200 can also impact the tool spindle 30, so that the movement in the axial direction of the tool spindle 30 can be realized. When the tool spindle 30 drills holes in an environmental component (such as a wall surface or a panel), the tool spindle 30 forms an impact force on the environmental component, thereby improving the drilling efficiency of the handheld tool 1. Moreover, the structure of the handheld tool 1 of the embodiment of the present invention is compact and simple in structure, and is convenient to carry.

[0205] As Figure 2 , Figure 5 , Figure 7 and Figure 9-12 shown, the intermittent impact assembly 230 includes an energy storage mechanism 231 in contact with the ram 200, and a conversion member 232 and a curved surface guiding portion 233 disposed between the guide member 210 and the ram 200. The intermittent impact assembly 230 further includes the energy storage mechanism 231. Both the conversion member 232 and the curved surface guiding portion 233 are located between the guide member 210 and the ram 200, and one end of the energy storage mechanism 231 is in contact with the ram 200. Thus, by constructing the specific shape of the curved surface guiding portion 233, the movement trajectory of the conversion member 232 can be guided. The conversion member 232 can be linked with the ram 200, and the ram 200 moves along the trajectory of the curved surface guiding portion 233 under the action of the conversion member 232.

[0206] Further, as Fig.13 and Figure 17-Figure 18 shown, a baffle 100 may be provided on the transmission shaft 10. The baffle 100 is sleeved on the outer peripheral wall of the transmission shaft 10. The energy storage mechanism 231 is located between the ram 200 and the baffle 100, and the end of the energy storage mechanism 231 away from the ram 200 can cooperate with the baffle 100. When the ram 200 moves a certain distance toward the energy storage mechanism 231, the ram 200 and the baffle 100 can compress the energy storage mechanism 231. Thus, the energy storage mechanism 231 can form a driving force on the ram 200. Of course, other structures can also be adopted for the axial limiting manner of the energy storage mechanism, which will not be elaborated here.

[0207] As Figure 11-Figure 12As shown, in some embodiments of the present invention, the curved surface guiding portion 233 may be formed in a ring shape. The curved surface guiding portion 233 may surround along the circumferential direction of the transmission shaft 10. Specifically, the curved surface guiding portion 233 may include a climbing section 233a and a dropping section 233b. One end of the dropping section 233b is connected to one end of the climbing section 233a, and the other end of the dropping section 233b extends towards the other end of the climbing section 233a. Further, the climbing section 233a may be in a spiral shape, and the dropping section 233b may be in a straight line shape and extend along the axial direction of the transmission shaft 10. Preferably, in order to ensure that the ram forms sufficient impact force on the tool spindle 30 and the volume of the hand tool 1 is compact, the climbing height of the climbing section 233a in the axial direction is greater than 3 mm and less than or equal to 15 mm. Preferably, the climbing height is greater than or equal to 4 mm and less than or equal to 8 mm. Preferably, the climbing height is 5 mm.

[0208] When the conversion member 232 cooperates with the climbing section 233a, the conversion member 232 rolls from one end of the climbing section 233a towards the other end of the climbing section 233a, and the ram 200 moves towards the baffle 100. The ram 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 climbing section 233a and rolls towards the dropping section 233b, the energy storage mechanism 231 can push the ram 200 to drop from the end of the dropping section 233b close to the baffle 100 towards the end of the dropping section 233b close to the tool head, that is, the ram 200 drops rapidly towards the direction away from the baffle 100 and close to the tool head. A part of the ram 200 approaches and impacts the part 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 ram 200 forms a hammering on the tool spindle 30 and the tool head.

[0209] Further, as Figure 7 、 Fig.15 shown, an installation groove 203 may be provided on the end face of the ram 200 close to the energy storage mechanism 231. The end of the energy storage mechanism 231 may be located in the installation groove 203, and the end of the energy storage mechanism 231 may abut against the bottom wall of the installation groove 203. Thereby, the assembly stability between the energy storage mechanism 231 and the ram 200 can be improved.

[0210] As Fig.12As shown, in some embodiments of the present invention, the curved surface guiding portion 233 may include multiple segments, and each segment includes a climbing segment 233a and a dropping segment 233b. There may be multiple conversion members 232, and the multiple conversion members 232 may be spaced apart along the circumferential direction of the ram 200. In this embodiment, to ensure the rationality of the overall design of the hand tool, the outer diameter of the middle ram 200 is between 15 mm and 50 mm. Preferably, the outer diameter of the ram is between 20 mm and 40 mm. The slope height is greater than 3 mm and less than or equal to 15 mm. Preferably, the climbing height is greater than or equal to 4 mm and less than or equal to 8 mm. More preferably, the climbing height is 5 mm. It can be understood that, to ensure that the conversion member 232 can climb smoothly, preferably, the number of segments is 2 to 7, and particularly preferably, the number of segments is 3 - 4. In this embodiment, the number of segments of the climbing segment 233a is preferably 3.

[0211] It should be noted that, as introduced above, the conversion member 232 and the curved surface guiding portion 233 are located between the ram 200 and the guiding member 210. Specifically, the conversion member 232 is located on one of the guiding member 210 and the ram 200, and the curved surface guiding portion 233 is located on the other of the guiding member 210 and the ram 200. As Figure 16-18 shown, in some other examples of the present invention, the conversion member 232 may be located on the guiding member 210, and the curved surface guiding portion 233 may be located on the ram 200. For example, a receiving groove 211 is provided on the inner peripheral wall of the guiding member 210. A part of the conversion member 232 may be located in the receiving groove 211. A curved surface guiding portion 233 may be provided on the outer peripheral wall of the ram 200, and another part of the conversion member 232 may cooperate with the curved surface guiding portion 233. As Figure 16-18 shown, in some other examples of the present invention, the conversion member 232 may be located on the guiding member 210, and the curved surface guiding portion 233 may be located on the ram 200. For example, a receiving groove 211 is provided on the inner peripheral wall of the guiding member 210. A part of the conversion member 232 may be located in the receiving groove 211. A curved surface guiding portion 233 may be provided on the outer peripheral wall of the ram 200, and another part of the conversion member 232 may cooperate with the curved surface guiding portion 233. Thus, the assembly relationship between the conversion member 232, the curved surface guiding portion 233 and the ram 200, the guiding member 210 can be realized. Therefore, by using the cooperation relationship between the conversion member 232 and the curved surface guiding portion 233 and the relative movement between the conversion member 232 and the curved surface guiding portion 233, the relative movement of the ram 200 relative to the guiding member 210 can be realized, and the ram 200 can move relative to the transmission shaft 10 along the axis direction of the transmission shaft 10. The movement track of the conversion member 232 on the curved surface guiding portion 233 is the preset path of the ram 200.

[0212] Please continue to refer to Fig.11 and Fig.12As shown, in the present invention, since the above-mentioned climbing section 233a and dropping section 233b are provided inside the guide member 210, when the motor 60 rotates forward, in the "impact mode", the ram 200 impacts the tool spindle 30 to achieve the hammering effect. However, when the motor 60 rotates in reverse, the above-mentioned conversion member 232 needs to cross the dropping section 233b and move to the climbing section 233a. However, in order to ensure the impact effect of the ram 200, the dropping section 233b is substantially parallel to the axis. Therefore, when the conversion member 232 rotates axially, the conversion member 232 cannot cross the dropping section 233b, resulting in "stalling" of the motor and even burning out of the machine.

[0213] Therefore, referring to Figure 28-Figure 30, the hand-held tool 1 further includes an impact ring 11a that is non-rotatably fixed to the housing 80. The impact ring 11a is provided with first end teeth 12a, and the guide member 210 is provided with second end teeth 213a that can engage with the first end teeth 12a. When the motor 60 rotates in the first direction, the first end teeth 12a limit the rotation of the guide member 213 through the second end teeth 213a that engage with them. The conversion member 232 moves along the curved surface guiding portion in a preset direction, causing the ram 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 teeth 213a and the guide member 213 rotate relative to the first end teeth 12a that engage with them under the drive of the motor 60, that is, the second end teeth 213a on the guide member 213 perform a climbing motion relative to the first end teeth 12a. The first end teeth 12a include a plurality of first tooth teeth 121a, and the first tooth teeth 121a include a guiding section 121b and a stopping section 121c. The guiding section 121b is connected to the free end of the stopping section 121c. The second end teeth 213a are composed of a plurality of second tooth teeth 2131a. When the motor 60 rotates in the first direction, the second tooth teeth 2131a move from the stopping section 121c to the guiding section 121b, and the stopping section 121c abuts against the second tooth teeth 2131a, so that the guide member 210 cannot rotate. When the motor 60 rotates in the second direction, when the second tooth teeth 2131a move from the guiding section 121b to the stopping section 121c, the second tooth teeth 2131a can move along the guiding section 121b, so that the guide member 213 rotates relative to the first end teeth 12a. The guiding section 121b and the stopping section 121c are sequentially arranged at intervals along the circumferential direction of the first end teeth 12a, and the stopping section 121c is parallel to the axis of the transmission shaft 10. When the second tooth teeth 2131a move from the stopping section 121c to the guiding section 121b, the side of the second tooth teeth 2131a that abuts against the stopping section 121c is parallel to the stopping section 121c. The impact ring 11a can move axially to achieve the engagement or separation of the first end teeth 12a and the second end teeth 213a. When the first end teeth 12a are separated from the second end teeth 213a, the guide member 210 rotates under the drive of the motor, and the tool is in a non-impact mode. It can be understood that in this embodiment, when the impact ring 11a can move axially, the impact ring 11a in this embodiment not only has the function of "preventing jamming", but also has the function realized by the impact switching ring 430 described in the above other embodiments of the present invention. In other words, in the above embodiments, by setting the tooth shapes of the first tooth pattern 212 and the second tooth pattern 431 in the above embodiments to the tooth shapes of the first tooth teeth 121a and the second tooth teeth 2131a in this embodiment, the mode switching mechanism 40 in the above embodiments not only has the mode switching function, but also has the function of preventing jamming in the impact mode.

[0214] Such as Figure 5 、 Figure 8-Figure 10 , Fig.13 and Fig.15 As shown in Figure 8-Figure 10 , Fig.13 and Fig.15 , according to some embodiments of the present invention, the hammer impact mechanism 20 further has a disengaging clutch mechanism 220, and the clutch mechanism 220 is arranged to transmit the rotational movement between the transmission shaft 10 and the ram 200. It can be understood that the clutch mechanism 220 can engage the transmission shaft 10 with the ram 200, and the clutch mechanism 220 can also disengage the transmission shaft 10 from the ram 200. When the clutch mechanism 220 engages the transmission shaft 10 with the ram 200, the rotational movement of the transmission shaft 10 can be transmitted to the ram 200 through the clutch mechanism 220, thereby driving the ram 200 to rotate; when the clutch mechanism 220 disengages the two, the mating relationship between the clutch mechanism 220 and the ram 200 is released, the transmission shaft 10 rotates relative to the ram 200, and the ram 200 is stationary relative to the guide member 210. Thus, the movement of the ram 200 can be controlled by the clutch mechanism 220, so as to control whether the ram 200 impacts the tool spindle 30, and further the working state of the hand-held tool 1 can be changed. In some embodiments of the present invention, the clutch mechanism 220 is arranged to be closed by a force transmitted through the tool spindle 30. It can be understood that whether there is a mating relationship between the clutch mechanism 220 and the ram 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 ram 200. For example, when the tool head or the tool spindle 30 abuts during the working condition (i.e., when the tool spindle 30 receives an axial load), the clutch mechanism 220 is closed, and the hand-held tool 1 is switched to the impact state.

[0215] As Figure 5 shown in Figure 5 , the tool spindle 30 can be switched between a first position and a second position relative to the transmission shaft 10 under the action of an axial force. When the tool spindle 30 is in the second position, the ram 200 can be driven by the transmission shaft 10 to rotate and can move along a preset path relative to the guide member 210, so as to impact 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 transmission shaft 10 cannot drive the ram 200 to rotate. The tool spindle 30 includes a connection end connected to the transmission shaft 10 and an output end connected to the tool head. A cavity 120 with an axial opening is provided on one side of the transmission shaft 10 close to the connection end. The cavity 120 can extend along the axial direction of the transmission shaft 10. The connection end of the tool spindle 30 extends into the cavity 120 from the opening. The inner wall of the cavity 120 and the outer wall of the connection end of the tool spindle 30 are engaged by splines 370 extending axially, so that the tool spindle 30 can axially move relative to the transmission shaft 10 and can rotate with the transmission shaft 10. Specifically, as Figure 2As shown, ribs 340 are provided on the outer wall of the tool spindle 30 and the inner wall of the cavity 120, and grooves 350 that are radially recessed are formed between adjacent ribs 340 on the tool spindle 30, so that the inner wall of the cavity 120 can cooperate with the grooves 350.

[0216] Continue to refer to Figure 5 , Figure 8-Figure 10 , Fig.13 and Fig.15 , a radial hole 110 is provided on the side wall of the cavity 120. The radial hole 110 penetrates the side wall 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 within the radial hole 110. The above-mentioned receiving portion 201 may be provided on the inner peripheral wall of the ram 200. Refer to Fig.13 and Fig.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 above-mentioned groove 350. The clutch member 221 moves along the radial hole 110 in a direction away from the receiving portion 201 of the ram 200 and closer to the groove 350, so that the clutch member 221 is disengaged from the ram 200; refer to Fig. 9 and Figure 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 above-mentioned radial hole 110, that is, there is no longer a space for receiving the clutch member 221 at the position on the tool spindle 30 corresponding to the radial hole 110. During the movement of the tool spindle 30, the tool spindle 30 squeezes the clutch member 221 so that the clutch member 221 moves along the radial hole 110 in a direction closer to the receiving portion 221 of the ram. A part of the clutch member 221 is located in the radial hole 110, and at the same time, another part is located in the receiving portion 201. The ram 200 can rotate together with the transmission shaft 10 under the action of the clutch member 221. It should be noted that in other embodiments of the present invention, the above-mentioned cavity 120 may also be located at the connection end of the tool spindle 30, and one end of the transmission shaft 10 connected to the tool spindle 30 extends into the cavity 120.

[0217] Embodiment 5

[0218] Next, refer to Figures 1 - 27 to describe in detail the hand tool 1 according to multiple embodiments of the present invention. It should be understood that the following description is only an exemplary illustration and not a specific limitation of the present invention.

[0219] As Figures 1 - 15 shown, the hand tool 1 according to the embodiment of the present invention includes a motor 60, a transmission shaft 10, a tool spindle 30, a reset member 70, a hammer impact mechanism 20, an impact receiving portion 400, a pressure retaining ring 410, and a mode adjustment knob 420.

[0220] Specifically, the motor 60 is connected to the transmission shaft 10. The motor 60 can drive the transmission shaft 10 to rotate along the axis direction of the transmission shaft 10, and the transmission shaft 10 rotates about its own axis. The transmission shaft 10 can be formed into a cylindrical shape with one end open, that is, the transmission shaft 10 can form a cavity 120 with one end open. The cavity 120 can extend along the axis direction of the transmission shaft 10. The tool spindle 30 can penetrate into the transmission shaft 10 from the open end of the cavity 120. The other end of the transmission shaft 10 can form a flat square 140, and torque transmission is carried out with the motor 60 through the flat square 140. The reset member 70 is located in the cavity 120, and one end of the reset member 70 is axially abutted against the tool spindle 30, and the other end of the reset member 70 is abutted against the bottom wall of the cavity 120 far from the opening. The reset member 70 can constantly push the tool spindle 30 to move from the bottom wall of the cavity 120 towards the opening end of the cavity 120.

[0221] As Figure 2 shown, one end of the tool spindle 30 close to the transmission shaft 10 can include a first section 310, a second section 320 and a third section 330. The first section 310 is connected to one end of the second section 320, and one end of the second section 320 is 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 penetrates into the cavity 120 of the transmission shaft 10. A part of the first section 310 can penetrate into the cavity 120, and another part of the first section 310 is located outside the cavity 120. The cross-sectional radius of the third section 330 is smaller than the cross-sectional radius of the first section 310. The outer peripheral wall of the second section 320 is an arc surface. A plurality of convex ribs 340 are provided on the outer peripheral wall of the third section 330. The plurality of convex ribs 340 are arranged at intervals along the circumferential direction of the third section 330. Any one of the convex ribs 340 extends along the axis direction of the third section 330. Any two adjacent convex ribs 340 can be configured to form a groove 350.

[0222] On the inner peripheral wall of the transmission shaft 10 corresponding to the cavity 120, a plurality of convex blocks can be provided. The plurality of convex blocks are arranged at intervals along the circumferential direction of the transmission shaft 10. Any one of the convex blocks extends along the axis direction of the transmission shaft 10. Any two adjacent convex blocks can be configured to form a mating groove. Any one of the convex ribs 340 corresponds to a mating groove, and each convex rib 340 can penetrate into its corresponding mating groove. When the transmission shaft 10 rotates, the convex rib 340 can abut against at least one of the two convex blocks corresponding to the mating groove, so as to drive the tool spindle 30 to rotate along the circumferential direction of the transmission shaft 10. In the axis direction of the transmission shaft 10, the tool spindle 30 can move relative to the transmission shaft 10, and the tool spindle 30 can complete sliding in the axis direction of the transmission shaft 10.

[0223] As Figure 5 、 Figures 8 - 10 and Figure 13 、 Figure 15As shown, the hammer impact mechanism 20 includes a ram 200, a guide member 210, a clutch mechanism 220, and an intermittent impact assembly 230. Among them, 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 guiding portion 233.

[0224] As Figure 5 , Figures 8 - 10 and Figure 13 , Figure 15 shown, the ram 200 is sleeved on the outer peripheral wall of the transmission shaft 10. The ram 200 is close to the end of the transmission shaft 10 away from the reset member 70. The inner peripheral wall of the ram 200 is spaced apart from the outer peripheral wall of the transmission shaft 10. Radial holes 110 may be provided on a part of the transmission shaft 10 sleeved inside the ram 200. The radial holes 110 penetrate the transmission shaft 10 in the radial direction of the transmission shaft 10. The clutch member 221 may be located in the radial holes 110 and the clutch member 221 may move in the radial holes 110. A receiving portion 201 may be provided on the inner peripheral wall of the ram 200. The receiving portion 201 may penetrate the ram 200 along the axial direction of the transmission shaft 10. The receiving portion 201 may be configured as a groove 201a. The groove 201a may be formed by recessing a part of the inner peripheral wall of the ram 200 towards the radial outside of the ram 200. The clutch member 221 may be configured as a steel ball. The diameter of the steel ball is greater than or equal to 3 mm and less than or equal to 8 mm. The bottom wall of the groove 201a may be formed as an arc surface, and the arc surface may be recessed towards the radial outside of the ram 200.

[0225] When the clutch mechanism 220 is in the closed state, when the steel ball moves between the transmission shaft 10 and the ram 200, that is, when a 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 201a, the part of the steel ball located in the groove 201a may cooperate and abut against the groove 201a. When the steel ball rotates with the transmission shaft 10, the steel ball may drive the ram 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 transmission shaft 10 and the tool spindle 30, that is, when a 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 350, the transmission shaft 10 is spaced apart from the ram 200, and the ram 200 is in a stationary state.

[0226] It should be noted that the position of the steel ball can be switched by the positional relationship between the tool spindle 30 and the transmission shaft 10. When the tool head is in the working state and bears the axial abutting force from the working condition, that is, when the tool spindle 30 moves towards the direction close to the reset member 70, the reset member 70 is compressed. The first section 310 of the tool spindle 30 is opposite to the through hole 110. The first section 310 will squeeze the steel ball, and the steel ball moves radially from the groove 350 into the groove body 201a along the through hole 110. A part of the steel ball cooperates with the through hole 110, and the other part cooperates with the groove body 201a. Thus, the ram 200 of the transmission shaft 10 rotates, and the clutch mechanism 220 is in the engaged state, and the hand 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 member 70. The tool spindle 30 moves from the first section 310 being opposite to the through hole 110 to the third section 330 being opposite to the through hole 110. Therefore, the first section 310 no longer squeezes the steel ball, and the steel ball moves along the through hole 110 into the groove 350 under the action of the ram 200 and disengages from the groove body 201a. The transmission shaft 10 cannot drive the ram 200 to rotate, and the clutch mechanism 220 is in the disengaged state. Refer to Figure 15 , in this embodiment, when the clutch mechanism 220 is in the disengaged state, the steel ball still 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.

[0227] As Figure 5 , Figures 8 - 10 and Figure 13 , Figure 15 As shown in

[0228] Refer to Figures 16 - 18 , different from the embodiment shown in Figures 1 - 15 , in other embodiments of the present invention, a receiving groove 211 may be provided on the inner peripheral wall of the guide member 210. A part of the conversion member 232 may be located within the receiving groove 211, and the conversion member 232 is connected to the guide member 210 (such as by snap connection). A curved surface guiding portion 233 may be provided on the outer peripheral wall of the ram 200, and another part of the conversion member 232 may cooperate with the curved surface guiding portion 233.

[0229] As Figure 5 , Figures 7 - 10, Figure 13 , Figure 15 , the end face of the ram 200 facing the reset member 70 may be provided with an installation groove 203. A baffle 100 may be provided on the transmission shaft 10. The baffle 100 is sleeved on the outer peripheral wall of the transmission shaft 10. The baffle 100 is connected to the transmission shaft 10 and is opposite to the installation 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 may extend into the installation groove 203. The end of the energy storage mechanism 231 may abut against the bottom wall of the installation groove 203. The other end of the energy storage mechanism 231 may abut against the baffle 100. The energy storage mechanism 231 may be set as an annular spring. The annular spring may be sleeved on the transmission shaft 10.

[0230] As Figure 2 , Figure 5 , Figure 1 , Figures 9 - 10 and Figure 13 shown, an embedding groove 202 may be provided on the outer peripheral wall of the ram 200. A part of the conversion member 232 may be located in the embedding groove 202 to connect the conversion member 232 with the ram 200. A part of the conversion member 232 located outside the embedding groove 202 may cooperate with the curved surface guiding portion 233 so that the conversion member 232 can move along the curved surface guiding portion 233, so that the ram 200 moves along the path of the curved surface guiding portion 233 under the driving of the rotational force of the transmission shaft 10.

[0231] When the conversion member 232 cooperates with the climbing section 233a, the conversion member 232 rolls from the other end of the climbing section 233a towards the one end of the climbing section 233a, and the ram 200 moves towards the baffle 100. The ram 200 and the baffle 100 may compress the energy storage mechanism 231; when the conversion member 232 is at one end of the climbing section 233a and rolls towards the falling section 233b, the energy storage mechanism 231 may constantly push the ram 200 to fall from one end of the falling section 233b towards the other end of the falling section 233b, and the ram 200 moves in a direction away from the baffle 100.

[0232] As Figure 5 , Figure 9 and Figure 13As shown, an impact receiving portion 400 may be provided on the tool spindle 30. 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 outside the first section 310 of the tool spindle 30. The impact receiving portion 400 is located outside the transmission shaft 10. The impact receiving portion 400 is connected to the tool spindle 30 (such as by clamping or welding). After the ram 200 moves a certain distance in the direction away from the baffle 100, the ram 200 may contact the impact receiving portion 400. And due to the pushing action of the energy storage mechanism 231, the ram 200 may form an impact effect on the impact receiving portion 400, so that the tool spindle 30 may move in the axial direction of the transmission shaft 10 in the direction away from the reset member 70.

[0233] Since the environmental components (such as walls or flat plates) drilled by the hand-held tool 1 have a load effect on the tool spindle 30, the tool spindle 30 will move in the direction close to the reset member 70. In this way, 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 also move in the axial direction of the transmission shaft 10 under the impact action of the ram 200 and the external force of the environmental components.

[0234] The above introduces that when the hand-held tool 1 is in the working state, that is, when the tool head is under the action of the axial force, the hand-held tool 1 can realize the hammering function. However, in actual operation, in some working conditions, the operator does not need the hammering function. Therefore, the hand-held tool of the present invention also has a mode adjustment mechanism 40.

[0235] As Figure 6 shown, the outer peripheral wall of the impact receiving portion 400 may include a first surface 401, a second surface 402 and a third surface 403. One end of the first surface 401 is connected to the second surface 402, and the other end of the second surface 402 is connected to the third surface 403. The extending directions of the first surface 401 and the third surface 403 are the same. The first surface 401 and the third surface 403 are spaced apart in the radial direction of the impact receiving portion 400. The first surface 401 is located radially outside the third surface 403. The first surface 401, the second surface 402 and the third surface 403 are configured as a stepped surface 404. A pressure retaining ring 410 is sleeved outside the impact receiving portion 400 corresponding to the third surface 403. The impact receiving portion 400 corresponding to the first surface 401 can axially limit the pressure retaining ring 410 on the third surface 403.

[0236] As Figures 3 - 6As shown, the mode adjustment knob 420 is rotatably sleeved on the pressure stop ring 410. The pressure stop ring 410 is provided with a stop portion 411, and the inner peripheral wall of the mode adjustment knob 420 is provided with a flange 421. The flange 421 is annular and extends along the circumferential direction of the pressure stop ring 410. The flange 421 can form a channel 422, and the channel 422 penetrates the flange 421 along the axial direction of the pressure stop ring 410. The stop portion 411 can pass through the channel 422.

[0237] As Figures 3 - 4 shown, the stop portion 411 includes a fixed section 411a, a connecting section 411b, and a mating section 411c. The fixed section 411a extends from the pressure stop ring 410. One end of the connecting section 411b is connected to the fixed section 411a, and one end of the mating section 411c is connected to the other end of the connecting section 411b. The mating section 411c is adapted to pass through the channel 422. The fixed section 411a and the connecting section 411b are spaced apart along the axial direction of the pressure stop ring 410. The connection part between the connecting section 411b and the fixed section 411a has a smooth transition, and the connection part between the connecting section 411b and the mating section 411c has a smooth transition.

[0238] Among them, when the stop portion 411 abuts against the mode adjustment knob 420, the pressure stop ring 410 is stationary relative to the mode adjustment knob 420. The pressure stop ring 410 further abuts against the impact receiving portion 400 corresponding to the first surface 401, and the impact receiving portion 400 is stationary. The impact receiving portion 400 further limits the movement of the tool spindle 30. The external force applied by the 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 ram 200 is spaced apart from the transmission shaft 10. The motor 60 drives the transmission shaft 10 to rotate, and the transmission shaft 10 further drives the tool spindle 30 to rotate. The tool spindle 30 only has rotational movement.

[0239] When the stop portion 411 is located in the channel 422, the stop 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 member 70, and further drives the clutch member 221 to be placed between the transmission shaft 10 and the ram 200. The transmission shaft 10 can drive the ram 200 to rotate. The ram 200 can move along the axial direction of the transmission shaft 10 under the cooperation of the conversion member 232 and the curved surface guiding portion 233, and strike the impact receiving portion 400. The impact receiving portion 400 can further drive the pressure stop ring 410 to move within the inner ring of the mode adjustment knob 420. The tool spindle 30 has both axial movement and circumferential rotation.

[0240] In other embodiments of the present invention, the mode adjustment mechanism 40 can also be other structures.

[0241] Different from Figures 1 - 15 the embodiment shown, inFigures 19 - 26 In the illustrated embodiment, the mode adjustment mechanism 40 includes an impact switching ring 430, a buffer 440 and a mode switching button 450. Specifically, the guide member 210 has a first tooth pattern 212, and the mode adjustment mechanism 40 includes an impact switching ring 430, which is movably mounted on the hammer 200, and the impact switching ring 430 has a second tooth pattern 431 that matches the first tooth pattern 212. One end of the buffer 440 abuts against the impact switching ring 430 to push the impact switching ring 430 toward the guide member 210. The mode switching button 450 is rotatably mounted on the impact switching ring 430, and the mode switching button 450 is rotatable relative to the impact switching ring 430. The inner peripheral wall of the mode switching button 450 is provided with a guide block 451, and the outer peripheral wall of the impact switching ring 430 is provided with a matching block 432 that matches the guide block 451, and the impact switching ring 430 is axially movable but non-rotatably fixed to the housing.

[0242] Rotate the mode switch button 450, wherein when the guide block 451 and the matching block 432 are against each other, the first tooth pattern 212 and the second tooth pattern 431 are spaced apart. At this time, the guide member 210 is movable relative to the impact switching ring 430. Driven by the intermittent impact assembly 230, the guide member 210 can rotate along with the hammer 200. The hammer 200 and the guide member 210 are relatively stationary. Therefore, the hammer 200 will not hit the tool spindle 30; continue to rotate the mode switch button 450, when the guide block 451 and the matching block 432 are offset, the first tooth pattern 212 and the second tooth pattern 431 are engaged, so that the guide member 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 member 210. The guide member 210 and the impact switching ring 430 are relatively stationary. The hammer 200 can move linearly relative to the guide member 210 along a preset path and hit the tool spindle 30 in at least one operating state. In this embodiment, the axial movement of the impact switching ring 430 is achieved by rotating the mode switch 450. In other embodiments, in order to achieve the axial movement of the impact switching ring, a dial button connected to the impact switching ring 430 can also be provided, and the axial movement of the impact switching ring 450 can be directly driven by turning the dial button.

[0243] like Figure 20As shown, the first tooth pattern 212 includes a protruding portion 212a. The second tooth pattern 431 includes a guide section 431a and a stop section 431b. The guide section 431a may include a straight section and an inclined section. One end of the inclined section is connected to the free end of the stop section 431b, and the other end of the inclined section is connected to one end of the straight section. The stop section 431b extends along the axial direction of the impact switching ring 430, and the straight section is perpendicular to the stop section 431b. There may be multiple stop sections 431b, and the multiple stop sections 431b may be arranged at intervals along the circumferential direction of the guide member 210. There is a guide section 431a between any two adjacent stop sections 431b, and the two ends of any guide section 431a are respectively connected to two adjacent stop sections 431b. There may be multiple protruding portions 212a, and the multiple protruding portions 212a correspond to the multiple stop sections 431b one by one. The protruding portion 212a may be formed into a triangle. The free end of the protrusion 212 a may be formed as a tip 212 a 1 .

[0244] Among them, when the motor 60 rotates forward, there are two situations, one of which is: the guide block 451 and the matching block 432 are against each other, and the first tooth pattern 212 and the second tooth pattern 431 are spaced apart. At this time, the guide member 210 is movable relative to the impact switching ring 430, and the guide member 210 can rotate with the hammer 200 under the drive of the intermittent impact assembly 230, and the hammer 200 and the guide member 210 are relatively stationary; the other situation is: when the guide block 451 and the matching block 432 are staggered, the protrusion 212a and the stop section 431b are stop-stopped, and the first tooth pattern 212 and the second tooth pattern 431 are relatively stationary, so that the guide member 210 and the impact switching ring 430 can be connected. At this time, the impact switching ring 430 can limit the movement of the guide member 210, and the guide member 210 and the impact switching ring 430 are relatively stationary. The hammer 200 can make linear motion relative to the guide member 210 according to a preset path and impact the tool spindle 30 in at least one operating state. When the motor 60 reverses, the protrusion 212a can slide along the guide section 431a, and relative rotation can be formed between the first tooth pattern 212 and the second tooth pattern 431. The guide member 210 can rotate relative to the impact switching ring 430, and the guide member 210 can rotate with the hammer 200.

[0245] In the related art, when the first tooth pattern 212 is in contact with the second tooth pattern 431, the guide member 210 and the impact switching ring 430 are relatively stationary. When the motor 60 is reversed, the conversion member 232 stops at the drop section 233b, which will hinder the rotation of the motor 60, thereby damaging the performance of the guide member 210 and the motor 60, and affecting the service life of the handheld tool 1. Compared with the related art, the handheld tool 1 of the embodiment of the present invention considers more factors and has good safety performance.

[0246] and Figure 20 The embodiment shown is different in thatFigures 28 - 30 In the illustrated embodiment, the hand-held tool 1 further includes an impact ring 11a that is non-rotatably fixed to the housing 80. The impact ring 11a is provided with first end teeth 12a, and the guide member 210 is provided with second end teeth 213a that can engage with the first end teeth 12a. When the motor 60 rotates in the first direction, the first end teeth 12a limit the rotation of the guide member 213 through the second end teeth 213a engaged therewith, and the conversion member 232 moves along the curved surface guiding portion in a preset direction to cause the ram 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 teeth 213a and the guide member 213 rotate relative to the first end teeth 12a engaged therewith under the drive of the motor 60, that is, the second end teeth 213a on the guide member 213 perform a climbing motion relative to the first end teeth 12a. The first end teeth 12a include a plurality of first teeth 121a, and the first teeth 121a include a guiding section 121b and a stopping section 121c. The guiding section 121b is connected to the free end of the stopping section 121c. The second end teeth 213a are composed of a plurality of second teeth 2131a. When the motor 60 rotates in the first direction, the second teeth 2131a move from the stopping section 121c to the guiding section 121b, and the stopping 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, when the second teeth 2131a move from the guiding section 121b to the stopping section 121c, the second teeth 2131a can move along the guiding section 121b, so that the guide member 213 rotates relative to the first end teeth 12a. The guiding section 121b and the stopping section 121c are sequentially arranged at intervals along the circumferential direction of the first end teeth 12a, and the stopping section 121c is parallel to the axis of the transmission shaft 10. When the second teeth 2131a move from the stopping section 121c to the guiding section 121b, the side of the second teeth 2131a abutting against the stopping section 121c is parallel to the stopping section 121c. The impact ring 11a can move axially to achieve the engagement or separation of the first end teeth 12a and the second end teeth 213a. When the first end teeth 12a are separated from the second end teeth 213a, the guide member 210 rotates under the drive of the motor, and the tool is in a non-impact mode. It can be understood that in this embodiment, when the impact ring 11a can move axially, the impact ring 11a in this embodiment not only has the function of "preventing jamming", but also has the functions realized by the impact switching ring 430 described in the above other embodiments of the present invention.

[0247] Refer to Figure 31As shown, when the present invention provides another embodiment, in this embodiment, the ram 200 is sleeved outside the transmission shaft 10, and the clutch member 221 is used to selectively rotatably connect the transmission shaft 10 and the ram 200. The rotation of the ram 200 relative to the guide member 210 realizes the axial movement of the ram 200, and at the same time compresses the spring, that is, the energy storage mechanism for energy storage. When the ram 200 completes climbing, under the action of the energy storage mechanism, it moves rapidly along the axis of the tool spindle 30 towards the free end of the tool spindle 30, thereby realizing the axial impact on the tool spindle 30. During the process of the ram 200 impacting the tool spindle 30, there is a surface on the end face of the ram 200 facing the free end of the tool spindle 30 that contacts the tool spindle 30, and this surface is called the "impact surface" on the ram 200. In this embodiment, the impact surface 2001 on the ram 200 protrudes outward relative to other surfaces on the end face of the ram 200 on the side facing the free end of the tool spindle 30. That is to say, on the end face of the ram 200 on the side facing the free end of the tool spindle 30, it is a stepped end face, and the impact surface 2001 in contact with the tool spindle 30 is higher than other end faces, that is, the impact surface 2001 is closer to the free end of the tool spindle 30 relative to other end faces. Compared with the impact surface being lower than other end faces, the advantage of the impact surface being higher than other end faces is that higher impact efficiency and better impact effect can be obtained. The higher impact efficiency and better impact effect are mainly reflected in the reduction of the loss of impact energy during the impact process. Here, the free end of the tool spindle 30 refers to the end of the tool spindle 30 close to the working head, that is, the end of the tool spindle far from the motor.

[0248] In this embodiment, the ram 200 is located on the inner circumferential side of the guide member 210, and the curved surface guiding portion 233 is arranged between the ram 200 and the guide member 210. Compared with the scheme where the ram is distributed on the outer circumferential side of the guide member, this technical solution can make the impact surface 2001 on the ram 200 closer to the axis of the tool spindle 30, and thus higher impact efficiency can be obtained, that is, less energy loss will occur during the impact process.

[0249] In addition, if the diameter range of the impact surface on the ram can match the diameter of the tool spindle, the impact effect can also be improved to a certain extent, that is, the energy loss during the impact process will be reduced. In this embodiment, the selectable range of the diameter of the impact surface 2001 on the ram 200 is 6 - 25 mm. The so-called matching of the diameter of the impact surface on the ram and the tool spindle means that during the impact process of the impact surface on the ram and the tool spindle, the part of the end face of the tool spindle in contact with the impact surface can be called the impacted surface, and the diameter of the impact surface on the ram and the diameter of the impacted surface on the tool spindle are kept as consistent as possible, which can be understood as matching.

[0250] If the ram 200 directly abuts against the transmission shaft 10, during the axial movement of the ram 200 relative to the transmission shaft 10, due to the contact friction during the long-term cooperation between the ram 200 and the clutch member 221 to transmit torque, barbs will be generated on the inner surface of the ram 200, thus affecting the axial movement of the ram 200. In particular, the impact energy output from the ram 200 to the tool spindle 30 will be reduced. To solve the above problems, in this embodiment, the following technical solutions are provided: The ram 200 is linearly movably supported on the inner circumferential surface of the guide member 210. Further, a clearance fit can also be provided between the ram 200 and the transmission shaft 10. Specifically, a clearance is provided between the inner surface of the ram 200 and the outer surface of the transmission shaft 10. For example, the unilateral clearance can be 0.1 mm to 0.2 mm. Of course, the specific value of this small clearance is not limited to the above example, and the present application does not make a specific limitation here.

[0251] In this embodiment, the ram 200 is linearly movably supported on the inner circumferential surface of the guide member 210, and the guide member 210 is fixed to the housing of the hand tool. It can also be said that the ram 200 is supported on the housing.

[0252] In other embodiments, when the ram is located outside the guide member, that is, the ram surrounds the guide member, the ram can also be linearly movably supported on the housing of the hand tool. In this embodiment, the guide member located inside the ram can be rotated, and the ram only moves linearly and does not rotate. The curved surface guiding portion can be provided on the inner circumferential side of the ram, and the conversion member, that is, the steel ball, is provided on the outer circumferential surface of the guide member. In this way, the rotation of the guide member can drive the axial movement of the ram through the curved surface guiding portion and the conversion member, and further enable the ram to impact the tool spindle under the action of the energy storage mechanism.

[0253] In the present invention, as the component to be impacted, the lower the mass of the tool spindle, the smaller the energy loss during the impact process. However, the smaller the mass of the tool spindle, one technical solution to make the mass of the tool spindle small is to reduce the diameter of the tool spindle, that is, to reduce the volume of the tool spindle. In this way, to a certain extent, the strength of the tool spindle will be affected. To enable the tool spindle to maintain as high a strength as possible under the conditions of small size and mass, the present invention provides a technical solution. Refer to Figure 31As shown in the figure, in this embodiment, the main function of the tool spindle 30 is to rotatably connect with the transmission shaft 10. Therefore, the rotating connection is also the place with the highest strength requirement. In this embodiment, the connection method between the tool spindle 30 and the transmission shaft 10 adopts a hexagonal shape mating, that is, the tool spindle 30 is an external hexagonal cylinder, and the transmission shaft 10 is an internal hexagonal aperture. The external hexagon of the tool spindle 30 is mated with the internal hexagon hole of the transmission shaft 10 to achieve the rotational connection. In this embodiment, the position of the internal hexagonal aperture of the transmission shaft 10 is set on the side close to the free end of the tool spindle 30. Correspondingly, the position of the external hexagonal cylinder of the tool spindle 30 is set on the side corresponding to the internal hexagonal aperture and close to the free end of the tool spindle. The advantage of this setting is that the connection mechanism with high strength requirements is set at the middle position or the position slightly forward of the middle of the tool spindle 30 to reduce the probability of the tool spindle strength failure. Here, "forward" refers to being close to the free end of the tool spindle.

[0254] It should be noted that in the hand-held tool of the present invention, the hand-held tool includes a transmission mechanism, a hammer impact mechanism, and a tool spindle. Among them, the transmission mechanism includes a transmission shaft that rotates and outputs after passing through a motor and a gear reduction mechanism. The tool spindle is rotationally driven by the transmission shaft, and the tool spindle can rotationally drive the working head to achieve the rotational operation of the hand-held tool. Moreover, the tool spindle also needs to bear the impact of the hammer impact mechanism, and then can transmit the axial impact to the working head. The hammer impact mechanism includes an impact shaft, and the impact shaft can drive one of the ram and the guide member to rotate. The rotational drive of the impact shaft can be directly or indirectly realized by the transmission shaft. Here, the impact shaft can drive one of the ram and the guide member to rotate, which can be understood as that under the drive of the impact shaft, the ram can rotate relative to the guide member, so that relative rotation can occur between the ram and the guide member, and then the ram can climb relative to the guide member, so that it can impact the tool spindle under the drive of the energy storage mechanism. In different embodiments, it can be that the ram rotates and the guide member does not rotate, or it can be that the ram does not rotate and the guide member rotates. No matter which embodiment, the impact shaft is the element that drives the rotating movement, and then relative rotation is achieved between the two.

[0255] In the present invention, the tool spindle, the transmission shaft, and the impact shaft have corresponding functions. In the present invention, the three shafts with the above corresponding functions are indispensable. However, in other embodiments, the tool spindle can also act as the impact shaft, that is to say, there will be a shaft with two functions: it can both rotationally drive the working head and drive the ram to rotate relative to the guide member. In other embodiments, the transmission shaft can also act as the impact shaft, that is to say, the transmission shaft not only drives the rotation of the tool spindle, but also can drive one of the ram and the guide member to rotate.

[0256] In the description of this specification, the description with reference to terms such as "one embodiment", "some embodiments", "schematic embodiments", "examples", "specific examples", or "some examples" means that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described may be combined in any one or more embodiments or examples in a suitable manner.

[0257] Although the embodiments of the present invention have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, substitutions, and variations can be made to these embodiments without departing from the principles and spirit of the present invention, and the scope of the present invention is defined by the claims and their equivalents.

Claims

1. A hand-held tool, comprising a motor, a tool spindle having a central axis, a transmission shaft driven by the motor to rotate, and a hammer impact mechanism capable of providing an axial impact to the tool spindle; The hammer impact mechanism includes a relatively rotatable ram and a guide member, and an energy storage mechanism in contact with the ram. One of the ram and the guide member is provided with a curved surface guiding portion, and the other of the ram and the guide member is provided with a conversion member. When the ram rotates relative to the guide member, the curved surface guiding portion drives the ram to move in a first direction against the acting force of the energy storage mechanism through the conversion member; the energy storage mechanism drives the ram to move in a second direction opposite to the first direction, so that the ram generates an impact force on the tool spindle in the axial direction of the transmission shaft, realizing the movement of the tool spindle in the central axis direction; It is characterized in that: The hammer impact mechanism includes an impact shaft, and the impact shaft can drive one of the ram and the guide member to rotate; The transmission shaft is non-rotatably connected to the impact shaft.

2. The hand-held tool according to claim 1, It is characterized in that: The transmission shaft and the impact shaft are integrally provided.

3. The hand-held tool according to claim 2, It is characterized in that: The transmission shaft is selectively rotatably connected to the ram.

4. The hand-held tool according to claim 3, It is characterized in that: A first clutch member is provided between the transmission shaft and the ram. The first clutch member is movably provided on one of the transmission shaft and the ram, and a first receiving portion is provided on the other of the transmission shaft and the ram; the cooperation between the first clutch member and the first receiving portion can realize the rotational connection between the transmission shaft and the ram, and when the first clutch member is separated from the first receiving portion, the transmission shaft and the ram can rotate relative to each other.

5. The hand-held tool according to claim 1, It is characterized in that: The tool spindle and the impact shaft are integrally provided.

6. The hand-held tool according to claim 5, It is characterized in that: The tool spindle is selectively rotatably connected to the ram.

7. The hand-held tool according to claim 6, It is characterized in that: A second clutch member is provided between the tool spindle and the ram. The second clutch member is movably provided on one of the tool spindle and the ram, and a second receiving portion is provided on the other of the tool spindle and the ram; the cooperation between the second clutch member and the second receiving portion can realize the rotational connection between the tool spindle and the ram, and when the second clutch member is separated from the second receiving portion, the tool spindle and the ram can rotate relative to each other.

8. The hand-held tool according to claim 1, It is characterized in that: The ram surrounds the tool spindle, the transmission shaft and the impact shaft in at least one plane.

9. The hand-held tool according to claim 8, It is characterized in that: The guide member surrounds the ram in at least one plane.

10. The hand-held tool according to claim 1, It is characterized in that: The ram is provided with an impact surface facing the tool spindle, and the impact surface can contact the tool spindle during the impact process. The impact surface is closer to the rotation axis of the tool spindle than the curved surface guide portion.

11. The hand tool according to claim 10, wherein: The guide sleeve is sleeved outside the ram, the curved surface guide portion is arranged on the inner circumferential surface of the guide sleeve, and the conversion member is arranged on the outer circumferential surface of the ram.

12. The hand tool according to claim 10, wherein: The ram has an end surface facing the tool spindle, and the impact surface is closer to the free end of the tool spindle than the end surface.

13. The hand tool according to claim 1, wherein: The curved surface guide portion includes a plurality of climbing sections and corresponding dropping sections. When the conversion member passes through the climbing sections, the conversion member drives the ram to move in the first direction against the acting force of the energy storage mechanism; when the conversion member passes through the dropping sections, the energy storage mechanism drives the ram to move in the second direction opposite to the first direction so as to impact the tool spindle; the number of the conversion members is the same as the number of the climbing sections.

14. The hand tool according to claim 1, wherein: The energy storage mechanism is arranged as an elastic member.

15. A hand tool, comprising a motor, a housing accommodating the motor, a tool spindle, a transmission shaft driven by the motor to rotate, and a hammer impact mechanism capable of providing an axial impact to the tool spindle; wherein: The hammer impact mechanism includes a relatively rotatable ram and a guide member, an impact shaft rotatably connected to the transmission shaft, and an energy storage mechanism abutted against the ram. A curved surface guide portion is arranged on one of the ram and the guide member, and a conversion member is arranged on the other of the ram and the guide member. In the impact mode, one of the ram and the guide member is driven by the impact shaft to rotate relative to the other. The curved surface guide portion drives the ram to move in the first direction along the central axis of the tool spindle against the acting force of the energy storage mechanism through the conversion member; the energy storage mechanism drives the ram to move in the second direction opposite to the first direction along the central axis of the tool spindle, so that the ram generates an impact force on the tool spindle in the axial direction of the transmission shaft, and realizes the movement of the tool spindle in the central axis direction; The ram is linearly supported on the housing.

16. The hand tool according to claim 15, wherein: The guide sleeve is sleeved outside the ram. In the impact mode, the guide member is fixedly arranged relative to the housing, the ram is driven by the impact shaft to rotate relative to the guide member, and the ram is linearly supported on the inner circumferential surface of the guide member.

17. The hand tool according to claim 16, wherein: The curved surface guide portion is arranged on the inner circumference of the guide member, and the conversion member is arranged on the outer circumference of the ram.

18. The hand tool according to claim 15, wherein: The drive shaft is integrally provided with the impact shaft.

Images