WO2019158114A1

WO2019158114A1 - Handheld power tool

Info

Publication number: WO2019158114A1
Application number: PCT/CN2019/075127
Authority: WO
Inventors: 谢明健; 李佶; 钟红风; 张士松; 毋宏兵
Original assignee: 苏州宝时得电动工具有限公司
Priority date: 2018-02-14
Filing date: 2019-02-14
Publication date: 2019-08-22
Also published as: EP3753676A1; CN209774563U; CN110153965A; EP3753676A4

Abstract

A hammer impact mechanism (20), a handheld power tool (1) having the hammer impact mechanism, and an attachment having the hammer impact mechanism. The hammer impact mechanism comprises a hammer (200) and a guide member (210) capable of rotating relative to each other, and an energy storage mechanism (231) abutting the hammer. One of the hammer and the guide member is provided with a curved guide portion (233), and the other is correspondingly provided with a conversion member (232). The curved guide portion comprises a plurality of upward sections (232a) and downward sections (232b) corresponding to the upward sections. When the conversion member passes the upward section, the conversion member drives the hammer to overcome the force of the energy storage mechanism to move in a first direction. When the conversion member passes the downward section, the energy storage mechanism drives the hammer to move in a second direction opposite to the first direction to implement an impact. The relative rotational speed of the hammer rotating relative to the guide member is 1000 to 2500 rpm. The ratio of the impact frequency of the hammer to the relative rotational speed is 2 to 4 times per rotation.

Description

Hand-held power tool

Technical field

The present invention relates to a hand-held power tool, and more particularly to a hand-held power tool having an axial impact function.

Background technique

In impact drill products with axial impact, the impact structure will have different impact effects. The traditional impact structure is used to move the static end teeth. The main impact force comes from the operator's application of the abutting force between the tool spindle and the working surface. The moving end teeth fixedly connected with the tool spindle form an axial climbing along the static end teeth. The axial movement of the tool spindle. Compared with the impact structure of the static and dynamic end teeth, the active impact structure has greater impact force. During the impact process, the axial impact on the tool spindle is realized by the active impact structure, instead of relying on the operator to the tool spindle. The application of abutting force between the working faces. The common active impact structure has a cam-type active impact structure, that is, the impact drill utilizes a cam structure to cause the ram to perform a ramping compression spring energy storage before the impact, and then the spring releases the stored energy to the ram to make the ram along the shaft. The rapid movement and the impact on the tool spindle, the above-mentioned actions are repeated under the continuous rotation of the cam structure, thereby providing an intermittent axial impact force to the tool spindle. Therefore, the active impact technology is a technology that replaces the traditional dynamic and static end-tooth impact technology to achieve high efficiency, high impact force and user experience of impact drilling, and how to obtain more in the development of active impact structure. High drilling efficiency is also a major problem and opportunity in related fields, and it also provides some room for improvement.

Summary of the invention

The invention provides a hand-held impact drill with high impact drilling efficiency. Among them, through the selection of the number of cam climbing tracks in the active impact structure and the selection of the spindle speed range of the tool, the two parameters are optimally combined to achieve high impact drilling efficiency for the hand tool device with impact function. , which enhances the user experience.

The present invention provides a technical solution: a hammer impact mechanism comprising a relatively rotatable ram and a guide member, and an energy storage mechanism abutting the ram, the ram and the guide member thereof One of the curved guide portions is disposed on the other of the guide members, and the curved guide portion includes a plurality of climbing sections and a falling section corresponding to the climbing section. When the conversion member passes the climbing section, the conversion member drives the ram to move in a first direction against the force of the energy storage mechanism; when the conversion member passes the drop segment, the The energy storage mechanism drives the ram to move in a second direction opposite to the first direction to achieve an impact; the relative rotational speed of the ram relative to the rotation of the guide is 1000-2500 rpm, and the impact frequency of the ram is The ratio of the relative rotational speeds is 2-4 times per revolution.

Preferably, the number of the climbing sections comprises 2-4.

Preferably, the number of the climbing sections includes three.

Preferably, the climbing section includes a starting point and an ending point, and the distance between the starting point and the ending point on the axis is 4-15 mm.

Preferably, the distance is preferably 4-8 mm.

Preferably, the curved guide portion is circumferentially disposed on an inner circumferential surface of the guide member, and the conversion member is disposed on an outer circumferential surface of the ram.

Preferably, the guiding member has an end surface perpendicular to the moving direction of the ram, and the climbing section has a climbing angle of 5-25 degrees with respect to the end surface.

Preferably, the drop section is disposed obliquely and extends in a direction away from the climbing section along a circumferential direction of the guide.

The present invention also provides another technical solution: a hand-held power tool comprising the hammer impact mechanism of claim 1, a motor, and a tool spindle; the tool spindle has an axis, and the tool spindle is The motor is driven to rotate about the axis, and the ram can intermittently impact the tool spindle along the axis.

Preferably, the relative rotational speed is the same as the rotational speed of the tool spindle.

Preferably, the hammer impact mechanism further includes an impact shaft capable of driving the ram to rotate relative to the guide, the impact shaft being rotationally driven by the motor.

Preferably, the hand tool device further includes a buffer member having one end in contact with the housing of the hand-held power tool and the other end contacting the end surface of the ram with the free end of the tool spindle, the buffer member being capable of The second direction produces an extrusion deformation.

Preferably, the cushioning member is compressed by the ram in the second direction by a maximum amount of 2 mm.

Preferably, the distance is preferably 4-8 mm.

Preferably, the cushioning member is a rubber member or a spring.

Preferably, the hand-held power tool further includes a transmission shaft that drives rotation of the tool spindle, and the hammer impact mechanism further includes an impact shaft that drives relative rotation of the ram relative to the guide member, the transmission shaft and the transmission shaft The rotation speed of the impact shaft is the same.

Preferably, the transmission shaft is disposed coaxially with the impact shaft.

Preferably, the hand-held power tool further includes a drive shaft that drives rotation of the tool spindle, the ram surrounding the drive shaft and the tool spindle in at least one plane.

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

The present invention also provides another technical solution: an accessory having an impact function for detachably connecting with a hand-held power tool main body, characterized in that the accessory comprises the hammer of claim 1. An impact mechanism, and a tool spindle; the tool spindle having an axis about which the tool spindle is rotatable, the hammer being capable of intermittently impacting the tool spindle along the axis.

Preferably, the accessory includes an accessory housing for receiving the hammer impact mechanism, the hand-held power tool body including a tool housing that is connectable to the tool housing.

Preferably, the hand-held power tool main body includes a transmission shaft that is rotated and output by a transmission, and the transmission shaft is rotatably coupled to the tool main shaft.

Preferably, the hammer impact mechanism includes an impact shaft capable of driving the ram to rotate relative to the guide member, the impact shaft being rotatably coupled to the output shaft.

Preferably, the impact shaft has no rotational connection with the tool spindle.

Preferably, the accessory further includes a connecting shaft, one end of the connecting shaft is rotatably connected to the output shaft, and the other end is connected to the impact shaft without a relative rotation.

Preferably, the impact shaft is selectively connectable to the ram without rotation.

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

Preferably, the attachment further includes a mounting assembly for mounting the working head to the tool spindle, the mounting assembly being detachably connectable to the tool spindle.

In the cam type hammer impact mechanism, if the rotational speed of the ram relative to the guide member is too high, the conversion member, that is, the falling position of the steel ball in this embodiment will fall on the climbing section of the next climbing track. , in turn, cause certain harm. If the rotational speed of the ram relative to the guide member is too low, the number of hits per ram during the unit time will be reduced, that is, the accumulated striking energy per unit time will be reduced, thereby reducing the impact force of the tool in the impact mode. In addition, regarding the steel ball collision orbit problem, there is another influencing factor is the number of climbing tracks. The larger the number of climbing tracks, the greater the probability that the steel ball will hit the track. Therefore, the number of climbing tracks needs to be The speed of the ram is linked to determine the probability of a steel ball hitting the track.

"Steel ball hitting track" refers to the case where the steel ball as the connecting member falls in the climbing section of the next cycle section when falling from the highest point of the climbing section in the cycle section in the impact mode. Here, the steel ball is only a preferred embodiment as a coupling, and in other preferred forms, different options are also possible.

Among them, there are two hazards of the steel ball hitting the track: First, it affects the impact efficiency of this time, that is, the energy saved by the spring during the climbing of the steel ball will be caused by the steel ball hitting the climbing section of the climbing track. A certain amount of energy loss is generated. Second, the long-term impact of the steel ball and the cam track's climbing track will cause the climbing track to deform, affecting the straightness of the axial movement of the ram in the guiding member, which will affect the reliability and life of the cam-type impact structure.

In the structural design with the same rotation speed of the tool spindle and the ram, when the rotation speed of the tool spindle is too high, the rpm speed is too high, and the probability of the steel ball hitting the track is increased. When the rotation speed of the tool spindle is too low, on the one hand, the ram speed is low, so that the accumulated energy per unit time is insufficient, and the breaking force in the impact mode is insufficient. On the other hand, the rotation speed of the tool spindle is too low, which causes the rotation speed of the working head to be low, the chip removal ability is poor, and the drilling resistance is large, which leads to low drilling efficiency.

Therefore, in the design structure in which the tool spindle and the ram speed are the same, in order to obtain the highest possible drilling efficiency without the link hitting the rail, the rotational speed value of the tool spindle has an optimal range, which cannot be too high. Otherwise, it will cause the steel ball to hit the track. On the other hand, it will also bring about the stall phenomenon caused by the insufficient torque of the ram in the overshoot. However, the speed should not be too low, otherwise the slamming speed will be too low, resulting in insufficient energy and insufficient breaking force. In addition, in order to avoid the occurrence of steel ball collision orbit, the rotation speed of the tool spindle needs to be combined with the number of climbing rails.

The number of hill-climbing tracks distributed over a circle also affects the probability of the steel ball hitting the track. The reason is explained as follows: If there are too many orbital periods distributed on one circumference, that is, the number of graded orbits is too large, the arc length of each track will be reduced, and the horizontal distance of the steel ball will not change, resulting in impact. The probability of the track increases. The case of hitting the track here refers to the phenomenon that the ram strikes the steel ball in contact with the track during the high-speed movement.

In order to alleviate the "steel ball hitting track", the present invention provides another technical solution, in which a horizontal section is added in the period of the curved surface guiding portion, so that each period segment includes a horizontal section, a climbing section and a falling section, and a horizontal section The falling section is located on both sides of the climbing section, that is, the starting point and the ending point of the climbing section are respectively connected to the horizontal section and the falling section. By increasing the horizontal section to increase the flight distance of the steel ball, thereby reducing the probability of the steel ball hitting the track.

In addition, during the operation of the impact mode, when the tool spindle is separated from the working surface, a noise similar to the impact will occur. After analysis, it is found that the steel ball is driven by the hammer at the highest point of the climbing track. The impact sound generated by the high-speed moving movement between the ball and the track.

In order to solve the above problems, the present invention provides another technical solution, in the path of the ram moving in the impact direction, a cushioning member is arranged between the ram and the casing, so that the steel ball and the climbing rail before the high-speed impact will The energy saved by the compression spring is unloaded. The technical solution is that the hand tool device further includes a buffer member capable of deforming along a moving direction of the ram, one end of the buffer member is in contact with the housing, and the other end of the buffer member It is in contact with the end surface of the ram.

The invention also proposes a hand-held tool, which can optimize the internal structure under the premise of ensuring high impact efficiency, the body is compact and compact, the operation is convenient, and the user experience is better.

The above object of the present invention can be achieved by the following technical solutions: a hand tool comprising at least two modes of operation, an impact mode and a non-impact mode, comprising: a housing; a power mechanism disposed on the housing; a motor and a motor driven transmission mechanism; a tool spindle having a central axis, the tool spindle being driven by the transmission mechanism and rotating about the central axis; the tool spindle having a first end remote from the power mechanism and Close to the second end of the power mechanism, the first end is provided with a collet for mounting the working head; the hammer impact mechanism comprises: a ram, a guiding member, and one of the ram and the guiding member a curved guide portion on the upper side, a conversion member disposed on the other, and an energy storage mechanism abutting against the ram; in the impact mode, the ram is rotated relative to the guide member, and the curved guide portion passes through The conversion member can drive the ram to move in a first direction along the central axis against the urging force of the energy storage mechanism, and the energy storage mechanism can drive the ram along the middle The axis moves in a second direction opposite the first direction to impact the tool spindle; in the non-impact mode, the ram does not rotate relative to the guide; the hand tool is configured to adjust the work a mode adjustment mechanism of the mode, the mode adjustment mechanism at least partially radially overlapping the hammer impact mechanism; the housing including a first housing portion for receiving the hammer impact mechanism, the first housing portion The radial dimensions range from 45 mm to 70 mm.

Preferably, the mode adjustment mechanism radially overlaps at least a portion of at least one of the guide member and the ram.

Preferably, the mode adjustment mechanism includes an impact switching ring and a mode switching button, the mode switching button operatively driving the impact switching ring to move between a first position and a second position; In a position, the impact switching ring is engaged with the hammer impact mechanism, the guide member and the ram can be rotated relative to each other, the hand tool is in an impact mode; and the impact switching ring is in the second position. The impact switching ring is separated from the hammer impact mechanism, the relative rotation between the guiding member and the ram is not possible, the hand tool is in a non-impact mode; the impact switching ring and the mode switching button are At least one of the guide members at least partially overlaps the radial direction.

Preferably, the guiding member is provided with a first tooth pattern, and the impact switching ring is provided with a second tooth pattern. In the impact mode, the first tooth pattern is engaged with the second tooth pattern; In the impact mode, the first dent is disengaged from the second ridge.

Preferably, the mode switching button is rotatably connected to the housing, the impact switching ring has no relative rotational connection with respect to the housing, and the mode switching button drives the impact switching ring along a central axis of the tool spindle mobile.

Preferably, the hammer impact mechanism comprises an impact shaft, the impact shaft is disposed between the transmission mechanism and the tool spindle, the ram is sleeved outside the impact shaft, and the impact shaft can drive the The ram is rotated and has no rotational connection with the tool spindle.

Preferably, the guiding member is sleeved on an outer side of the ram.

Preferably, the ram is movably supported on an inner circumferential surface of the guide member along the central axis.

Preferably, the guiding member is a hollow cylinder, and the curved guiding portion is disposed on an inner wall of the guiding member, and an outer wall of the ram is provided with an insertion groove for mounting the conversion member.

Preferably, the energy storage mechanism is an elastic member, and the curved surface guiding portion is a cam surface formed on an inner wall of the guiding member, the cam surface has a climbing portion and a falling portion, and the conversion member is The elastic member accumulates elastic potential energy during the movement of the climbing section toward the falling section; the elastic member releases the elastic potential energy when the switching member is dropped from the climbing section to the falling section Driving the ram to impact the tool spindle.

Preferably, the ratio of the outer diameter of the hammer impact mechanism to the radial dimension of the first casing portion is between 0.6 and 0.9.

Preferably, the power mechanism outputs a rotation speed equal to the rotation speed of the impact shaft, wherein the impact shaft can drive the hammer to rotate relative to the guide member; the mode adjustment mechanism and the hammer impact mechanism At least partially axially overlapping.

Preferably, the mode adjustment mechanism is provided with an impact switching ring that at least partially axially overlaps the guide of the hammer impact mechanism.

Preferably, the hand tool body has an axial length of 185 mm to 250 mm.

Preferably, the hand tool body has an axial length of 190 mm to 230 mm.

Preferably, the curved guiding portion is provided with a plurality of climbing sections and a falling section corresponding to the climbing section in a circumferential direction, and when the conversion member passes the climbing section, the ram strikes One direction of movement; when the conversion member passes the drop section, the ram moves in a second direction to achieve an impact, and the number of the climbing sections is 2 to 4.

As can be seen from the technical solutions provided by the embodiments of the present application, the hand tool provided by the present application is used in the hand tool by providing a power mechanism, a tool spindle, and a hammer impact mechanism having an intermittent impact assembly, a ram and a guide. In the case of impact drilling, the tool spindle rotates about the central axis, and the ram reciprocates along the central axis direction when the intermittent impact assembly cooperates with the guide member, periodically impacting The tool spindle forms an active impact, wherein since the hammer impact mechanism is arranged at the first casing portion, the radial dimension of the first casing portion can be controlled between 45 mm and 70 mm, as a whole The compact and compact body makes it easy to operate and has a better user experience.

The additional aspects and advantages of the invention will be set forth in part in the description which follows.

The invention provides a hand-held tool, which improves the impact energy by controlling the quality of the component, thereby ensuring that the hand tool has high impact efficiency and improves the user experience.

The above object of the present invention can be achieved by the following technical solutions: a hand tool comprising: a power mechanism; a tool spindle having a central axis, the tool spindle being driven by the power mechanism and rotating about the central axis; The tool spindle has a first end remote from the power mechanism and a second end adjacent to the power mechanism, the first end is provided with a chuck for mounting a working head; the tool spindle has a mass range of 40 grams to Between 100 grams; a hammer impact mechanism comprising: a ram, a guide, a curved guide disposed on one of the ram and the guide, a conversion member disposed on the other, and the ram The abutting energy storage mechanism, when the ram is rotated relative to the guiding member, the curved guiding portion moves the ram against the urging force of the energy storage mechanism in a first direction by the conversion member, The energy storage mechanism drives the ram to move in a second direction opposite the first direction; in the case of the hand tool for impact drilling, the tool spindle rotates about the central axis The striker reciprocates in the axial direction of the central periodically strike the tool spindle.

Preferably, the hand tool further includes a transmission shaft disposed between the power mechanism and the tool spindle, the ram is sleeved outside the transmission shaft and is matched with the transmission shaft. The drive shaft can simultaneously drive the ram and the tool spindle to rotate.

Preferably, the hand tool further includes a transmission shaft, wherein the transmission shaft is a hollow rotary body, and a portion of the tool spindle adjacent to the first end protrudes into the transmission shaft, and a mass range of the tool spindle is preferably The guiding member is sleeved on the outer side of the ram.

Preferably, the ram is movably supported on an inner circumferential surface of the guide member.

Preferably, the first end of the tool spindle is provided with a mounting hole for engaging the working head, and an outer side of the first end of the tool spindle is provided with a mounting accessory, and the mounting hole and the mounting accessory are formed In a quick-change chuck for mounting the working head, a sum of masses of the quick-change chuck and the tool spindle ranges from 50 g to 150 g; the working head is snapped into the quick-change clip After the head, it can move along the central axis.

Preferably, the first end of the tool spindle is provided with a jaw type by means of a fixed connection, and the sum of the mass of the jaw type chuck and the tool spindle ranges between 120 grams and 450 grams.

Preferably, the jaw type chuck comprises: a core body fixed at one end to the first end of the tool spindle, an operating shell sleeved outside the core body, and a collet connected to the core body, The density of the core ranges from 1 g/cm ³ to 8 g/cm ³ .

As can be seen from the technical solutions provided by the embodiments of the present application, the hand tool provided by the present application is used in the hand tool by providing a power mechanism, a tool spindle, and a hammer impact mechanism having an intermittent impact assembly, a ram and a guide. In the case of impact drilling, the tool spindle rotates about the central axis, and the ram reciprocates along the central axis direction when the intermittent impact assembly cooperates with the guide member, periodically impacting The tool spindle forms an active impact. In order to obtain as much impact energy as possible for the impacted part, the tool spindle is controlled to have a mass range between 40 grams and 100 grams.

The present invention provides a hand tool that has the advantage of high work efficiency.

The above object of the present invention can be achieved by the following technical solutions: a hand tool comprising: a motor; a drive shaft driven by the motor to rotate about an axis of the drive shaft; a tool spindle, by the drive a shaft rotation drive; a hammer impact mechanism having a ram that can reciprocally impact the tool spindle in an axial direction of the tool spindle; and a collet that is fixedly coupled to the tool spindle; The ram strikes the tool spindle reciprocally in an axial direction of the tool spindle in at least one operating state, the chuck including a core fixedly coupled to the tool spindle, the material of the core being fabricated The density is from 1 g/cm3 to 5 g/cm3, and the hand tool has a rated torque of less than or equal to 55 Nm.

Preferably, the core is made of an aluminum alloy material.

Preferably, the collet further includes a claw and a locking ring, the locking ring is sleeved on the core, and the claw for clamping the tool head is disposed at an end of the core.

Preferably, the jaws have a density of from 5 g/cm3 to 8 g/cm3.

Preferably, the hammer impact mechanism includes a guide member rotatable relative to the ram, and an energy storage mechanism abutting the ram, one of the ram and the guide member being provided with a curved surface a guide portion, the other of the ram and the guide member is provided with a conversion member, the curved surface guide portion includes a plurality of climbing sections and a falling section, when the ram is rotated relative to the guiding member, The climbing section drives the ram to move in a first direction against the urging force of the energy storage mechanism by the conversion member, and the energy storage mechanism drives the energy storage mechanism when the conversion member passes the falling section The ram moves in a second direction opposite to the first direction to effect an impact.

Preferably, the hammer impact mechanism further includes a detachable clutch mechanism, the clutch mechanism being configured to transmit a rotational motion.

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

Preferably, the ratio of the rotational speed value of the tool spindle to the maximum power value of the motor is greater than or equal to 174.

The present invention also provides a technical solution: a chuck attachment, comprising: a chuck, a tool spindle, the tool spindle fixedly connected with the chuck; and a hammer impact mechanism having a ram, the ram Capturing the tool spindle reciprocally in an axial direction of the tool spindle; the chuck attachment for detachably connecting with an output shaft of the hand tool body, wherein: the guide member is operated in at least one of the hammers The tool reciprocally impacts the tool spindle in an axial direction of the tool spindle, the chuck including a core fixedly coupled to the tool spindle, and the material of the core is made to have a density of 1 g/cm 3 to 5 g / Cm3, the hand tool has a rated torque of less than or equal to 55 Nm.

Preferably, the core is made of an aluminum alloy material.

DRAWINGS

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

2 is an exploded view of a partial structure of a hand tool according to an embodiment of the present invention;

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

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

Figure 5 is a cross-sectional partial structural view of a hand tool according to an embodiment of the present invention;

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

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

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

9 is a partial cross-sectional structural view of a hand tool according to an embodiment of the present invention;

Figure 10 is an enlarged view of the structure at D in Figure 9;

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

Figure 12 is a cross-sectional structural view of a guide of a hand tool according to an embodiment of the present invention;

Figure 13 is a cross-sectional partial structural view of a hand tool according to an embodiment of the present invention;

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

Figure 15 is an enlarged view of the structure at F in Figure 13;

Figure 16 is an exploded view of a partial structure of a hand tool according to an embodiment of the present invention;

Figure 17 is a cross-sectional partial structural view of a hand tool according to an embodiment of the present invention;

Figure 18 is a cross-sectional partial structural view of a hand tool according to an embodiment of the present invention;

19 is an exploded view of a partial structure of a hand tool according to an embodiment of the present invention;

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

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

Figure 22 is an enlarged view of the structure at G in Figure 21;

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

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

Figure 25 is a cross-sectional partial structural view of a hand tool according to an embodiment of the present invention;

Figure 26 is a cross-sectional partial structural view of a hand tool according to an embodiment of the present invention;

Figure 27 is a cross-sectional structural view of a hand tool according to an embodiment of the present invention;

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

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

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

Figure 31 is a partial cross-sectional view showing the output shaft in a depressed position in accordance with an embodiment of the present invention;

Figure 32 is a partial cross-sectional view of the output shaft in a release position in accordance with an embodiment of the present invention;

Figure 33 is a developed perspective view of a curved surface guiding portion according to an embodiment of the present invention;

Figure 34 is a partial cross-sectional view showing the ram in a first state in an impact mode in accordance with an embodiment of the present invention;

Figure 35 is a partial cross-sectional view showing the ram in a second state in an impact mode in accordance with an embodiment of the present invention;

Figure 36 is a partial cross-sectional view showing the ram in a third state in an impact mode in accordance with an embodiment of the present invention;

Figure 37 is a schematic view showing the assembly of the attachment and the tool body in accordance with an embodiment of the present invention;

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

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

Detailed ways

The present invention will be further described in detail below with reference to the accompanying drawings and embodiments. It is understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.

It is to be noted that, unless otherwise defined, when an element is referred to as "in" another element, it can be directly on the other element or a central element. When an element is considered to be "connected" to another element, it can be directly connected to the other element or. The terms "vertical", "horizontal", "left", "right", and the like, as used herein, are for the purpose of illustration and are not intended to be the only embodiment. The "speed" or "rotation speed" as used herein refers to the rotational speed or rotational speed of the corresponding component of the tool under no-load conditions.

All technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs, unless otherwise defined. The terminology used in the description of the present invention is for the purpose of describing particular embodiments and is not intended to limit the invention. The term "and/or" used herein includes any and all combinations of one or more of the associated listed items.

In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", " After, "Left", "Right", "Vertical", "Horizontal", "Top", "Bottom", "Inside", "Outside", "Clockwise", "Counterclockwise", "Axial", The orientation or positional relationship of the "radial", "circumferential" and the like is based on the orientation or positional relationship shown in the drawings, and is merely for convenience of description of the present invention and simplified description, and does not indicate or imply the indicated device or component. It must be constructed and operated in a particular orientation, and is not to be construed as limiting the invention. Furthermore, features defining "first" and "second" may include one or more of the features, either explicitly or implicitly. In the description of the present invention, "a plurality" means two or more unless otherwise stated.

In the description of the present invention, it should be noted that the terms "installation", "connected", and "connected" are to be understood broadly, and may be fixed or detachable, for example, unless otherwise explicitly defined and defined. Connected, or integrally connected; can be mechanical or electrical; can be directly connected, or indirectly connected through an intermediate medium, can be the internal communication of the two components. The specific meaning of the above terms in the present invention can be understood in a specific case by those skilled in the art.

Example 1

As shown in FIGS. 1-26, 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.

Specifically, as shown in FIGS. 2, 5, 9, 13, 17 - 18, 21, 23, and 25 - 26, the motor 60 can drive the drive shaft 10 to rotate, and the drive shaft 10 It is rotatable about the axis of the drive shaft 10. The hammer impact mechanism 20 includes a ram 200 that is sleeved on the outside of the propeller shaft 10 and that can be driven to rotate by the propeller shaft 10. It can be understood that the motor 60 is coupled to the drive shaft 10, and the term "connected" as used herein may mean that the motor 60 is directly coupled to the drive shaft 10, for example, the output of the motor 60 may be directly coupled to the end of the drive shaft 10. "Connected" may also mean that the motor 60 is indirectly coupled to the drive shaft 10. For example, the motor 60 may be directly coupled to the intermediate drive assembly and directly coupled to the drive shaft 10 via the intermediate drive assembly.

The motor 60 can drive the drive shaft 10 to rotate, i.e., the motor 60 can drive the drive shaft 10 to rotate about its central axis. The ram 200 can be jacketed on the outer wall of the drive shaft 10, and the ram 200 can be coupled with the drive shaft 10, and the drive shaft 10 can further rotate the ram 200 about the axis of the drive shaft 10. It should be noted that the term “connection” as used herein may 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 shown in FIGS. 5-9, the hand tool 1 further includes a tool spindle 30. One end of the tool spindle 30 is coupled to the drive shaft 10, the other end is used to connect the tool head, and the tool spindle 30 is movable relative to the drive shaft 10, and the tool spindle 30 is movably coupled to the drive shaft 10, for example, the tool spindle 30 is movable relative to the drive shaft 10 in the axial direction of the drive shaft 10 and is non-rotatably coupled, that is, the tool spindle 30 is driven by the drive shaft 10. Turn. It should be noted that, as shown in FIG. 27 , the ram 200 in the embodiment may be sleeved on the outside of the tool spindle 30 or partially sleeved on the outside of the tool spindle 30 , and a part of the ram 200 may be sleeved on the outside of the transmission shaft 10 .

As shown in FIGS. 2, 5-13, the hammer impact mechanism 20 further includes a guide 210 disposed outside the ram 200, and an intermittent impact assembly 230. When the ram 200 rotates, the intermittent impact assembly 230 directs the ram 200 to move linearly relative to the guide 210 in a predetermined path and strike the tool spindle 30 in at least one operating state. In other words, the hammer impact mechanism 20 includes the ram 200, the guide 210, and the intermittent impact assembly 230, and the guide 210 is sheathed to the outer peripheral wall of the ram 200. Preferably, in order to enable the hammer 200 to generate the required hammering force when striking the tool spindle 30, the weight of the hammer 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 make the tool The mass is not too heavy, and at the same time the structure of the complete machine is compact. Preferably, the weight of the ram 200 is less than or equal to 60% of the sum of the weights of the collet 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 collet 50 and the tool spindle 30.

As shown in FIGS. 25-26, the tool spindle 30 is fixedly coupled to the collet 50 by means of a screw connection. Specifically, in the present embodiment, the tool spindle 30 is provided with an external thread 300 near the end of the collet 50, and the collet is provided. The screw 50 is internally provided with a threaded hole 500 that is coupled to the external thread 300. The tool spindle 30 and the collet 50 are coupled to the threaded hole 500 by the external thread 300. It should be noted that the motor 60 drives the tool spindle 30 to rotate in the first direction (forward direction) or in the second direction (reverse direction) opposite to the first direction, in order to prevent the tool spindle 30 and the chuck 50 from being The threaded connection is disengaged during operation, and a reverse screw 90 is further disposed between the collet 50 and the tool spindle 30. Here, the "reverse screw 90" means the thread direction on the screw and the thread of the external thread 300 described above. The opposite direction. In this type of connection, the hammering force of the hammer 200 against the tool head needs to be transmitted to the tool head via the reverse screw 90, that is, the hammer 200 transmits the hammering force to the tool spindle 30, and then passes through the tool spindle 30. It is transmitted to the counter-screw 90, and finally the hammer force is transmitted to the tool head by the counter-screw 90, and thus the hammering force transmitted to the tool head by the ram 200 is largely lost.

Accordingly, the present invention also provides another way of connecting the tool spindle 30 to the collet 50. Referring to Figure 21, this type of connection is eliminated compared to the above-described connection between the tool spindle 30 and the collet 50. The reverse screw 90 prevents the tool spindle 30 from being disengaged from the tool head during operation by applying an adhesive between the external thread 300 and the threaded hole 500. At the same time, the front end of the tool spindle 30 has a projection (not shown) ) for abutting the tool head so that the impact can be transmitted directly from the tool spindle 30 to the tool head, reducing energy loss during impact.

When the ram 200 rotates, the intermittent impact assembly 230 can control the movement path of the ram 200, and the movement path can both rotate the ram 200 in the circumferential direction of the transmission shaft 10, and can cause the ram 200 to follow the transmission. The axis 10 is moved in the axial direction so that the ram 200 can strike the tool spindle 30, thereby completing the movement of the tool spindle 30 relative to the drive shaft 10.

According to the hand tool 1 of the embodiment of the present invention, by providing the guiding member 210 and the intermittent impact assembly 230, the intermittent impact assembly 230, the tamper 200 and the guiding member 210 can be used to guide the ram 200 for linear motion and collide. The hammer 200 can also strike the tool spindle 30 so that movement of the tool spindle 30 in the axial direction can be achieved such that when the tool spindle 30 is drilled on an environmental component such as a wall or panel, the tool spindle 30 impacts the environmental components. Therefore, the drilling efficiency of the hand tool 1 can be improved, and the hand tool 1 of the embodiment of the invention has a compact structure and a simple structure, and can be conveniently carried.

As shown in FIG. 2, FIG. 5, FIG. 7 and FIG. 9 to FIG. 12, according to some embodiments of the present invention, the intermittent impact assembly 230 includes an energy storage mechanism 231 that abuts the ram 200 and is disposed on the guide 210 and collides with A conversion member 232 and a curved guide portion 233 between the hammers 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 guide 210 and the ram 200, and one end of the energy storage mechanism 231 abuts against the ram 200. Thus, the specific shape of the curved surface guiding portion 233 can be configured to guide the movement trajectory of the conversion member 232, the conversion member 232 can be interlocked with the ram 200, and the ram 200 can be along the curved guiding portion under the action of the conversion member 232. Track motion of 233.

Further, as shown in FIG. 13 and FIG. 17 to FIG. 18, the transmission shaft 10 may be provided with a baffle 100. The baffle 100 is sheathed on the outer peripheral wall of the propeller shaft 10. The accumulator mechanism 231 is located at the ram 200 and the baffle 100. Between the one end of the accumulator mechanism 231 away from the ram 200 can be engaged with the baffle 100. When the ram 200 is moved a certain distance toward the energy storage mechanism 231, the ram 200 and the shutter 100 can compress the energy storage mechanism 231. Thereby, the energy storage mechanism 231 can form a urging force for the ram 200. Of course, other structures may be adopted for the axially defining manner of the energy storage mechanism 231, and details are not described herein again.

As shown in FIGS. 11-12, in some embodiments of the present invention, the curved surface guiding portion 233 may be formed in an annular shape, and the curved surface guiding portion 233 may be circumferentially wound in the circumferential direction of the transmission shaft 10, specifically, the curved surface guiding portion 233. A climbing section 233a and a falling section 233b may be included, 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 is extended toward the other end of the climbing section 233a. Further, the climbing section 233a may be in a spiral shape, the falling section 233b may be in a straight line shape, and the falling section 233b may extend in the axial direction of the transmission shaft 10. Preferably, in order to ensure that the ram 200 forms a sufficient impact force on the tool spindle 30, and the volume of the hand tool 1 is compact, the climbing 233a has a climbing height in the axial direction of more than 3 mm and less than or equal to 15 mm, preferably, climbing The height is greater than or equal to 4 mm and less than or equal to 8 mm, and 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 axial direction of the transmission shaft 10.

When the switching member 232 is engaged with the climbing portion 233a, the switching member 232 rolls from one end of the climbing portion 233a toward the other end of the climbing portion 233a, and the ram 200 moves toward the shutter 100, and the hammer 200 and the shutter 100 can be compressed. The energy storage mechanism 231; when the conversion member 232 is located at the other end of the climbing section 233a and rolling toward the falling section 233b, the energy storage mechanism 231 can push the ram 200 from the falling section 233b toward the end of the shutter 100 toward the falling section 233b to approach the tool. The other end of the head is dropped, that is, the ram 200 is quickly dropped away from the baffle 100 and in the direction of the tool head, and a portion of the ram 200 approaches and strikes a portion of the tool spindle 30 located outside the drive shaft 10, thereby causing the tool spindle 30 to be opposed The drive shaft 10 is moved in the axial direction of the drive shaft 10, and the ram 200 forms a hammering of the tool spindle 30 and the tool head.

Further, as shown in FIG. 7 and FIG. 15, the end surface of the ram 200 adjacent to the energy storage mechanism 231 may be provided with a mounting groove 203, and the end of the energy storage mechanism 231 may be located in the mounting groove 203, and the end of the energy storage mechanism 231 The portion may abut against the bottom wall of the mounting groove 203. Thereby, the assembly stability of the energy storage mechanism 231 and the ram 200 can be improved.

As shown in FIG. 12, in some embodiments of the present invention, the curved guide portion 233 may include a plurality of segments, each segment including a climbing segment 233a and a falling segment 233b. The conversion member 232 may be plural, and the plurality of conversion members 232 may be spaced apart in the circumferential direction of the ram 200. In order to ensure the rationality of the overall design of the hand tool 1, the outer diameter of the middle ram 200 is between 15 mm and 50 mm, preferably, the outer diameter of the ram 200 is between 20 mm and 40 mm, and the climbing height is greater than 3 mm and less than Equal to 15 mm, preferably, the climbing height is greater than or equal to 4 mm and less than or equal to 8 mm, and 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 segment 233a is preferably 3

It should be noted that, as described 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 between the guiding member 210 and the ram 200, and the curved surface is guided. The portion 233 is located at the other of the guide member 210 and the ram 200. As shown in FIGS. 16-18, in other examples of the present invention, the conversion member 232 may be located on the guide member 210, and the curved guide portion 233 is located on the ram 200. For example, the inner peripheral wall of the guiding member 210 is provided with a receiving groove 211, and a part of the switching member 232 may be located in the receiving groove 211. The outer peripheral wall of the ram 200 may be provided with a curved guiding portion 233, and another part of the converting member 232 may be The curved surface guiding portion 233 is fitted. As shown in FIGS. 16-18, in other examples of the present invention, the conversion member 232 may be located on the guide member 210, and the curved guide portion 233 is located on the ram 200. For example, the inner peripheral wall of the guiding member 210 is provided with a receiving groove 211, and a part of the switching member 232 may be located in the receiving groove 211. The outer peripheral wall of the ram 200 may be provided with a curved guiding portion 233, and another part of the converting member 232 may be The curved surface guiding portion 233 is fitted. Thereby, the assembly relationship between the conversion member 232 and the curved surface guiding portion 233 and the ram 200 and the guide member 210 can be realized, so that the cooperation relationship between the conversion member 232 and the curved surface guiding portion 233 and the conversion member 232 and the curved surface guiding portion 233 can be utilized. The relative movement between the rams 200 relative to the guide 210 can be achieved, and the ram 200 can be moved relative to the drive shaft 10 in the axial direction of the drive shaft 10. The trajectory of the movement of the conversion member 232 at the curved surface guiding portion 233 is the preset path of the ram 200.

In this embodiment, the ram 200 rotates, the guide member 210 is fixed, and the rotation of the ram 200 and the curved guide portion 233 relative to the guide member 210 causes the ram 200 to move in the axial direction, thereby being under the action of the energy storage mechanism 231. Impact motion is applied to the tool spindle 30. During the impact movement, the conversion member 232 provided on the inner circumferential surface of the guide member 210 does not move in position, and may rotate in the accommodation groove 211, but no relative positional movement occurs.

As shown in FIG. 2, FIG. 16, and FIG. 19, in some embodiments of the present invention, the conversion member 232 may be provided as a steel ball, as shown in FIGS. 11-12, preferably, in order to ensure the strength of the steel ball, steel The diameter of the ball is greater than 4 mm and less than or equal to 10 mm, and more preferably, the diameter of the steel ball is greater than or equal to 4 mm and less than or equal to 6 mm, and the diameter of the steel ball in this embodiment is 5 mm. The curved surface guiding portion 233 may be provided as a cam surface or a cam groove. Therefore, the cam surface or the cam groove can define the movable path of the steel ball, and the steel ball can move in the cam surface or the cam groove, and the steel ball has a smooth outer surface, which can not only reduce the conversion member 232 and the curved surface guide portion. The relative motion friction between the 233 improves the smoothness of the movement of the conversion member 232 in the curved surface guiding portion 233, and the steel ball has high structural strength and good wear resistance, thereby ensuring the performance of the intermittent impact assembly 230. It should be noted that the “cam” mentioned herein may mean that the curved guide portion 233 protrudes from the inner peripheral wall of the guide member 210 or the curved guide portion 233 protrudes from the outer peripheral wall of the ram 200.

Further, the steel ball and the curved surface guiding portion 233 may be point or line contact. It can be understood that, during the movement of the steel ball in the curved surface guiding portion 233, the steel ball is always in contact with the curved surface guiding portion 233 as a point or line contact. It is advantageous to reduce the friction between the steel ball and the curved surface guiding portion 233. For example, the radius of curvature of the cam surface may be substantially the same as or slightly larger than the radius of the steel ball, thereby improving the fit of the steel ball to the cam surface, thereby improving the assembly stability, wear resistance and life of the steel ball and the cam surface.

As shown in FIG. 2, FIG. 16, and FIG. 19, in some embodiments of the present invention, the energy storage mechanism 231 may be provided as an elastic member. For example, the energy storage mechanism 231 may be a spring or an elastic rubber member, thereby simplifying The installation and assembly of the energy storage mechanism 231 can also reduce the manufacturing cost of the energy storage mechanism 231.

As shown in Figures 5, 8-10, 13 and 15, in accordance with some embodiments of the present invention, the hammer impact mechanism 20 further has a detachable clutch mechanism 220 that is configured for transmission. Rotational motion between the drive 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 is engaged with the ram 200, the rotational motion of the transmission shaft 10 can be transmitted through the clutch mechanism 220. The ram 200 is driven to drive the ram 200 to rotate; when the clutch mechanism 220 and the ram 200 are disengaged, that is, the cooperation relationship between the clutch mechanism 220 and the ram 200 is released, the transmission shaft 10 can be rotated relative to the ram 200. The ram 200 is stationary relative to the guide 210. Thereby, the movement of the ram 200 can be controlled by the clutch mechanism 220, thereby controlling whether the ram 200 hits the tool spindle 30, and thus the operation mode of the tool spindle 30 can be controlled.

Further, the clutch mechanism 220 can be configured to be closed by a force transmitted via the tool spindle 30, that is, when the tool head abuts in the working condition (axial load), the clutch mechanism 220 can automatically close, achieve impact, and hold The tool 1 is in an impact state. Thus, whether or not 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. Thereby, it is possible to easily change the working state switching of the hand tool 1, and no additional control structure is required.

Further, the clutch mechanism 220 is operatively switchable between a closed state and a disengaged state, and when the clutch mechanism 220 is in the closed state, the striker 200 is driven to rotate by the drive shaft 10; when the clutch mechanism 220 is in the disengaged state, The striker 200 cannot be driven by the drive 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 be engaged with the ram 200 or disengaged from the ram 200, and the clutch mechanism 220 can be under the action of the tool spindle 30. Switch between states. When the clutch mechanism 220 is engaged with the ram 200, the drive shaft 10 can drive the ram 200 to rotate. When the clutch mechanism 220 and the ram 200 are disengaged, the ram 200 cannot be driven by the drive shaft 10. Thereby, the movement of the ram 200 can be controlled by the clutch mechanism 220, so that the hand tool 1 can automatically realize the impact function or enter the impact state when the load is working.

As shown in FIG. 5, FIG. 8 to FIG. 10, FIG. 13 and FIG. 15, in some examples of the present invention, the clutch mechanism 220 includes a clutch member 221 disposed on one of the transmission shaft 10 and the ram 200, and is disposed on The accommodating portion 201 of 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 is engaged with the shape of the accommodating portion 201, and when the clutch mechanism 220 is disengaged, the clutch member The 221 is separated from the accommodating portion 201.

It can be understood that the clutch mechanism 220 includes the clutch member 221 and the accommodating 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 accommodating portion 201. When the clutch mechanism 220 is in the engaged state, the clutch member 221 is engaged with the accommodating portion 201, and when the clutch mechanism 220 is in the disengaged state, the clutch member 221 is separated from the accommodating portion 201. Thereby, the working state of the clutch mechanism 220 can be switched by the assembly relationship of the clutch member 221 and the accommodating portion 201.

As shown in FIG. 5, FIG. 8 to FIG. 10, FIG. 13 and FIG. 15, in some examples of the present invention, the clutch member 221 may be provided in a spherical shape or a column shape, and the receiving portion 201 may be provided as a groove body 201a. Both the spherical or columnar shape have a smooth outer surface, and the smooth outer surface has less friction during the movement, thereby facilitating the state switching of the clutch member 221. Providing the accommodating portion 201 as the trough body 201a is not only convenient to set but also facilitates engagement 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 accommodating portion 201. Further, the bottom wall of the groove body 201a may be formed as a curved surface, and the curved surface may be recessed toward the radially outer side of the ram 200. Thereby, the groove body 201a can wrap the portion separating member 221, so that the cooperation stability of the clutch member 221 and the groove body 201a can be improved.

According to some embodiments of the invention, the tool spindle 30 is axially movable relative to the drive shaft 10 but is non-rotatably coupled. 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. In the axial direction of the drive shaft 10, the tool spindle 30 is relative to the drive shaft 10 Movable. Thereby, the transmission shaft 10 can drive the tool spindle 30 to rotate in the circumferential direction of the transmission shaft 10, and the tool spindle 30 can also complete the sliding in the axial direction of the transmission shaft 10.

For example, as shown in FIG. 5, how the closure or disengagement of the clutch mechanism 220 and how the tool spindle 30 can be pivoted relative to the drive shaft 10 will be specifically described below with reference to the drawings in the axial movement of the tool spindle 30 relative to the drive shaft 10. A mobile but non-rotatable connection. The tool spindle 30 is movable from a first position to a second position via an axial force, and the ram 200 can be driven to rotate by the drive shaft 10 when the tool spindle 30 is in the second position Moving relative to the guide member 210 in a predetermined path, thereby striking the tool spindle 30 along an axis of the tool spindle 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 connecting end connected to the drive shaft 10 and an output end connected to the tool head. The side of the drive shaft 10 near the connecting end is provided with an axially open cavity 120, and the cavity 120 can be along the drive shaft 10. Extending in the axial direction, the connecting end of the tool spindle 30 extends from the opening into the cavity 120. The inner wall of the cavity 120 and the outer wall of the connecting end of the tool spindle 30 are engaged by the axially extending splines 370 so that the tool spindle 30 can be opposed The drive shaft 10 moves axially and is rotatable with the drive shaft 10. Specifically, as shown in FIG. 2, the outer wall of the tool spindle 30 and the inner wall of the cavity 120 are provided with the ribs 340, and the adjacent ribs 340 on the tool spindle 30 form a radially concave groove 350 to The inner wall of the cavity 120 can be mated with the recess 350.

Continuing to refer to FIG. 5, FIG. 8 to FIG. 10, FIG. 13 and FIG. 15, a radial hole 110 is defined in the side wall of the cavity 120, and 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 is movable in the radial hole 110. The inner peripheral wall of the hammer 200 may be provided with the above-mentioned receiving portion 201. When the clutch mechanism 220 is in the engaged state, that is, referring to FIGS. 13 and 15, when the tool spindle 30 is moved to the first position, the radial hole 110 corresponds to the position of the groove 350 described above, and the clutch member 221 is along the radial hole. 110 moves away from the accommodating portion 201 of the ram 200 and in the direction of the groove 350, so that the clutch member 221 is disengaged from the ram 200; see FIGS. 9 and 10, when the tool spindle moves to the second position, The groove 350 no longer corresponds to the position of the radial hole 110 described above, that is, there is no space for the clutch member 221 to be accommodated at the position corresponding to the radial hole on the tool spindle 30, and the tool spindle 30 is squeezed during the movement. The clutch member 221 moves the clutch member 221 along the radial hole 110 toward the accommodating portion 221 of the ram, so that a part of the clutch member is located in the radial hole 110 while another portion is located in the accommodating portion 201, and the ram 200 rotates. Under the action of the clutch member 221, it can rotate together with the transmission shaft 10. It should be noted that, in other embodiments of the present invention, the cavity 120 may be located at the 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. The method will be described in detail later in this specification.

As shown in FIGS. 5, 9, and 13, in accordance with some embodiments of the present invention, the tool spindle 30 is provided with an impact receiving portion 400 that mates with the ram 200. It can be understood that the tool spindle 30 can be provided with an impact receiving portion 400, and the ram 200 can strike the impact receiving portion 400, whereby the ram 200 can drive the tool spindle 30 by impacting the impact receiving portion 400, thereby making it possible to The tool spindle 30 drives the tool head to move relative to the drive shaft 10 in the axial direction of the drive shaft 10.

Further, as shown in FIG. 2, the impact receiving portion 400 may be formed in an annular shape, the impact receiving portion 400 is fixed to the outer peripheral wall of the tool spindle 30, and the impact receiving portion 400 is located outside the transmission shaft 10, and the impact receiving portion 400 and the tool spindle are 30 is connected, for example, the impact receiving portion 400 can be engaged with the tool spindle 30, and the impact receiving portion 400 can also be welded to the tool spindle 30. Thereby, when the ram 200 strikes the tool spindle 30, the contact area between the impact receiving portion 400 and the ram 200 can be enlarged, so that the stability of the impact force applied by the ram 200 to the impact receiving portion 400 can be improved.

Example 2

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

As shown in Figures 1, 5, 13, 21, 23, 25-27, the drive shaft 10 can be driven to rotate by a motor 60 that is rotatable 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 drive shaft 10. The hammer impact mechanism 20 has a ram 200 that is sleeved on the outside of at least one of the drive shaft 10 and the tool spindle 30 and that can be driven to rotate by the drive shaft 10. In other words, as shown in FIG. 1, FIG. 5, FIG. 13, FIG. 21, FIG. 23, FIG. 25 to FIG. 26, the ram 200 may be jacketed on the transmission shaft 10, or, as shown in FIG. 27, the ram 200 may be jacketed. The tool spindle 30 can also be a ram 200 that is both over the drive shaft 10 and the tool spindle 30. The drive shaft 10 can directly or indirectly drive the ram 200 to rotate.

As shown in FIG. 1 , FIG. 5 , FIG. 13 , FIG. 21 , FIG. 23 , and FIG. 25 to FIG. 27 , the hammer impact mechanism 20 further includes a guide member 210 that is sleeved on the outer side of the ram 200 . The tool spindle 30 can be switched from the first position to the second position via the action of an axial force. In other words, there is an external force acting in the direction of the axis of the tool spindle 30 acting on the tool spindle 30, so that the tool spindle 30 can be made The first position is switched to the second position. 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 be moved relative to the guide 210 in a predetermined path 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.

According to the hand tool 1 of the embodiment of the present invention, by applying a force in the axial direction of the tool spindle 30, the position of the tool spindle 30 can be switched, and thus the relationship between the hammer 200 and the transmission shaft 10 can be controlled, and Further, the ram 200 is guided by the intermittent impact assembly 230 for linear motion, and the ram 200 can also strike the tool spindle 30, so that the movement of the tool spindle 30 in the axial direction can be achieved, so that the tool spindle 30 is in an environmental component such as a wall or When the plate is drilled, the tool spindle 30 forms an impact force on the environment component, so that the drilling efficiency of the hand tool 1 can be improved. Moreover, the hand tool 1 of the embodiment of the present invention has a compact structure and a simple structure, and is convenient to carry.

As shown in Figures 25-27, in accordance with some embodiments of the present invention, the two ends of the tool spindle 30 are respectively a connection end 380 and an output end 390, the connection end 380 is coupled to the drive shaft 10, and the output end 390 is coupled to the tool head. When the direction of the axial force experienced 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 received by the tool spindle 30 is from the output end 390 of the tool spindle 30 to the direction of the connection end 380, the tool The main shaft 30 is switchable to a second position that is mated with respect to the drive shaft 10. When the tool spindle 30 is subjected to a force in the direction from the connection end 380 of the tool spindle 30 to the output end 390, the tool spindle 30 is switched to a first position that is mated with respect to the drive shaft 10. Thereby, the positional state of the tool spindle 30 can be switched by the action direction of the external force applied to the tool spindle 30, and the operating state of the hand tool 1 can be switched.

As shown in Figures 1, 5, 13, 21, 23, 25-27, in some embodiments of the invention, the hand tool 1 further includes a mode adjustment mechanism 40, the mode adjustment mechanism 40 being operatively Switching between the first mode state and the second mode state, in the first mode state, the tool spindle 30 is switchable relative to the drive shaft 10 between the first position and the second position, that is, the mode adjustment mechanism 40 is in the In a mode state, the hand tool 1 can generate an axial impact under the action of an axial load, hereinafter referred to as the "impact mode"; in the second mode state, the tool spindle 30 abuts the mode adjustment mechanism 40 axially. In order to restrict the tool spindle 30 from being switched from the first position to the second position, that is, when the mode adjustment mechanism 40 is in the second mode state, the hand tool 1 has no impact, regardless of whether the tool spindle 30 is subjected to an axial load, Hereinafter, the mode is referred to as "non-impact mode".

Further, as shown in FIG. 1, FIG. 5, FIG. 13, FIG. 21, FIG. 23, FIG. 25 to FIG. 27, the hand tool 1 further includes a mode adjusting mechanism 40, and the mode adjusting mechanism 40 is operatively in the first mode state and The second mode transitions between states. When the mode adjusting mechanism 40 is in the first mode state, the guiding member 210 is fixed to the housing 80, that is, the guiding member 210 is stationary with respect to the housing 80, and the ram 200 can be moved along the preset path along the guiding member 210 to rotate the tool when rotating. The main shaft 30; when the mode adjusting mechanism 40 is in the second mode state, the guiding member 210 is rotatably disposed on the housing 80, that is, the guiding member 210 is movable relative to the housing 80, and the ram 200 has no impact on the tool spindle 30. Thereby, the operating state of the control guide 210 can be controlled by controlling the state of the mode adjusting mechanism 40, so that the cooperation relationship between the ram 200 and the guide 210 can be controlled, and the working state of the ram 200 can be controlled to realize Switching of the working state of the hand tool 1.

As shown in FIG. 19 to FIG. 20, in some embodiments of the present invention, the mode adjusting mechanism 40 includes a first rib 212 disposed on the guiding member 210, and an impact switching member provided with the second rib 431. The member is axially movable but non-rotatably fixed within the housing 80 of the hand tool 1, in particular, the impact switching member is an impact switching ring 430, and the impact switching ring 430 is movably jacketed to the ram 200. Wherein, when the mode adjusting mechanism 40 is in the first mode state, the first rib 212 is engaged with the second rib 431; when the mode adjusting mechanism 40 is in the second mode state, the first rib 212 and the second rib 431 Interspersed.

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 are relatively movable. The impact switching ring 430 is provided with a second rib 431, and the guiding member 210 is provided with a first tooth. The pattern 212, the first rib 212 and the second rib 431 can be coupled to each other, so that the guiding member 210 can be connected to the impact switching ring 430. At this time, the impact switching ring 430 can define the movement of the guiding member 210, the guiding member. The 210 is relatively stationary with the impact switching ring 430, and the ram 200 is linearly movable relative to the guide 210 in a predetermined path and strikes the tool spindle 30 in at least one operating state.

It is also possible to switch the position of the impact switching ring 430 such that the first rib 212 is spaced apart from the second rib 431. At this time, the guide 210 is movable relative to the impact switching ring 430, and the guide 210 is in the intermittent impact assembly. Under the driving of 230, the hammer 200 can be rotated together with the ram 200, and the ram 200 and the guiding member 210 are relatively stationary. Therefore, the positional relationship and the assembly relationship of the guide 210 and the impact switching ring 430 can be adjusted by adjusting the cooperation relationship between the first rib 212 and the second rib 431, so that the movement state of the guide 210 can be controlled, and then The movement state of the tool spindle 30 is increased to control the operation mode of the hand tool 1.

Further, as shown in FIG. 19 and FIG. 21 to FIG. 26, the mode adjusting mechanism 40 further includes a buffering member 440. One end of the cushioning member 440 abuts against the impact switching ring 430 to constantly push the impact switching ring 430 toward the guiding member 210. Thus, the cushioning member 440 can often push the impact switching ring 430 close to the guiding member 210, so that the first rib 212 can be engaged with the second rib 431.

Further, as shown in FIG. 19 to FIG. 24, the mode adjusting mechanism 40 further includes a mode switching button 450. The mode switching button 450 is rotatably sleeved on the impact switching ring 430, 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 guiding block 451. The outer peripheral wall of the impact switching ring 430 is provided with a mating block 432 adapted to the guiding block 451, and the rotation mode switching button 450, wherein when the guiding block 451 is When the engaging block 432 is axially abutted, the guiding block 451 pushes the impact switching ring 430 to compress the buffering member 440 to move away from the guiding member 210, and the first rib 212 is spaced apart from the second rib 431; when the guiding block 451 When the mating block 432 is offset, the impact switching ring 430 moves in the direction of the guide member 210 by the cushioning member 440, and the first serration 212 meshes with the second serration 431.

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 to change the cooperation state between the guiding block 451 and the mating block 432. . Thereby, the cooperation relationship between the first rib 212 and the second rib 431 can be controlled by switching the cooperation relationship between the guiding block 451 and the mating block 432. Further, as shown in FIG. 20, the guiding block 451 has a guiding slope 451a to guide the fitting block 432. Thereby, the cooperation relationship between the guiding block 451 and the fitting block 432 can be conveniently switched.

In other embodiments of the present invention, the mode adjustment mechanism 40 can also adopt other configurations. Specifically, referring to FIGS. 2-5, 9, and 13, the mode adjustment mechanism 40 includes a pressure limiting ring 410 and a mode adjustment knob 420. . The pressure limiting ring 410 is sleeved on the transmission shaft 10, specifically sleeved on the impact receiving portion 400, and the pressure limiting ring 410 is rotatable relative to the transmission shaft 10 but is not axially movable, and the mode adjusting button 420 is rotatably sleeved. Stop ring 410. The pressure limiting ring 410 is provided with an abutting portion 411. The inner peripheral wall of the mode adjusting knob 420 is provided with a passage 422 adapted to pass the abutting portion 411, and the passage 422 extends in the axial direction of the transmission shaft 10.

Wherein, when the mode adjusting mechanism 40 is in the first mode state, the abutting portion 411 and the mode adjusting button 420 are stopped; when the mode adjusting mechanism 40 is in the second mode state, the abutting portion 411 corresponds to the position of the channel 422, the tool The spindle 30 is capable of driving the axial movement of the pressure lock ring along the tool spindle. Thereby, the adjustment of the movement state of the ram 200 can be achieved by adjusting the relative positional relationship between the abutting portion 411 of the pressure limiting ring 410 and the mode adjusting knob 420, so that the operating mode of the tool spindle 30 can be adjusted. Specifically, as shown in FIG. 3 to FIG. 4, the mode adjusting button 420 further includes a flange 421 disposed on the inner peripheral wall of the mode adjusting button 420. The flange 421 is annular and extends in the circumferential direction of the pressure limiting ring 410. The flange 421 is penetrated in the axial direction of the check ring 410. Thus, the flange 421 can define a passage 422 that can also withstand the abutment portion 411.

As shown in Figures 3-4, in some embodiments of the invention, the abutment portion 411 includes a fixed segment 411a, a connecting segment 411b, and a mating segment 411c. The fixing section 411a extends from the pressure limiting ring 410, one end of the connecting section 411b is connected to the fixing section 411a, and one end of the fitting section 411c is connected to the other end of the connecting section 411b, and the fitting section 411c is adapted to pass through the passage 422, the fixing section 411a and the connection. The segments 411b are spaced apart in the axial direction of the check ring 410. Further, the portion where the connecting portion 411b is connected to the fixed portion 411a smoothly transitions; or the portion where the connecting portion 411b is connected with the engaging portion 411c smoothly transitions.

As shown in FIGS. 2 and 6, in some embodiments of the present invention, the outer peripheral wall of the impact receiving portion 400 has a stepped surface 404, and the check ring 410 and the stepped surface 404 are stopped. Thus, the stepped surface 404 can define the movement of the check ring 410, avoiding the check ring 410 from the impact receiving portion 400.

As shown in FIG. 25 to FIG. 27, in some embodiments of the present invention, one end of the transmission shaft 10 connected to the connection end 380 is a transmission end 130, and one of the connection end 380 and the transmission end 130 is provided with an axial hole 360. One end projects into the axial bore 360. For example, the end face of the drive end 130 of the drive shaft 10 may be provided with an axial bore 360 extending along the axial direction of the drive shaft 10, the axial bore 360 being open toward the connection end 380 of the tool spindle 30, the tool spindle 30 The end of the connecting end 380 can extend into the axial bore 360. For another example, the connecting end 380 of the tool spindle 30 may be provided with an axial hole 360 extending along the axial direction of the tool spindle 30, and the axial hole 360 is open toward the driving end 130 of the transmission shaft 10, the transmission shaft 10 The end of the drive end 130 can extend into the axial bore 360. A connection manner for providing an opening on the connecting end of the tool spindle 30 to facilitate the insertion of the transmission shaft 10 has been described in the above-mentioned Embodiment 1, and will not be described herein. The connection manner in which the opening is provided on the transmission end face of the drive shaft 10 will be described in detail below.

As shown in Figures 25-27, the inner wall of the axial bore 360 and the outer wall of the other end are provided with splines 370 for effecting torque transfer between the drive shaft 10 and the tool spindle 30. Thereby, the connection stability between the drive shaft 10 and the tool spindle 30 can be improved, and not only the rotation of the tool spindle 30 and the drive shaft 10 in the circumferential direction but also between the tool spindle 30 and the drive shaft 10 can be Relative movement in the direction of the axis.

Further, as shown in FIG. 13 and FIG. 25 to FIG. 27, a radial groove may be formed between the splines 370 extending into the other end portion of the axial hole 360, and the outer wall of the axial hole 360 is provided. The radial hole 110, when the tool spindle 30 is in the first position, the radial hole 110 corresponds to the radial groove position, the steel ball can at least partially fall into the radial groove and be disengaged from the ram; When the axial force from the output end 390 to the connecting end 380 is received, 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 connected with the ram 200 to realize that the transmission shaft can drive the ram 200 to rotate. Therefore, by controlling the relative positional relationship between the steel ball and the radial groove, the cooperation relationship between the ram 200 and the tool spindle 30 or the transmission shaft 10 can be controlled, so that the movement state of the ram 200 can be controlled, and thus The working state of the tool spindle 30 is controlled to switch the operating mode of the hand tool 1.

As shown in FIGS. 1, 5, 13, 21, 23, 25-27, the hammer impact mechanism 20 further includes an intermittent impact assembly 230, in accordance with some embodiments of the present invention. When the drive shaft 10 drives the ram 200 to rotate, the intermittent impact assembly 230 forces the ram 200 to move linearly relative to the guide 210 in a predetermined path and strike the tool spindle 30 in at least one operating state. It will be appreciated 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 the movement path can both rotate the ram 200 in the circumferential direction of the transmission shaft 10, and can also make the ram The movement of 200 in the axial direction of the drive shaft 10 allows the ram 200 to strike the tool spindle 30, thereby completing the sliding of the tool spindle 30 relative to the drive shaft 10.

As shown in FIG. 2, FIG. 5, FIG. 7 and FIG. 9 to FIG. 12, according to some embodiments of the present invention, the intermittent impact assembly 230 includes an energy storage mechanism 231 that abuts the ram 200 and is disposed on the guide 210 and collides with A conversion member 232 and a curved guide portion 233 between the hammers 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. 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 Abuts the ram 200. Thus, the specific shape of the curved surface guiding portion 233 can be configured to guide the movement trajectory of the conversion member 232, and the conversion member 232 can be interlocked with the ram 200, and the ram 200 can drive the conversion member 232 along the circumference of the transmission shaft 10. Rotating in the direction, the conversion member 232 can move the ram 200 along the trajectory of the curved guide portion 233.

Further, as shown in FIG. 13 and FIG. 17 to FIG. 18, the transmission shaft 10 may be provided with a baffle 100. The baffle 100 is sheathed on the outer peripheral wall of the propeller shaft 10. The accumulator mechanism 231 is located at the ram 200 and the baffle 100. Between the one end of the accumulator mechanism 231 away from the ram 200 can be engaged with the baffle 100. When the ram 200 is moved a certain distance toward the energy storage mechanism 231, the ram 200 and the shutter 100 can compress the energy storage mechanism 231. Thereby, the energy storage mechanism 231 can form a urging force for the ram 200.

As shown in FIGS. 11-12, 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 be circumferentially wound in the circumferential direction of the transmission shaft 10, and the curved surface guiding portion 233 may include a climbing The slope section 233a and the drop section 233b, one end of the drop section 233b is connected to one end of the climbing section 233a, and the other end of the falling section 233b extends toward the other end of the climbing section 233a. Further, the climbing section 233a may be in a spiral shape. The falling section 233b may be in a straight line shape, and the falling section 233b extends in the axial direction of the transmission shaft 10. At least a portion of the conversion member 232 can be mated with the curved surface guide portion 233. Preferably, in order to ensure that the ram has sufficient impact force on the tool spindle 30 and the volume of the hand tool 1 is compact, the climbing 233a has a climbing height in the axial direction of more than 3 mm and less than or equal to 20 mm, preferably, the climbing height. It is between 4 mm and 15 mm, preferably, the climbing height is 10 mm.

When the switching member 232 is engaged with the climbing portion 233a, the switching member 232 rolls from one end of the climbing portion 233a toward the other end of the climbing portion 233a, and the ram 200 moves toward the shutter 100, and the hammer 200 and the shutter 100 can be compressed. The energy storage mechanism 231; when the conversion member 232 is located at the other end of the climbing section 233a and rolling toward the falling section 233b, the energy storage mechanism 231 can push the ram 200 from the falling section 233b toward the end of the shutter 100 toward the falling section 233b to approach the tool. The other end of the head is dropped, that is, the ram 200 is moved away from the shutter 100 and in the direction of the tool head, and a portion of the hammer 200 approaches and strikes a portion of the tool spindle 30 located outside the transmission shaft 10, thereby causing the tool spindle 30 to be opposed to The drive shaft 10 moves in the axial direction of the drive shaft 10, and the ram 200 forms a hammering of the tool spindle 30 and the tool head.

As shown in FIG. 12, in some embodiments of the present invention, the curved guide portion 233 may include a plurality of segments, each segment including a climbing segment 233a and a falling segment 233b. The conversion member 232 may be plural, and the plurality of conversion members 232 may be spaced apart in 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, and more preferably, the climbing height is 5 mm. . It can be understood that, in order to ensure the smooth transition 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 segment 233a is preferably 3

It should be noted that the assembly position and the assembly relationship of the conversion member 232 and the curved surface guiding portion 233 on the ram 200 and the guide member 210 are not particularly limited. In some embodiments of the invention, the transition member 232 is located in one of the guide member 210 and the ram 200, and the curved guide portion 233 is located at the other of the guide member 210 and the ram 200. Thereby, the assembly relationship between the conversion member 232 and the curved surface guiding portion 233 and the ram 200 and the guide member 210 can be realized, so that the cooperation relationship between the conversion member 232 and the curved surface guiding portion 233 and the conversion member 232 and the curved surface guiding portion 233 can be utilized. The relative movement between the rams 200 relative to the guide 210 can be achieved, and the ram 200 can be moved relative to the drive shaft 10 in the axial direction of the drive shaft 10. The movement path of the conversion member 232 at the curved surface guiding portion 233 is a preset path of the ram 200.

As shown in FIGS. 9-12, in some examples of the invention, the transition member 232 can be located on the ram 200 and the curved guide 233 is located on the guide 210. For example, as shown in FIG. 2, FIG. 5, FIG. 7 and FIG. 11 to FIG. 12, the outer peripheral wall of the ram 200 may be provided with an embedding groove 202, and a part of the conversion member 232 may be located in the embedding groove 202, and the guiding member 210 A curved guide portion 233 is provided on the inner peripheral wall, and a further portion of the conversion member 232 can be engaged with the curved guide portion 233.

As shown in FIGS. 16-18, in other examples of the present invention, the conversion member 232 may be located on the guide member 210, and the curved guide portion 233 is located on the ram 200. For example, the inner peripheral wall of the guiding member 210 is provided with a receiving groove 211, and a part of the switching member 232 may be located in the receiving groove 211. The outer peripheral wall of the ram 200 may be provided with a curved guiding portion 233, and another part of the converting member 232 may be The curved surface guiding portion 233 is fitted.

As shown in FIG. 2, FIG. 16, and FIG. 19, in some embodiments of the present invention, the conversion member 232 may be provided as a steel ball, as shown in FIGS. 11-12, preferably, in order to ensure the strength of the steel ball, steel The diameter of the 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 may be provided as a cam surface or a cam groove. Therefore, the cam surface or the cam groove can define the movable path of the steel ball, and the steel ball can move in the cam surface or the cam groove, and the steel ball has a smooth outer surface, which can not only reduce the conversion member 232 and the curved surface guide portion. The relative motion friction between the 233 improves the smoothness of the movement of the conversion member 232 in the curved surface guiding portion 233, and the steel ball has high structural strength and good wear resistance, thereby ensuring the performance of the intermittent impact assembly 230. It should be noted that the “cam” mentioned herein may mean that the curved guide portion 233 protrudes from the inner peripheral wall of the guide member 210 or the curved guide portion 233 protrudes from the outer peripheral wall of the ram 200.

As shown in FIGS. 2, 16, and 19, in some embodiments of the present invention, the energy storage mechanism 231 may be provided as an elastic member. For example, the energy storage mechanism 231 may be a spring or an elastic rubber member. Thereby, the installation 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 may be formed in a ring shape, and the energy storage mechanism 231 may be jacketed on the outer peripheral wall of the transmission shaft 10. Thereby, the assembly of the energy storage mechanism 231 is facilitated, and the urging force of the damper 200 by the uniform energy storage mechanism 231 can be uniform.

Example 3

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

Specifically, as shown in FIGS. 1, 2, and 5, the drive shaft 10 is driven to rotate by the motor 60 and rotates 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 is wound around the drive shaft 10. The axis rotates. It can be understood that the motor 60 is coupled to the drive shaft 10. It should be noted that the term "connected" as used herein may mean that the motor 60 is directly connected to the drive shaft 10. For example, the output of the motor 60 may be coupled to the drive shaft 10. The ends are directly connected. "Connected" may also mean that the motor 60 is indirectly connected to the drive shaft 10. For example, the motor 60 may be directly coupled to the intermediate drive assembly and directly coupled to the drive shaft 10 via the intermediate drive assembly.

The tool spindle 30 is axially movable relative to the drive shaft 10 but is connected in a rotationally fixed manner. In other words, in the circumferential direction of the drive shaft 10, the tool spindle 30 and the drive shaft 10 are relatively stationary, in the axial direction of the drive shaft 10. Upper, the tool spindle 30 is movable relative to the drive shaft 10. The drive shaft 10 can drive the tool spindle 30 to rotate in the circumferential direction of the drive shaft 10, and the tool spindle 30 can also perform sliding in the axial direction of the drive shaft 10.

As shown in FIG. 2, FIG. 5 to FIG. 13, the hammer impact mechanism 20 has a ram 200 which is sleeved outside the transmission shaft 10 and can be driven to rotate by the transmission shaft 10. It can be understood that the hammer impact mechanism 20 includes the ram 200, and the ram 200 can be jacketed on the outer peripheral wall of the transmission shaft 10. The ram 200 can be coupled with the transmission shaft 10, and the transmission shaft 10 can further drive the ram 200 around the transmission. The axis of the shaft 10 rotates. It should be noted that the term “connection” as used herein may 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 shown in Figures 5, 8-10, 13 and 15, in accordance with some embodiments of the present invention, the hammer impact mechanism 20 further has a detachable clutch mechanism 220 that is configured for transmission. Rotational motion between the drive 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 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 cooperation relationship between the clutch mechanism 220 and the ram 200 is released, and the transmission is cancelled. The shaft 10 rotates relative to the ram 200, and the ram 200 is stationary relative to the guide 210. Thereby, the movement of the ram 200 can be controlled by the clutch mechanism 220, thereby controlling whether the ram 200 hits the tool spindle 30, and thus the operating state of the hand tool 1 can be changed. In some embodiments of the invention, the clutch mechanism 220 is configured to be closed by a force transmitted via the tool spindle 30. It can be understood that whether 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. If the tool head or tool spindle 30 abuts the operating condition (ie, when the tool spindle 30 is subjected to an axial load), the clutch mechanism 220 is closed and the hand tool 1 is switched to the impact state. Therefore, when the hand tool 1 is in the working state, when the tool head abuts on the working condition, the hand tool 1 can automatically switch to the impact state, which is hereinafter referred to as the "shock mode".

It should be noted that, in actual work, not all working conditions are suitable for the hand tool 1 to work under impact. In many cases, the operator wants the tool head or tool spindle 30 to be received when the hand tool 1 is in operation. When the load of the working condition is still in a non-impact working state, the following is referred to as a "non-impact working mode".

Therefore, in order to adapt the hand tool 1 to various working conditions, the hand tool 1 further includes a mode adjusting mechanism 40, which can be shown in FIGS. 2-6, 13-15, and 19-30. Operable between the first mode state and the second mode state, when the mode adjustment mechanism 40 is in the first mode state (ie, as shown in FIGS. 5-6, 9-10, 21-22, and 25) In the position shown), the ram 200 can be driven to rotate by the drive shaft 10 to linearly move in a predetermined path and strike the tool spindle 30 in at least one operating state, in other words, the drive shaft 10 can cooperate with the ram 200. The drive shaft 10 can provide power to the ram 200 to move the ram 200 along a predetermined path, and the ram 200 can strike the tool spindle 30 during movement; when the mode adjustment mechanism 40 is in the second mode state (as shown in the figure) 13 - Fig. 15, Fig. 23 - Fig. 24 and Fig. 26), the drive shaft 10 cannot drive the ram 200 to rotate, and the ram 200 has no impact on the tool spindle 30.

According to the hand tool 1 of the embodiment of the present invention, by setting the mode adjusting mechanism 40 and changing the cooperation relationship between the transmission shaft 10 and the ram 200 by switching the state of the mode adjusting mechanism 40, it is possible to control whether the ram 200 is facing the tool spindle. 30 has an impact effect, thereby enabling switching between the impact mode and the non-impact mode of the hand tool 1, thereby improving the performance of the hand tool 1, making the structure of the hand tool 1 compact, simple, and diversified, and at the same time convenient to carry.

It can be understood that the clutch mechanism 220 includes the clutch member 221 and the accommodating 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 accommodating portion 201. When the clutch mechanism 220 is in the closed state, the clutch member 221 is engaged with the accommodating portion 201, and when the clutch mechanism 220 is in the disengaged state, the clutch member 221 is separated from the accommodating portion 201. Thereby, the working state of the clutch mechanism 220 can be switched by the assembly relationship of the clutch member 221 and the accommodating portion 201.

For example, as shown in FIG. 5, the tool spindle 30 is switchable between the first position and the second position relative to the drive shaft 10 via 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 210 in a predetermined path, thereby striking the tool spindle 30 along the axis of the tool spindle 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 connecting end connected to the drive shaft 10, and an output end connected to the tool head. The side of the drive shaft 10 near the connecting end is provided with an axially open cavity 120, and the cavity 120 can be Extending along the axial direction of the drive shaft 10, the connecting end of the tool spindle 30 extends from the opening into the cavity 120. The inner wall of the cavity 120 and the outer wall of the connecting end of the tool spindle 30 are engaged by the axially extending splines 370. The tool spindle 30 is axially movable relative to the drive shaft 10 and is rotatable with the drive shaft 10. Specifically, as shown in FIG. 2, the outer wall of the tool spindle 30 and the inner wall of the cavity 120 are provided with ribs 340, and the adjacent ribs 340 on the tool spindle 30 form a radially recessed groove 350 therebetween. The inner wall of the cavity 120 can be mated with the recess 350.

Continuing to refer to FIG. 5, FIG. 8 to FIG. 10, FIG. 13 and FIG. 15, a radial hole 110 is defined in the side wall of the cavity 120, and 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 is movable in the radial hole 110. The inner peripheral wall of the hammer 200 may be provided with the above-mentioned receiving portion 201. Referring to Figures 13 and 15, when the clutch mechanism 220 is in the disengaged state, that is, when the tool spindle 30 is moved to the second position, the radial hole 110 corresponds to the position of the groove 350 described above, and the clutch member 221 is radially bored. 110 moves away from the accommodating portion 201 of the ram 200 and in the direction of the groove 350, so that the clutch member 221 is disengaged from the ram 200; see FIGS. 9 and 10, when the clutch mechanism 220 is in a closed state, that is, When the tool spindle moves to the second position, the groove 350 no longer corresponds to the position of the radial hole 110, that is, the space corresponding to the radial hole on the tool spindle 30 no longer has space for the clutch member 221 to be accommodated. The main shaft 30 presses the clutch member 221 during the movement to move the clutch member 221 along the radial hole 110 toward the accommodating portion 221 of the ram, so that a part of the clutch member 221 is located in the radial hole 110 while another portion Located in the accommodating portion 201, the ram 200 rotates 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 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.

As shown in FIG. 2, FIG. 5, FIG. 7 and FIG. 9 to FIG. 12, according to some embodiments of the present invention, the intermittent impact assembly 230 includes an energy storage mechanism 231 that abuts the ram 200 and is disposed on the guide 210 and collides with A conversion member 232 and a curved guide portion 233 between the hammers 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 guide 210 and the ram 200, and one end of the energy storage mechanism 231 abuts against the ram 200. Thereby, the specific shape of the curved surface guiding portion 233 can be configured to guide the movement trajectory of the conversion member 232, the conversion member 232 can be interlocked with the ram 200, and the ram 200 can be along the curved guiding portion under the action of the conversion member 232. Track motion of 233.

Further, as shown in FIG. 13 and FIG. 17 to FIG. 18, the transmission shaft 10 may be provided with a baffle 100. The baffle 100 is sheathed on the outer peripheral wall of the propeller shaft 10. The accumulator mechanism 231 is located at the ram 200 and the baffle 100. Between the one end of the accumulator mechanism 231 away from the ram 200 can be engaged with the baffle 100. When the ram 200 is moved a certain distance toward the energy storage mechanism 231, the ram 200 and the shutter 100 can compress the energy storage mechanism 231. Thereby, the energy storage mechanism 231 can form a urging force for the ram 200. Of course, other structures may be adopted for the axially defining manner of the energy storage mechanism, and details are not described herein again.

As shown in FIG. 11 to FIG. 12, in some embodiments of the present invention, the curved surface guiding portion 233 may be formed in an annular shape, and the curved surface guiding portion 233 may be circumferentially wound in the circumferential direction of the transmission shaft 10, specifically, the curved surface guiding portion 233 A climbing section 233a and a falling section 233b may be included, 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 is extended toward the other end of the climbing section 233a. Further, the climbing section 233a may be in a spiral shape, the falling section 233b may be in a straight line shape, and the falling section 233b may extend in the axial direction of the transmission shaft 10. Preferably, in order to ensure that the ram has sufficient impact force on the tool spindle 30 and the volume of the hand tool 1 is compact, the climbing 233a has a climbing height in the axial direction of more than 3 mm and less than or equal to 15 mm, preferably, the climbing height. It is 4 mm or more and 8 mm or less, and preferably, the climbing height is 5 mm.

As shown in FIGS. 5, 9, and 13, in accordance with some embodiments of the present invention, the tool spindle 30 is provided with an impact receiving portion 400 that mates with the ram 200. It can be understood that the tool spindle 30 can be provided with an impact receiving portion 400, and the ram 200 can strike the impact receiving portion 400, whereby the ram 200 can drive the tool spindle 30 by impacting the impact receiving portion 400, thereby making it possible to The tool spindle 30 moves relative to the drive shaft 10 in the axial direction of the drive shaft 10.

As shown in FIG. 12, in some embodiments of the present invention, the curved guide portion 233 may include a plurality of segments, each segment including a climbing segment 233a and a falling segment 233b. The conversion member 232 may be plural, and the plurality of conversion members 232 may be spaced apart in the circumferential direction of the ram 200. In order to ensure the rationality of the overall design of the hand tool, the outer diameter of the middle hammer 200 is between 15 mm and 50 mm, preferably, the outer diameter of the hammer is between 20 mm and 40 mm, and 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, and 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 segment 233a is preferably 3

It should be noted that, as described 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 between the guiding member 210 and the ram 200, and the curved surface is guided. The portion 233 is located at the other of the guide member 210 and the ram 200. As shown in FIGS. 16-18, in other examples of the present invention, the conversion member 232 may be located on the guide member 210, and the curved guide portion 233 is located on the ram 200. For example, the inner peripheral wall of the guiding member 210 is provided with a receiving groove 211, and a part of the switching member 232 may be located in the receiving groove 211. The outer peripheral wall of the ram 200 may be provided with a curved guiding portion 233, and another part of the converting member 232 may be The curved surface guiding portion 233 is fitted. As shown in FIGS. 16-18, in other examples of the present invention, the conversion member 232 may be located on the guide member 210, and the curved guide portion 233 is located on the ram 200. For example, the inner peripheral wall of the guiding member 210 is provided with a receiving groove 211, and a part of the switching member 232 may be located in the receiving groove 211. The outer peripheral wall of the ram 200 may be provided with a curved guiding portion 233, and another part of the converting member 232 may be The curved surface guiding portion 233 is fitted. Thereby, the assembly relationship between the conversion member 232 and the curved surface guiding portion 233 and the ram 200 and the guide member 210 can be realized, so that the cooperation relationship between the conversion member 232 and the curved surface guiding portion 233 and the conversion member 232 and the curved surface guiding portion 233 can be utilized. The relative movement between the rams 200 relative to the guide 210 can be achieved, and the ram 200 can be moved relative to the drive shaft 10 in the axial direction of the drive shaft 10. The movement path of the conversion member 232 at the curved surface guiding portion 233 is a preset path of the ram 200.

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

As shown in FIG. 19 to FIG. 20, in some embodiments of the present invention, the mode adjusting mechanism 40 includes a first rib 212 disposed on the guiding member 210, and an impact switching member provided with the second rib 431. The member is axially movable but non-rotatable and fixed in the housing of the hand tool 1. The specific impact switching member is the impact switching ring 430, and the impact switching ring 430 is movably fitted to the ram 200. Wherein, when the mode adjusting mechanism 40 is in the first mode state, the first rib 212 is engaged with the second rib 431; when the mode adjusting mechanism 40 is in the second mode state, the first rib 212 and the second rib 431 Interspersed.

Further, as shown in FIG. 19 and FIG. 21 to FIG. 26, the mode adjusting mechanism 40 further includes a buffering member 440. One end of the cushioning member 440 abuts against the impact switching ring 430 to constantly push the impact switching ring 430 toward the guiding member 210. Thus, the cushioning member 440 can often push the impact switching ring 430 close to the guide member 210, so that the first rib 212 can be engaged with the second rib 431.

In other embodiments of the present invention, the mode adjusting mechanism 40 can also adopt other structures. Specifically, referring to FIG. 2 to FIG. 5, FIG. 9 and FIG. 13, the mode adjusting mechanism 40 includes a pressure limiting ring 410 and a mode adjusting button 420. . The pressure limiting ring 410 is sleeved on the transmission shaft 10, specifically sleeved on the impact receiving portion 400, and the pressure limiting ring 410 is rotatable relative to the transmission shaft 10 but is not axially movable, and the mode adjusting button 420 is rotatably sleeved. Stop ring 410. The pressure limiting ring 410 is provided with an abutting portion 411. The inner peripheral wall of the mode adjusting knob 420 is provided with a passage 422 adapted to pass the abutting portion 411, and the passage 422 extends in the axial direction of the transmission shaft 10.

As shown in FIGS. 2 and 6, in some embodiments of the present invention, the outer peripheral wall of the impact receiving portion 400 has a stepped surface 404, and the check ring 410 and the stepped surface 404 are stopped. Thus, the stepped surface 404 can define the movement of the check ring 410 to prevent the check ring 410 from being detached from the impact receiving portion 400.

Example 4

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

Specifically, the direction of rotation of the motor 60 includes a first direction and a second direction, one of the first direction and the second direction may be a clockwise direction and the other may be a counterclockwise direction. The motor 60 can drive the drive shaft 10 to rotate. The tool spindle 30 is coupled to the drive shaft 10, and the tool spindle 30 is movable relative to the drive shaft 10, for example, the tool spindle 30 is movable relative to the drive shaft 10. The hammer impact mechanism 20 includes a ram 200 and a guide 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 hand tool 1 of the embodiment of the present invention, by providing the guiding member 210 and the intermittent impact assembly 230, the intermittent impact assembly 230, the tamper 200 and the guiding member 210 can be used to guide the ram 200 for linear motion and collide. The hammer 200 can also strike the tool spindle 30 so that movement of the tool spindle 30 in the axial direction can be achieved such that when the tool spindle 30 is drilled on an environmental component such as a wall or panel, the tool spindle 30 impacts the environmental components. Therefore, the drilling efficiency of the hand tool 1 can be improved, and the hand tool 1 of the embodiment of the invention has a compact structure and a simple structure, and can be conveniently carried.

As shown in FIG. 2, FIG. 5, FIG. 7 and FIG. 9 to FIG. 12, the intermittent impact assembly 230 includes an energy storage mechanism 231 that abuts against the ram 200 and a conversion member 232 that is disposed between the guide 210 and the ram 200. And a curved surface guiding portion 233. The intermittent impact assembly 230 further includes an energy storage mechanism 231, and both the conversion member 232 and the curved surface guiding portion 233 are located between the guide 210 and the ram 200, and one end of the energy storage mechanism 231 abuts against the ram 200. Thereby, the specific shape of the curved surface guiding portion 233 can be configured to guide the movement trajectory of the conversion member 232, the conversion member 232 can be interlocked with the ram 200, and the ram 200 can be along the curved guiding portion under the action of the conversion member 232. Track motion of 233.

Further, as shown in FIG. 7 and FIG. 15, the end surface of the ram 200 adjacent to the energy storage mechanism 231 may be provided with a mounting groove 203, and the end of the energy storage mechanism 231 may be located in the mounting groove 203, and the end of the energy storage mechanism 231 The portion may abut against the bottom wall of the mounting groove 203. Thereby, the assembly stability of the accumulator mechanism 231 and the ram 200 can be improved.

Referring to FIG. 11 and FIG. 12, in the present invention, since the above-mentioned climbing section 233a and falling section 233b are provided inside the guiding member 210, when the motor 60 rotates in the forward direction, it is hit in the "impact mode". The hammer 200 hits the tool spindle 30 to achieve a hammering action, but when the motor 60 rotates in the reverse direction, the above-mentioned conversion member 232 needs to pass over the falling section 233b and move to the climbing section 233, but in order to ensure the impact of the hammer 200. The falling section 233b is substantially coaxially parallel, so when the switching member 232 is rotated in the axial direction, the switching member 232 cannot cross the falling section 233b, causing the motor to "block" or even burn the machine.

Therefore, referring to Figures 28-30, the hand tool 1 further includes a non-rotatable impact ring 11a fixed to the housing 80. The impact ring 11a is provided with a first end tooth 12a, and the guide member 210 is provided with a first end The second end tooth 213a of the tooth 12a is engaged. When the motor 60 rotates in the first direction, the first end tooth 12a restricts the rotation of the guide member 213 by the second end tooth 213a engaged with the tooth, and the conversion member 232 is preset along the curved guide portion. The directional movement causes the ram 200 to strike the tool spindle 30 in at least one operating state; when the motor 60 is rotated in the second direction, the second end teeth 213a and the guide 213 are driven by the motor 60 relative to the same The one end tooth 12a rotates, that is, the second end tooth 213a on the guide member 213 performs a hill-climbing motion with respect to the first end tooth 12a. The first end tooth 12a includes a plurality of first teeth 121a. The first tooth 121a includes a guiding portion 121b and a stopping portion 121c. The guiding portion 121b is coupled to the free end of the stopping portion 121c, and the second end tooth 213a The second tooth 2131a is composed of a plurality of second teeth 2131a. When the motor 60 rotates in the first direction, the second tooth 2131a is moved by the stop segment 121c to the guiding segment 121b, and the stopping segment 121c abuts the second tooth 2131a. Therefore, the guide member 210 is not rotatable; when the motor 60 is rotated in the second direction, when the second tooth 2131a is moved by the guide segment 121b to the stop segment 121c, the second tooth 2131a can follow The guide section 121b moves so that the guide member 213 rotates relative to the first end tooth 12a. The guide segment 121b and the stop segment 121c are sequentially spaced apart along the circumferential direction of the first end tooth 12a, and the stop segment 121c is parallel to the axis of the drive shaft 10. When the second tooth 2131a is moved by the stopper section 121c to the guide section 121b, the side where the second tooth 2131a abuts the stopper section 121c is parallel to the stopper section 121c. The impact ring 11a is axially movable to engage or disengage the first end tooth 12a and the second end tooth 213a. When the first end tooth 12a is separated from the second end tooth 213a, the guide 210 is at the Rotating under the drive of the motor, the tool is in a non-impact mode. It can be understood that, in the present embodiment, when the impact ring 11a is axially movable, the impact ring 11a in this embodiment not only has the function of “anti-blocking” but also has the description in the above other embodiments of the present invention. The function of the impact switching ring 430, in other words, in the above embodiment, the first tooth of the first tooth pattern 212 and the second tooth pattern 431 of the above embodiment is set to the first tooth in the embodiment. The tooth shape of the 121a and the second tooth 2131a, the mode switching mechanism 40 in the above embodiment has not only the mode switching function but also the anti-blocking function in the impact mode.

As shown in Figures 5, 8-10, 13 and 15, in accordance with some embodiments of the present invention, the hammer impact mechanism 20 further has a detachable clutch mechanism 220 that is configured for transmission. Rotational motion between the drive 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 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 cooperation relationship between the clutch mechanism 220 and the ram 200 is released, and the transmission is cancelled. The shaft 10 rotates relative to the ram 200, and the ram 200 is stationary relative to the guide 210. Thereby, the movement of the ram 200 can be controlled by the clutch mechanism 220, thereby controlling whether the ram 200 hits the tool spindle 30, and thus the operating state of the hand tool 1 can be changed. In some embodiments of the invention, the clutch mechanism 220 is configured to be closed by a force transmitted via the tool spindle 30. It can be understood that whether 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. If the tool head or tool spindle 30 abuts the operating condition (ie, when the tool spindle 30 is subjected to an axial load), the clutch mechanism 220 is closed and the hand tool 1 is switched to the impact state.

As shown in FIG. 5, the tool spindle 30 is switchable between a first position and a second position relative to the drive shaft 10 via 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 210 in a predetermined path 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 connecting end connected to the drive shaft 10, and an output end connected to the tool head. The side of the drive shaft 10 near the connecting end is provided with an axially open cavity 120, and the cavity 120 can be Extending along the axial direction of the drive shaft 10, the connecting end of the tool spindle 30 extends from the opening into the cavity 120. The inner wall of the cavity 120 and the outer wall of the connecting end of the tool spindle 30 are engaged by the axially extending splines 370. The tool spindle 30 is axially movable relative to the drive shaft 10 and is rotatable with the drive shaft 10. Specifically, as shown in FIG. 2, the outer wall of the tool spindle 30 and the inner wall of the cavity 120 are provided with ribs 340, and the adjacent ribs 340 on the tool spindle 30 form a radially recessed groove 350 therebetween. The inner wall of the cavity 120 can be mated with the recess 350.

Continuing to refer to FIG. 5, FIG. 8 to FIG. 10, FIG. 13 and FIG. 15, a radial hole 110 is defined in the side wall of the cavity 120, and 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 is movable in the radial hole 110. The inner peripheral wall of the hammer 200 may be provided with the above-mentioned receiving portion 201. Referring to Figures 13 and 15, when the clutch mechanism 220 is in the disengaged state, that is, when the tool spindle 30 is moved to the second position, the radial hole 110 corresponds to the position of the groove 350 described above, and the clutch member 221 is radially bored. 110 moves away from the accommodating portion 201 of the ram 200 and in the direction of the groove 350, so that the clutch member 221 is disengaged from the ram 200; see FIGS. 9 and 10, when the clutch mechanism 220 is in a closed state, that is, When the tool spindle 30 is moved to the second position, the groove 350 no longer corresponds to the position of the radial hole 110 described above, that is, there is no space for the clutch member 221 to be accommodated at the position corresponding to the radial hole 110 on the tool spindle 30. The tool spindle 30 presses the clutch member 221 during the movement to move the clutch member 221 along the radial hole 110 toward the accommodating portion 221 of the ram, so that a part of the clutch member 221 is located in the radial hole 110 while The other part is located in the accommodating portion 201, and the ram 200 is rotated by the clutch member 221 to rotate together with the transmission shaft 10. It should be noted that, in other embodiments of the present invention, the cavity 120 may also be located at the 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.

Example 5

A hand tool 1 according to various embodiments of the present invention will be described in detail below with reference to Figs. It is to be understood that the following description is only illustrative and not restrictive.

As shown in FIG. 1 to FIG. 15, the hand tool 1 of 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 limiting ring 410, and a mode adjustment. Button 420.

Specifically, the motor 60 is coupled to the drive shaft 10, and the motor 60 can drive the drive shaft 10 to rotate in the axial direction of the drive shaft 10, and the drive shaft 10 rotates about the axis of the drive shaft 10. The drive shaft 10 can be formed in a cylindrical shape with one end open, that is, the drive shaft 10 can form a cavity 120 that is open at one end. The cavity 120 can extend along the axial direction of the drive shaft 10, and the tool spindle 30 can be opened from the cavity 120. One end penetrates into the transmission shaft 10, and the other end of the transmission shaft 10 can form a flat square 140, and the torque is transmitted through the flat 140 and the motor 60. The reset member 70 is located in the cavity 120, and one end of the reset member 70 and the tool spindle 30 In the axial abutment, the other end of the reset member 70 abuts against the bottom wall of the cavity 120 away from the opening. The reset member 70 can often push the tool spindle 30 from the bottom wall of the cavity 120 toward the open end of the cavity 120.

As shown in FIG. 2, one end of the tool spindle 30 adjacent to the drive shaft 10 may include a first segment 310, a second segment 320, and a third segment 330. The first segment 310 is coupled to one end of the second segment 320, and one end of the second segment 320 Connected to the third segment 330. The axis of the first segment 310 coincides with the axis of the third segment 330, and the third segment 330 extends completely into the cavity 120 of the drive shaft 10, a portion of the first segment 310 can extend into the cavity 120, the first segment 310 The other portion is located outside the cavity 120, the cross-sectional radius of the third segment 330 is less than the cross-sectional radius of the first segment 310, and the outer peripheral wall of the second segment 320 is a curved surface. The outer peripheral wall of the third segment 330 is provided with a plurality of ribs 340, and the plurality of ribs 340 are arranged along the circumferential direction of the third segment 330, and any one of the ribs 340 is along the axial direction of the third segment 330. Extending, any two adjacent ribs 340 can be configured as grooves 350.

A plurality of protrusions may be disposed on the inner peripheral wall of the transmission shaft 10 corresponding to the cavity 120. The plurality of protrusions are arranged along the circumferential direction of the transmission shaft 10, and any one of the protrusions is along the axis of the transmission shaft 10. The direction extends. Any two adjacent bumps may be configured as a mating slot, and any one of the ribs 340 corresponds to one mating slot, and each of the ribs 340 may extend into its corresponding mating slot. When the transmission shaft 10 rotates, the rib 340 can abut against at least one of the two protrusions corresponding to the engagement groove, so that the tool spindle 30 can be rotated in the circumferential direction of the transmission shaft 10. In the axial direction of the drive shaft 10, the tool spindle 30 is movable relative to the drive shaft 10, and the tool spindle 30 can complete the sliding in the axial direction of the drive shaft 10.

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

As shown in FIG. 5, FIG. 8 to FIG. 10, FIG. 13, and FIG. 15, the ram 200 is sheathed on the outer peripheral wall of the propeller shaft 10, and the ram 200 is adjacent to the end of the propeller shaft 10 away from the restoring member 70, and the inner peripheral wall of the ram 200 It is spaced apart from the outer peripheral wall of the drive shaft 10. A radial hole 110 may be disposed in a portion of the transmission shaft 10 of the ram 200. The radial hole 110 penetrates the transmission shaft 10 in a radial direction of the transmission shaft 10. The clutch member 221 may be located in the radial hole 110. The 221 can move within the radial bore 110. The accommodating portion 201 may be disposed on the inner peripheral wall of the ram 200. The accommodating portion 201 may pass through the ram 200 in the axial direction of the propeller shaft 10. The accommodating portion 201 may be provided as a trough body 201a, which may pass through the inner peripheral wall of the ram 200. A part is recessed toward the radially outer side of the hammer 200 to construct the groove body 201a, and the clutch member 221 may be provided 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 trough body 201a may be formed as an arcuate surface that may be recessed toward the radially outer side of the ram 200.

When the clutch mechanism 220 is in the closed state, the steel ball moves between the transmission shaft 10 and the ram 200, that is, a part of the steel ball is located in the radial hole 110, and another part of the steel ball is located in the groove body 201a, and is located in the groove body. A part of the steel ball in 201a can be matched with the groove body 201a. When the steel ball rotates with the transmission shaft 10, the steel ball can drive the ram 200 to rotate in the circumferential direction of the transmission shaft 10. When the clutch mechanism 220 is in the disengaged state, when the steel ball moves between the drive shaft 10 and the tool spindle 30, that is, a part of the steel ball is located in the radial hole 110, and another part of the steel ball is located in the groove 350, the transmission The shaft 10 is spaced apart from the ram 200 and the ram 200 is in a stationary state.

It should be noted that the position of the steel ball can be switched by the positional relationship of the tool spindle 30 with respect to the transmission shaft 10. When the tool head is in operation and subjected to an axial abutment force from the operating condition, that is, when the tool spindle 30 is moved toward the reset member 70, the reset member 70 is compressed, and the first segment 310 of the tool spindle 30 and the radial hole are compressed. 110, the first segment 310 will squeeze the steel ball, the steel ball moves radially from the groove 350 along the radial hole 110 into the groove body 201a, a part of the steel ball cooperates with the radial hole 110, and the other part and the groove body 201a cooperates, so that the drive shaft 10 is slammed into the hammer 200, 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 is under the action of the reset member 70. Moving toward the tool head, the tool spindle 30 is moved relative to the radial hole 110 by the first segment 310 to the third segment 330 opposite to the radial hole 110. Therefore, the first segment 310 no longer extrudes the steel ball, steel The ball moves under the action of the ram 200 along the radial hole 110 into the groove 350 and is disengaged from the groove 201a. The transmission shaft 10 cannot drive the ram 200 to rotate, and the clutch mechanism 220 is in a disengaged state. Referring to Figure 15, in the present embodiment, when the clutch mechanism 220 is in the disengaged state, the steel ball remains at least partially within the radial bore 110 to facilitate switching of the clutch mechanism 220 between the engaged and disengaged states.

As shown in FIG. 5, FIG. 8 to FIG. 10, FIG. 13, and FIG. 15, the guide member 210 is attached to the outer peripheral wall of the ram 200, and the inner peripheral wall of the guide member 210 is formed with a curved surface guiding portion 233, and the curved surface guiding portion 233 can be formed as The annular curved surface guide portion 233 may be circumferentially wound in the circumferential direction of the transmission shaft 10. The curved surface guiding portion 233 may include a plurality of segments, each of which corresponds to a conversion member 232. Each segment includes a climbing segment 233a and a falling segment 233b. The climbing section 233a may be in a spiral shape, and the falling section 233b may be in a straight line shape. The conversion member 232 can be provided as a steel ball.

Referring to FIGS. 16-18, different from the embodiment shown in FIG. 1 to FIG. 15, in other embodiments of the present invention, the inner peripheral wall of the guiding member 210 may be provided with a receiving groove 211, and a part of the converting member 232 may be It is located in the receiving groove 211, and the conversion member 232 is connected (eg, snapped) to the guiding member 210. The outer peripheral wall of the ram 200 may be provided with a curved guiding portion 233, and a further portion of the converting member 232 may cooperate with the curved guiding portion 233.

As shown in FIGS. 5, 7 to 10, 13, and 15, the mounting groove 203 may be provided to the end surface of the hammer 200 toward the reset member 70. A baffle 100 may be disposed on the propeller shaft 10. The baffle 100 is sheathed on the outer peripheral wall of the propeller shaft 10. The baffle 100 is coupled to the propeller shaft 10, and the baffle 100 is opposite to the mounting slot 203. The accumulator mechanism 231 is located between the ram 200 and the baffle 100. One end of the accumulator mechanism 231 can protrude into the mounting groove 203, and the end of the accumulator mechanism 231 can abut against the bottom wall of the mounting groove 203. The energy storage mechanism 231 The other end can be opposed to the baffle 100. The energy storage mechanism 231 can be provided as an annular spring that can be jacketed to the drive shaft 10.

As shown in FIG. 2, FIG. 5, FIG. 1, FIG. 9, FIG. 10 and FIG. 13, the outer peripheral wall of the ram 200 may be provided with an embedding groove 202, and a part of the conversion member 232 may be located in the embedding groove 202 to make the conversion member. 232 is coupled to the ram 200, and a portion of the conversion member 232 located outside the insertion groove 202 can be engaged with the curved surface guiding portion 233, so that the conversion member 232 can be moved along the curved surface guiding portion 233, so that the tamper 200 is rotated at the transmission shaft 10 The movement along the path of the curved guide portion 233 is driven.

When the switching member 232 is engaged with the climbing portion 233a, the switching member 232 rolls from the other end of the climbing portion 233a toward one end of the climbing portion 233a, and the ram 200 moves toward the shutter 100, and the hammer 200 and the shutter 100 can be compressed. The energy storage mechanism 231; when the conversion member 232 is located at one end of the climbing section 233a and rolls toward the falling section 233b, the energy storage mechanism 231 can often push the ram 200 to fall from one end of the falling section 233b toward the other end of the falling section 233b. The hammer 200 moves in a direction away from the baffle 100.

As shown in FIG. 5, FIG. 9, and FIG. 13, the tool spindle 30 may be provided with an impact receiving portion 400. The impact receiving portion 400 may be fixedly coupled to the tool spindle 30. The impact receiving portion 400 may be formed in a ring shape, and the impact receiving portion 400 may be formed. The first section 310 of the tool spindle 30 can be jacketed, the impact receiving portion 400 being located outside of the drive shaft 10, and the impact receiving portion 400 being coupled (eg, snapped or welded) to the tool spindle 30. When the ram 200 is moved a distance away from the baffle 100, the ram 200 can come into contact with the impact receiving portion 400, and due to the urging action of the accumulator mechanism 231, the ram 200 can form an impact on the impact receiving portion 400. The effect is such that the tool spindle 30 can be moved in the direction away from the reset member 70 in the axial direction of the drive shaft 10.

Since the environmental component (such as a wall or a flat plate) drilled by the hand tool 1 has a load on the tool spindle 30, the tool spindle 30 moves toward the reset member 70 again, so that the tool spindle 30 can be made Rotating in the circumferential direction of the transmission shaft 10 under the belt action of the transmission shaft 10, the tool spindle 30 can be moved in the axial direction of the transmission shaft 10 by the impact of the ram 200 and the external force of the environmental member.

The above describes that the hand tool 1 can perform the hammering function when the hand tool 1 is in the working state, that is, the tool head is under the axial force. However, in actual operation, the operator does not need a hammering function under some operating conditions, and therefore, the hand tool of the present invention also has a mode adjusting mechanism 40.

As shown in FIG. 6, 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, the first surface 401 being coupled to one end of the second surface 402, and the other end of the second surface 402 Connected to the third surface 403, the first surface 401 is aligned with the extending direction of the third surface 403, the first surface 401 and the third surface 403 are spaced apart in the radial direction of the impact receiving portion 400, and the first surface 401 is located at the third surface. The radially outer side of the surface 403. The first surface 401, the second surface 402, and the third surface 403 are configured as a stepped surface 404. The pressure limiting ring 410 is sleeved on the impact receiving portion 400 corresponding to the third surface 403. The impact receiving portion 400 corresponding to the first surface 401 can axially define the pressure limiting ring 410 on the third surface 403.

As shown in FIGS. 3-6, the mode adjustment knob 420 is rotatably fitted to the pressure stop ring 410. The pressure limiting ring 410 is provided with an abutting portion 411. The inner peripheral wall of the mode adjusting knob 420 is provided with a flange 421 which is annular and extends in the circumferential direction of the pressure limiting ring 410. The flange 421 can define the passage 422. The passage 422 penetrates the flange 421 in the axial direction of the check ring 410, and the abutment portion 411 can pass through the passage 422.

As shown in FIGS. 3 to 4, the abutting portion 411 includes a fixing portion 411a, a connecting portion 411b, and a fitting portion 411c. The fixing section 411a extends from the pressure limiting ring 410, one end of the connecting section 411b is connected to the fixing section 411a, and one end of the fitting section 411c is connected to the other end of the connecting section 411b, and the fitting section 411c is adapted to pass through the passage 422, the fixing section 411a and the connection. The segments 411b are spaced apart in the axial direction of the check ring 410. The portion where the connecting portion 411b is connected to the fixed portion 411a smoothly transitions, and the portion where the connecting portion 411b is connected with the engaging portion 411c smoothly transitions.

When the abutting portion 411 and the mode adjusting button 420 are stopped, the pressure limiting ring 410 is stationary with respect to the mode adjusting button 420, and the pressure limiting ring 410 is further stopped by the impact receiving portion 400 corresponding to the first surface 401. The receiving portion 400 is stationary, the impact receiving portion 400 further defines the movement of the tool spindle 30, and 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, and the hammer 200 The motor shaft 60 is driven to rotate the drive shaft 10, and the drive shaft 10 further drives the tool spindle 30 to rotate. The tool spindle 30 has only a rotational movement.

When the abutting portion 411 is located in the passage 422, the abutting portion 411 can move in the passage 422, and 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, thereby driving the clutch member 221 to be placed on the transmission shaft. 10 and the ram 200, the drive shaft 10 can drive the ram 200 to rotate, and the ram 200 can move along the axis direction of the transmission shaft 10 and collide with the impact receiving portion under the cooperation of the conversion member 232 and the curved guiding portion 233. 400. The impact receiving portion 400 further drives the pressure limiting ring 410 to move within the inner ring of the mode adjusting knob 420. The tool spindle 30 has both the movement in the axial direction and the rotation in the circumferential direction.

Mode adjustment mechanism 40 may also be of other constructions in other embodiments of the invention.

Different from the embodiment shown in FIGS. 1-15, in the embodiment shown in FIGS. 19-26, the mode adjustment mechanism 40 includes an impact switching ring 430, a cushioning member 440, and a mode switching button 450. Specifically, the guiding member 210 has a first tooth pattern 212, the mode adjusting mechanism 40 includes an impact switching ring 430, the impact switching ring 430 is movably sleeved on the ram 200, and the impact switching ring 430 has the same resistance as the first tooth pattern 212. The second tooth 431 is provided. One end of the cushioning member 440 abuts against the impact switching ring 430 to constantly push the impact switching ring 430 toward the guide 210. The mode switching button 450 is rotatably sleeved on the impact switching ring 430. The mode switching button 450 is rotatable relative to the impact switching ring 430. The inner peripheral wall of the mode switching button 450 is provided with a guiding block 451, and the outer peripheral wall of the impact switching ring 430 is provided. The mating block 432 is adapted to the guiding block 451, and the impact switching ring 430 is axially movable but non-rotatably fixed to the housing.

The mode switching button 450 is rotated, wherein when the guiding block 451 is opposite to the mating block 432, the first rib 212 is spaced apart from the second rib 431. At this time, the guiding member 210 is movable relative to the impact switching ring 430. The guide member 210 can be rotated along with the ram 200 by the intermittent impact assembly 230. The ram 200 and the guide member 210 are relatively stationary. Therefore, the ram 200 does not hit the tool spindle 30; When the guiding block 451 is offset from the engaging block 432, the first rib 212 is engaged with the second rib 431, so that the guiding member 210 can be connected to the impact switching ring 430. At this time, the impact switching ring 430 can be The movement of the guide member 210 is defined. The guide member 210 is relatively stationary with the impact switching ring 430. The ram 200 can move linearly relative to the guide member 210 in a predetermined path and strike 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 the rotation mode switching 450. In other embodiments, in order to realize the axial movement of the impact switching ring, a dial connected to the impact switching ring 430 may also be provided, by dialing The toggle moves axially to directly drive the axial movement of the impact switching ring 450.

As shown in FIG. 20, the first rib 212 includes a raised portion 212a. The second tooth 431 includes a guiding section 431a and a stopping section 431b. The guiding section 431a may include a straight section and an inclined section. One end of the inclined section is connected to the free end of the abutting section 431b, and the other end of the inclined section is flat. Connect one end of the straight section. The abutting portion 431b extends in the axial direction of the impact switching ring 430, and the straight portion is perpendicular to the abutting portion 431b. There may be a plurality of the abutting segments 431b, the plurality of abutting segments 431b may be arranged along the circumferential direction of the guiding member 210, and any one of the two adjacent abutting segments 431b may have a guiding segment 431a. Both ends of the guiding section 431a are respectively adjacent to two adjacent abutting sections 431b. There may be a plurality of convex portions 212a, and the plurality of convex portions 212a are in one-to-one correspondence with the plurality of abutting portions 431b. The raised portion 212a may be formed in a triangular shape. The free end of the raised portion 212a may be formed as a tip end 212a1.

When the motor 60 is rotating forward, there are two cases, one of which is that the guiding block 451 is opposite to the mating block 432, and the first rib 212 is spaced apart from the second rib 431. At this time, the guiding member 210 Relative to the impact switching ring 430, the guiding member 210 can be rotated with the ram 200 under the driving of the intermittent impact assembly 230, and the ram 200 and the guiding member 210 are relatively stationary; another case is: When the guiding block 451 is offset from the engaging block 432, the protruding portion 212a and the abutting portion 431b are stopped, and the first rib 212 and the second rib 431 are relatively stationary, so that the guiding member 210 can be connected to the impact switching ring 430. At this time, the impact switching ring 430 can define the movement of the guiding member 210, the guiding member 210 is relatively stationary with the impact switching ring 430, and the ram 200 can be linearly moved relative to the guiding member 210 according to a preset path and in at least one operating state. Hit the tool spindle 30. When the motor 60 is reversed, the convex portion 212a can slide along the guiding portion 431a, and the first tooth pattern 212 and the second tooth pattern 431 can form a relative rotation, and the guiding member 210 can rotate relative to the impact switching ring 430. The guide 210 can rotate with the ram 200.

In the related art, when the first rib 212 is in contact with the second rib 431, the guide 210 and the impact switching ring 430 are relatively stationary. When the motor 60 is reversed, the switching member 232 is stopped at the falling section 233b. This may hinder the rotation of the motor 60, thereby damaging the performance of the guide 210 and the motor 60, affecting the service life of the hand tool 1. Compared with the related art, the hand tool 1 of the embodiment of the present invention has more considerations and has good security performance.

Different from the embodiment shown in FIG. 20, in the embodiment shown in FIGS. 28-30, the hand tool 1 further includes a non-rotatable impact ring 11a fixed to the housing 80, and the impact ring 11a is provided with a first One end tooth 12a, the guide member 210 is provided with a second end tooth 213a engageable with the first end tooth 12a. When the motor 60 rotates in the first direction, the first end tooth 12a passes through the second end tooth 213a meshing therewith. The restriction guide 213 rotates, and the conversion member 232 moves in a predetermined direction along the curved guide portion 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 tooth 213a And the guide member 213 is rotated relative to the first end tooth 12a engaged therewith by the motor 60, that is, the second end tooth 213a on the guide member 213 is ramped relative to the first end tooth 12a. The first end tooth 12a includes a plurality of first teeth 121a. The first tooth 121a includes a guiding portion 121b and a stopping portion 121c. The guiding portion 121b is coupled to the free end of the stopping portion 121c, and the second end tooth 213a The second tooth 2131a is composed of a plurality of second teeth 2131a. When the motor 60 rotates in the first direction, the second tooth 2131a is moved by the stop segment 121c to the guiding segment 121b, and the stopping segment 121c abuts the second tooth 2131a. Therefore, the guide member 210 is not rotatable; when the motor 60 is rotated in the second direction, when the second tooth 2131a is moved by the guide segment 121b to the stop segment 121c, the second tooth 2131a can follow The guide section 121b moves so that the guide member 213 rotates relative to the first end tooth 12a. The guide segment 121b and the stop segment 121c are sequentially spaced apart along the circumferential direction of the first end tooth 12a, and the stop segment 121c is parallel to the axis of the drive shaft 10. When the second tooth 2131a is moved by the stopper section 121c to the guide section 121b, the side where the second tooth 2131a abuts the stopper section 121c is parallel to the stopper section 121c. The impact ring 11a is axially movable to engage or disengage the first end tooth 12a and the second end tooth 213a. When the first end tooth 12a is separated from the second end tooth 213a, the guide 210 is at the Rotating under the drive of the motor, the tool is in a non-impact mode. It can be understood that, in the present embodiment, when the impact ring 11a is axially movable, the impact ring 11a in this embodiment not only has the function of “anti-blocking” but also has the description in the above other embodiments of the present invention. The impact switches the functions implemented by the ring 430.

23 is a cross-sectional view of a hand tool according to an embodiment of the present invention, including a motor 60 and a transmission mechanism including a transmission shaft 10, a hammer impact mechanism 20, and a tool spindle 30. The drive shaft 10 is driven to rotate by the motor 60 to rotate the drive shaft 10 about the axis of the drive shaft. The drive shaft 10 then drives the tool spindle 30 to rotate about the axis of the tool spindle. In the present embodiment, the axis of the drive shaft 10 is coaxial with the axis of the tool spindle 30, and the drive shaft 10 is sleeved outside the tool spindle 30 and is rotatably coupled to the tool spindle 30 by a flat fit. The connection between the transmission shaft 10 and the tool spindle 30 is not limited to the structure in the embodiment. In other embodiments, the axis of the transmission shaft 10 and the tool spindle 30 may also be parallel non-collinear, and the transmission shaft 10 may also be It is not set outside the tool spindle 30.

31, 32 and 11, the hammer impact mechanism 20 includes a ram 200, a guide 210, and an intermittent impact assembly 230 disposed between the ram 200 and the guide 210. The ram 200 is capable of intermittent axial impact on the tool spindle 30 to provide a higher hitting energy to the tool spindle 30. The axial impact motion of the ram 200 is achieved by the intermittent impact assembly 230. In the present embodiment, the intermittent impact assembly 230 includes a curved surface guiding portion 233 disposed on the guiding member 210, and a conversion member 232 that connects the curved surface guiding portion 233 and the ram 200 so that the curved surface guiding portion 233 can drive the ram 200 The energy storage mechanism 231 is compressed in the opposite direction to the impact direction to perform energy storage. The intermittent impact assembly 230 further includes an energy storage mechanism 231 that abuts the ram 200, and the energy storage mechanism 231 can drive the ram 200 to move in the impact direction. The direction of impact here is the direction of movement of the ram 200 from the rear to the front in the direction parallel to the axis of the tool spindle 30. In the present invention, the impact direction of the ram is the second direction, and the first direction is a direction opposite to the impact direction. Among them, the direction near the free end of the tool spindle 30 is forward. In other embodiments, the curved guide portion may also be disposed on the ram.

The curved surface guide portion includes a plurality of climbing sections and a falling section. When the switching member 232 passes the climbing section, the conversion member 232 drives the ram 200 to move in the first direction against the urging force of the energy storage mechanism 231, and the conversion member 232 is dropped. In the segment, the energy storage mechanism 231 drives the ram 200 to move in a second direction opposite to the first direction to effect the impact tool spindle 30. In the present invention, "the conversion member passes the climbing section" can be understood as a process in which the conversion member contacts and climbs the climbing section during the movement of the opposite curved guide portion, where the conversion member can be movable or not. As long as the conversion member has relative motion with respect to the curved guide portion. "The conversion member passes the drop section" can be understood as the conversion member is in the escape space formed by the drop section, and the conversion member may not be in contact with the drop section, which will be described in detail below.

In the present embodiment, the curved surface guiding portion 233 is disposed on the guiding member 210, and the guiding member 210 is fixedly disposed with respect to the housing. The conversion member 232 is disposed on the ram 200, and is coupled with the curved surface guiding portion 233 by the conversion member 232. The hammer 200 is driven to rotate relative to the guide member 210 to cause the ram 200 to climb on the curved guide portion 233, that is, the ram 200 moves rearward along the axis. When the ram 200 moves backward along the axis, the energy storage mechanism 231 performs energy storage. When the ram 200 climbs up to the highest point on the climbing section of the curved surface guiding portion 233, the energy stored by the energy storage mechanism 231 also corresponds. The ground is at its maximum. The falling section of the curved surface guide 233 forms a drop avoidance space for providing a drop space for the ram 200. When the ram 200 is in the falling space formed by the falling section, the energy stored by the accumulator mechanism 231 is converted into the kinetic energy of the ram 200, that is, the accumulator mechanism 231 drives the ram 200 to move in the impact direction to apply the shaft to the tool spindle 30. To the impact.

In the present embodiment, the ram 200 is rotationally driven by the propeller shaft 10, and the ram 200 is sleeved on the outer side of the propeller shaft 10. The motor 60 drives the drive shaft 10 to rotate, and the drive shaft 10 drives the tool spindle 30 to rotate. The drive shaft 10 can selectively drive the ram 200 to rotate, that is, the drive shaft 10 drives the hammer impact structure 20 to move.

In the present embodiment, the curved surface guiding portion 233 is a cam surface, and the curved surface guiding portion 233 is disposed on the guiding member 210, the conversion member 232 is a steel ball, the energy storage mechanism 231 is a spring, and the rotation of the ram 200 causes the hammer impact mechanism 20 Movement, the rotational drive of the ram 200 is achieved by the drive shaft 10. However, it is not limited to the specific form and structure in this embodiment, and other structural solutions capable of moving the ram forward along the axis are within the scope of the present invention. For example, in other embodiments, the conversion member may also be a cam end surface disposed on one of the ram and the guide member, a curved surface guide portion disposed on the other of the ram and the guide member, and a cam end surface and a curved surface guide portion. By the cooperation of the end face to form the cooperation of the active cam surface and the passive cam surface, the rotary motion can be converted into a linear motion, and combined with the action of the energy storage mechanism, the axial impact motion of the ram can be realized.

Specifically, FIG. 2 is an exploded perspective view of one embodiment of the present invention. Referring to FIG. 2, the adapter 232 may be disposed as a steel ball. 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, and the diameter of the steel ball in this embodiment is 5 mm. The curved surface guiding portion 233 may be provided as a cam surface or a cam groove. Therefore, the cam surface or the cam groove can define the movable path of the steel ball, and the steel ball can move in the cam surface or the cam groove, and the steel ball has a smooth outer surface, which can not only reduce the conversion member 232 and the curved surface guide portion. The relative motion friction between the 233 improves the smoothness of the movement of the conversion member 232 in the curved surface guiding portion 233, and the steel ball has high structural strength and good wear resistance, thereby ensuring the performance of the intermittent impact assembly 230. It should be noted that the “cam” mentioned herein may mean that the curved guide portion 233 protrudes from the inner peripheral wall of the guide member 210 or the curved guide portion 233 protrudes from the outer peripheral wall of the ram 200.

Further, in the present embodiment, the outer peripheral wall of the ram 200 is provided with an insertion groove 202. A part of the steel ball as the adapter 232 may be located in the insertion groove 202, and the adapter 232 is connected to the ram 200. A part of the adapter 232 embedded in the outside of the groove 202 cooperates with the curved surface guiding portion 233, so that the adapter 232 can be moved along the curved surface guiding portion 233, so that the ram 200 is guided along the curved surface by the rotational force of the transmission shaft 10. The path of the portion 233 moves.

In the present embodiment, the curved surface guiding portion 233 is provided on the inner circumferential surface of the guide member 210 of one of the ram 200 and the guide member 210, and the adapter member 232 is disposed on the ram 200 of the other one. The connection relationship between the adapter 232 and the ram 200 is that a part of the adapter 232 is disposed in the insertion groove 202 on the ram 200, and the steel ball 232 can rotate in the insertion groove 202. Further, the number of the fitting grooves 202 on the outer circumferential surface of the ram 200 is set to three, and the corresponding three steel balls as the adapter 232 are also provided, and the corresponding curved surface guiding portion 233 includes three climbing sections.

In the present invention, in order to better describe the motion state of the ram in the impact mode in the present embodiment, the present invention provides a cross-sectional view of the ram in several different states during the operation of the impact mode, please refer to Figures 34-36 show. Figure 34 is a diagram showing the ram in the first state in the impact mode, that is, the ram is climbing, that is, the ram is on the climbing section, and at this time, the ram is compressing the energy storage mechanism to store energy. Figure 35 is a graphical representation of the ram in a second state, i.e., the ram is at the highest position of the climbing section, at which time the ram compresses the energy storage mechanism to the maximum extent, thereby maximizing energy savings. Figure 36 is a diagram in which the ram is in the third state, that is, the ram is in the escaping space formed by the falling section, at which time the energy storage mechanism releases energy and drives the ram to impact in the impact direction.

Specifically, as shown in FIG. 34, the tool spindle 30 is in a depressed position, and the transmission shaft 10 drives the ram 200 to rotate. Under the driving of the conversion member 232, the ram 200 is opposite to the curved surface guiding portion 233 on the inner circumferential side of the guide member 210. The climbing is performed, and the hammer 200 is compressed in the first direction A to store the energy.

On the basis of FIG. 34, during the process of continuing the hill climbing compression accumulator mechanism 231 in the first direction A, the energy storage mechanism 231 is compressed to the maximum compression amount, that is, the energy storage foundation 231 is at the maximum energy storage. At this time, that is, the ram 200 climbs up to the highest point of the climbing section, that is, the second state of the ram 200 shown in FIG.

When the ram 200 is at the highest point of the climbing section in FIG. 35, due to the continued rotation of the transmission shaft 10, the ram 200 is also rotated, and then runs into the escape area formed by the falling section, in which the area is The ram 200 is in contact with the energy storage mechanism 231, and the energy storage mechanism 231 storing sufficient energy drives the ram 200 to move in the second direction B opposite to the first direction A while releasing energy, thereby causing the ram 200 impact tool spindle 30.

The above process completes an impact for the ram 200. Since the curved guide portion 233 includes three climbing sections and a falling section corresponding to the climbing section, when the ram 200 passes the first climbing section and the falling section, an impact is completed. After that, the same impact movement will continue along the second climbing section and the falling section, and then the third impact movement will be carried out along the third climbing section and the falling section.

Since there are three climbing sections on the inner circumferential surface of the guiding member, that is, the impact hammer 200 performs three impact movements during one rotation, thereby increasing the impact frequency and thereby improving the impact drilling efficiency.

In some embodiments of the invention, the energy storage mechanism 231 may be provided as an elastic member, for example, the energy storage mechanism 231 may be a spring or an elastic rubber member. Thereby, the installation 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 may be formed in a ring shape, and the energy storage mechanism 231 may be jacketed on the outer peripheral wall of the transmission shaft 10. Thereby, the assembly of the energy storage mechanism 231 is facilitated, and the urging force of the damper 200 by the uniform energy storage mechanism 231 can be uniform.

In other embodiments, the ram can also be rotated, and the guide member rotates. In this embodiment, the transmission shaft is fixedly coupled with the guide member, that is, the drive shaft drives the guide member to rotate simultaneously with the tool spindle, that is, the guide member and the tool spindle. The rotation speed is the same, that is, the rotation speed of the tool spindle is the same as the rotation speed of the ram relative to the guide. The ram is non-rotatably coupled to the housing, ie the ram is axially movable relative to the housing but is not rotatable relative to each other. The drive shaft drives the guide member to rotate, and the rotation of the guide member drives the curved surface guide portion on the inner circumferential surface of the guide member to rotate, thereby driving the axial movement of the ram, thereby compressing the spring energy storage, and then axially moving along the impact direction to strike the cutter Spindle.

The foregoing describes the specific structure of the cam type hammer impact mechanism in the present embodiment. Due to the different impact principle, the cam type hammer impact mechanism has higher impact energy than the conventional dynamic and static end tooth type axial impact structure, that is, the cam type hammer The single impact energy of the impact mechanism is higher than that of the conventional dynamic and static end tooth type. In addition, it has been found that the accumulated impact energy per unit time also affects the impact effect, that is, if the accumulated impact energy per unit time is too low, the impact force will be insufficient, and the hard surface of concrete such as concrete cannot be broken. .

The parameters affecting the accumulated striking energy per unit time are as follows: First, the number of periodic segments on the curved guiding part, that is, the number of climbing tracks, the more the number of climbing tracks, the more impacts of the ram, the ram per The more the number of impacts that are rotated one revolution. The second is the rotation speed of the ram. The faster the ram is, the more the number of rotations of the ram per unit time, that is, the more impacts of the ram. Therefore, if the ram speed is too low, the accumulated striking energy per unit time will be too low, which will result in the inability to break the material. On the contrary, the higher the rotational speed of the ram, the greater the accumulated striking energy per unit time, and the stronger the breaking ability. The "rotation speed of the ram" as used herein may also be referred to as "the relative rotational speed of the ram", that is, the rotational speed of the ram relative to the guide or the guide. For example, in an embodiment in which the ram does not rotate only axially, and the guide rotates, the rotational speed of the ram can be understood as the relative rotational speed of the ram relative to the guide.

However, if the rpm of the ram is too high, it will bring about another problem. The speed of the ram is too high, and the time for the steel ball to fall from the highest point of the climbing section will be less, which will greatly increase the probability of the steel ball hitting the track. In addition, the more periodic segments of the curved guides distributed over one circumference, that is, the more the number of hill-climbing tracks, the shorter the length of each periodic segment, and thus the chance of the steel ball hitting the track. Therefore, whether the steel ball will hit the track, the speed of the ram is required to be combined with the number of the climbing track.

Referring to FIGS. 23, 31, and 32, in the present embodiment, the tool spindle 30 and the hammer 200 are simultaneously rotationally driven by the drive shaft 10, that is, the rotational speed of the tool spindle 30 and the hammer 200 are the same, and therefore, the steel ball The probability of hitting the track is also indirectly related to the rotational speed of the tool spindle 30. Further, the higher the rotational speed of the tool spindle 30, the higher the rotational speed of the working head is, and the higher the rotational speed of the working head is, the higher the drilling efficiency is when the striking energy is satisfied. On the contrary, the lower the rotation speed of the tool spindle 30 is, the lower the rotation speed of the working head is, and the chip removal ability is poor, the drilling resistance is large, the breaking ability is poor, and the phenomenon of inaction may occur.

In the embodiment in which the rotation speeds of the other tool spindles and the ram are the same, the tool spindle directly drives the ram rotation, that is, the drive shaft drives the tool spindle to rotate, and the tool spindle drives the ram to rotate. With respect to this embodiment, the technical solution that the drive shaft simultaneously drives the tool spindle and the ram rotation can save the axial dimension, that is, obtain a more compact power tool in the axial direction.

The influencing factors of the steel ball collision track are described in detail below with reference to FIG. Figure 33 is a developed perspective view of a curved surface guiding portion 233 in one embodiment of the present invention, and Figure 11 is a schematic view of a guiding member in one embodiment of the invention.

The curved surface guide portion 233 is distributed 360 degrees on the inner circumferential surface of the guide member 210 in Fig. 11, and in other embodiments, the curved surface guide portion may be distributed around the outer circumferential surface of the ram 360°. Fig. 33 is a schematic view showing the curved surface guiding portion 233 being developed in the circumferential direction. As shown in the figure, the curved surface guiding portion 233 includes three uniformly distributed, completely identical and end-to-end period segments, which may also be called hill-climbing tracks. These three periodic segments or hill-climbing tracks are respectively: ABCD, A1-B1 -C1-D1, A2-B2-C2-D2, wherein the end point D of the first period is connected to the starting point A1 of the second period, and the ending point D1 and the third of the second period are The starting point A2 of the period is connected, and the third period, that is, the ending point D2 of the last period is connected to the starting point A of the first period. Here, "uniform distribution" means that each of the three periodic segments is distributed at the same angle in the circumferential direction, and "identical" means that each of the three periodic segments includes exactly the same region segment. And the angle, height, length, etc. of each zone are exactly the same. In this embodiment, each period segment includes a horizontal section 233c, a climbing section 233a, a falling section 233b, and the length of each horizontal section is the same, and the climbing height and the climbing angle of each climbing section are the same, each The height and angle of the drop segment are the same. In other embodiments of the present invention, the horizontal segment may not be provided as long as the end point of the first periodic segment falling segment is disconnected from the starting point of the next periodic segment, which also serves to extend the steel ball in the first periodic segment. The flight distance over the range of the drop segment.

Referring to FIG. 33, the conversion member 232, that is, the steel ball in the present embodiment, in the impact operation mode, the steel ball is hit at the end point C of the climbing section BC of the first period, that is, the highest point. The hammer 200 continues to rotate, and the steel ball partially embedded in the groove 202 on the outer circumferential surface of the ram 200 rotates around the axis of the ram 200 at the same speed as the ram 200. In the case where the height of the climbing track is constant, the greater the rotational speed of the ram 200 and the steel ball, the greater the probability that the steel ball will hit the climbing section B1-C1 of the next period; the more the number of climbing tracks, The probability that the steel ball hits the climbing section B1-C1 of the next cycle segment is also greater. On the other hand, the higher the rotational speed of the ram 200, the greater the probability that the ram 200 will be blocked, because the higher the rotational speed of the ram, the lower the corresponding output torque. When the output torque is less than the torque required during the climbing process, the stall phenomenon occurs.

In the case where the rotational speed of the ram 200 and the number of climbing tracks are constant, the higher the height of the climbing track, the smaller the probability that the steel ball hits the climbing section of the next cycle, but the climbing track The higher the height, the greater the axial length of the ram, so the length of the fuselage is greater.

Based on the above analysis, in the present invention, the relative rotational speed range of the ram relative to the guide member is set to an optimal range of 1000-2500 rpm, and the impact frequency of the ram and the relative rotational speed of the ram in the present invention. The ratio is 2-4 times/rev. The impact frequency of the ram refers to the number of times the tool spindle rotates one lap and hits the tool spindle. The unit of measurement is times/minute, that is, the impact frequency refers to the number of times the tool spindle rotates for one minute, the number of times the hammer hits the tool spindle, and the hammer The relative rotational speed refers to the relative rotational speed between the ram and the guide, and the unit of measurement is revolutions per minute, that is, the relative rotational speed of the ram refers to the number of revolutions of the ram relative to the guide within one minute. The ratio of the impact frequency of the ram to the relative rotational speed of the ram is 2-4, and the unit of measurement of the corresponding ratio is sub-per minute, that is, the number of collisions of the ram during the one-turn of the tool spindle is 2-4. It should be noted that the impact frequency of the ram is a positive integer, and the relative rotational speed of the ram is also a positive integer, but the ratio of the two may be an integer or may not be an integer, that is, it may be a positive fraction. By increasing the impact frequency of the ram by the technical solution of increasing the number of climbing sections on the curved guiding portion, an integer multiple is obtained. However, in other technical solutions, the added multiple may also be a non-integer. For example, in some embodiments, a speed increasing mechanism may be added between the transmission mechanism and the hammer impact mechanism for increasing the rotational speed of the output of the transmission mechanism to cause rotation to be transmitted to the hammer impact mechanism. The speed is getting bigger. Since the rotational speed of the output of the transmission mechanism is directly transmitted to the tool spindle, the rotational speed of the tool spindle is the same as the rotational speed of the output of the transmission mechanism, and the rotational speed transmitted to the hammer impact mechanism is greater than the rotational speed of the tool spindle. As for the multiple of the increase, it depends on the setting of the speed increasing mechanism. Preferably, the speed increasing mechanism may be a planetary gear speed increasing mechanism, and the gear ratio of the planetary gear speed increasing mechanism, that is, the ratio of the output end speed to the input end speed, is a multiple of the speed increasing. Since the gear ratio is small, the multiples added by this technical solution may be decimals.

In other embodiments, the planetary gear speed increasing mechanism may be replaced with another type of speed increasing mechanism, as long as the rotational speed of the output end of the speed increasing mechanism is greater than the rotational speed of the input end.

In other embodiments, different types of speed increasing mechanisms may be superimposed, for example, the technical solution of the planetary gear speed increasing mechanism and the technical solution for increasing the number of climbing sections on the curved guiding portion may be superimposed and used. The speed increase multiple is the product of the gear ratio of the speed increasing mechanism and the number of climbing sections. For example, in other embodiments, the ram is rotated, the guide member disposed outside the ram does not rotate, and the curved inner guiding surface is provided with a curved guiding portion, and the number of climbing portions on the curved guiding portion is set to two, and the transmission is set. The axis drives the tool spindle to rotate. In addition, a planetary gear speed increasing mechanism is arranged between the transmission shaft and the ram, the input end of the transmission shaft driving planetary gear speed increasing mechanism is rotated, the output end of the planetary gear speed increasing mechanism drives the ram to rotate, and the rotation speed of the transmission shaft is The rotational speed of the input end of the planetary gear speed increasing mechanism is the same, the rotational speed of the output end of the planetary gear increasing mechanism is the same as the rotational speed of the ram, and the transmission ratio of the planetary gear increasing mechanism is 1.6. Then in this embodiment, the tool spindle rotates once, and the number of times the hammer hits the tool spindle is 3.2 times, that is, in this embodiment, the ratio of the impact frequency of the hammer to the relative rotational speed of the ram relative to the guide member It is 3.2, the unit of measurement of the impact frequency of the ram, the unit of measurement of the relative rotational speed of the ram relative to the guide, and the unit of measurement of the ratio, refer to the above.

The relative rotational speed of the ram referred to in the present invention refers to the relative rotational speed between the ram and the guide. The same rotation speed as used in the present invention means that the values of the rotation speed are the same.

The optimal range of the relative rotational speed of the ram 200 relative to the guide member 210 is 1000-2500 rpm, and the range has a maximum value and a minimum value. The reason for the maximum value selection is whether the steel ball hits the track or is blocked. phenomenon. In the process of selecting the maximum value of 2,500 rpm, a large number of experiments were carried out, and it was called experiment A. Before the start of the experiment, the number of climbing tracks was first set to three, and the height of the climbing track was set. Set to 9 mm, on this basis, a large number of selective experiments were performed on the rotational speed of the ram 200. During the experiment, when the rotational speed of the ram 200 is less than or equal to 2300 rpm, no steel ball hits the track and the stall phenomenon occurs, but when the rotational speed of the ram 200 is equal to 2600 rpm, it appears. The phenomenon of motor stalling. In order to overcome the phenomenon of steel ball collision orbit caused by improper position of the falling point of the steel ball, based on the original experimental conditions, the rotational speed of the ram 200 is set to 2500 rpm, at which time there is no steel ball collision track and ram. Stalled phenomenon.

The reason why the turret 200 rotational speed minimum value 1000 rpm is selected is whether the accumulated energy per unit time is sufficient, and in the present embodiment, both the tool spindle 30 and the ram 200 are rotationally driven by the propeller shaft 10, and are rotated. The speed is the same, therefore, the selection of the minimum speed of the ram 200 also takes into account the effect that the rotational speed of the tool spindle 30 is too small. If the rotation speed of the tool spindle 30 is too small, the drill chip has poor chip removal capability, and the drilling resistance is large, which leads to low drilling efficiency. On the other hand, the rotation speed of the tool spindle 30 is too small, which will affect the impact mode. The rotational speed of the drill bit, which affects the drilling efficiency, also affects the drilling efficiency in the drilling and screwdriver mode, which in turn affects the operating experience.

In the process of Experiment A, the selection of the number of climbing tracks is three first, and then adjusted to two. The selection and adjustment of this value is based on another experiment, which is called Experiment B.

In Experiment B, before starting, the rotational speed of the tool spindle 30 is set. The speed is selected according to the tool spindle speed on the multi-function drill with the axial impact drill function in the prior art, and a preferred speed is selected. For 1800 rpm, one of the criteria for judging whether it is better or not can be: select the speed value of the medium upper limit within the speed range under which it is based. Regarding the height of the climbing track, an experiment was carried out by selecting a climbing height of 10 mm. On this basis, the number of the climbing rails is set to two, three, and four respectively, that is, when the number of the climbing rails is two, the hammer 200 rotates once a week, and the tool spindle 30 is impacted. Twice; when the number of climbing rails is three, the hammer 200 strikes the tool spindle 30 three times per revolution; when the number of climbing rails is four, the hammer 200 rotates once a week, impacting the tool spindle 30 Times. Then use the same specification of the working head, that is, the drill bit, to perform the same depth drilling experiment on the concrete working face of the same material, and record the corresponding drilling completion time in seconds (S). Conventional passive impact drills are also involved in the comparison. The traditional passive impact here refers to the impact structure of the axial impact by the engagement of the static and static teeth.

The traditional electric and static end-tooth impact structure of the electric drill is also involved in the comparison.

In this experiment, four samples were given, namely “Sample 1”, “Sample 2”, “Sample 3”, and “Sample 4”. Among them, “Sample 1” represents the cam-type active impact drill, and the climbing section The number is two; "sample 2" means that the cam type active impact drill has three climbing sections; "sample 3" represents the cam type active impact drill, and the number of climbing sections is four; "Sample 4" indicates that the impact drill uses a conventional passive impact structure, that is, a passive impact structure of a static and static end tooth type. In addition, this experiment uses the average method, that is, each sample is subjected to a group of experiments, each group of experiments is repeatedly operated six times, and six times of punching operations are repeated, and each time of operation is recorded, and the average is taken. The value gives the average drilling time value for each set of experiments for each sample.

When the height of the climbing track is 9mm, the specific experimental data during the experiment is shown in Figure 1 below, and the experimental results of the corresponding output are as shown in the column chart, Table 2.

In Figure 1, "the curved surface guide includes two climbing sections", "the curved guiding portion includes three climbing sections", and the "surface guiding portion includes four climbing sections" respectively refers to the climbing in the active impact structure in the impact drill The number of tracks is set to two, three, or four, respectively. "Drive passive impact" refers to the impact structure in the impact drill using a dynamic and static end-toothed impact structure.

Chart 1

According to the experimental values and the average value information of Fig. 1, it can be found that under the same working conditions, the same drill bit is used to punch the same depth of holes on the same material, and the time required for different impact structures is not the same. Among them, the least time is 5 seconds, that is, the number of climbing rails is three active impact structures, that is, when the climbing track is set to three, and the impact of the hammer is three times per revolution, the time is the shortest. The most efficient. The second time is 6.33 seconds, that is, the active impact structure with four climbing track numbers, that is, when the number of climbing tracks is set to four, and the impact of the hammer for four times per revolution, the time used. The second is short and the efficiency is second highest. Next, the third time in use is 7.86 seconds, that is, the active impact structure with two climbing track numbers, that is, when the climbing track is set to two, and the hammer strikes twice per rotation, The time taken is greater than the impact of the hammer three or four times per revolution, ranking third and efficiency third. The longest time is 8.15 seconds, which is the transmission passive punching structure. That is to say, the transmission passive impact structure takes longer than the active impact structure, that is, the impact drilling efficiency of the passive impact structure is smaller than that of the active impact structure. effectiveness.

The above conclusion can be expressed more intuitively in the following chart 2, which is a histogram derived from the average value information in the chart 1.

Chart 2

As shown in Figure 2, it can be intuitively found that the same task under the same conditions is completed, and the active impact structure has a shorter drilling time than the transmission impact structure. Moreover, in the active impact structure, when the number of climbing rails is set to three, the drilling time is the shortest, followed by the number of climbing rails is four, and the number of climbing rails is set to two, the drilling time longest.

Here, the drilling efficiency is compared by drilling time, because the same work task is completed under the same working conditions, and the shorter the drilling time, the higher the drilling efficiency.

Later, the high-speed climbing was changed to 8mm and 9mm, and two sets of experiments were carried out under the same experimental conditions. The experimental results were the same as those of the climbing height of 10 mm: the time spent on the active impact structure drilling Less time than the passive impact impact structure of the transmission. Moreover, in the active impact structure, when the number of climbing rails is three, the time used is the shortest, the number of climbing rails is four, the time used is second, and the number of climbing rails is two, the most time is used. long.

Therefore, when the rotational speed of the ram is (1000-2500) revolutions per minute and the number of climbing rails is (2-4), the drilling efficiency will be the highest.

Regarding the height of the hill-climbing track, the present invention also gives an optimum range (4-15) mm, and experiment C is performed to verify this numerical range.

When the rotational speed of the ram and the tool spindle and the number of climbing rails satisfy an optimal range, the height of the climbing rail affects the magnitude of the impact energy and the axial length of the fuselage. In other words, in the case where the tool spindle and the ram are fixed and the number of the climbing track is constant, the higher the height of the climbing track, the larger the amount of spring compression, the greater the energy saved, and the ram is obtained. The hit energy is also greater. However, if the height of the climbing track is too high, the axial length of the ram is longer, which undoubtedly increases the length of the whole machine.

Before the start of experiment C, the experimental conditions were first set: the rotational speed of the ram was set to 1800 rpm according to the above-mentioned rotational speed range, and the number of climbing tracks was set to three. On the basis of this, the data of the correspondence between the height of the climbing track and the impact energy of the impact ram is shown in Table 3 below. The "impact energy" here refers to the energy generated by a single impact of the hammer, rather than the accumulated impact energy when the hammer is rotated one revolution.

Chart 3

According to the data in Figure 3, it can be found that when the height of the climbing track is less than 4mm, the impact energy will be less than 0.1J. Since the drilling target of the active impact drill includes concrete, the work of the hardness material has certain requirements for the impact energy, and the impact If the energy is too low to break the working surface of the hardness material, or if it is barely capable of breaking, it is impossible to work within the normal drilling efficiency. Therefore, when the track height is less than 4 mm, it is considered that the demand for a certain breaking energy cannot be satisfied.

When the height of the climbing track is 15mm, the impact energy is 0.9J, which should be able to meet the working surface of the universal high hardness material to which the impact drill is adapted. When the climbing height is greater than 15mm, the impact energy obtained by the hammer lock can be satisfied, even if the excess is satisfied, and the climbing shaft height is greater than 15mm, the axial length of the whole machine is also increased. Therefore, the height greater than 15mm is not the preferred range. .

In addition, there is a climbing angle with respect to the climbing section, that is, the inclination of the climbing surface of the climbing section with respect to the horizontal plane, and the horizontal plane refers to the surface perpendicular to the ram axis or the tool spindle axis. In the present invention, based on the foregoing technical solution, combining the climbing angle range of the climbing section makes the present invention have a better effect. Regarding the climbing angle, if the climbing angle is too small, the circumferential length of the ram or the circumferential surface of the guiding member is limited, and the number of the periodic segments is limited, that is, the number of the climbing segments is also limited. If the climbing angle is too large, the probability that the ram will block during the climbing process will become larger. Based on the above considerations, in the present invention, the climbing angle is set in the range of 5-25 degrees, so that the number of climbing sections on the curved guiding portion is neither restricted, and the ram is not prone to climb and climb. Stalling phenomenon.

Further, in the present invention, in order to include that the ram does not block, the power supplied by the motor also needs to be within a certain range, and the power range is at least 180-300 W.

In addition, in the present invention, the rotational speed of the motor shaft is 18000-26000 rpm, and in order to obtain the rotational speed range of 1000-2500 rpm of the ram or the tool spindle, the required reduction ratio of the planetary gear transmission is 7.2. The range of -26.

In addition, for the climbing section and the falling section included in the curved surface guiding portion of the present invention, it is necessary to explain that the climbing section can drive the ram to move in the axial direction through contact with the conversion member, that is, the steel ball, that is, climbing the slope. . For the drop section, in the present invention, the drop section is formed with a drop space for dropping the ram in the space. The steel ball as the conversion member should be understood by the drop section as follows: the steel ball is in the falling space formed by the falling section, and in other embodiments, it can also be understood that the steel ball is on the surface of the curved guiding portion of the falling section.

In other embodiments, the drop segment is also operable. For example, if the drop segment is disposed obliquely and extends away from the climbing segment in the circumferential direction of the guide, reference may be made to the illustration of the drop segment in FIG. In this technical solution, the steel ball can be slowly slid down along the drop segments CD, C1-D1, C2-D2. The effect is to make the steel ball at the highest point of the climbing section. When the motor suddenly stops, the steel ball can follow the falling section. The slope slowly slides down, avoiding the steel ball directly hitting the tool spindle, because the hammer hits the tool spindle during the stop state, which will produce a bad operating experience.

In addition, in other embodiments, the hammer impact mechanism of the present invention may also be used in combination with a non-electric drill type tool, as long as the tool requires the function of the hammer impact mechanism, such as an electric hammer, etc., and will not be enumerated here.

In addition, in other embodiments, the hammer impact mechanism of the present invention can also be detachably mounted as an accessory and the main body of the electric drill. When the active impact function is required, the attachment is installed, and when the active impact function is not required, Replace the accessory with another functional accessory you need. The attachment with the hammer impact mechanism is more convenient to use, and also allows the tool to have a variety of functions.

Referring to FIG. 37, in the illustrated embodiment, the attachment 730 can be detachably coupled to the tool body 740. Wherein, the attachment 730 includes a hammer impact mechanism 20, and a tool spindle 30 capable of receiving intermittent reciprocating axial impact from the hammer impact mechanism 20, in particular, the tool spindle can receive an axial reciprocating impact from the ram 200 .

The accessory 730 further includes an accessory housing 731 for accommodating the hammer impact mechanism 20. The tool body 740 includes a main body housing 741 capable of accommodating a motor in the tool body 740 and a speed reduction mechanism, etc., the accessory housing 731 and the main body housing The body 741 can be detachably connected, and the specific connection manner can be tightened by screws; the axial connection can also be made by a snap-fit manner, and the circumferential connection is performed by a form fit.

In the present embodiment, the attachment 730 further includes a connecting shaft 733 that is coupled to the tool spindle 30 in a rotationally fixed manner to enable rotation of the tool spindle 30, and the connecting shaft 733 is also rotatable relative to the hammer 200. The connection is performed to drive the ram 200 to rotate relative to the guide member 210, thereby implementing the hill-climbing movement compression accumulating mechanism 231, thereby causing the accumulator mechanism 231 to drive the ram 200 against the tool spindle 30.

In the present embodiment, the tool body 740 further includes an output shaft 742 that is rotatably output. When the accessory 730 is mounted with the hand tool body, the output shaft 742 is rotatably coupled to the connecting shaft 733 to rotatably drive the rotation of the connecting shaft 733. In turn, the rotation of the tool spindle 30 and the hammer 200 is driven. The output shaft 742 on the tool body 740 herein is two shafts different from the tool spindle 30 on the attachment 730. The tool spindle 30 is the one used to receive the impact of the hammer 200, and the output shaft 742 is a tool. A shaft on the body 740 is used as an output on the tool body 740 that can be mated with other types of accessories to perform other corresponding functions.

In the present embodiment, the attachment 730 further includes a mounting assembly 732 detachably coupled to the tool spindle 30 for mounting the working head on the tool spindle 30 to enable the tool spindle 30 to rotatably drive the working head for rotation.

Wherein, the specific structure of the mounting assembly 732 is not shown in FIG. 37. Referring to the structure in the embodiment of FIG. 23, the mounting assembly 732 may preferably be a jaw-type drill chuck, mainly including capable of clamping or loosening work. The jaws of the head, the core body for mounting the jaws, and the nut sleeve capable of moving the jaws forward and backward by the screw drive, etc., are not described herein again.

In other embodiments, the mounting assembly can also be other forms of mounting components that can be mounted with a working head, such as a mounting assembly (not shown) that includes a clutch member that can optionally engage the tool spindle with the working head. The axial connection, in particular, the clutch member may be a steel ball that moves between the two positions in the groove to switch the tool spindle and the working head in both the axial connection and the axial separation mode. The mounting assembly also includes an operating member that is operable to move the steel ball from the axially coupled position to the axially separated position. The mounting assembly also includes a reset member, which is generally a spring that provides a biasing force to move the steel ball from the axially disengaged position to the axially coupled position. The rotary connection between the tool spindle and the working head in the mounting assembly is achieved by a form fit. For example, the tail of the working head may be an outer hexagonal cylinder, and the free end of the tool spindle may be set as an inner hexagonal hole. In addition, the mounting assembly can also refer to the batch head on the screwdriver and the corresponding tool spindle mounting structure, and the mounting structure of the hammer head and the tool spindle on the hammer, which will not be described herein.

In the embodiment of Fig. 37, the hammer impact mechanism included in the attachment is the same as the hammer impact mechanism described above, and the hammer 200 in the hammer impact mechanism 20 is capable of reciprocally striking the tool spindle 30. In this embodiment, the hammer impact mechanism 20 includes a ram 200, a guide 210, a curved guide portion 233 provided on the guide, and a conversion member 232, which is a steel ball provided on the ram 200, abuts against the ram 200. Energy storage mechanism 231. When the ram 200 rotates relative to the guide 210, the engagement of the curved guide 233 with the conversion member 232, that is, the steel ball, enables the ram 200 to move in the first direction while the energy storage mechanism 231 stores energy. When the energy storage mechanism 231 completes the energy saving, that is, when the ram 200 climbs to the highest point of the climbing section of the curved guide portion, the energy storage mechanism 231 drives the ram 200 to move in the second direction, thereby impacting the tool spindle 30.

In addition, in the embodiment shown in FIG. 37, the attachment 730 having an impact function includes a hammer impact mechanism 20, a mounting assembly 732, a tool spindle 30, and a coupling shaft 733 that drives the tool spindle 30 and the hammer 200 to rotate.

In other embodiments, the accessory may not include a mounting component.

In other embodiments, the accessory may not include the connecting shaft, that is to say, in this embodiment, the accessory includes a hammer impact mechanism and a tool spindle, and the tool spindle is used to intermittently reciprocate the hammer, the tool spindle and the tool body. The output shaft 742 of the 740 is rotatably connected, and the tool spindle drives the ram or one of the guide members to rotate, so that the ram can climb the slope, thereby realizing the impact under the action of the energy storage mechanism. In this embodiment, the tool spindle can also Rotate the rotating work of the working head.

In the present invention, "non-rotatably connected" can be understood to mean that one element can drive another element to rotate, and the rotational speed of both is the same.

Therefore, in the cam type active impact structure, the ram is ramped along the axis under the action of the cam track, that is, the curved guide portion, thereby implementing the impact on the tool spindle by the energy storage mechanism. In different embodiments, the cam track, that is, the position where the curved guide portion is disposed may also be different, and may be disposed on the ram or on the guide member; the positional relationship between the guide member and the ram is also set. Differently, the guiding member may be on the outer circumferential side of the ram or on the inner circumferential side of the ram; and the ram and the guiding member may be both the rotating and the axial movement of the ram, the guiding member is fixed, or It is the ram that does not rotate and only moves axially, and the guide rotates. Therefore, the manner in which the ram and the guide member and the cam track are disposed is not limited to this embodiment, and structural combination may be performed with each other as long as the axial movement of the ram can be realized. Such an axially moving ram can provide an energy storage opportunity for the energy storage mechanism to prepare for impacting the tool spindle. In the embodiment in which the ram only moves axially and does not rotate, the "relative rotational speed" is understood to be the relative rotational speed at which the ram rotates relative to the guide.

In the present embodiment, the rotational speed of the ram affects the amount of striking energy accumulated per unit time, and the probability that the steel ball hits the track. Therefore, the rotational speed of the ram and the number of times the ram climbs a week, that is, climbing An optimal combination of the number of slope tracks is made to obtain a relatively high energy output per unit time without stalling. The numerical range setting of the optimized combination also satisfies other embodiments, as long as the active impact structure of the embodiment includes a ram, a cam track, and the number of the climbing tracks in the cam track affects the axis generated by the rotation of the ram. The number of collisions. Of course, the same applies to the embodiment in which the ram only moves axially and does not rotate. For example, in this embodiment, the ram does not rotate only axially, the cam guide is disposed inside the ram, and the cam track is disposed at On the outer circumferential surface of the cam guide, the rotation of the cam guide causes the rotation of the cam track to drive the ram to move axially. In this embodiment, the optimized combination of the present invention is such that the relative rotational speed of the ram relative to the guide rotates in the range of 1000-2500 rpm, and the number of climbing tracks of the cam track is 2-4. It can satisfy the highest possible impact energy under the condition that no steel ball hits the track. In this embodiment, the relative rotational speed of the ram relative to the rotation of the guide member is also the rotational speed of the guide member.

In the embodiment shown in FIG. 31, the transmission shaft 10 and the tool spindle 30 are rotatably connected by a flat side, and the transmission shaft 10 and the ram 200 are selectively rotatably connected by the clutch member 221, and therefore, in the present embodiment, The tool spindle 30 has the same rotational speed as the hammer 200. Therefore, in Experiment A, it is also the optimal combination of the rotational speed range of the tool spindle and the number of climbing rails. The technical effect obtained is: obtaining the highest possible drilling hole under the condition that the steel ball collision track is not met. effectiveness.

In addition, in the embodiment of Fig. 31, the drive shaft 10 is rotationally coupled to the tool spindle 30 and the ram 200 such that the output shaft 30 can be aligned with the ram 200 at a rotational speed to achieve a higher impact. If the output shaft 30 and the ram 200 have a speed difference in the rotational speed, then the ram 200 will also rotate relative to the output shaft 30 while striking the output shaft 30, which will cause energy loss and reduce the impact effect. . Here, "rotational connection" can be understood as a rotary drive, ie the rotation of the drive shaft 10 can be simultaneously transmitted to the tool spindle 30 and the ram 200.

In the present embodiment, the transmission shaft 10 is sleeved outside the output shaft 30, and the ram 200 is sleeved outside the transmission shaft 10. The sleeve relationship in the present embodiment is such that the transmission shaft 10, the output shaft 30, and the ram 200 The projections in the axial direction are at least partially overlapped, or the ram 200 encloses the drive shaft 10 and the tool spindle 30 in at least one plane, saving axial dimensions and reducing the length of the fuselage in the axial direction, Make the overall body short and compact.

In the present embodiment, the guide member 210 is sleeved on the outer circumferential side of the ram 200, and the guide member 210 surrounds the ram 200, the tool spindle 30, and the drive shaft 10 that drives the ram 200 to rotate, at least in one plane. In this technical solution, the projections of the guide member 210, the ram 200, the tool spindle 30 and the transmission shaft 10 in the axial direction are at least partially overlapped, which saves the axial dimension and makes the length of the whole machine short and compact. In this embodiment, the guiding member is sleeve-shaped and sleeved outside the ram. In other embodiments, the guiding member may not be sleeve-shaped, as long as the matching with the ram can be realized to realize the axial movement of the ram. Just fine.

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, wherein the transmission mechanism includes a transmission shaft that is rotated and output through a motor and a gear reduction mechanism, and the tool spindle is driven. The shaft is driven by rotation, and the tool spindle can rotate and drive the working head to realize the rotating operation of the hand tool. Moreover, the tool spindle also needs to bear the impact of the hammer impact mechanism, thereby transmitting the axial impact to the working head. The hammer impact mechanism includes an impact shaft that is capable of driving rotation of the ram relative to the guide member, and the rotational drive of the impact shaft can be achieved directly or indirectly by the drive shaft. Here, the impact shaft can drive the rotation of the ram relative to the guide member. It can be understood that the impact shaft drives the ram and the one of the guide members to rotate, so that the relative rotation between the ram and the guide member can be generated, thereby enabling the ram to be opposite. The guide climbs up so as to be able to strike the tool spindle under the drive of the energy storage mechanism.

In the present invention, the tool spindle, the drive shaft, and the impact shaft have corresponding functions. In the present invention, three shafts having the above-described corresponding functions are indispensable, but in other embodiments, the tool spindle can also function as The impact shaft, that is to say, has one shaft that has two functions: it can rotate the driving head, and can also drive the ram to rotate relative to the guide. In other embodiments, the drive shaft can also act as an impact shaft, that is, the drive shaft drives both the rotation of the tool spindle and the rotation of the ram relative to the guide.

In addition, after analysis and research, it is found that during the operation of the impact mode, there is also a situation in which the steel ball collides with the orbit. Specifically, referring to FIG. 23-3, when the lifting tool tool spindle 30 is separated from the working surface, since the hand tool 1 is not subjected to the axial abutting force, the tool spindle 30 will be under the bias of the reset member 70. Press the position to the release position. Fig. 31 is a view showing a state in which the tool spindle 30 is in the depressed position, and Fig. 32 is a view showing a state in which the tool spindle 30 is in the release position. During the impact mode operation, the tool spindle 30 is in the depressed position, which is closer to the ram 200 in the axial direction than the release position, and the spring is still compressed before the ram 200 strikes the tool spindle 30. The state, that is, the spring has accumulated energy is being prepared to be released. At this time, if the tool spindle 30 is separated from the work surface, the tool spindle 30 will be in the release position, that is, further away from the hammer 200, so that the impact surface of the hammer 200 will occur before the impact surface of the tool spindle 30 contacts. Upon impact on the curved surface guide portion 233 on the inner circumferential surface of the guide member 210, a steel ball collision orbit phenomenon occurs again. The hazard caused by the collision of the steel ball in this case is that the ram impacts the track and transmits it to the casing, which causes the burr to appear on the track, and the hammer is stuck and transmitted to the user through the impact.

The depressed position of the tool spindle 30 refers to the position of the movement of the tool spindle 30 due to the operator's downforce when in the operating state, and the release position of the tool spindle 30 refers to the resetting of the tool spindle 30 when it is not in operation. The position of the movement under the influence of 70. The axial distance between the tool spindle 30 and the ram 200 can be understood as the axial distance between the impact surface of the tool spindle 30 and the impact surface of the ram 200, and the tool spindle 30 is closer to or away from the ram in the axial direction. 200 can also make this understanding. The impact surface can be understood as the end face when the hammer 200 and the tool spindle 30 are axially impacted during the impact mode operation.

In order to solve the above problems, the present invention provides a technical solution in which a cushioning member 710 is disposed between the ram 200 and the impact mechanism housing 720 along the impact direction of the ram 200, so that after the tool spindle 30 is returned to the release position, The ram 200 directly hits the cushioning member 710 to unload the impact energy applied to the ram 200 by the accumulator mechanism 231, preventing the ram 200 from directly hitting the impact mechanism housing 720. The position of the cushioning member 710 is between the ram 200 and the impact mechanism housing 720, where "between" can be understood as between the two end faces of the ram 200 and the impact mechanism housing 720 or both Between the planes where the end faces are located, or it can be understood that the position of the cushioning member can satisfy the impact of the hammer 200 to the free end of the tool spindle 30, and the impact energy can be released to the cushioning member 710 first, and the cushioning member 710 can also be A small amount of energy is released onto the impact mechanism housing 720.

The cushioning member 710 may be a rubber ring or a spring member. In the present embodiment, a rubber ring is used, and in the present embodiment, the cushioning member 710, specifically the rubber ring, can be substantially compressed by the hammer 200. 2mm. The amount of compression of the rubber ring that can be compressed by the ram 200 affects the impact stroke and the buffering effect; if the compression amount is too large, the impact stroke is much reduced, and it needs to be compensated by the lengthening of the whole machine. If the compression amount is too small, the buffering effect is lowered.

Another embodiment of the present invention will now be described with reference to Figures 1 - 38, which detail a hand tool 1 in accordance with various embodiments of the present invention. It is to be understood that the following description is only illustrative and not restrictive.

The hand tool 1 provided in the embodiment of the present invention may include a housing 80, a power mechanism, a tool spindle 30, a hammer impact mechanism 20, and the like. Wherein, the hammer impact mechanism 20 may include: an intermittent impact assembly 230, a ram 200, and a guide 210. The specific composition, function, structure, and the like of the above various components in the hand tool 1 can be referred to the specific description in the above embodiments.

The intermittent impact assembly 230 may include: a curved surface guiding portion 233 disposed on one of the ram 200 and the guiding member 210, a conversion member disposed on the other, and abutting the ram 200 The energy storage mechanism 220, when the ram 200 rotates relative to the guide 210, the curved guide portion 233 causes the ram 200 to overcome the force of the energy storage mechanism 220 toward the first through the conversion member In the directional movement, the energy storage mechanism 220 drives the ram 200 to move in a second direction opposite to the first direction. Wherein, the first direction may be away from the direction of the chuck of the hand tool 1.

In different embodiments, the specific positions of the conversion member and the curved surface guiding portion 233 are different, and their respective corresponding motion states are also different. As shown in FIG. 11, in some embodiments, a curved guide portion 233 may be disposed on an inner surface of the guide member 210; correspondingly, the conversion member may be located in the ram 200. At this time, the conversion member may be the conversion member 232 described in the above embodiment. In use, the conversion member 232 can guide the ram 200 to rotate relative to the guide member 210 against the urging force of the energy storage mechanism 220. At this time, the conversion member 232 can perform a hill climbing motion in the curved surface guide portion 233.

In other embodiments, the curved guide portion 233 may be disposed on an outer surface of the ram 200. Accordingly, the conversion member may be fixed to an inner surface of the guide member 210. In use, the guide member 210 and the conversion member may be in a stationary state, the ram 200 drives the curved surface guiding portion 233 to rotate relative to the guiding member 210 and the conversion member, and the ram 200 provided with the curved surface guiding portion 233 is at the conversion member and the curved surface guiding portion. With the cooperation of 233, the force of the energy storage mechanism 220 is overcome to move in the first direction.

The power mechanism may include a motor 60 and a speed reduction mechanism 601 for decelerating the output speed of the motor 60. Specifically, the speed reduction mechanism 601 can be a three-stage planetary gear reduction mechanism 601. Of course, the speed reduction mechanism 601 can also be in other forms, which is not specifically limited herein.

The tool spindle 30 can be a rotary body having a central axis. The tool spindle 30 is driven by the power mechanism and is rotatable about a central axis. Wherein, the body of the tool spindle 30 extends along the longitudinal direction, having a first end remote from the power mechanism and a second end adjacent to the power mechanism. The first end of the tool spindle 30 is provided with a collet for mounting the working head. The second end of the tool spindle 30 can be directly connected to the speed reduction mechanism 601 in the power mechanism. Of course, the second end of the tool spindle 30 can also be indirectly connected to the speed reduction mechanism 601 through the intermediate transmission member. The intermediate transmission member may be the transmission shaft 10. Of course, the intermediate transmission member may be in other manners, which is not specifically limited herein.

For a hand tool, it has at least an impact drilling mode. In the case where the hand tool is in the impact drilling mode, that is, for impact drilling, the tool spindle 30 rotates about the central axis, and the hammer 200 is opposite to the guide 210. While the rotary motion is being engaged, the intermittent impact assembly 230 cooperates with the guide member 210 to reciprocate along the central axis direction to periodically strike the tool spindle 30. Subsequent tool spindle 30 transmits torque and impact forces to the working head on the chuck for impact drilling.

The work head may be a drill bit. Of course, the work head may also be different according to the actual application scenario, and the present application is not specifically limited herein. The case where the ram 200 rotates relative to the guide 210 is specifically a speed difference between the ram 200 and the guide 210. Specifically, the ram 200 and the guiding member 210 can be rotated one by one; and the ram 200 and the guiding member 210 can also rotate. When both the ram 200 and the guiding member 210 are rotated, the ram 200 and the guiding member 210 can rotate in the same direction with a speed difference, or the ram 200 and the guiding member 210 can be reversely rotated with a speed difference.

The hand tool 1 can have multiple functional modes, for example, it can include: an impact mode and a non-impact mode. In the impact mode, it may be specifically an impact drilling mode or the like; in the non-impact mode, it may be specifically a screwdriver mode. Of course, the specific function mode can be adaptively integrated and selected according to actual needs, and the present application does not specifically limit it. Correspondingly, a multi-function hand tool can also be provided with a mode adjustment mechanism to switch between different modes. For details, refer to the detailed description in the embodiment 2, and the details are not described herein.

The tool spindle 30 serves as a transmission shaft on the one hand for transmitting the torque of the power mechanism to the chuck, thereby driving the working head in the chuck to rotate; on the other hand, as the impacted member during the impact, the hammer 200 is to be hit. The impact force after the impact is transmitted to the working head through the collet, thereby achieving the impact drilling of the working head. The tool spindle 30 also does not impact the shaft in some embodiments.

The hand tool 1 has a first housing portion 650 for receiving the hammer impact mechanism 20. Specifically, the cross-sectional shape of the outer contour of the first casing portion 650 may be a circular shape, and may be other shapes, such as a regular polygon, etc., which is not specifically limited herein. The following is an example in which the cross-sectional shape of the outer contour of the first casing portion 650 is a circle, and other shapes may be referred to analogously, and the details are not described herein again.

Since the hammer impact mechanism 20 and the mode adjustment mechanism 40 are reasonably distributed at the first casing portion 650, the radial dimension of the first casing portion 650 can be controlled within a predetermined size range, for example, 45 mm to 70 mm. between. Specifically, the mode adjustment mechanism 40 and the hammer impact mechanism 20 at least partially overlap radially. When the mode adjusting mechanism 40 and the hammer striking mechanism 20 have overlapping portions in the radial direction, the radial dimension can be saved, and the radial dimension at the first casing portion 650 is limited to a smaller extent as much as possible. Thereby, the body is compact and compact, the operation is convenient, and the user experience is better.

Specifically, the mode adjustment mechanism 40 radially overlaps at least a portion of at least one of the guide 210 and the ram 200.

For example, as shown in FIG. 21, the mode adjustment mechanism 40 includes an impact switching ring 430 that partially overlaps the guide 210 in the radial direction. Further, in addition to the radial overlap of the guide member 210 and the impact switching ring 430 (i.e., the projection in the radial direction has a coincident portion), in order to ensure that the radial dimension at the first cabinet portion 650 is controlled within a predetermined size range, the hand-held Other components in tool 1 can also be reasonably overlapping in the radial direction. Of course, other components may be expanded and arranged according to actual needs, and the present application is not specifically limited herein. Specifically, the radial dimension of the first casing portion 650 of the hand tool 1 can be adapted according to the specific model of the hand tool 1, the operating parameters, the component configuration, and the like.

For example, as shown in FIGS. 19 and 20, in particular, the mode adjustment mechanism 40 may include an impact switching ring 430 and a mode switching button 450. At least one of the impact switching ring 430 and the mode switching button 450 at least partially radially overlaps the guide member 210.

The mode switch button 450 operatively drives the impact switch ring 430 to move between a first position and a second position. When the impact switching ring 430 is in the first position, the impact switching ring 430 is engaged with the hammer impact mechanism 20, and the relative rotation between the guiding member 210 and the ram 200 can be generated. In the impact mode; when the impact switching ring 430 is in the second position, the impact switching ring 430 is separated from the hammer impact mechanism 20, and the relative rotation between the guiding member 210 and the ram 200 is not possible. The hand tool 1 is in a non-impact mode.

The impact switching ring 430 can cooperate with the guiding member 210 in the hammer impact mechanism 20 to switch between the impact mode and the non-impact mode of the hand tool 1. Specifically, the guiding member 210 is provided with a first rib 212, and the impact switching ring 430 is provided with a second rib 431. In the impact mode, the first rib 212 and the second tooth The rib 431 is engaged; in the non-impact mode, the first rib 212 is disengaged from the second rib 431.

In other embodiments of the present invention, the mode adjustment mechanism 40 can also adopt other configurations. Specifically, referring to FIGS. 2-5, 9, and 13, the mode adjustment mechanism 40 includes a pressure limiting ring 410 and a mode adjustment knob 420. . The pressure limiting ring 410 is an impact switching ring for cooperating with the mode adjusting button 420 to implement an impact switching function. The check ring 410 has an overlapping portion with the guide member 210 and the ram 200 in the radial direction.

Specifically, the mode switching button 420 is rotatably connected to the housing 80, and the impact switching ring has no relative rotational connection with respect to the housing 80, and the mode switching button 420 drives the impact switching ring along the tool. The central axis of the spindle 30 moves.

The hand tool 1 provided in the embodiment of the present invention has a radial dimension of 45 mm at the first casing portion 650 in order to enable it to enter a small space and to make the appearance dimension more harmonious. 70 mm range. When the radial dimension at the first casing portion 650 of the hand tool 1 is within the above range, the ratio of the outer diameter of the hammer striking mechanism 20 to the radial dimension of the first casing portion 650 is between 0.6 and 0.9.

The ratio of the outer diameter of the hammer impact mechanism 20 to the radial dimension of the first casing portion 650 may vary depending on the configuration of the components of the hand tool 1. According to some embodiments of the invention, the hand tool 1 may also include a torque adjustment mechanism that can be used to adjust the output torque to accommodate different application conditions.

Specifically, the torque adjustment mechanism includes any one of the following: a mechanical torque adjustment structure, and an electronic torque adjustment mechanism. The ratio of the outer diameter of the hammer impact mechanism 20 to the radial dimension of the first casing portion 650 is in a different range depending on the torque adjustment mechanism.

As shown in Figures 21 and 22, in one embodiment, the torque adjustment mechanism can be a mechanical torque adjustment mechanism. The mechanical torque adjustment mechanism may generally include an adjustment cover rotatably disposed on the casing of the hand tool 1, an adjustment unit mated with the adjustment cover, a cushioning member 440 mated with the adjustment unit, and the like. The adjusting unit can adjust the amount of compression of the cushioning member 440 when the adjusting cover rotates, thereby adjusting the amount of preloading of the accumulator mechanism 231 in linkage with the axial direction. The adjustment unit can be in the form of an impact switching ring 430. The inside of the adjusting cover may be provided with an internal thread, and the corresponding outer side of the impact switching ring 430 is provided with an internal thread matched with the internal thread, and the two are connected by a threaded fit.

Since the adjusting cover takes up a certain radial dimension, the ratio of the outer diameter of the outer diameter of the hammer striking mechanism 20 to the first casing portion 650 is generally not more than 0.9 at the adjusting cover.

As shown in FIG. 38, in another embodiment, the torque adjustment mechanism can be an electronic torque adjustment mechanism. The electronic torque adjustment mechanism may generally include a current threshold setting unit electrically connected to the controller, a current detecting unit, and the like.

When in use, the user can select the desired current threshold through the current threshold setting unit according to the actual working condition. After the hand tool 1 is started, the current detecting unit detects the operating current of the motor. When the working current reaches the selected current threshold, the controller issues a specific control command to control the operation of the motor or the like. The current threshold setting unit may be specifically in the form of a knob, and may of course be in other forms. The current threshold setting unit may be disposed on the casing of the handle position of the hand tool 1. The current detecting unit can set the inside of the casing at the handle position.

Since the electronic torque adjustment mechanism is opposite to the mechanical torque adjustment mechanism, it is not necessary to provide the mechanical adjustment cover and the adjustment unit at the first casing portion 650, and the radial dimension is not additionally occupied, so the outer diameter of the hammer impact mechanism 20 is The radial dimension ratio of the first casing portion 650 can be controlled to be not less than 0.6. When the ratio of the outer diameter of the hammer impact mechanism 20 to the radial dimension of the first casing portion 650 is less than 0.6, the arrangement between the various components in the first casing portion 650 is less rational, the space utilization ratio is lower, and the space is increased. The radial dimension of the first housing portion 650.

For example, in a case where the hammer impact mechanism 20 is properly arranged, the size of the first casing portion 650 and the hammer impact mechanism 20 is a casing disposed outside the hammer impact mechanism 20, and at this time, the hammer impact mechanism 20 The ratio of the radial dimension to the first casing portion 650 may be 0.6 or more, and the theoretically larger the better, it may be close to about 0.9.

According to some embodiments of the present invention, the rotational speed of the power mechanism output is the same as the rotational speed of the impact shaft, wherein the impact shaft can drive the ram 200 to rotate relative to the guide 210. The mode adjustment mechanism 40 is at least partially axially overlapped with the hammer impact mechanism 20, and when the mode adjustment mechanism 40 and the hammer impact mechanism 20 at least partially overlap in the axial direction, that is, the mode adjustment structure and the hammer impact mechanism 20 are axially projected. When the overlapping portion is provided, the length of the whole tool of the hand tool 1 is reduced, so that the appearance ratio of the whole machine is coordinated, and the user is convenient to hold.

The impact shaft may be a shaft that can cause the ram 200 to rotate relative to the guide member 210. In particular, the impact shaft can be different in different embodiments. For example, for an embodiment having both the transmission shaft 10 and the tool spindle 30, as shown in FIG. 21, the impact shaft is a transmission shaft 10, and the transmission shaft 10 can drive the ram 200 to rotate relative to the guide member 210; or, as shown in FIG. As shown, the impact shaft is a tool spindle 30 that can drive the ram 200 to rotate relative to the guide member 210.

In the hand tool provided in the embodiment of the present specification, since a plurality of climbing rails are arranged in the circumferential direction between the ram 200 and the guiding member 210, the shaft (the transmission shaft 10) directly connected to the output end of the power mechanism is rotated one time. In this case, the ram 200 can achieve multiple impacts to achieve better impact efficiency without the need to provide an additional ram speed increase mechanism.

In general, the axial length of the body of the hand tool 1 provided by the embodiments of the present specification may be 185 mm to 250 mm. The axial length may be the length of the body of the hand tool 1 in the direction of the axis corresponding to the tool spindle 30. Specifically, the axial length of the body of the hand tool 1 may include a housing 80 and a portion of the collet 50 that extends out of the housing 80, but does not include a working head (bit) portion that is mounted on the collet 50. Generally, the axial length affecting the fuselage mainly includes: a motor 60 disposed in the housing 80, a transmission mechanism, and a hammer impact mechanism 20.

For the hammer impact mechanism 20, after a reasonable structural design, it has basically reached the size optimization. For example, in particular, the mode adjustment mechanism 40 includes an impact switching ring 430 that partially overlaps the guide 210 in the axial direction. Further, the respective components of the hammer impact mechanism 20 are also overlapped with each other in the axial direction. For example, the guide member 210 and the ram 200 at least partially overlap in the axial direction. The intermittent impact assembly is also at least partially superposed in the axial direction between the ram 200 and the guide 210. Overall, the axial length of the body of the hand tool 1 can be between 190 mm and 230 mm. If it is necessary to further reduce the axial length of the body of the hand tool 1, the motor 60 can select a brushless motor under the premise of satisfying the working parameters of the existing hand tool 1, thereby further reducing the axial length of the body of the hand tool 1. . The axial length of the body of the hand tool 1 provided in this specification can be controlled to an average of about 200 mm.

According to some embodiments of the invention, the hand tool 1 may also include a drive shaft 10. Specifically, the transmission shaft 10 is disposed between the power mechanism and the tool spindle 30. The ram 200 is sleeved outside the transmission shaft 10 and is in driving engagement with the transmission shaft 10. The drive shaft 10 can simultaneously drive the ram 200 and the tool spindle 30 to rotate.

When the drive shaft 10 can simultaneously drive the ram 200 and the tool spindle 30 to rotate, since the ram 200 and the tool spindle 30 are simultaneously driven by the drive shaft 10, there is no relative rotation between the two, so that the ram 200 strikes the tool spindle 30. There is no additional energy loss in the circumferential direction, which preferably ensures a large impact energy at the working head.

In addition, in the case where the guide member 210 is stationary and the ram 200 needs to be driven to rotate along the guide member 210, if the output of the ram 200 is not driven by the output shaft 10, an additional transmission mechanism may be required. Or a combination of a transmission mechanism and a power mechanism to drive the ram 200 to rotate relative to the guide member 210. If a new transmission mechanism or a combination of the transmission mechanism and the power mechanism is additionally provided, not only the size of the hand tool 1 is increased, the complexity of the structure and the manufacturing cost are increased, but also the rotation speed between the hammer 200 and the tool spindle 30 is ensured. Consistent, it may be necessary to introduce a new control mechanism.

According to some embodiments of the present invention, the guiding member 210 may be sleeved on the outer side of the ram 200.

A conversion member 232 and a curved surface guiding portion 233 are disposed between the guiding member 210 and the ram 200. The specific shape of the curved surface guiding portion 233 can be configured to guide the movement track of the conversion member 232, and the conversion member 232 can be realized with the ram 200. In conjunction, the ram 200 moves along the trajectory of the curved guide 233 under the action of the conversion member.

As shown in FIG. 11 to FIG. 12, in some embodiments of the present invention, the curved surface guiding portion 233 may be formed in an annular shape, and the curved surface guiding portion 233 may be circumferentially wound in the circumferential direction of the transmission shaft 10, specifically, the curved surface guiding portion 233 A climbing section 233a and a falling section 233b may be included, 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 is extended toward the other end of the climbing section 233a. Among them, a climbing section 233a and a falling section 233b cooperate to form a climbing track. In the circumferential direction of the curved surface guiding portion 233, one or a plurality of climbing rails may be provided according to the circumference of the curved surface guiding portion 233.

With the embodiment in which the guide member 210 is sleeved on the outside of the ram 200, the embodiment in which the guide member 210 is disposed inside the ram 200 can increase the circumference of the curved guide portion 233 such that the curved guide portion 233 is disposed in the circumferential direction. The plurality of climbing tracks can improve the impact frequency of the hand tool 1 under the premise of ensuring that the motor is not blocked, thereby improving the impact efficiency of the hand tool 1.

In some embodiments, the curved surface guiding portion 233 is provided with a plurality of climbing sections 233a and a falling section 233b corresponding to the climbing sections 233a in the circumferential direction, when the conversion member passes the climbing section 233a The ram 200 moves in a first direction; when the conversion member passes the drop portion 233b, the ram 200 moves in a second direction to achieve an impact, and the number of the climbing segments 233a is 2 to 4

When the curved surface guiding portion 233 is provided with 2 to 4 climbing portions 233a in the circumferential direction, when the motor 30 drives the ram 200 to rotate one turn, the number of times the ram 200 strikes in the direction of the tool spindle 30 is equal to the number of times of the climbing portion 233a. It is 2 to 4 times, and it is possible to ensure that the hand tool 1 has a high impact frequency without increasing the rotational speed of the tamper 200 in the circumferential direction.

Further, the ram 200 is movably supported on an inner circumferential surface of the guide member 210.

In some embodiments of the invention, the ram 200 is located within an annular cavity between the guide 210 and the drive shaft 10. Wherein, in the impact mode, the ram 200 reciprocates along the central axis direction in cooperation with the intermittent impact assembly 230 and the guide member 210 to periodically strike the tool spindle 30. The ram 200 moves axially relative to the drive shaft 10 as the ram 200 reciprocates in the direction of the central axis. Applicant has found that 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, the contact friction between the ram 200 and the clutch member 221 during long-term cooperation in transmitting torque is The ram 200 will cause barbs on the inner surface, thereby affecting the axial movement of the ram 200, and in particular, reducing the impact energy of the ram 200 output to the tool spindle 30.

In order to overcome the above problem, the ram 200 can be supported on the inner circumferential surface of the guide member 210 while allowing a clearance fit between the ram 200 and the transmission shaft 10. Specifically, a gap is provided between the inner surface of the ram 200 and the outer surface of the transmission shaft 10, for example, the one-side gap may be 0.1 mm to 0.2 mm. Certainly, the specific value of the small gap is not limited to the above examples, and the present application is not specifically limited herein. The outer surface of the ram 200 can abut against the inner circumferential surface of the guide member 210, and the ram 200 can be driven to rotate by the transmission shaft 10. When the ram 200 rotates, the intermittent impact assembly 230 directs the ram 200 to move linearly relative to the guide 210 in a predetermined path and strike the tool spindle 30 in at least one operating state. During the movement of the ram 200 relative to the guide 210, the trajectory of the ram 200 may be a spiral trajectory in which the circular motion trajectory and the linear motion trajectory are combined.

For example, the composition of the intermittent impact component 230, the structure of the guide member 210, and the principle of forming an active impact can be referred to the detailed descriptions in the first embodiment to the fifth embodiment, and the details are not described herein again.

For the embodiment in which the guiding member 210 is sleeved outside the ram 200 and the ram 200 is supported on the guiding member 210, the curved guiding portion 233 may be disposed on the inner wall of the guiding member 210, and the outer wall of the ram 200 is disposed. There is an insertion groove for mounting the conversion member 232. Specifically, the curved surface guiding portion 233 may be a cam surface formed on the inner wall of the guiding member 210. The cam surface has a climbing section 233a and a falling section 233b. During the movement of the switching member from the climbing section 233a toward the falling section 233b, the elastic member accumulates the elastic potential energy; when the switching member 232 is dropped from the climbing section 233a to the falling section At 233b, the elastic member releases the accumulated elastic potential energy, and the driving hammer 200 impacts the tool spindle 30 to form an active impact.

Other embodiments of the present invention are described in detail below with reference to Figs. It is to be understood that the following description is only illustrative and not restrictive.

The intermittent impact assembly 230 may include: a curved surface guiding portion 233 disposed on one of the ram 200 and the guiding member 210, a conversion member disposed on the other, and abutting the ram 200 The energy storage mechanism 220, when the ram 200 rotates relative to the guide 210, the curved guide portion 233 causes the ram 200 to overcome the force of the energy storage mechanism 220 toward the first through the conversion member In the directional movement, the energy storage mechanism 220 drives the ram 200 to move in a second direction opposite to the first direction. Wherein, the first direction may be a direction away from the chuck of the hand tool 1 .

The power mechanism may include a motor 60 and a speed reduction mechanism for decelerating the output speed of the motor 60. Specifically, the speed reduction mechanism may be a three-stage planetary gear reduction mechanism. Of course, the speed reduction mechanism may also be in other forms, which is not specifically limited herein.

The tool spindle 30 can be a rotary body having a central axis. The tool spindle 30 is driven by the power mechanism and is rotatable about a central axis. Wherein, the body of the tool spindle 30 extends along the longitudinal direction, having a first end remote from the power mechanism and a second end adjacent to the power mechanism. The first end of the tool spindle 30 is provided with a collet for mounting the working head 600. The second end of the tool spindle 30 can be directly connected to the speed reduction mechanism in the power mechanism. Of course, the second end of the tool spindle 30 can also be indirectly connected to the speed reduction mechanism through the intermediate transmission member. The intermediate transmission member may be the transmission shaft 10. Of course, the intermediate transmission member may be in other manners, which is not specifically limited herein.

For a hand tool, it has at least an impact drilling mode in which the tool spindle 30 rotates about a central axis in the case of a hand-held tool in an impact drilling mode, ie for impact drilling, in which the hammer 200 is subjected to the intermittent impact The assembly 230, in cooperation with the guide member 210, reciprocates along the central axis direction to periodically strike the tool spindle 30. The subsequent tool spindle 30 transmits torque and impact forces to the working head 600 on the collet to effect impact drilling. The work head 600 may be a drill bit. The work head 600 may also be different according to the actual application scenario. The present application is not specifically limited herein.

The hand tool can have multiple functional modes, for example, it can include: an impact mode and a non-impact mode. In the impact mode, it may be specifically an impact drilling mode or the like; in the non-impact mode, it may be specifically a screwdriver mode. Of course, the specific function mode can be adaptively integrated and selected according to actual needs, and the present application does not specifically limit it. Correspondingly, a multi-function hand tool can also be provided with a mode adjustment mechanism to switch between different modes. For details, refer to the detailed description in the embodiment 2, and the details are not described herein.

The tool spindle 30 serves on the one hand as a drive shaft for transmitting the torque of the power mechanism to the chuck, thereby driving the working head 600 in the chuck; on the other hand, as the impacted member during the impact, the hammer 200 is to be hit. The impact force after the impact is transmitted to the working head 600 through the collet, thereby achieving the impact drilling of the working head 600.

The following is an analysis of the collision motion in which the ram 200 and the tool spindle 30 participate.

For the ram 200 and the tool spindle 30, it is generally made of a material having a higher hardness, and the collision of the two can be equivalent to a non-elastic collision. For the ram 200, the mass is relatively fixed due to limitations of the axial and radial dimensions of the machine. In the case where the mass of the ram 200 is fixed, in order to obtain higher impact efficiency, the smaller the mass of the tool spindle 30 as the impact member, the greater the impact energy obtained.

Although theoretically, the smaller the mass of the tool spindle 30 as the impacted member, the better, but because the tool spindle 30 functions as the transmission shaft 10, it has a certain strength requirement. Overall, the greater the span of the support bearing for supporting the tool spindle 30, the greater the length of the tool spindle 30, and the larger the diameter of the tool bearing, on the premise that the material of the tool spindle 30 is constant. The strength of the tool spindle 30 is greater.

In summary, in order to make the tool spindle 30 meet the strength requirements, the mass of the tool spindle 30 is reduced as much as possible, and high impact energy is obtained, thereby obtaining better impact efficiency. The mass range of the tool spindle 30 is Between 40 grams and 100 grams.

Specifically, the mass range of the tool spindle 30 can be adaptively adjusted according to actual usage scenarios, such as the magnitude of the transmitted torque. For example, for a small torque hand tool (such as a 20 Nm electric drill), since the transmission torque is small and the shaft strength requirement is small, the diameter of the tool spindle 30 can be made small, so that the mass is small and can be close to or equal to 40 grams.

For high-torque electric drills (such as 80Nm electric drills), due to the large transmission torque, the shaft strength is required to be large, and the diameter of the tool spindle 30 is large, so that the mass is large and can be close to or equal to 100 grams.

According to some embodiments of the invention, the hand tool may also include a drive shaft 10. Specifically, the transmission shaft 10 is disposed between the power mechanism and the tool spindle 30. The ram 200 is sleeved outside the transmission shaft 10 and is in driving engagement with the transmission shaft 10. The drive shaft 10 can simultaneously drive the ram 200 and the tool spindle 30 to rotate.

When the drive shaft 10 can simultaneously drive the ram 200 and the tool spindle 30 to rotate, since the ram 200 and the tool spindle 30 are simultaneously driven by the drive shaft 10, there is no relative rotation between the two, so that the ram 200 strikes the tool spindle 30. There is no additional energy loss in the circumferential direction, which preferably ensures that the working head 600 can output a large impact energy.

In addition, in the case where the guide member 210 is stationary and the ram 200 needs to be driven to rotate along the guide member 210, if the output of the ram 200 is not driven by the output shaft 10, an additional transmission mechanism may be required. Or a combination of a transmission mechanism and a power mechanism to drive the ram 200 to rotate relative to the guide member 210. If a new transmission mechanism or a combination of the transmission mechanism and the power mechanism is additionally provided, not only the size of the hand tool is increased, the complexity of the structure and the manufacturing cost are increased, but also the rotation speed between the hammer 200 and the tool spindle 30 is ensured. It may also be necessary to introduce a new control mechanism.

Further, according to some embodiments of the present invention, the transmission shaft 10 is a hollow rotating body, and a portion of the tool spindle 30 near the first end projects into the transmission shaft 10, and the tool spindle 30 The mass range is between 50 grams and 80 grams.

For the drive shaft 10 provided with a hollow swivel structure, a portion thereof is sleeved outside the tool spindle 30, and an end near the power mechanism cooperates with the bearing for providing radial support for the tool spindle 30. By arranging the drive shaft 10 outside the tool spindle 30, the support function of the partial tool spindle 30 is shared, so that the axial length and diameter of the tool spindle 30 can also be reduced to some extent. Specifically, the mass range of the tool spindle 30 can be reduced to between 50 grams and 80 grams.

For example, for small torque hand tools, such as electric drills, the strength needs to be guaranteed to have a certain safety factor, so that the minimum mass of the tool spindle 30 can be increased to some extent.

For high-torque hand tools, such as electric drills, it is necessary to consider the size of the hand tool head when the torque is guaranteed. If the size is too large, the redundancy and appearance and the accessibility are both problematic. Therefore, the drive shaft 10 and The relationship of the tool spindle 30 sleeve can appropriately reduce the quality of the tool spindle 30 to ensure the optimal combination of size, appearance and performance.

As shown in FIG. 11 to FIG. 12, in some embodiments of the present invention, the curved surface guiding portion 233 may be formed in an annular shape, and the curved surface guiding portion 233 may be circumferentially wound along the circumferential direction of the transmission shaft 10, specifically, the curved surface guiding portion. The 233 may include a climbing section 233a and one drop 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 is extended toward the other end of the climbing section 233a. Among them, a climbing section 233a and a falling section 233b cooperate to form a climbing track. In the circumferential direction of the curved surface guiding portion 233, one or a plurality of climbing rails may be provided according to the circumference of the curved surface guiding portion 233.

With the embodiment in which the guide member 210 is sleeved on the outside of the ram 200, the embodiment in which the guide member 210 is disposed inside the ram 200 can increase the circumference of the curved guide portion 233 such that the curved guide portion 233 is disposed in the circumferential direction. A plurality of climbing tracks improve the impact frequency of the hand tool under the premise of ensuring that the motor is not blocked, thereby improving the impact efficiency of the hand tool.

In some embodiments of the present invention, the ram 200 is located within an annular cavity between the guide 210 and the drive shaft 10. Wherein, in the impact mode, the ram 200 reciprocates along the central axis direction in cooperation with the intermittent impact assembly 230 and the guide member 210 to periodically strike the tool spindle 30. The ram 200 moves axially relative to the drive shaft 10 as the ram 200 reciprocates in the direction of the central axis. Applicant has found that 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, the barbs 200 and the steel ball 221 transmit torque contact friction for a long time. Thus, the axial movement of the ram 200 is affected, in particular, the impact energy output from the ram 200 to the tool spindle 30 is reduced.

In order to overcome the above problem, the ram 200 can be supported on the inner circumferential surface of the guide member 210 while leaving a gap between the ram 200 and the transmission shaft 10. Specifically, a small clearance fit may be provided between the inner surface of the ram 200 and the outer surface of the drive shaft 10, for example, the single-sided gap may be 0.1 mm to 0.2 mm. Certainly, the specific value of the small gap is not limited to the above examples, and the present application is not specifically limited herein. The outer surface of the ram 200 can abut against the inner circumferential surface of the guide member 210, and the ram 200 can be driven to rotate by the transmission shaft 10. When the ram 200 rotates, the intermittent impact assembly 230 directs the ram 200 to move linearly relative to the guide 210 in a predetermined path and strike the tool spindle 30 in at least one operating state. During the movement of the ram 200 relative to the guide 210, the trajectory of the ram 200 may be a spiral trajectory in which the circular motion trajectory and the linear motion trajectory are combined.

For details, the composition of the intermittent impact component 230, the structure of the guide member 210, and the principle of forming an active impact can be referred to the detailed descriptions in the above-mentioned Embodiments 1 to 5, and the details are not described herein again.

In some embodiments of the present invention, referring to FIG. 39, the first end of the tool spindle 30 is provided with a mounting hole 613 for engaging the working head 600, adjacent to the first end of the tool spindle 30. A mounting attachment is provided on the outer side, and the mounting hole 613 and the mounting attachment form a quick-change chuck 610 for mounting the work head 600. After the working head 600 is snapped into the quick-change collet 610, it can move along the central axis.

For the quick change chuck 610, it may be in the form of an SDS (Special Direct System) type output head. Specifically, the body of the quick change chuck 610 may be formed by the first end of the tool spindle 30. The first end of the tool spindle 30 is provided with a mounting hole 613 for engaging with the working head 600. When the working head 600 is inserted into the mounting hole 613, the two can form a circumferentially constrained engaging structure.

In a specific embodiment, the position at which the working head 600 is engaged with the mounting hole 613 may be formed in a circumferential direction in which a plurality of projections 611 are fitted to the dimples 612. Specifically, the protrusion 611 may be disposed on the inner wall of the mounting hole 613 or may be disposed on the working head 600. Similarly, the recess 612 may be disposed on the working head 600 or may be disposed on the inner wall of the mounting hole 613. on. For example, the mounting hole 613 may be a circular hole as a whole, and a plurality of protrusions 611 are provided on the wall of the hole of the mounting hole 613 in the circumferential direction. Correspondingly, the outer wall of one end of the working head 600 engaged with the mounting hole 613 is provided with a recess 612 matching the protrusion 611.

The number of the protrusions 611 may be two, and is symmetrically distributed along the circumferential direction of the tool spindle 30. The dimples 612 on the working head 600 can be divided into two groups, one of which is used to cooperate with the protrusions 611 to realize the transmission of torque, hereinafter referred to as a twisting pit. Specifically, the set of twisted holes may include two pits disposed opposite each other along the circumferential direction of the work head 600. Specifically, the twisting pit on the working head 600 is in a semi-open form, and has an opening on a side close to the casing. When the twisting hole of the working head 600 is engaged with the protrusion 611 of the mounting hole 613, the working head 600 is circumferentially stationary with respect to the tool spindle 30 without relative rotation, thereby being able to be driven by the tool spindle 30 to achieve synchronization. Turn.

In addition, another set of dimples for accommodating steel balls, hereinafter referred to as steel ball locking pits, may be provided on the working head 600 to prevent the working head 600 from falling out of the quick-change chuck 610. The set of steel ball locking pits may include two dimples disposed opposite each other along the circumferential direction of the working head 600. The steel ball locking pit is a non-penetrating long groove, and the steel ball diameter is smaller than the length of the steel ball locking pit, and can be small along the central axis of the tool spindle 30 after the working head 600 is snapped into the quick-change chuck 610. The range of axial swaying, in conjunction with the impact mode, achieves impact drilling.

In another specific embodiment, the mounting hole 613 may be in the form of an inner hexagonal hole. When the mounting hole 613 is an inner hexagonal hole, one end of the working head 600 engaged with the mounting hole 613 has a hexagonal cross section. When the working head 600 having a hexagonal cross section is inserted into the inner hexagonal hole, the working head 600 is relatively stationary in the circumferential direction with respect to the tool spindle 30, and is relatively movable in the axial direction.

When the collet is in the form of the quick change collet 610 described above, the sum of the masses of the quick change collet 610 and the tool spindle 30 ranges between 50 grams and 150 grams. This mass range is primarily based on the mass range of the tool spindle 30 between 40 grams and 100 grams, while the quality of the mounting attachment of the quick change chuck 610 is typically determined between 10 grams and 50 grams.

Specifically, the mounting attachment may vary depending on the specific form of the quick change collet 610. For example, when the quick-change type collet 610 is installed in the manner of the inner hexagonal hole, the mounting accessory mainly includes a component such as a steel ball connected, and the mass thereof is about 10 g; when the quick-change type collet 610 is installed When the method is "four-pit" type installation, the installation accessories mainly include: lock sleeve, steel ball, pressure plate and other components, the quality of which is about 50 grams. Of course, the quick-change chuck 610 is not limited to the above description, and other modifications may be made by those skilled in the art in light of the technical essence of the present application, but the functions and effects thereof are the same as or similar to the present application. All should be covered by the scope of this application.

Referring to FIG. 21 or FIG. 23 or FIG. 27, in other embodiments of the present invention, the first end of the tool spindle 30 is provided with a jaw type clamp by means of a fixed connection, the jaw clamp The head includes a core body fixed at one end to the first end of the tool spindle 30, an operating casing sleeved outside the core body, and a collet connected to the core body.

For a jaw type collet, the collet can generally include three split jaws that can hold the work heads 600 of different sizes and different cross sections, and are generally more versatile. The jaw type collet has a core, which may be a hollow, rotary body as a whole, and one end of which may be sleeved at the first end of the tool spindle 30. The core body and the tool spindle 30 can be connected and fixed by a thread or the like at a mating position. The other end of the core may also be connected to the split jaws by means of a screw connection or the like. Wherein, the core body and the split claw are formed with a tapered hole having a predetermined taper, and when the core body and the split claw are relatively rotated, the opening or closing of the split claw can be realized. In addition, the specific transmission relationship, the connection manner, and the like of the jaw type can be referred to the specific description in the above embodiments, and the details are not described herein again.

In the case of impact drilling, since the chuck and the tool spindle 30 as a whole are used as the impacted member, the smaller the better, the better. Wherein, the density of the core may be between: 1 g/cm 3 (g/cm 3 ) to 8 g/cm 3 (g/cm 3 ). Specifically, the material of the core may be any one of the following: plastic, aluminum, steel, and the like. In principle, the density of the core is preferably as small as possible while ensuring that the core has sufficient strength of use.

When the collet is a jaw type chuck, the sum of the mass of the jaw type chuck and the tool spindle 30 may range from 120 grams to 450 grams.

Among them, the main factors affecting the quality of the jaw type chuck may include: the material of the core body, the specific structure of the core body, and the material of the operation shell. For the jaw type chuck as shown in FIG. 21 or FIG. 23 or FIG. 27, in the case where the material of the operation casing is plastic, if the material of the core body is plastic, the sum of the masses of the core body and the operation casing is about It is 80 g; if the material of the core is aluminum, the sum of the mass of the core and the operating shell is about 160 g; if the material of the core is steel, the mass of the core is about 260 g. In the case where the material of the operating casing is steel, if the material of the core is steel, the mass of the core is about 300 grams. In addition, if the structure of the core is modified to match the two-component jaws, the quality of the core will increase to some extent, for example, to about 350 grams. Of course, when the core is of other very special structure, the quality thereof may be greater, and the present application is not specifically limited herein.

When the chuck is a jaw type chuck, the mass range of the jaw type chuck can be between 80 grams and 350 grams, taking into account various factors affecting the quality of the chuck, correspondingly, the jaw type clamp The sum of the mass of the head and the tool spindle 30 can be between 120 grams and 450 grams.

As shown in FIG. 21, FIG. 23, FIG. 25 to FIG. 27, the tool spindle 30 is fixedly coupled to the collet 50 by means of screwing. Specifically, in the present embodiment, the tool spindle 30 is disposed near one end of the collet 50. The external thread 300, the core 501 of the collet 50 is internally provided with a threaded hole 500 mated with the external thread 300, and the tool spindle 30 and the collet 50 are connected to the threaded hole 500 by the external thread 300.

The chuck 50 includes a core 501, a claw 502 and a locking ring 503. The locking ring 503 is sleeved on the core 501, and the claw 502 for clamping the tool head is disposed at the end of the core 501. The core 501 A threaded hole 500 is provided. Preferably, in order to enable the kinetic energy of the ram 200 to be transmitted to the tool head more efficiently when striking the tool spindle 30, the tool head can obtain greater kinetic energy and improve drilling efficiency. Based on the principle of conservation of momentum during inelastic collisions, it is necessary to obtain a greater speed after the impact of the tool head, so that the quality of the collet 50 can be reduced. Here, preferably, the material of the core 501 is made to have a density of 1 g/cm 3 to 5 g/cm 3 . For example, the core 501 may be made of an aluminum or aluminum alloy material. The material of the claw 502 is made to have a density of 5 g/cm 3 to 8 g/cm 3 . For example, the jaws 502 can be made of a stainless steel material to ensure the strength of the jaws 502. The core 501 can also be made of a plastic material in the case where the strength satisfies the requirements, so that the tool head can obtain greater kinetic energy than the core using aluminum or aluminum alloy after the impact.

Hand tool 1 has a rated torque of less than or equal to 55 Nm. Rated torque means that the hand tool 1 can work normally within the rated torque range. If the hand tool 1 is operated beyond the rated torque, it may cause abnormal conditions in the hand tool 1, such as reduced service life or damaged parts. It can be understood that since the core 501 is made of an aluminum or aluminum alloy material, and the aluminum or aluminum alloy cannot be subjected to heat treatment, the core 501 of the present invention has a strength lower than that of a core made of stainless steel. Moreover, the core body 501 needs to be adapted to the working head, the claw 502, and the like having specifications. Therefore, it is inconvenient to improve the structure thereof, so that the core body 501 has high strength, and the power rating of the hand tool 1 can be guaranteed. When the hand tool 1 is working normally, the drilling speed is increased.

The torque, speed and power of the motor have the following relationship: T = 9549 * P / n.

Specifically, T represents the rated torque of the hand tool 1 in units of cow meters; P represents the maximum power of the motor in kilowatts; n represents the speed output after the motor is decelerated by the speed reducer, which in this embodiment is the tool spindle Speed, in revolutions per minute (r/min). When the rated torque of the hand tool 1 is less than or equal to 55 Nm, it can be found that 55 ≥ 9549 P/n, that is, n/P ≥ 173.618, which can be rounded up to obtain n/P ≥ 174.

It can be understood that since the density of the material of the core 501 is from 1 g/cm 3 to 5 g/cm 3 , the quality of the core 501 of the present invention is lower than that of the core made of stainless steel of the prior art, so that the hand tool can be made. The overall quality of 1 is reduced. Moreover, since the core 501 is located at the front of the hand tool 1, the handle for holding the hand tool is located at the middle rear portion of the hand tool 1, and the lowering of the quality of the core 501 can also shift the center of gravity of the hand tool 1 toward the handle. The center of gravity of the hand tool 1 is brought close to the handle, so that the handle is easily operated by the handle, and the grip is comfortable.

Drilling was performed using two hand tools that differ only in core 501 material. The hand tool was fitted with the same 8 mm diameter tool head and a 50 mm deep hole was drilled into the concrete. That is, using two hand tools that differ only in core 501 material, two identically sized holes are drilled in the same material in the same environment. Each hand tool drills 3 times, records the time taken to drill the two hand tools, and calculates the average time used for each hand tool. The drilling efficiency is the drilling depth divided by the time spent drilling. . As shown in Table 4, a hand tool uses a steel collet core with an average time of 15.26 seconds for drilling, and another hand tool uses an aluminum collet core for the average diameter of the hole. The time is 10.00 seconds. It can be seen that the use of the core of aluminum or aluminum alloy can improve the drilling efficiency of the hand tool 1 and shorten the time taken for drilling, and can be shortened by about 30% in the above experiment, and the effect is obvious.

Table 4

The present invention also provides a collet attachment that includes a collet 50, a tool spindle 30, and a hammer impact mechanism 20 that is fixedly coupled to the collet 50. The hammer impact mechanism 20 has a ram 200 that can reciprocally impact the tool spindle 30 in the axial direction of the tool spindle 30; the collet attachment is detachably coupled to the output shaft of the hand tool body. The output shaft of the hand tool body referred to herein is two shafts different from the tool spindle. The tool spindle is used to receive the hammer impact, and the output shaft is the shaft in the hand tool body. The output shaft may be a drive shaft or an output shaft of the reducer, and the output shaft is an output portion on the body of the hand tool for outputting rotational power. The hand tool body is used to provide power, and the output shaft of the hand tool body can be mated with other types of accessories to achieve other corresponding functions.

It will be understood that although the above embodiments have described the specific embodiments of the present invention in detail, it is also to be noted that:

(1) The hammer impact mechanism 20 is not limited to the above structure, and the hammer impact mechanism should be understood in particular as a hammer impact mechanism having at least one ram 200 that reciprocates linearly in the axial direction of the tool spindle. For example, the hammer impact mechanism springs and/or pneumatically and/or hydraulically drives the ram by means of a chute device, by means of bearings and/or by means of an eccentric unit. Therefore, the hammer impact mechanism may be a pneumatic hammer impact mechanism or an eccentric hammer impact mechanism. In particular, the pneumatic hammer impact mechanism may be configured such that the crank linkage mechanism drives the piston of the compression cylinder to reciprocate to generate compressed air, and the compressed air drives the ram to hammer the tool spindle. In particular, the eccentric hammer impact mechanism may be provided as a hammer impact structure that is rotated by a linear motion that produces a rotational axis perpendicular to the rotational motion. Preferably, the eccentric hammer impact mechanism has a rotationally fixed connection to the drive element. Eccentric element.

(2) In the present invention, the guide member 210 is not limited to the outer peripheral wall of the ram 200. In other embodiments, the guide member may be disposed on the inner circumferential side of the ram as long as the guide member and the ram are provided. The relative rotation of the ram can be achieved.

The technical features of the above-described embodiments may be arbitrarily combined. For the sake of brevity of description, all possible combinations of the technical features in the above embodiments are not described. However, as long as there is no contradiction between the combinations of these technical features, All should be considered as the scope of this manual.

The above-described embodiments are merely illustrative of several embodiments of the present invention, and the description thereof is more specific and detailed, but is not to be construed as limiting the scope of the invention. It should be noted that a number of variations and modifications may be made by those skilled in the art without departing from the spirit and scope of the invention. Therefore, the scope of the invention should be determined by the appended claims.

Claims

A hammer impact mechanism includes a relatively rotatable ram and a guide, and an energy storage mechanism abutting the ram,

a curved surface guiding portion is disposed on one of the ram and the guiding member, and the ram is disposed with a conversion member corresponding to the other of the guiding member.

The curved surface guiding portion includes a plurality of climbing sections and a falling section corresponding to the climbing section, and the conversion member drives the ram to overcome the energy storage when the conversion member passes the climbing section The force of the mechanism moves toward the first direction; when the conversion member passes the drop segment, the energy storage mechanism drives the ram to move in a second direction opposite to the first direction to achieve an impact;

It is characterized in that the relative rotational speed of the ram relative to the rotation of the guide member is 1000-2500 rpm, and the ratio of the impact frequency of the ram to the relative rotational speed is 2-4 times per revolution.
The hammer impact mechanism according to claim 1, wherein the number of the climbing sections comprises 2-4.
The hammer impact mechanism according to claim 2, wherein the number of the climbing sections comprises three.
The hammer impact mechanism according to claim 2, wherein the climbing section includes a starting point and an ending point, and the distance between the starting point and the ending point projected on the axis is 4-15 mm.
The hammer impact mechanism according to claim 4, wherein the distance is preferably 4-8 mm.
The hammer impact mechanism according to claim 1, wherein the curved guide portion is circumferentially disposed on an inner circumferential surface of the guide member, and the conversion member is disposed on an outer circumferential surface of the ram .
The hammer impact mechanism according to claim 6, wherein the guide member has an end surface perpendicular to a moving direction of the ram, and the climbing section has a climbing angle with respect to the end surface of 5 - 25 degree.
The hand-held power tool according to claim 7, wherein the drop section is disposed obliquely and extends in a direction away from the climbing section in a circumferential direction of the guide.
A hand-held power tool comprising the hammer impact mechanism of claim 1, a motor, and a tool spindle;

The tool spindle has an axis about which the tool spindle rotates under the drive of the motor, the hammer being capable of intermittently impacting the tool spindle along the axis.
The hand-held power tool according to claim 9, wherein said relative rotational speed is the same as a rotational speed of said tool spindle.
A hand-held power tool according to claim 9, wherein said hammer impact mechanism further comprises an impact shaft capable of driving said ram to rotate relative to said guide member, said impact shaft being rotationally driven by said motor.
The hand-held power tool according to claim 9, wherein the hand-held power tool further comprises one end in contact with the housing of the hand-held power tool, and the other end and the ram are free to face the tool spindle A cushioning member that contacts the end surface of the end, the cushioning member being capable of generating an extrusion deformation in the second direction.
The hand-held power tool according to claim 12, wherein the cushioning member is compressed by the ram in the second direction by a maximum amount of 2 mm.
The hand-held power tool according to claim 12, wherein the cushioning member is a rubber member or a spring.
A hand-held power tool according to claim 9, wherein said hand-held power tool further comprises a drive shaft for driving rotation of said tool spindle, said hammer impact mechanism further comprising driving said ram relative to said guide a relatively rotating impact shaft having the same rotational speed as the impact shaft.
The hand-held power tool of claim 15 wherein said drive shaft is disposed coaxially with said impact shaft.
A hand-held power tool according to claim 9, wherein said hand-held power tool further comprises a drive shaft for driving rotation of said tool spindle, said ram surrounding said drive shaft and at least one plane The tool spindle.
A hand-held power tool according to claim 17, wherein said guide member surrounds said ram in at least one plane.
An accessory having an impact function for detachably connecting with a hand-held power tool main body, characterized in that the accessory comprises the hammer impact mechanism of claim 1 and a tool spindle;

The tool spindle has an axis about which the tool spindle is rotatable, the ram being capable of intermittently impacting the tool spindle along the axis.
The accessory having an impact function according to claim 19, wherein said attachment comprises an accessory housing for housing said hammer impact mechanism, said hand-held power tool body comprising a main body housing, said accessory housing The body can be coupled to the body housing.
The accessory having an impact function according to claim 20, wherein said hand-held power tool body includes an output shaft that rotates, and said output shaft is rotatably coupled to said tool spindle.
The accessory having an impact function according to claim 21, wherein said hammer striking mechanism includes an impact shaft capable of driving said ram to rotate relative to said guide member, said impact shaft being rotatably coupled to said output shaft.
The impact-equipped attachment according to claim 22, wherein the impact shaft is non-rotatably connected to the tool spindle.
The accessory with impact function according to claim 22, wherein the attachment further comprises a connecting shaft, one end of the connecting shaft is rotatably connected to the output shaft, and the other end is non-rotating relative to the impact shaft. connection.
The accessory having an impact function according to claim 24, wherein said impact shaft is selectively connectable to said ram without rotational rotation.
The impact function attachment according to claim 24, wherein the impact shaft is integrally provided with the connecting shaft.
The accessory having an impact function according to claim 19, wherein said attachment further comprises a mounting assembly for mounting the working head to said tool spindle, said mounting assembly being detachably attachable to said tool spindle connection.
A hand tool comprising at least two modes of operation, an impact mode and a non-impact mode, comprising:

case;

a power mechanism disposed on the housing, including a motor and a transmission mechanism driven by the motor;

a tool spindle having a central axis, the tool spindle being driven by the transmission mechanism and rotating about the central axis;

The tool spindle has a first end remote from the power mechanism and a second end adjacent to the power mechanism, and the first end is provided with a chuck for mounting a working head;

a hammer impact mechanism comprising: a ram, a guide, a curved guide provided on one of the ram and the guide, a conversion member disposed on the other, and a storage abutting the ram In the impact mode, the ram is rotated relative to the guiding member, and the curved guiding portion can drive the ram against the urging force of the energy storage mechanism along the central axis by the conversion member Moving in a direction, the energy storage mechanism capable of driving the ram to move along the central axis in a second direction opposite to the first direction to impact the tool spindle; in the non-impact mode, the ram and The guide member has no relative rotation;

The hand tool is provided with a mode adjustment mechanism for adjusting the operation mode, the mode adjustment mechanism and the hammer impact mechanism at least partially radially overlapping;

The housing includes a first housing portion for receiving the hammer impact mechanism, the first housing portion having a radial dimension ranging from 45 mm to 70 mm.
A hand tool according to claim 28, wherein said mode adjustment mechanism radially overlaps at least a portion of at least one of said guide member and said ram.
A hand tool according to claim 29, wherein said mode adjustment mechanism includes an impact switching ring and a mode switching button, said mode switching button operatively driving said impact switching ring in a first position and a second position Movement between

When the impact switching ring is in the first position, the impact switching ring is engaged with the hammer impact mechanism, a relative rotation between the guiding member and the ram is generated, and the hand tool is in an impact mode; When the impact switching ring is in the second position, the impact switching ring is separated from the hammer impact mechanism, the relative rotation between the guiding member and the ram is not possible, and the hand tool is in a non-impact mode; At least one of the switching ring and the mode switching button at least partially radially overlaps the guide.
The hand tool according to claim 30, wherein the guiding member is provided with a first tooth pattern, and the impact switching ring is provided with a second tooth pattern, and in the impact mode, the first tooth pattern Engaging with the second rib; in the non-impact mode, the first rib is disengaged from the second ridge.
The hand tool according to claim 30, wherein said mode switching button is rotatably coupled to said housing, said impact switching ring is non-rotatably connected to said housing, said mode switching button driving The impact switching ring moves along a central axis of the tool spindle.
A hand tool according to claim 28, wherein said hammer impact mechanism comprises an impact shaft, said impact shaft being disposed between said transmission mechanism and said tool spindle, said ram being sleeved in said Outside the impact shaft, the impact shaft can drive the ram to rotate and has no rotational connection with the tool spindle.
A hand tool according to claim 28, wherein said guide member is sleeved on the outside of said ram.
A hand tool according to claim 34, wherein said ram is movably supported on an inner peripheral surface of said guide member along said central axis.
The hand tool according to claim 28, wherein the guide member is a hollow cylinder, and the curved guide portion is disposed on an inner wall of the guide member, and an outer wall of the ram is provided for mounting The insertion member of the conversion member.
A hand tool according to claim 36, wherein said energy storage mechanism is an elastic member, said curved surface guide portion being a cam surface formed on an inner wall of said guide member, said cam surface having a climbing section and Drop,

The elastic member accumulates elastic potential energy during movement of the conversion member toward the falling segment by the climbing portion;

When the conversion member is dropped from the climbing section to the falling section, the elastic member releases the elastic potential energy to drive the ram to impact the tool spindle.
The hand tool according to claim 28, wherein a ratio of an outer diameter of said hammer striking mechanism to a radial dimension of said first casing portion is between 0.6 and 0.9.
A hand tool according to claim 28, wherein

The rotational speed of the power mechanism is the same as the rotational speed of the impact shaft, wherein the impact shaft can drive the ram to rotate relative to the guide member;

The mode adjustment mechanism and the hammer impact mechanism at least partially axially overlap.
A hand tool according to claim 39, wherein said mode adjustment mechanism is provided with an impact switching ring that at least partially axially overlaps the guide of said hammer impact mechanism.
A hand tool according to claim 39, wherein said hand tool body has an axial length of from 185 mm to 250 mm.
A hand tool according to claim 41, wherein said hand tool body has an axial length of from 190 mm to 230 mm.
The hand tool according to claim 39, wherein said curved guide portion is provided with a plurality of climbing sections in a circumferential direction and a falling section corresponding to said climbing sections, said switching member passing said When the climbing section is up, the ram moves in a first direction; when the conversion member passes the falling section, the ram moves in a second direction to achieve an impact, and the number of the climbing sections is 2 To four.