WO2018054311A1

WO2018054311A1 - Electric tool

Info

Publication number: WO2018054311A1
Application number: PCT/CN2017/102524
Authority: WO
Inventors: 谢明健; 张士松; 郑悦
Original assignee: 苏州宝时得电动工具有限公司
Priority date: 2016-09-20
Filing date: 2017-09-20
Publication date: 2018-03-29

Abstract

An electric tool, comprising: a housing (110); a motor (120); a working shaft (130); a hydraulic impact unit (140) for enabling the working shaft (130) to intermittently rotate and comprising a rotating member (142) fitted onto the working shaft (130); a switching component (160) comprising a clutch member (161) and an operating member (162) driving the clutch member (161). The clutch member (161) is capable of switching between a first position and a second position; the clutch member (161) is at the first position to connect the working shaft (130) and the rotating member (142), and the rotating member (142) rotates to drive the working shaft (130) to continuously rotate; the clutch member is at the second position, and is disconnected from at least one of the working shaft (130) and the rotating member (142), and the rotating member (142) rotates to drive the working shaft (130) to intermittently rotate; the clutch position of the clutch member (161) is at the side of the hydraulic impact unit (140) distant from the motor. Only the sealing between one end of the rotating member (142) and the working shaft (130) needs to be considered, and the sealing between the hydraulic impact unit (140) and the working shaft (130) can be ensured.

Description

electrical tools

Technical field

The present invention relates to power tools, and more particularly to a power tool of various functions.

Background technique

The traditional power tool that uses the hydraulic impact unit to realize the impact wrench function needs to implement the drill mode (ie, the drill mode and/or the screwdriver mode), and needs to consider switching between the impact wrench mode and the drill batch function mode, resulting in The sealing scheme between the working shaft and the oil pressure impact unit is complicated.

Summary of the invention

Based on this, it is necessary to provide a simple electric power tool with a sealing scheme between the working shaft and the oil pressure impact unit.

A power tool includes a housing; a working shaft; a power unit for generating rotational power; and a hydraulic impact unit for intermittently rotating the working shaft, including a rotation that is sleeved on the working shaft and that can be driven to rotate by the power unit. Forming a closed space between the rotating member and the working shaft, the closed space is provided with hydraulic oil, and the hydraulic impact unit further comprises a piston member located in the closed space, on the working shaft a guiding groove is provided, the piston member is radially movable in the guiding groove, the working shaft has a first end in the closed space and a second end for connecting the working head, and the second end Extending the enclosed space away from the power device; the power tool further includes a clutch member, and the clutch member is switchable between a first position and a second position, wherein the clutch member is in the first position, The working shaft can be driven to rotate continuously, and the working shaft can be driven to intermittently rotate when the clutch member is in the second position.

Preferably, the rotating member is fixedly connected to the power device, and the clutch member connects the rotating member and the working shaft when the clutch member is in the first position; the clutch member is in the first In the two positions, the clutch member is disengaged from at least one of the working shaft and the rotating member.

Preferably, the working shaft is fixed with a matching member, and the clutch member is fixedly connected with the connecting member when the clutch member is in the first position.

Preferably, the clutch member is switched between the first position and the second position by axial movement, and when the clutch member is in the second position, the clutch member is disengaged from the working shaft and Rotating member connection.

Preferably, the power device comprises a motor and a gear mechanism connected to the output end of the motor, the gear mechanism comprises a carrier, and the oil pressure impact unit is provided with a first sealing end cover near one end of the motor, the carrier and the carrier The first sealed end cap is fixedly connected.

Preferably, the carrier is integrally formed with the first sealed end cap.

Preferably, the enclosed space includes a high pressure chamber capable of sealing a portion of hydraulic oil, the high pressure chamber being formed between the working shaft and the piston member.

Preferably, the first end of the working shaft in the closed space is provided with an axial hole, and the guiding groove is symmetrically disposed on both sides of the axial hole and communicates with the axial hole, the axial hole a movable member fixed relative to the rotating member is disposed, and when the clutch member is in the second position, the movable member is driven to rotate relative to the working shaft, and the hydraulic pressure of the hydraulic oil sealed between the piston member and the working shaft is Can make a difference.

Preferably, the power tool further includes a control component including an operation member for triggering a work instruction and a control circuit for executing a work instruction, the operation member being capable of triggering control when the clutch member is in the first position The assembly selectively causes the power tool to be in a screwdriver mode or an electric drill mode, the operating member being capable of triggering the control assembly to place the power tool in an impact wrench mode when the clutch member is in the second position.

Preferably, the operating member is movably disposed relative to the housing, and the operating member is movable in a first stroke of the corresponding screwdriver mode, a second stroke corresponding to the electric drill mode, and a third stroke corresponding to the impact wrench mode.

Preferably, the housing is respectively provided with at least one gear position indication corresponding to the first, second, and third strokes, and when the operating member moves to a position corresponding to the gear position indication, the electric tool performs corresponding The output in the working mode that matches the gear position indication.

Preferably, the enclosed space includes a high pressure chamber capable of generating a high oil pressure, the high pressure chamber being formed between the rotating member, the working shaft and the piston member.

Preferably, the inner wall of the rotating member is provided with a plurality of sealing portions, and a surface of the working shaft is provided with a radial portion, and the rotating portion and the piston member are simultaneously sealed and sealed during the rotating of the rotating member The high pressure chamber is formed when the portion is in contact.

Preferably, one end of the clutch member is coupled to the power unit and is axially moved to selectively connect the other end to one of the rotating member and the working shaft outside the enclosed space, and in the first position, the clutch The other end of the member is coupled to the working shaft outside the enclosed space, and in the second position, the other end of the clutch member is coupled to the rotating member.

The invention also provides another power tool, comprising: a housing; a working shaft for driving the working head;

a power device for generating rotational power; a hydraulic impact unit for intermittently rotating the working shaft, comprising a rotating member sleeved on the working shaft, the rotating member and the working shaft form an enclosed space, a hydraulic oil is disposed in the closed space, the hydraulic impact unit further includes a piston member located in the closed space, and the working shaft is provided with a guiding groove, and the piston member is radially movable in the guiding groove. The rotating member and the output end of the power device are fixedly connected, and the power tool further includes a clutch member, wherein the clutch member is switchable between a first position and a second position, in the first position, The clutch member connects the rotating member and the working shaft, and the working shaft can be driven to continuously rotate; in the second position, the working shaft can be driven to intermittently rotate.

Preferably, the power device comprises a motor, the oil pressure impact unit is provided with a first sealing end cap near one end of the motor, and the working shaft is located near the first end of the first sealing end cover. Within the space.

The invention also provides another power tool, comprising: a housing; a motor for generating power; a working shaft for driving the working head; and a hydraulic impact unit for intermittently rotating the working shaft, including sleeve working a rotating member on the shaft, a closed space in which the hydraulic oil is disposed in the rotating member, and a piston member that is assembled in the guiding groove of the working shaft in a radial movement in the closed space; the switching assembly, including the clutch member The clutch member is switchable between a first position and a second position, wherein the clutch member connects the working shaft and the rotating member when the clutch member is in the first position; In the second position, the clutch member is disengaged from at least one of the working shaft and the rotating member, and the working shaft can be driven to generate intermittent rotation, wherein the clutching position of the clutch member is located at a hydraulic impact unit away from the motor One side.

Preferably, one end of the working shaft is used to connect the working head, and the other end of the working shaft is provided with an axial hole, and the axial hole has a movable member built therein to rotate together with the rotating member, a guide hole is communicated with the axial hole through a radial hole, and a ball is disposed between the guide groove and the axial hole. An inner portion of the rotating member is provided to force the piston member to move radially toward the movable member;

When the clutch member is in the second position, the thrust portion is not in radial contact with the piston member, the axial hole communicates with the closed space, and hydraulic oil in the closed space can enter the An axial hole; when the abutting portion abuts against the piston member in the radial direction, the axial hole forms a partition space with the closed space, and the piston member moves radially along the guiding groove toward the axial hole The partition space is reduced in volume to form the high-pressure chamber; the piston member abuts against the abutting portion in a radial direction to be disengaged from the abutting portion, and the rotating member impacts The piston member radially impacts the piston member while circumferentially impacting the working shaft.

Preferably, the urging portion has a climbing surface and an abutting surface, and the top of the piston member has a transition surface and a contact surface. During the rotation of the urging portion, the climbing surface slides along the transition surface and forces the piston member diameter The movement is made until the abutment surface abuts the contact surface in the radial direction.

Preferably, the inner wall of the rotating member is provided with a plurality of sealing portions, and a surface of the working shaft is provided with a radial portion. During the rotating of the rotating member, the sealing portion simultaneously forms a contact with the radial portion and the piston member. The high pressure chamber.

Preferably, when the clutch is in the first position, the operating member can be operated to control the control circuit to change the output torque of the motor.

Preferably, the operating member is operable to control an output rotational speed of the motor when the clutch member is in the second position.

Preferably, the switching assembly further includes an operating unit for driving the clutch member, the operating unit is configured to drive the clutch member to switch between the first position and the second position, the power tool further comprising a control component, The control assembly includes an operating member and a control circuit that is triggered by the operating member for operating to change an output torque of the motor when the clutch is in the first position.

Preferably, a gear mechanism is disposed between the motor and the rotating member, and the rotating member is driven to rotate by the gear mechanism, and the gear mechanism is a primary reduction gear.

The invention also provides another power tool, comprising: a housing; a motor for generating power;

a working shaft for driving the working head; a hydraulic impact unit for intermittently rotating the working shaft, The invention comprises a rotating member sleeved on the working shaft, the rotating member is provided with an enclosed space in which the hydraulic oil is stored, and further comprises a piston member which can be assembled in the guiding groove of the working shaft in a radial movement in the closed space. a switching assembly including a clutch member, wherein the clutch member is switchable between a first position and a second position, wherein the clutch member connects the working shaft and the rotating member when the clutch member is in the first position The rotating member rotates to drive the working shaft to continuously rotate together; when the clutch member is in the second position, the clutch member is disengaged from at least one of the working shaft and the rotating member, and the rotating member rotates when The working shaft generates an intermittent rotation, wherein the clutching position of the clutch member is located on a side of the oil pressure impacting unit away from the motor.

The above electric tool realizes the function of the impact wrench by using the oil pressure impact unit, and realizes switching between the impact wrench mode and the drill batch mode by selectively connecting the clutch member to the rotating member of the oil pressure impact unit and the working mode, wherein the clutch member and the working device The mating portion of the shaft is located at one side of the hydraulic impact unit, and is adjacent to the working shaft for driving one end of the working head, and the other end of the working shaft is sealed by the rotating member, thereby only considering one end of the rotating member and the working shaft The seal between them ensures the seal between the oil pressure impact unit and the working shaft.

In one of the embodiments, the enclosed space includes a high pressure chamber capable of generating a high oil pressure, the high pressure chamber being located between the working shaft and the piston member.

In one embodiment, one end of the working shaft is provided with an axial hole, and the other end is for driving the working head, and the axial hole has a cam shaft built therein to rotate together with the rotating member, The outer surface of the working shaft is further provided with a radial passage for accommodating the piston member, and the radial passage communicates with the axial hole through a radial hole, and the radial passage further accommodates a blocked passage a ball toward the hole, the rotating member being internally provided with an urging portion for forcing the piston member to move radially toward the cam shaft;

When the urging portion and the piston member are not in radial contact, the axial hole communicates with the closed space, and hydraulic oil in the closed space can enter the axial hole; the urging portion is radially opposed When the piston member is caught, the cam shaft isolates the axial hole from the closed space, and the ball blocks the radial hole, and the hydraulic oil keeps the piston member in the diameter of the abutting portion Upward abutment state;

The urging portion impacts the working shaft in a circumferential direction while the piston member moves radially, in a process of not abutting the piston member in the radial direction to abut against the piston member.

In one embodiment, the urging portion has a climbing surface and an abutting surface, and the top of the piston member has a transition surface and a contact surface, and the climbing surface advances along the transition surface during the rotation of the urging portion Force live The plug moves radially until the abutment surface abuts the contact surface in the radial direction.

In one of the embodiments, the enclosed space includes a high pressure chamber capable of generating a high oil pressure, the high pressure chamber being formed between the rotating member, the working shaft, and the piston member.

In one embodiment, the inner wall of the rotating member is provided with a plurality of sealing portions, and a surface of the working shaft is provided with a radial portion, and the rotating member is formed when the sealing portion is in contact with the radial portion. The high pressure chamber.

In one embodiment, the inner wall of the rotating member is provided with four sealing portions in the circumferential direction, two of the radial portions, and two of the piston members, and two piston members are disposed between The elastic member is configured to provide an elastic force for maintaining a sealing contact between the piston member and the inner wall of the rotating member, the radial portion and the piston member being offset in a circumferential direction of the working shaft;

During the rotation of the rotating member, when the sealing portion is in contact with the radial portion, the rotating member urges the high-pressure oil in the high-pressure chamber to push the piston member to move radially, and when the piston member moves in the radial direction, the working is impacted in the circumferential direction. axis.

In one of the embodiments, when the clutch is in the first position, the operating member can be operated and cause the control circuit to change the output torque of the motor.

In one of the embodiments, the operating member is operable to operate the output rotational speed of the motor when the clutch member is in the second position.

In one embodiment, the power tool further includes an operating member that drives the clutch member, the operating member includes a first operating member and a second operating member, wherein the first operating member is configured to drive the clutch member at Switching between a first position and a second position for operating to change an output torque of the motor when the clutch is in the first position.

In one of the embodiments, the motor shaft of the motor drives the rotating member to rotate by a primary gear reduction system.

The invention also provides a small power tool with vibration, comprising: a housing; a motor for generating power; a working shaft for driving the working head; and a hydraulic impact unit for intermittently rotating the working shaft, including a rotating member sleeved on the working shaft, the rotating member is provided with an enclosed space in which the hydraulic oil is stored, and further includes a piston member that can be assembled in the guiding groove of the working shaft in a radial movement in the closed space. The enclosed space includes a high pressure chamber capable of generating a high oil pressure, the high pressure chamber being formed in the a working shaft and the piston; a switching assembly including a clutch member, wherein the clutch member is switchable between a first position and a second position, the clutch member is in the first position, the clutch member Connecting the working shaft and the rotating member, the rotating member rotates to drive the working shaft to continuously rotate together; when the clutch member is in the second position, the clutch member and the working shaft and the rotating member are at least one Disengagement, when the rotating member rotates, the rotating member can intermittently push the piston member to move radially and intermittently impact the working shaft in the circumferential direction by the piston member.

The above electric tool adopts a hydraulic impact unit to realize an impact wrench function, the hydraulic oil can reduce vibration during impact, and the clutch member can selectively connect the rotating shaft in the working shaft and the impact unit, and can complete the impact wrench mode and the working shaft of the working shaft. The conversion of the continuous mode achieves the purpose of a multi-function gun drill with little vibration.

In one of the embodiments, the switching assembly further includes an operating member that drives the clutch member, the operating member being operatively capable of controlling an output torque of the motor when the clutch member is in the first position.

In one embodiment, the switching assembly further includes an operating member that drives the clutch member, the operating member being operatively capable of controlling an output rotational speed of the motor when the clutch member is in the second position.

In one of the embodiments, the operating member is rotatably operable about an axis of the working shaft.

In one embodiment, the switching assembly further includes an operating member that drives the clutch member, the operating member includes a first operating member and a second operating member, wherein the first operating member is configured to drive the clutch member at The first position is switched between the second position and the second position for controlling the output torque and the rotational speed of the motor.

When the urging portion and the piston member are not in radial contact, the axial hole communicates with the closed space, and the sealing Hydraulic oil in the closed space can enter the axial hole;

When the urging portion abuts against the piston member in the radial direction, the cam shaft isolates the axial hole from the closed space, and the ball blocks the radial hole, and the hydraulic oil causes the piston member Maintaining a radial contact with the urging portion;

In one embodiment, the urging portion has a climbing surface and an abutting surface, and the top of the piston member has a transition surface and a contact surface, and the climbing surface advances along the transition surface during the rotation of the urging portion The piston member is forced to move radially until the abutment surface abuts the contact surface in the radial direction.

In one of the embodiments, the switching assembly further includes an operating member that drives the clutch member, the operating member moving in an axial direction parallel to the working shaft to drive the clutch member.

In one embodiment, the switching assembly further includes an operating member for driving the clutch member, the operating member includes a rotatable switching ring, the switching ring is provided with a first driving slot, and the clutch member is connected There is a sliding pin that cooperates with the first driving groove, and the switching ring can axially move the clutch member through the sliding pin during the rotation.

The invention also provides a power tool with an impact wrench function and a hammer drill function to improve work efficiency, comprising: a housing; a motor for generating power; a working shaft for driving the working head; and a hydraulic impact unit The utility model relates to an intermittent rotation of the working shaft, comprising a rotating member sleeved on the working shaft, the rotating member is provided with an enclosed space in which the hydraulic oil is stored, and further comprises a radial movement in the closed space. a piston member in the guiding groove of the working shaft;

The switching assembly includes a first clutch member, wherein the first clutch member is switchable between a first position and a second position, and when the first clutch member is in the first position, the clutch member is coupled to the a working shaft and a rotating member, the rotating member rotates together to drive the working shaft to continuously rotate; when the clutch member is in the second position, the first clutch member and the working shaft and the rotating member are separated from each other When the rotating member rotates, the working shaft generates intermittent rotation;

The impact drill function conversion mechanism includes a movable end tooth fixed to the working shaft and rotatable together with the working shaft, and rotatably sleeved on the working shaft and capable of meshing with the movable end tooth in the axial direction of the working shaft a static end tooth, a second clutch member, and a second clutch member having two positions, wherein the first clutch member is in the In the first position, and when the second clutch is in the first position, the movable end teeth are in contact with the stationary end teeth.

The above electric tool adopts a hydraulic impact unit to realize the function of the impact wrench, and the working shaft is changed from the execution of the impact wrench to the continuous rotation by connecting or separating the clutch member and the rotating member of the hydraulic impact unit selectively. On the basis of the impact drill function conversion mechanism, the working shaft can select to perform the axial impact action, thereby having the function of the impact wrench and the impact drill function, meeting the operation requirements under complicated working conditions, and improving the working efficiency.

In one embodiment, the power tool further includes an operating member that is operable to move the first clutch member and the second clutch member, wherein the operating member has a first stroke when moved, a second stroke, a third stroke, and a fourth stroke, wherein the first clutch is disengaged from at least one of the working shaft and the rotating member when the operating member is in the first stroke; when the operating member is in the second stroke, The first clutch member connects the rotating member and the working shaft; when the operating member is in the third stroke, the first clutch member connects the rotating member and the working shaft, and the output power of the motor is different from the second stroke The output power of the motor; when the operating member is in the fourth stroke, the first clutch member connects the rotating member and the working shaft, and the second clutch member is driven to a position that restricts the rotation of the stationary end teeth.

In one of the embodiments, the operating member is capable of controlling the output torque of the motor when moving within the second range of travel.

In one of the embodiments, the operating member is capable of controlling the rotational speed of the motor when moving within the first range of travel.

In one embodiment, the operating member includes a first operating member and a second operating member, wherein the first operating member, the second stroke, the third stroke, and the fourth stroke are implemented when the first operating member is operated Switching; when the first operating member is in the first stroke, the second operating member can be operatively changed to output the rotational speed of the motor, and when the first operating member is in the second or third stroke, the second operating member The output torque of the motor can be operatively changed.

In one of the embodiments, the operating member is moved in a rotational manner when operated.

In one embodiment, the power tool includes a control circuit coupled to the motor, the control circuit including an annular switch fixed to the housing, the operating member having a spring piece in contact with the ring switch, and the spring piece when the operating member is operated The change in contact position with the ring switch changes the output torque or speed of the motor.

In one embodiment, the power tool further includes an operating member, the operating member including a rotating switching ring, the switching ring is provided with a first driving groove, and the clutch member is connected with a sliding pin that cooperates with the first driving groove, and the switching ring can axially move the clutch member through the sliding pin during the rotating process a second driving slot is formed on an edge of the switching ring, and the second clutch member is connected with a locking pin that cooperates with the second driving slot, and the switching ring can be used to act on the pin during rotation The second clutch member is axially moved.

In one of the embodiments, the clutch position of the first clutch member is located on a side of the oil pressure impact unit away from the motor.

In one of the embodiments, the clutch position of the first clutch member is located on a side of the oil pressure impact unit adjacent to the motor.

The present invention also provides another power tool different from the above, comprising a housing, a power system disposed in the housing, having an output shaft for providing a rotary output; and an impact unit including a rotating member and a hydraulic portion. a rotating member coupled to the output shaft; a working shaft coupled to the rotating member by a hydraulic portion; a switching assembly disposed between the rotating member and the working shaft for locking the rotating member and the working shaft Separation action.

Preferably, the power tool further includes a mating member that performs functional switching by locking and disengaging between the rotating member and the mating member.

Preferably, the switching assembly has an axially movable and circumferentially fixed locking member disposed on one of the rotating member and the adapter, and a circumference disposed on the other of the rotating member and the adapter To the fixed portion to be locked, the locking member can be locked or separated from the portion to be locked.

Preferably, the locking member is a clutch member sleeved on the rotating member, and the inner wall of the clutch member is formed with a connecting structure that is circumferentially engaged with the outer circumferential wall of the rotating member and axially slidably connected, The locking member is locked and disengaged between the rotating member and the mating member by being circumferentially engaged and axially slidably engaged or disengaged from the mating member.

Preferably, the outer circumferential wall of the rotating member is formed with a plurality of axially extending sliding grooves, and the inner wall of the clutch member is formed with a slider embedded in the sliding groove; the clutch member is adjacent to the mating One end of the piece and one of the mating members are formed with a clutch projection, and the clutch member is adjacent to one end of the mating member and the The other of the mating members is formed with a clutch groove adapted to engage the clutch projection to lock the rotary member and the adapter.

Preferably, the switching assembly is further provided with a switching member for driving the locking member, the switching member and the locking member are axially fixedly disposed by an axial dimension between the switching member and the locking member. The change drives the locking member to reciprocate axially.

Preferably, the switching member includes a switching ring that is axially positioned and rotatably disposed relative to the power system, the axially-scaled structure having a shape that is circumferentially disposed and axially offset on the switching ring a first driving slot that is moved, and a switching lever that is circumferentially positioned and axially slidable relative to the power system; the switching lever has a protruding pin embedded in the first driving slot at one end, the switching lever The other end is slidably circumferentially and axially locably coupled to the locking member, or a biasing force acting axially on the locking member is applied to the locking member to apply a thrust against the biasing force or pull.

Preferably, the electric power tool further has a shifting mechanism including a multi-stage speed reducing mechanism; the multi-stage speed reducing mechanism has one end connected to the output shaft and the other end connected to the driving portion of the hydraulic pulse unit.

Preferably, the shifting mechanism further includes a shifting lever; the shifting assembly is further formed with a shifting operation groove including axially offset in the circumferential direction, and the shifting lever is inserted into the shifting operation groove at one end.

Preferably, the biasing force is applied by a plurality of springs symmetrically disposed between the locking member and the rotating member.

DRAWINGS

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

Figure 2 is a plan view of the power tool shown in Figure 1;

Figure 3 is a schematic cross-sectional view of the power tool of Figure 1, wherein the power tool is in an impact wrench mode;

Figure 4 is a schematic cross-sectional view of the power tool of Figure 1, wherein the power tool is in a drill mode;

Figure 5 is an assembled view of the operation knob, the switching assembly and the impact unit;

Figure 6 is an exploded view of the assembly shown in Figure 5;

Figure 7 is a partial cross-sectional view of another embodiment of the power tool, wherein the power tool is in a continuous output mode;

Figure 8 is a partial cross-sectional view of the power tool of Figure 7, wherein the power tool is in an impact wrench mode;

Figure 9 is a schematic cross-sectional view showing the assembly of the impact unit and the working shaft;

Figure 10 is a schematic cross-sectional view of the impact unit A-A of Figure 9 illustrating the state of the camshaft at different positions during rotation of the rotating member of the impact unit;

14 to 17 are schematic cross-sectional views of the impact unit B-B of Fig. 9, illustrating the state of the cam shaft at different positions during the rotation of the rotating member of the impact unit;

Figure 18 is a schematic cross-sectional view showing another embodiment of the impact unit assembled with the working shaft;

Figure 19 is a cross-sectional view showing the C-C direction of the operation of the impact unit of Figure 18;

Figure 20 is a schematic view showing the state of the impact unit a in Figure 19;

Figure 21 is a cross-sectional view of a power tool in still another embodiment;

Figure 22 is an assembled view of the operating button, the switching assembly and the impact unit in the embodiment shown in Figure 21;

Figure 23 is a cross-sectional view of the assembled view of Figure 22;

Figure 24 is a cross-sectional view showing a power tool according to still another embodiment;

Figure 25 is a side view of the power tool shown in Figure 24;

Figure 26 is a cross-sectional view taken along line D-D of Figure 25 when the power tool is in the impact wrench mode;

Figure 27 is a cross-sectional view taken along line E-E of Figure 25 when the power tool is in the impact wrench mode;

Figure 28 is a cross-sectional view taken along line D-D of Figure 25 when the power tool is in the screwdriver or drill mode;

Figure 29 is a cross-sectional view taken along line E-E of Figure 25 when the power tool is in the screwdriver or drill mode;

Figure 30 is a cross-sectional view taken along line D-D of Figure 25 when the power tool is in the impact drill mode;

Figure 31 is a cross-sectional view taken along line E-E of Figure 25 when the power tool is in the impact drill mode;

Figure 32 is an exploded view of a partial assembly of the power tool;

Figure 33 is a schematic structural view of an operating member and a ring switch;

FIG. 34 is a schematic diagram of the power tool in an impact wrench mode when the clutch position of the power tool and the working shaft of the power tool are located on the right side of the impact unit;

35 is a schematic view showing the clutching position of the power tool of the power tool and the working shaft in the right side of the impact unit, and the power tool is in a continuous mode;

36 is a schematic view showing a first operation interface of a power tool according to still another embodiment;

37 to 40 are schematic diagrams showing states of the switching ring in different functional modes in the first operation interface;

Figure 41 is a schematic view showing a second operation interface of the electric power tool according to still another embodiment;

42 to 45 are schematic diagrams showing states of the switching ring in different functional modes in the second operation interface;

Figure 46 is a schematic view showing a second operation interface of the electric power tool according to still another embodiment;

47 to 50 are schematic diagrams showing states of the switching ring in different functional modes in the third operation interface;

Figure 51 is a schematic view showing a fourth operation interface of the electric power tool according to still another embodiment;

52 to 55 are schematic diagrams showing states of the switching ring in different functional modes in the fourth operation interface;

Figure 56 is a schematic view showing a second operation interface of the electric power tool of the embodiment shown in Figure 1;

57 is a schematic view showing a third operation interface of the electric power tool of the embodiment shown in FIG. 1;

Figure 58 is a schematic illustration of a third operational interface of the power tool of the embodiment of Figure 1.

detailed description

In order to facilitate the understanding of the present invention, the present invention will be described more fully hereinafter with reference to the accompanying drawings. Preferred embodiments of the invention are shown in the drawings. However, the invention may be embodied in many different forms and is not limited to the embodiments described herein. Rather, these embodiments are provided so that the understanding of the present disclosure will be more fully understood.

It should be noted that when an element is referred to as being "fixed" to another element, it can be directly on the other element or the element can be present. When an element is considered to be "connected" to another element, it can be directly connected to the other element or. In contrast, when an element is referred to as being "directly on" another element, the <RTIgt; The terms "vertical," "horizontal," "left," "right," and the like, as used herein, are for illustrative purposes only.

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.

A preferred embodiment of a multi-power tool will be described in detail below with reference to the accompanying drawings.

Referring to FIG. 1 to FIG. 4 , the electric tool 100 includes a housing 110 , a power unit, a working shaft 130 , an impact unit 140 , a control circuit , a matching component 150 , and a switching component 160 . The power device is configured to output power, and the impact unit 140 In order to cause the working shaft 130 to generate an impact motion (ie, intermittent rotation or pulse rotation) in the circumferential direction, the switching assembly 160 can drive the adapter 150 and the impact unit 140 to select Optionally, the power tool 100 can be switched between an impact wrench mode and a continuous mode (ie, continuous rotation). In continuous mode, the working axis only rotates continuously without intermittent rotation.

In one embodiment, referring to FIGS. 3 and 4, the housing 110 is used to receive and position other components of the power tool 100 and is a support frame for the power tool 100. The housing 110 includes a first portion 112 for mounting a power unit (not shown). The power unit of the present embodiment includes at least a motor 120 and a battery pack 170 for mating. As shown in FIG. 1, the first portion 112 further has a handle portion 1122 for holding, and the battery pack 170 is disposed at the end of the handle portion 1122. The motor 120, the handle portion 1122, and the battery pack 170 are disposed above and below, and the size in the lateral direction can be reduced, and at the same time conform to human body operating habits. The first part 112 is a Hough type, which is formed by splicing the left and right halves. The housing 110 further includes a second portion 113 on one side of the first portion 112, one end of which is embedded in the first portion 112, and the working shaft 130 extends from the other end of the second portion 113 for mating the working head. In Fig. 3, the housing 110 is actually formed by splicing three parts. Of course, the second portion 113 can also be formed by two-half splicing. Further, the two halves of the second portion 113 can be integrated with the two halves of the first portion 112, that is, at this time, the entire housing 110 is left and right. Two halves are spliced together.

The motor 120 is placed in the first portion 112, and the axial direction of the motor 120 coincides with the arrangement direction of the first portion 112 and the second portion 113, and also coincides with the axial direction of the working shaft 130. The motor 120 can be powered by a DC motor from the aforementioned battery pack 170.

Referring to FIG. 3, FIG. 4 and FIG. 9 to FIG. 17, the impact unit 140 is a piston type hydraulic impact unit, and the impact unit 140 includes a rotating member 142 that is driven to rotate by a power unit, and is sleeved outside one end of the working shaft 130. A closed space 143 is formed between the end of the working shaft 130, and the hydraulic oil 144 is enclosed in the closed space 143.

The working shaft 130 extends into the end of the rotating member 142 and is provided with an axial hole 131, which is also referred to as a first end in this embodiment. A movable member is connected to the rotating member 142. The specific movable member in this embodiment is specifically a cam shaft 145. The camshaft 145 extends into the axial bore 131 and has a rotational space within the axial bore 131 that is rotated with the follower member 142. When the clutch member 161 is in the second position, the movable member is driven to rotate relative to the working shaft, and the oil pressure sealed between the piston member and the working shaft can be changed when the clutch member is in the first position. The movable member, the rotating member 142 and the working shaft 130 rotate together.

The outer surface of the working shaft 130 is provided with a connecting passage 132 that communicates with the axial hole 131 and the closed space 143. During the rotation of the cam shaft 145, there is a position capable of isolating the axial hole 131 from the closed space 143; and also having a position allowing the axial hole 131 to communicate with the closed space 143, at which time the hydraulic oil 144 can be circulated.

The outer surface of the working shaft 130 is further provided with a guide groove 133 which is offset from the connecting passage 132 in the circumferential direction. The guide groove 133 is symmetrically disposed at least two places on both sides of the axis of the working shaft 130. The guide groove 133 extends in the radial direction of the working shaft 130, communicates with the axial hole 131 through the radial hole 134, and forms a radial through hole.

The guide groove 133 houses a piston member 146 and a ball 147. The piston member 146 is movable in the radial direction of the working shaft 130 in the guide groove 133. The ball 147 is sized to block the radial bore 134 to isolate the guide slot 133 from the axial bore 131.

The interior of the rotating member 142 is provided with a plurality of urging portions 1421 for forcing the piston member 146 to move radially toward the cam shaft 142. When the rotary member 142 rotates, the thrust portion 1421 and the cam shaft 145 both rotate, and the phases of the thrust portion 1421 and the cam shaft 145 are set to be shifted by 90 degrees.

As shown in FIGS. 8 and 12, wherein the cam shaft 145 allows the axial hole 131 to communicate with the closed space 143, the cam shaft 145 is in a horizontal position, and the abutting portion 1421 is located above the cam shaft 145, and does not abut the piston member. 146. When the urging portion 1421 is rotated by 90 degrees to maintain abutment with the piston member 146 in the radial direction, the cam shaft 145 is horizontally converted to vertical, and the connecting passage 132 is blocked to isolate the axial hole 131 from the closed space 143. As shown in Figure 11 and Figure 15. a process in which the piston member abuts against the abutting portion in a radial direction to abut against the abutting portion, the rotating member impacts the piston member, and the piston member moves in a radial direction while being circumferentially Impacting the working shaft

The urging portion 1421 has a climbing surface 1422 and an abutting surface 1423. The top of the piston member 146 includes a transition surface 1461 and a contact surface 1462. During the rotation of the urging portion 1421, the climbing surface 1422 smoothly climbs along the transition surface 1461 and advances. The piston member 146 is forced to move radially until the abutment surface 1423 abuts the contact surface 1462 in the radial direction. Both the climbing surface 1422 and the transition surface 1461 are provided as inclined surfaces for easy climbing.

Referring to Figures 11 through 12, Figures 15 through 16, the rotating member 142 is rotated in the direction indicated by the arrow in the figure. During the climbing of the abutting portion 1421 along the top of the piston member 146, the piston member 146 simultaneously urges the working shaft 130 to rotate, and the hydraulic oil 144 Beginning from the connecting passage 132 into the axial bore 131. When the urging portion 1421 abuts against the piston member 146 in the radial direction, the ball 147 blocks the radial hole 134, and the axial hole 131 around the cam shaft 145 A high-pressure oil-tight space is formed, and the piston member 146 is held at a position abutting against the abutting portion 1421 by the oil pressure. When the urging portion 1421 continues to rotate, the hydraulic oil 144 starts to enter the axial hole 131 from the connecting passage 132 while the urging portion 1421 is disengaged from the piston member 146, and simultaneously pushes the working shaft 130 to rotate, and the piston member 146 acts on the oil pressure. The lower portion is radially away from the axial hole 131 so as to abut against the next abutting portion 1421. Repeatedly, the impact unit 140 continues to generate an impact torque to the working shaft 130. The above process can be briefly summarized as that when the abutting portion 1421 and the piston member 146 are not in radial contact with each other when the clutch member is in the second position, the axial hole 131 communicates with the closed space, and is closed. The hydraulic oil in the space can enter the axial hole 131; when the abutting portion 1421 abuts against the piston member 146 in the radial direction, the axial hole 131 forms a partition space with the closed space, the piston The piece 146 moves radially along the guiding groove toward the axial hole, and the partition space is reduced in volume to form the high pressure chamber;

When the piston member 146 abuts against the abutting portion 1421 in the radial direction to be disengaged from the abutting portion 1421, the rotating member 142 impacts the piston member 146, and the piston member 146 has a diameter The working shaft is impacted circumferentially while moving.

Referring to Figures 3 and 4, a fitting 150 is also disposed within the housing 110. The adapter 150 is mounted to the working shaft 130 and can drive the working shaft 130 to rotate together. The power tool 100 also includes a switching assembly 160 that selectively connects the adapter 150 with the rotating member 142. When the switching assembly 160 is not connected to the adapter 150 and the rotating member 142, the rotation of the rotating member 142 does not act on the fitting 150, and the rotating member 142 of the impact unit 140 can rotate relative to the working shaft 130, and the impact unit 140 can work. The shaft 130 continuously generates an impact torque, enters the impact wrench mode, and performs the function of the impact wrench. When the switching component 160 is connected to the adapter 150 and the rotating member 142, when the rotating member 142 rotates, the working shaft 130 is rotated together by the connecting member 150, which is equivalent to locking the rotating member 142 and the working shaft 130 together, thereby impacting The unit 140 does not impact the working shaft 130, at which time the working shaft 140 will continuously rotate and the power tool 100 enters the continuous mode.

Referring to FIGS. 2 and 3, when it is required to switch between the impact wrench mode and the continuous mode, it is only necessary to make the switching assembly 160 in the state of connecting the adapter 150 and the rotating member 142 with the connecting member 150 and the rotating member 142. Switching between the states can be very convenient.

In one of the embodiments, the switching assembly 160 includes a clutch member 161 and an operating member 162 that drives the clutch member 161. The clutch member 161 is switchable between a first position and a second position in the axial direction of the working shaft 130. Wherein, referring to FIG. 3, the clutch member 161 is in its first position in the axial direction of the working shaft 130. At this time, the clutch member 161 has a mating relationship with the rotating member 142 and the adapter member 150, and the clutch member is fixedly coupled to the adapter member and the rotating member. The clutch member 161 connects the rotating member 142 with the adapter 150 to effect torque transfer, and the power tool 100 is in a continuous mode.

When it is required to switch from the continuous mode to the impact wrench mode, only the operating member 162 needs to be operated, and the clutch member 161 is axially moved and separated from the adapter 150, that is, the clutch member 161 is only connected to the rotating member 142, but The connector 150 is disengaged. Referring to FIG. 4, the rotating member 142 cannot transmit torque to the adapter 150. The power tool 100 will enter the impact wrench mode.

In the electric power tool 100 shown in FIG. 3 and FIG. 4, the clutch member 161 is a clutch gear that can slide axially, and is disposed to maintain a mating relationship with the outer ring of the rotating member 142, and is selectively matched with the adapter member 150. The connection relationship may of course be exactly the opposite, that is, when the clutch member is in the second position, the clutch member is connected to one of the oil pressure impact unit 140 or the adapter member 150, and is realized by the axial sliding by the second The position switches to the first position. It can be understood that, since the oil pressure impacting unit has a certain length in the axial direction, it is preferable that the clutch member 161 can be engaged with the outer circumferential surface of the rotating member 142 in the second position, that is, the clutch member 161 is set. The sleeve is sleeved on the outer side of the rotating member 142. The clutch member 161 and the adapter member 150 can be splined or relatively axially slid. The coupling member 161 and the rotating member 142 can also be connected or relatively axially slid by splines.

In one embodiment, the adapter 150 and the working shaft 130 are two pieces that are assembled together. In another embodiment, the adapter 150 is integral with the working shaft 130, and the adapter 150 can be considered to be part of the working shaft 130.

In one embodiment, as shown in Figures 3 and 4, the clutch member 161 is selectively coupled to the working shaft 130 in front of the impact unit 140, i.e., disengaged. The front side here means that in the axial direction of the working shaft 130, the clutching position of the clutch member 161 and the working shaft 130 is located on the left side of the rotating member 142, that is, the side of the impact unit 140 away from the motor 120, closer to the impact unit 140. The working shaft 130 extends from one end of the housing 110 (the left end of the working shaft 130 in Fig. 4 for driving one end of the working head). The clutch position is a position at which the clutch member 161 and the working shaft 130 are engaged to disengage.

Further, the clutching position of the clutch member 161 and the working shaft 130 is located between the rotating member 142 and one end of the working shaft 130. Since the rotating member 142 is sleeved outside the other end of the working shaft 130 (the right end of the working shaft 130 in FIG. 4) and forms a closed space 143 with the end of the working shaft 130, that is, it works. The right end of the shaft 130 is located within the enclosed space 130. When the clutching position of the clutch member 161 and the working shaft 130 is between the rotating member 142 and the other end of the working shaft 130, when considering the seal between the rotating member 142 and the working shaft 130, it is only necessary to consider that the rotating member 142 is close to the clutch member. The seal between the side of the 161 and the working shaft 130, that is, in Fig. 4, only the seal between the left side of the rotating member 142 and the working shaft 130 needs to be considered, whereby the design of the sealing scheme can be simplified.

It can be seen from the above description that a closed space 143 is formed between the working shaft 130 and the rotating member 142. One end of the working shaft is located in the closed space, and the other end protrudes from the closed space 143 for connecting the working head, that is, the working shaft has the same a first end in the enclosed space 143 and a second end for connecting the working head, and the second end protrudes away from the power device in an enclosed space;

Wherein the clutch member 161 is switchable between a first position and a second position, and when the clutch member 161 is in the first position, the rotating member 142 rotates continuously with the working shaft 130; When the clutch member 142 is in the second position, the rotating member 142 generates intermittent rotation with respect to the working shaft 130. Specifically, the clutch member connects the rotating member 142 and the working shaft 130 extending out of the closed space, so that when the rotating member 142 rotates, the working shaft 130 is continuously rotated together; when the clutch member 161 is in the second position, the clutch member 161 Disengagement from at least one of the working shaft 130 and the rotating member 142 outside the extended sealing space causes the rotating shaft to intermittently rotate when the rotating member rotates. That is, the clutch member 161 is switchable between a first position and a second position in which the working shaft 130 can be driven to continuously rotate when the clutch member 161 is in the first position, the clutch member 161 In the second position, the working shaft 130 can be driven to rotate intermittently.

Continuing to refer to FIG. 3 and FIG. 4 , in the embodiment, the power device further includes a gear mechanism connected to the output end of the motor 120. Specifically, the gear mechanism is a planetary reduction gear. It is understood that the planetary reduction gear according to actual needs. It can be a multi-stage planetary reduction gear or a first-stage planetary reduction gear. The rotating member 142 is connected to the output end of the power unit, and when the power unit rotates, the rotating member 142 is rotated. Specifically, the power unit is fixedly coupled to the rotating member 142 by a carrier adjacent to the impact unit 140 or an end remote from the motor 120. The first end of the impact unit 140 near the motor 120 is provided with a first sealed end cover 149. The end of the planetary frame that is far from the impact unit 140 is fixedly connected to the first sealed end cover 149. Of course, the two can also be integrally formed; When the mechanism is a multi-stage planetary reduction gear, the planetary carrier that is away from the motor 120 or close to the first sealed end cover 149 in the multi-stage carrier can be rotated The piece 142 is fixedly attached or integrally formed.

In another embodiment, the rotating member 142 can also be selectively connected to the power unit through the clutch member 161 to achieve continuous rotation or intermittent rotation, so that the rotating member 142 and the power unit are fixed relative to the above embodiment. The connection saves energy by allowing the rotating member 142 to continuously rotate in both the intermittent mode and the continuous mode.

7 and 8, the power tool 100a includes a housing 110a, a power unit, a working shaft 130a, an impact unit 140a, a control circuit, a mating member 150a, and a switching assembly 160a. The motor 120a is used to output power, and the impact unit 140a is used. In order to cause the working shaft 130a to generate an impact motion (ie, intermittent rotation or pulse rotation) in the circumferential direction, the switching assembly 160a can be selectively engaged with one of the mating member 150a and the impact unit 140a, thereby causing the power tool 100a. It is possible to switch between the impact wrench mode and the continuous mode (ie continuous rotation). In the continuous mode, the working shaft 130a is continuously rotated only, and intermittent rotation is not generated. The impact unit 140a is a piston type hydraulic impact unit. The impact unit 140a includes a rotating member 142a that is driven to rotate by a power unit, and is sleeved on an outer side of one end of the working shaft 130a to form a closed space 143a with the working shaft 130a. The closed space 143a is enclosed with a hydraulic oil 144a, that is, one end of the working shaft 130a is located in the sealed space 143a, and the other end extends out of the closed space 143a for connecting the working head. The power unit in this embodiment includes a motor 120a connected to the motor 120a for decelerating the planetary gear mechanism. The planetary reduction mechanism in this embodiment is a first-stage planetary gear reduction mechanism including a carrier 171a. The switching assembly 160a includes a clutch member 161a and an operating member 162a that drives the clutch member 161a, and the clutch member 161a is switchable between a first position and a second position in the axial direction of the operating shaft 130a. Referring to FIG. 7, when the clutch member 161a is in the first position of the working shaft 130a, the clutch member 161a has a mating relationship with the mating member 150a, the power device drives the working shaft 130a to rotate, and the power tool 100a is in the continuous mode.

Referring to FIG. 8, when it is required to switch from the continuous mode to the impact wrench mode, that is, when the clutch member 161a needs to be moved from the first position to the second position on the working shaft 130a, only the operating member 162a needs to be operated to make the clutch member The axial movement of the 161a is separated from the adapter 150a, that is, the clutch member 161a is only connected to the rotary member 142a, but is disengaged from the adapter member 150a.

Different from the above embodiment, the carrier (or power unit) in this embodiment is not fixedly coupled to the rotating member 142a, but is selectively coupled to the rotating member 142a via the clutch member 161a.

Specifically, referring to FIG. 7, one end of the clutch member 161a is connected to the carrier 171a. In this embodiment, the clutch member 161a is circumferentially fixed on the carrier, is axially movable, and is axially slid to be engaged with the mating member 150a. In cooperation, the mode of driving the working shaft 130a to achieve continuous output is achieved. It should be noted that at this time, the rotating member 142a does not rotate.

Referring to Fig. 8, one end of the clutch member 161a is connected to the carrier 171a, and the other end is connected to the rotating member 142a, and at this time, the clutch member 161a is disengaged from the working shaft 130a, that is, no longer mated with the mating member 150a. .

In this embodiment, one end of the clutch member 161a is mated with the carrier 171a, and the clutch member 161a is axially moved, and selectively cooperates with one of the working shaft 130a and the rotating member 142a to realize continuous or intermittent output. .

7 and 8, it is shown that one end of the working shaft 130a is located in the closed space 143a, and the other end protrudes from the closed space 143a. Therefore, the present embodiment not only achieves reduction between the working shaft 130a and the rotating member 142a by using the illustrated structure. The sealing problem at one end, by the selective rotation of the rotating member 142a, also achieves energy savings relative to the above embodiment.

In addition, in this embodiment, in order to better fix the rotating member 142a in the housing 110a, a groove 145a is disposed at one end of the rotating member 142a near the carrier, and the carrier 171a is provided with a protruding shaft 1710a, a protruding shaft The 1710a is rotatably secured within the recess 145a.

In another embodiment, the clutching position of the clutch member 161 and the working shaft 130 may also be disposed on the right side of the rotating member 142, that is, on the side of the impact unit 140 near the motor 120. At this time, the right end of the working shaft 130 protrudes from the rotating member 142, and the left and right sides of the rotating member 142 are sealed with the working shaft 130. The function switching of the electric tool 100 can also be realized when the clutch member 161 is moved. Referring to FIG. 2 to FIG. 6, the operating member 162 includes a switching ring 163 and an operating button 164. The operation button 164 is assembled on the outside of the switching ring 163 for driving the switching ring 163 to rotate. A support member 114 is fixed inside the housing 110, and a bearing 115 is disposed inside the support member 114. The rotating member 142 is fixed to the inner ring of the bearing 115, and the switching ring 163 is rotatably fitted outside the support member 114. The operating button 164 protrudes from the outer wall of the housing 110, and the entire switching ring is located inside the housing 110 to clean the exterior of the housing 110. An operation window 116 is provided on the outer wall of the housing 110, and with reference to FIG. 2, the operation button 164 is allowed to rotate within a range defined by the operation window 116.

When the operating button 164 is moved, the switching ring 163 can be driven to drive the clutch member 161 to generate an axial direction. exercise. Specifically, the switching ring 163 is provided with a first driving groove 165. The first drive groove 165 includes a first segment 1651 and a second segment 1652 that are spaced apart in the axial direction of the working shaft 130. The clutch member 161 is coupled to a slide pin 182 having a coupling with the first drive groove 165. The slide pin 182 can be moved in the front and rear directions of FIG. 5 under the push of the switching ring 163. Wherein, when the sliding pin 182 is located in the first segment 1651 of the first driving groove 165, the clutch member 161 is in its first position; when the sliding pin 182 is located in the second segment 1652 of the first driving groove 165 (refer to FIG. 5 Shown). The clutch member 161 is in its second position. Thus, by rotating the switching ring 163, the sliding pin 182 is switched between the first segment 1651 and the second segment 1652 to move the clutch member 161 in the axial direction of the working shaft 130, that is, the clutch member 161 is in its first position. Switching between the second position.

The operation button 164 is combined with the switching ring 163 and can be split. In other embodiments, the two may also be a one-piece component, that is, one portion of the switching ring 163 protrudes from the outer wall of the housing 100.

The slide pin 182 is disposed on one end of a push-pull rod 180. The push-pull rod 180 is substantially rod-shaped and extends along the axial direction of the working shaft 130. The other end of the push-pull rod 180 is fixedly or intermittently connected to the clutch member 161 to be capable of driving the clutch member 161 to move axially.

In the embodiment shown in FIGS. 2-6, the operating member 162 drives the clutch member 161 to move axially by rotating itself about the axis of the working shaft 130. In other embodiments, the operating member 162 is not limited to rotation. For example, the operating member 162 may be moved in a direction parallel to the axial direction of the working shaft 130 to drive the clutch member 161 to move axially.

Referring to FIG. 3 and FIG. 4, when switching between the continuous mode and the impact wrench mode, only the operation button 164 needs to be operated to drive the operating member 162, and the clutch member 161 is axially moved and then separated or mated with the adapter 150. can. That is, when the clutch member 161 is in the second position, it is disengaged from the working shaft 130.

Further, depending on the output torque and the rotational speed, the continuous mode can also be subdivided into a drill mode and a screwdriver mode, that is, when the clutch is in the first position, the control circuit controls the rotational speed of the motor and/or Torque allows the power tool to be selectively in the screwdriver mode or the drill mode. It should be noted that the screwdriver mode in the present invention means that the electric drill mode refers to that, in the outer wall of the housing 110, a gear position indicating portion 117 is disposed along the moving direction of the operating button 164, wherein Down to the top, the drill mode setting has a torque adjustment gear (the lowest gear position), and the screwdriver mode is further set to 5 A torque adjustment gear position to adapt to the operational requirements of different specifications of the screw.

Further, in order to adjust the torque in the continuous mode, and also to simplify the operation interface, the power tool 100 further includes a control component including an operation member 162 that triggers a work instruction and a control circuit that executes the work instruction, When the clutch member 161 is in the first position, the operating member 162 can trigger the control assembly to selectively cause the power tool to be in the screwdriver mode or the electric drill mode. When the clutch member 161 is in the second position, the operating member 162 can be triggered. The control assembly places the power tool 100 in an impact wrench mode. When the power tool 100 is in the screwdriver mode, the operating member 162 can be switched between different screwdriver positions, thereby causing the power tool 100 to perform different outputs. When the power tool 100 is in the impact wrench mode, the operating member 162 can be switched between different impact gear positions, thereby causing the power tool to perform different outputs. The operating member 162 is movably disposed relative to the housing, and the housing is provided with gear positions corresponding to the screwdriver, electric drill, and impact wrench modes respectively, when the operating member 162 is at a position corresponding to one of the gear positions. The power tool is capable of executing an output corresponding to one of the gear positions.

The power tool 100 is used to change the output torque and speed of the motor 120 through a control circuit coupled to the motor 120. Specifically, the control circuit simplifies the five gear position adjustments in the screwdriver mode. When the operation button 164 is in the first gear position of the screwdriver mode, the current of the motor 120 in the current screwdriver mode is detected. When the current of the motor 120 is less than the no-load current (can be preset according to requirements), the corresponding control motor 120 is at a low voltage voltage, such as the voltage of the motor 120 is less than or equal to a specific value when the no-load is controlled; If it is determined that the load current is not idling or greater than the preset load current, the voltage output of the motor 120 is changed correspondingly, and it is further determined whether the current current is greater than the highest current of the first gear position for a preset duration (can be advanced as needed) Set), if yes, stop or leave the motor in standby. Similarly, for the second gear position in the screwdriver mode, the steps are the same as those in the first gear position, and the judgment of the no-load, loading process and the control process can be the same as the first gear position, and the difference is the second gear position. The highest current value is different, that is, the torque and speed that can be output in the second gear position are different from the first gear position; similarly, the control principles of the third, fourth and fifth gear positions can be the same as the first and the first The second gear is the same, but the highest current value is different in different gear positions, so that the screwdriver can adapt to different screw heads in different screw positions.

It can be understood that when the clutch member 161 is in the second position, it corresponds to the gear position control in the impact wrench mode. The gear position control mode of the above-mentioned screwdriver mode can also be adopted, but the size of the corresponding parameter may be different, that is, the control circuit causes the power tool to be in different impact wrench positions by controlling the maximum current flowing through the motor 120.

It can be understood that, referring to FIG. 3, the control circuit can also have a variable element 192, wherein the state of the variable element 192 can be changed during the rotation of the operating member 162, so that the control circuit changes the output torque of the motor 120, thereby achieving The purpose of the output shaft 130 to output torque is adjusted.

When the state of the variable element 192 changes, the operating current of the motor 120 can be changed to achieve the purpose of changing the output torque of the motor 120. In one embodiment, the variable element 192 can be a sliding resistor. In other examples, the variable element 192 can also be a select switch, and the operating member 162 turns the variable element 182 into a different circuit, thereby changing the output torque of the motor 120.

The operating member 162 controls the output torque of the motor 120 in addition to the manner mentioned above by electronic control, and may also be mechanical. For example, an overload clutch is provided that interrupts the transmission of torque between the motor 120 and the working shaft 130 when the transmitted torque exceeds the overload torque.

Specifically, the operating member 162 is configured to continue to be operated after the clutch member 161 is switched from its second position (the power tool 100 is in the impact wrench mode) to the first position (the power tool 100 is in the continuous mode) And causing the control circuit to change the output torque of the motor 120. To achieve the above object, it is only necessary to provide such that the first segment 1651 of the first driving groove 165 has a sliding space allowing the sliding pin 182 to advance, and the sliding space does not allow the sliding pin 182 to be displaced in the axial direction of the working shaft 130. .

Similarly, in the impact wrench mode, a plurality of torque adjustment gear positions can also be provided. As shown in FIG. 2, the impact wrench mode is provided with two gear positions, and the output torque of the working shaft 130 is different under the two gear positions. To this end, the operating member 162 is further configured to continue to be operated and urged when the clutch member 161 is switched from its first position (the power tool 100 is in the continuous mode) to the first position (the power tool 100 is in the impact wrench mode) The control circuit changes the output torque of the motor 120. To achieve the above object, it is only necessary to provide such that the second section 1652 of the first driving groove 165 has a sliding space allowing the sliding pin 182 to advance, and the sliding space does not allow the sliding pin 182 to be displaced in the axial direction of the working shaft 130. .

For the power tool 100, the power tool 100 can be switched from the impact wrench mode to the continuous mode by operating the operating member 162, and then the motor torque can be continuously changed by operating the operating member 162. The torque is now adjusted. Therefore, the mode switching switch and the torque adjustment share one operating element, and the operation interface is simple and convenient to operate. Further, when the impact wrench mode is set to a plurality of gear positions, the power tool 100 can be switched from the continuous mode to the impact wrench mode by operating the operating member 162, and then the motor speed can be continuously changed by operating the operating member 162 to achieve an impact. Torque adjustment in the wrench mode, mode switching switch and torque adjustment share a single operating element, the operation interface is simple and easy to operate.

Further, the power tool 100 triggers the control circuit by using the operating member 162 to change the operating current of the motor 120, thereby changing the rotational speed and torque of the motor 120, thereby achieving the torque adjustment of the working shaft 130.

Further, since both the impact wrench mode and the screwdriver mode are provided. When high torque conditions are required, the impact wrench mode is used. The maximum torque of the screwdriver mode can be small. It can be used in small torque conditions and can obtain a considerable torque adjustment range. Therefore, the speed reduction mechanism 122 only uses the primary gear reduction system, that is, the motor shaft of the motor 120 can drive the rotary member 142 to rotate only by the primary gear reduction system, without setting a complicated multi-stage planetary gear system to satisfy the output torque of the working shaft 130. Adjustment requirements. Therefore, compared with the conventional mechanical impact unit and the multi-stage gear transmission power tool, the oil pressure impact unit and the first-stage gear reduction system are adopted, and the size is small, the cost is low, and the torque adjustment range is also wide.

The impact unit 140 is a hydraulic impact unit that utilizes the action of the hydraulic oil 144 to effect the impact of the working shaft 130. In other embodiments, the impact unit 140 may also be an impact unit of a mechanical impact structure. For example, the plurality of abutting portions 1421 of the rotating member 142 intermittently impact the impacting member on the working shaft in the circumferential direction to make the working shaft 130 In the impact wrench mode, the elastic element can be used to abut the impact element in the radial direction. After the impact is completed, the elastic element returns the impact element to receive the impact again.

In another embodiment, the impact unit 140 described above can also be replaced by the impact unit 240 shown in FIGS. 18 and 19. Accordingly, the working shaft 130 is replaced with a working shaft 230. The structure of the impact unit 240 and its working principle will be briefly described below with reference to the drawings.

The impact unit 240 includes a rotating member 242 that is driven to rotate by a motor. The rotating member 242 is sleeved outside the one end of the working shaft 230 and forms a closed space 243 with the working shaft 230. The inner wall of the rotating member 242 is provided with a plurality of sealing portions 2422.

A radial portion 232 for contacting the sealing portion 2422 is provided on the surface of the working shaft 230. The number of the radial portions 232 is less than the number of the sealing portions 2422. The surface of the working shaft 230 is provided in the circumferential direction and the radial direction. The portion 232 is staggered with a radial through hole 233. Two piston members 246 are disposed in the radial through holes 233. A hydraulic oil 244 is disposed between the two piston members 246, and an elastic member 247 is provided for providing an elastic force that maintains the piston member 246 in sealing contact with the inner wall of the rotary member 242. Further, a space between the piston member 246 and the inner wall of the radial through hole 233, and between the working shaft 230, the rotating member 242, and the piston member 246 is also filled with hydraulic oil 244. During the rotation of the rotating member 242, a high-pressure chamber capable of generating high oil pressure can be intermittently formed between the rotating member 242 and the working shaft 230, and the pivoting high-pressure chamber can seal the hydraulic oil in the partially sealed chamber, and the piston member 246 is radially During the movement, the working shaft 230 is intermittently impacted in the circumferential direction to realize the pulse rotation of the working shaft 230, thereby realizing the impact wrench mode.

When the rotating member 242 is rotated relative to the working shaft 230, the radial portion 232 can be brought into contact with the sealing portion 2422. Wherein, during the rotation of the rotating member 242, when the sealing portion 2422 is in contact with the radial portion 232, the high pressure chamber a is formed; when the sealing portion 2422 and the radial portion 232 are separated, the high pressure chamber a is disabled.

In one embodiment, the inner wall of the rotating member 242 is provided with four sealing portions 2422 in the circumferential direction, two radial portions 232 are disposed on the working shaft 230, and two piston members 246 are disposed in the working shaft 230, two An elastic member 247 is disposed between the piston members, wherein the radial portion 232 and the piston member 246 are offset in the circumferential direction of the working shaft;

Referring to the a state of the impact unit 240 in FIG. 19, during the rotation of the rotating member 242, when the sealing portion 2422 is in contact with the radial portion 2322, two high voltages are formed between the rotating member and the working shaft in the circumferential direction. a chamber a and two low pressure chambers b. The high oil pressure generated by the high pressure chamber a pushes the piston member 246 to move radially, and the piston member 246 radially moves while impacting the working shaft 230 in the circumferential direction, and the high pressure chamber a and the low pressure chamber b are spaced apart from each other.

The rotating member 242 continues to rotate relative to the working shaft 230 in the direction of the arrow in the figure, and will gradually reach the state of bd in FIG. 18 from the state a in FIG. 18, wherein the sealing portion 2422 is separated from the radial portion 2322, the high pressure chamber a and the low pressure. When the chamber b is in communication, the high pressure chamber a fails, and the elastic member 247 causes the piston member 246 to be reset.

When the rotating member 242 rotates once, the radial portion 232 and the sealing portion 2422 will come into contact again to achieve sealing, and the high pressure chamber a is formed again, so that the piston member 246 again drives the working shaft 230 to rotate on the circumference. Thus, the rotating member 242 is continuously rotated to cause the working shaft 230 to perform a gap-type rotation, that is, a pulse impact.

Similar to the impact unit 140, when the impact unit 240 and the working shaft 230 are used, the power tool 100 The clutching position of the clutch member 161 and the adapter member 150 may be disposed on the left side or the right side of the rotating member 242.

Referring to FIGS. 21-23, in another embodiment, the present invention further provides another power tool 100', including a housing 110', which includes a substantially cylindrical tubular housing (in the figure) Not shown), a handle portion 1122' disposed at an angle to the cylindrical casing, and a battery pack 170' detachably disposed at the bottom of the handle portion 1122'. The front end of the cylindrical casing is provided with a collet 109' for holding the working head for respectively holding different working heads (not shown) when the electric power tool 100' realizes different functions. The upper end portion of the handle portion 1122' is provided with a push button switch 103' for opening and closing the power tool 100'. Referring to Fig. 21, one end of the cylindrical housing on which the chuck 109' is located is the front end, and the other end is the rear end. The rear end of the housing receives the power unit, and the power unit has an output shaft that provides a rotational output. In this embodiment, the power device is a motor 120'. The motor 120' has a motor shaft for outputting a rotary motion; the front end of the output shaft is connected with an impact unit 140', and the impact unit 140' includes a rotating member 142'. The rotating member 142 is coupled to the motor shaft. Therefore, the motor shaft can drive the rotating member 142' to rotate; the impact unit 140' further includes a hydraulic portion 141', and the hydraulic portion 141' includes hydraulic oil 144'. The front end of the impact unit 140' is provided with a working shaft 130', and the rotating member 142' is coupled to the working shaft 130' via a hydraulic portion 141'; the power tool 100' further includes a switching assembly 160' disposed on the rotating member 142' and the work Between the shafts 130' is used for locking and separating the rotating member 142' and the working shaft 130'.

The power tool 100' also includes a mating member 150' that is integrally or fixedly coupled to the working shaft 130'. The switching assembly 160' includes a locking member disposed on the rotating member 142' or the fitting member 150', and is axially movable and circumferentially fixed, and the rotating member 142' or the fitting member 150' is correspondingly disposed. The locking portion is locked with the locking member; in this embodiment, the locking member is a clutch member 161' sleeved on the rotating member 142', and the inner wall of the clutch member 161' is formed to be circumferentially engaged with the outer circumferential wall of the rotating member 142'. The connecting structure of the axial sliding connection; the connecting member 150 ′ and the rotating member 142 ′ are realized by the coupling member 150 ′ close to the end of the fitting 150 ′ by the circumferential engagement and the axial sliding engagement with the fitting 150 ′. Interlocking and disengagement; it will be readily appreciated by those skilled in the art that the locking member can also be a spline disposed on the adapter 150' or the rotating member 142', or other form of locking member. In this embodiment, the outer circumferential wall of the rotating member 142' is formed with a plurality of axially extending sliding grooves 1420', and the inner wall of the clutch member 161' is formed with an embedded sliding groove. The slider 1610' of the 1420'; the one end of the clutch member 161' near the mating member 150' is provided with a clutch protrusion 1611', and the mating member 150' is provided with a clutch groove, and the clutch protrusion 1611' can be inserted into the clutch groove. A locked state is formed.

The switching assembly 160' further includes a switching member connected to the operating button 164'. The switching member can drive the locking portion to operate. The switching member and the clutch member 161' are axially fixedly disposed through the switching member and the clutch member 161'. The axial dimension change drives the locking member to reciprocate axially. The switching member includes a switching ring 163' axially positioned and rotatably disposed relative to the motor 120', the axially-scaled structure having a shape that is circumferentially disposed and axially offset on the switching ring 163' a first driving slot 165' and a switching lever 166' that is circumferentially positioned and axially slidable relative to the power system (motor 120'); the switching lever 166' has an embedded first driving slot 165' at one end The other end of the switching lever 166' is slidable in the circumferential direction and axially positioned to connect the clutch member 161'.

Optionally, the embodiment can also implement the speed adjustment. Specifically, the power tool 100 ′ further has a shifting mechanism, and the shifting mechanism includes a first-stage or multi-stage speed reduction mechanism (such as a first-stage or multi-stage planetary gear mechanism), and an axial direction. a reciprocating shifting lever 162'; one end of the multi-stage speed reducing mechanism is coupled to the motor shaft, and the other end is coupled to the impact unit 140', and the shifting ring 163' is further formed with a shifting operation slot including axially offset in the circumferential direction 168', one end of the shift lever 162' is embedded in the shift operating slot 168'; the axial movement of the shift lever 162' can be realized by the switching ring 163' to adjust the rotational speed of the output of the speed reducing mechanism; the technology is prior art ( See Chinese patent CN102335908A), the specific structure and working process will not be repeated here.

The continuous rotation function and the impact function of the embodiment are implemented as follows:

When the continuous rotation function is required, the toggle operation button 164' drives the switching ring 163' to rotate, so that the first driving groove 165' rotates accordingly, and the protruding pin at the rear end of the switching lever 166' is driven to move forward, thereby pushing and switching the lever. 166 'The fixedly connected clutch member 161 ′ moves forward, and the clutch protrusion 1611 ′ at the front end of the clutch member 161 ′ moves forward to be inserted into the clutch groove on the adapter 150 ′, thereby rotating the rotating member 142 ′ and the adapter member The 150' is locked together, at which time the rotating member 142' drives the working shaft 130' to continuously rotate.

When the impact rotation function needs to be realized, the toggle operation button 164' drives the switching ring 163' to rotate, so that the first driving groove 165' rotates accordingly, and the convex pin at the rear end of the switching lever 166' is driven to move backward, thereby pushing and switching. The fixed contact 161 ′ of the rod 166 ′ moves backward, and the clutch protrusion 1611 ′ at the front end of the clutch 161 ′ moves backward to leave the clutch groove on the fitting 150 ′, thereby rotating the rotating member 142 ′ and the fitting 150' is separated, at this time, the rotating member 142' does not drive the working shaft 130' to rotate, and the working shaft 130' rotates relative to the impact unit 140', causing the impact unit to form a high-voltage pulse and act on the working shaft 130', thereby forming an impact rotation. .

In another embodiment, the shift lever 166' cooperates with a biasing force acting on the clutch member 161' in the axial direction to apply a thrust or a pulling force against the biasing force to the clutch member 161'. The spring is applied symmetrically between the clutch member 161' and the rotating member 142'. In this embodiment, the switching lever 166' can only drive the clutch member 161' to move backward. In this embodiment, the switching lever 166' is switched. The front end is provided with an inwardly curved portion, and the rear end of the clutch member 161' is provided with an everted edge, and the front end of the switching lever 166' is engaged with the rear end of the clutch member 161', thereby switching the lever 166' The clutch member 161' can be driven to move backward; at the same time, a plurality of sets of springs 167' are symmetrically disposed between the clutch member 161' and the rotating member 142'. One end of the spring 167' is connected to the clutch member 161', and the other end is fixed to the rotation. The back end of piece 142'.

When the impact rotation function needs to be realized, the operation button 164' is toggled to drive the switching ring 163' to rotate, so that the first driving groove 165' rotates accordingly, and the convex pin at the rear end of the switching lever 166' is driven to move backward, thereby pushing and switching. The clutch member 161' fixedly connected to the clutch member 161' moves backward, and the clutch protrusion 1611' at the front end of the clutch member 161' moves rearward to leave the clutch groove on the adapter member 150', so that the rotary member 142' and the adapter member 150' is separated, at this time, the rotating member 142' does not drive the working shaft 130' to rotate, and the working shaft 130' rotates relative to the impact unit 140', causing the hydraulic portion to form a high-voltage pulse and act on the working shaft 130', thereby forming an impact rotation. .

When the continuous rotation function is required, the operation button 164' is toggled to drive the switching ring 163' to rotate, so that the first driving groove 165' rotates accordingly, and the protruding pin at the rear end of the switching lever 166' is moved forward. The shift lever 166' is separated from the clutch member 161', and the clutch member 161' moves forward under the action of the spring 7', and the clutch projection 1611' at the front end thereof is inserted into the clutch groove on the adapter member 150', thereby rotating the member The 142' is locked with the adapter 150', at which time the rotating member 142' drives the working shaft 130' to rotate continuously.

Referring to FIG. 24, in still another embodiment, a hammer drill function switching mechanism is added to the power tool 100 to obtain a power tool 300 having four functions. It has an impact wrench mode that can realize the impact wrench function, and also has a continuous mode (including drill mode and screwdriver mode), which can realize the drilling function and the screwdriver function, and can also switch to the impact drill mode to realize the impact drill function. Therefore, the following focuses on how to add a hammer drill function switching mechanism to the power tool 100 and how the hammer drill mode switches with other modes.

In one embodiment, the power tool 300 includes a housing 310, a motor 320, a working shaft 330, an impact unit 340, and a switching assembly 350. The principle of the impact unit 340 is the same as that of the impact unit 140 described above, and may be replaced by the impact unit 240 described above. Taking the impact unit 140 as the impact unit 340 as an example, the impact unit 340 causes the working shaft 330 to generate the impact wrench function in the same manner as the impact unit 140 causes the working shaft 230 to implement the impact wrench function. When the switching assembly 350 is operated, it is possible to selectively transmit torque between the rotating member 342 of the impact unit 340 and the working shaft 330, thereby realizing the conversion of the impact wrench mode and the continuous mode. Therefore, the structural details of the mating portion between the impact unit 340 and the working shaft 330 will not be described herein.

Referring to FIG. 24, the working shaft 330 is further spaced apart from the axial direction thereof with movable end teeth 361, static end teeth 362, second clutch members 363, and elastic positioning members 364. The movable end tooth 361 is disposed to be rotatable together with the working shaft 330, the static end tooth 362 is loosely fitted on the working shaft 330, and the second clutch member 363 is axially movable relative to the working shaft 330 (front in FIG. 24, The rear direction is used to control the static end teeth 362 to rotate or not, the elastic positioning member 364 is used to provide the elastic force acting on the second clutch member 363, and the second clutch member 363 needs to overcome the resistance of the elastic positioning member 364 to be axially The movement is either reset by the elastic force of the elastic positioning member 364.

The impact drill mode is further implemented in continuous mode. That is, when the power tool 300 is in the continuous mode, it can be further subdivided into a drill mode, a screwdriver mode, and a hammer drill mode to realize a drill function, a screwdriver function, and a hammer drill function, respectively.

The end surface of the movable end tooth 361 and the end surface of the stationary end tooth 362 mesh in the axial direction of the working shaft 330. The tooth-joining surface of the movable end tooth 361 and the static end tooth 362 is a sloped surface. Therefore, when the static end tooth 362 is restricted from being rotated by the second clutch member 363, the working shaft 330 rotates the movable end tooth 361 to act on the inclined surface. Next, a thrust in the axial direction of the working shaft 330 is generated which separates the movable end teeth 361 from the stationary end teeth 362 and drives the working shaft 330 to move in the axial direction thereof. In the case where the working shaft 330 is rotated at a high speed, the working shaft 330 will generate an axial impact of a certain frequency, so that the power tool 100 is in the impact drilling mode, and the impact drilling function is realized. When the stationary end teeth 362 are not constrained by the second clutch member 363, the power tool 300 is in a drill mode or a screwdriver mode.

The switching component 350 is used to implement the conversion of the impact wrench mode and the continuous mode, and is also used to control the axial movement of the second clutch member 363 to achieve the switching of the impact drill mode.

The switching assembly 350 includes a first clutch member 351 and an operating member 352 for controlling the first clutch member 351, wherein the first clutch member 351 is capable of being between a first position and a second position in the axial direction of the working shaft 330. Switching to selectively effect torque transfer with the rotating member 342 of the impact unit 340, thereby effecting the conversion of the impact wrench mode and the continuous mode. The operating member 352 is also used to control the axial movement of the second clutch member 363 to achieve switching of the impact drill mode.

Referring to Figures 26 and 27, the first clutch member 351 is axially in its second position, disengaged from the rotating member 342 of the impact unit 340, and there is no torque transmission therebetween, and the power tool 300 is in the impact wrench mode. Impact wrench function.

Referring to Figures 28 and 29, the operating member 352 is manipulated to move the first clutch member 351 to its first position to effect torque transmission to the rotary member 342 of the impact unit 340, and the power tool 300 is switched to the drill mode or the screwdriver mode in the continuous mode. . At this time, the stationary end teeth 362 are loosely fitted over the working shaft 330 without being restricted by the second clutch member 363.

Referring to Figures 30 and 31, the operation member 352 is continuously manipulated to axially move the second clutch member 363 to restrict the stationary end teeth 362 from rotating, and the power tool 300 is switched from the drill mode or the screwdriver mode to the impact drill mode.

In one embodiment, the first clutch member 351 is an axially slidable clutch gear that is disposed in a mating relationship with the working shaft 330 and selectively maintains a mating relationship with the rotating member 342, which may of course be reversed. The first clutch member 351 and the working shaft 330 can be splined or axially slid. The first clutch member 351 and the rotating member 342 can also be connected or relatively axially slid by splines.

Referring to Figures 32 and 33, in one embodiment, the operating member 352 includes a switching ring 353 and an operating button 354. The operation button 354 is assembled on the outside of the switching ring 353 for driving the switching ring 353 to rotate. The operating member 352 and the switching ring 353 can be fitted together by a convex embedded groove or the like. The switching ring 353 is sleeved on the outside of the housing 110. When the switching ring 353 rotates, the first clutch member 351 can move axially and the second clutch member 363 can move axially. The operating button 354 is disposed to be in rotational engagement with the housing 310. In other embodiments, the user can directly operate the switching ring 353 to effect its rotation. In other embodiments, the movement of the first clutch member 351 and the second clutch member 363 may be other motions than axial motion, such as rotation. The direction of movement of the first clutch member 351 and the second clutch member 363 is also not limited to the axial direction of the working shaft 330.

The switching ring 353 drives the first clutch member 351 to move by the first push-pull rod 370. In one embodiment, the switching ring 353 is provided with a first driving groove 355. The first driving groove 355 includes a first segment 3551 and a second segment 3552 which are spaced apart in the axial direction of the working shaft 330.

The first clutch member 351 is coupled to a slide pin 372 that cooperates with the first drive groove 355. The slide pin 372 is disposed on one end of the first push-pull rod 370. When the switching ring 353 rotates, the sliding pin 372 is driven to switch in the first segment 3551 and the second segment 3552, thereby realizing the axial movement of the first clutch member 351 to achieve connection or separation with the rotating member 342.

The switching ring 353 causes the second clutch member 363 to move axially by the second push-pull rod 380. In one embodiment, the edge of the switching ring 353 is provided with a second driving slot 356. The second push-pull rod 380 is coupled to or provided with a stop pin 382 that can extend into the second drive slot 356. The switching ring 353 moves the second push-pull rod 380 axially by acting on the stopper pin 382, thereby axially moving the second clutch member 363. In the direction of rotation of the switching ring 353, the timing of the axial movement of the stop pin 382 depends on the timing of switching to the impact drill mode.

The first clutch member 351 is coupled to the working shaft 230 on the left side of the rotating member 342. Similar to the power tool 100, the first clutch member 351 may also be coupled to the working shaft 230 on the left side of the rotating member 342.

For example, in the embodiment shown in Figures 34 and 35, the right end of the working shaft 330 extends beyond the rotating member 342. The position of the operating member 352 corresponds to the right shift, and the clutch position of the first clutch member 351 and the working shaft 330 is also disposed on the right side of the rotating member 342. Wherein the first clutch member 351 is driven by the motor through the speed reduction mechanism 322 The rotation is rotated and mated with the rotating member 342 by splines, so that the clutch member 361 can drive the rotating member 342 to rotate and can move axially relative to the rotating member 342. As shown in FIG. 34, the first clutch member 351 is coupled to the rotary member 342, but is disengaged from the working shaft 330, the working shaft 330 and the rotary member 342 are relatively rotatable, and the power tool 300 is in the impact wrench mode. As shown in FIG. 35, after the first clutch member 351 is axially moved, the working shaft 330 is spline-connected to realize torque transmission of the rotating member 342 and the working shaft 330, and the power tool 300 enters a continuous mode. In this continuous mode, Further implementation of the drill mode, the screwdriver mode and the impact drill mode.

The power tool 300 is also provided with a control circuit that is electrically coupled to the motor 320. By setting the control circuit, electronically limiting the output torque and/or speed: Since the torque of the permanent magnet excited DC motor is roughly proportional to the motor current, the corresponding torque can be limited by limiting the motor current.

The control circuit includes an annular switch 390 that is secured to the housing 110. The operation button 354 has a spring piece 3542 that is in contact with the ring switch 390. When the operation button 354 is rotated, the contact position of the elastic piece 3542 and the ring switch 390 is changed, and the output torque of the motor 320 is changed, thereby achieving the purpose of adjusting the output torque of the working shaft 330.

When the operation button 354 is rotated, the adjustment of the plurality of gear positions in the drilling mode and the adjustment of the plurality of gear positions in the screwdriver mode can be realized, and the adjustment of the plurality of gear positions in the impact wrench mode can also be realized.

In the embodiment shown in FIG. 26 to FIG. 31, when the plurality of function modes of the electric power tool 300 are switched, when the impact wrench mode is switched to the continuous mode, the mode may be switched to the drill mode first, or the screwdriver mode may be switched first. . The mode switching is performed in accordance with predetermined logic by setting the shape, position, and the like of the first driving groove 355 and the second driving groove 356. Mode switching in different sequences will be further explained in detail below with reference to the accompanying drawings.

Referring to Figure 36, a schematic diagram of a first operational interface of the power tool 300 is shown. Among them, from top to bottom are: impact wrench mode, with 2 gear positions; screwdriver mode, with 5 gear positions; drill mode, set 1 gear. It should be emphasized that the number of gears here is only an example to illustrate the mode switching principle under the operation interface, and the number of gear positions should not be limited thereto. The operation button 354 drives the switching ring 353 to have a first stroke, a second stroke, a third stroke and a fourth stroke in the rotation direction, and is used to implement different functional modes in different stroke stages.

Figures 37 through 40 illustrate the principle of mode switching at the first operational interface. Mode switching sequence It is “Impact Wrench Mode Screwdriver Mode Drill Mode Impact Drill Mode”. The operating button 354 is in the first stroke range, the first clutch member 351 is separated from the rotating member 342, the torque between the rotating member 342 and the working shaft 330 is transmitted, and the power tool 300 is in the impact wrench mode, as shown in FIG. . At this time, the stopper pin 382 on the second push rod 380 is located outside the second driving groove 356, and the sliding pin 372 on the second push rod 380 is located in the first segment 3551 of the first driving groove 355. When a plurality of gear positions are set in the impact wrench mode, the output speed of the motor 320 can be changed by operating the operation button 354.

As shown in FIG. 38, when it is required to switch from the impact wrench mode to the screwdriver mode, the operation button 354 is rotated to rotate the operation button 354 to the second stroke range, and the switching ring 353 will move the slide pin 372 to the first drive. In the second section 3552 of the slot 355, the first clutch member 351 is axially moved to the first position to effect torque transmission between the rotating member 342 and the working shaft 330. The relative position of the stop pin 382 and the switching ring 353 changes.

When the operation button 354 is rotated to the second stroke range, it is set to the screwdriver mode. Continuing to rotate the operation button 354, the operation button 354 enters its third stroke range, and can be switched from the screwdriver mode to the drill mode by changing the position at which the elastic piece 3542 is in contact with the ring switch 390, as shown in FIG. In the screwdriver mode, the output torque of the motor 320 is set to be different from the output torque in the drill mode.

Further, in the screwdriver mode, there are a plurality of torque adjustment gear positions. That is, if the operation button 354 is rotated in the second stroke range, the position where the elastic piece 3542 is in contact with the ring switch 390 can be changed, and the output torque of 320 is further changed a plurality of times, thereby realizing the torque adjustment in the screwdriver mode.

In the screwdriver mode and the drill mode, the clutch members 352 are both in the first position, and the working shaft 230 continues to rotate together with the rotating member 342.

Continuing to rotate the operating button 354, the operating button 354 will enter its fourth range of travel. As shown in FIG. 40, the stopper pin 382 enters the second driving groove 356 and axially moves the second clutch member 363 to restrict the rotation of the static end tooth 362, and the position of the clutch member 352 remains unchanged, and is still in the first position. The axial impact of the working shaft 330 is achieved, thereby completing the switching from the drilling mode to the impact drill mode.

When the operation button 354 is rotated in the reverse direction, the mode switching sequence is just the opposite.

In the first operation interface, the torque adjustment in the screw mode and the adjustment of each function mode share a single adjustment component, and the operation interface is simple.

Under the above operation interface, operating the operation button 354 to control the output torque and the rotational speed of the motor through the electronic The way to control. Further, the operation of the operation button 354 to control the output torque and the rotational speed of the motor may also be by mechanical control. For example, an overload clutch is provided, and when the transmitted torque exceeds the overload torque, the overload clutch interrupts the torque transmission between the motor 320 and the working shaft 330.

Referring to Figure 41, a schematic illustration of a second operational interface of the power tool 300 is shown. Figures 42 through 45 illustrate the principle of mode switching at the second operational interface. Similar to the first operation interface, the operation button 354 drives the switching ring 353 to have a first stroke, a second stroke, a third stroke and a fourth stroke in the rotation direction, and is used in different stroke stages. Implement different functional modes. The first stroke corresponds to the impact wrench mode, the second stroke corresponds to the screwdriver mode, the third stroke corresponds to the drilling mode, and the fourth stroke corresponds to the impact drill mode.

The difference from the first operation interface is that the mode switching mode is "impact drilling mode".

Drill mode

Impact wrench mode

The screwdriver mode is different from the switching mode of each function mode in the first operation interface. Therefore, if the power tool 300 is initially in the impact wrench mode, it can be switched to the drill mode and then switched to the impact drill mode; or switch first In the drill mode, switch back to the impact wrench mode, then switch to the drill mode, and then switch to the impact drill mode. In other words, the mode switch under the second operation interface is equivalent to the first operation compared to the first operation interface. The execution order of each stroke under the interface has been adjusted.

In one embodiment, as shown in FIG. 41, since the impact wrench mode is located between the drill mode and the screwdriver mode, the shape of the first drive groove 355 is also improved accordingly. Specifically, compared with the first operation interface, the first driving groove 355 is changed to a three-stage type with a narrow middle and a wide end. Thus, when the switching ring 353 is rotated by the operating button 354, the sliding pin 372 is switched between the narrow and wide portions of the first driving groove 355 to drive the first clutch member 351 to move axially in the front-rear direction.

In one embodiment, the setting operation button 354 first executes the fourth stroke range, and the power tool 300 is in the impact drill mode. As shown in FIG. 42, the stopper pin 382 is located in the second driving groove 356, and the second clutch member 363 is in the limit static state. The position at which the end teeth 362 rotate. The first clutch member 351 is in a position to achieve a torque transmission between the rotary member 342 and the operating shaft 330.

When the impact drill mode is switched to the drill mode, the operation button 354 drives the switching ring 353 to rotate to the third stroke range, and the second clutch member 363 moves axially to a position where the static end tooth 362 is no longer restricted, so that the impact function is disabled. Enter the drill mode as shown in Figure 43. The sliding pin 372 is in the first driving slot 355 The location has changed.

The operation button 354 is continuously caused to rotate the switching ring 353 to the first stroke range. As shown in FIG. 44, the sliding pin 372 is in a narrow portion to the middle of the first driving groove 355, and the first clutch member 351 is axially moved to no. The position of the rotating member 342 and the working shaft 330 is reconnected to switch into the impact wrench mode.

Continuing to rotate the operating button 354 to the second stroke range, the other wider portion of the first driving slot 355 cooperates with the sliding pin 372. As shown in FIG. 45, the first clutch member 351 is again in the rotating member 342. The position of the torque transmission is realized with the working shaft 330, thereby switching into the screwdriver mode. To adjust the torque in the screwdriver mode, continue to turn the operation button 354.

Similar to the first type of operation interface, in the second operation interface, the output torque of the motor 320 in the screw mode is set to be different from the output torque in the drill mode. And further, the screwdriver mode is set to have a plurality of torque adjustment gear positions. That is, if the operation button 354 is rotated in the second stroke range, the position where the elastic piece 3542 is in contact with the ring switch 390 can be changed, and the output torque of 320 is further changed a plurality of times, thereby realizing the torque adjustment in the screwdriver mode. Therefore, the operation button 354 can be operatively changed the output torque of the motor 320 at the second stroke and the third stroke.

Similar to the first type of operating interface, the operating button 354 can also be operated to change the output speed of 320 in the impact wrench mode. Moreover, it can also be realized by changing the position at which the elastic piece 3542 is in contact with the ring switch 390.

In the second operation interface, the torque adjustment in the screw mode and the adjustment of each function mode also share a single adjustment component, and the operation interface is simple.

Referring to Figure 46, a schematic illustration of a third operational interface of the power tool 300 is shown. The third operation interface is based on the second operation interface, and the operation button 354 is divided into a first operation member 3543 and a second operation member 3544, wherein the first operation member 3543 is a mode switching button for implementing the impact drill mode. The switching between the drilling mode, the impact wrench mode and the screwdriver mode; the second operating member 3544 is a torque switching button for adjusting the plurality of gear positions in the screw mode.

Referring to FIGS. 47 to 50, the mode switching sequence performed by the operation first operating member 3543 is identical to that of FIGS. 42 to 43. The difference from the second operation interface is that when the torque is adjusted in the screwdriver mode, instead of continuing to rotate the first operating member 3543, the second operating member 3544 is operated instead. Change In other words, the first operating member 3543 is configured to drive the switching 353 to perform switching of the first stroke, the second stroke, the third stroke, and the fourth stroke. The second operating member 3544 is specifically designed to perform torque adjustment in the screwdriver mode.

The advantage of providing two operating members is that the first operating member 3543 needs to be rotated a relatively small distance when it is required to switch from the screwdriver mode to the other mode. For example, the screwdriver mode is switched to the hammer drill mode, and the first operating member 3543 can be rotated less than the second operating interface, since the stroke required by the first operating member 3543 when the torque adjustment in the screwdriver mode is omitted is omitted. Distance, improve efficiency.

51 to 55 are schematic views of a fourth operation interface of the power tool 300. In the fourth operation interface, the switching sequence of each mode is exactly the same as the mode switching mode of the second and third operation interfaces, wherein the difference from the second operation interface is: torque adjustment in the screwdriver mode With automatic electronic torque adjustment, there is no need to take the method of turning the operation button 354. The difference from the third operation interface is that the torque control in the screwdriver mode adopts automatic electronic torque adjustment, and does not need to take the manner of rotating the second operating member 3544.

The principle of automatic electronic torque adjustment is as follows: as the load increases, the current of the motor increases, the speed decreases, and the current threshold is set. When the current reaches a predetermined threshold, the motor is stopped, thereby improving the accuracy of the torque adjustment. .

For example, the first current threshold is set; the controller of the motor controls the motor speed to maintain a predetermined value of the speed; and detects the motor current. When the motor current reaches the first current threshold, the controller controls the motor to stop.

Further, after setting the first current threshold, setting a second current threshold lower than the first current threshold, when the motor current reaches the second current threshold, the controller controls the rotation speed of the motor to remain at the predetermined speed The value is N1. The predetermined value of the rotational speed N1 is lower than the rotational speed of the motor in the normal operating state, so that the motor can react quickly in subsequent control. For the power tool 100, it has an impact wrench mode, a drill mode, and a screwdriver mode, and its operation interface is not limited to that shown in FIG. 2, and correspondingly, other mode switching sequences are also possible.

As shown in FIG. 56, the power tool 100 can also have a second operational interface. The operating member 164 is a knob that is sleeved outside the switching ring 163, and rotates the switching ring 163 by rotation. Torque adjustment is also achieved by rotating the operating member 164, in the same manner as the first type of operating interface of the power tool 300.

As shown in FIG. 57, the power tool 100 can also have a third operational interface. The operating member 164 is a knob that is sleeved outside the switching ring 163, and rotates the switching ring 163 by rotation. The operating member 164 further includes a first operating member 1642 for effecting mode switching, and a second operating member 1644 for achieving torque adjustment in the screwdriver mode. The use of two operating parts reduces the number of turns that can be made when switching back to the impact wrench mode. The mode switching sequence is: impact wrench mode, screwdriver mode, drill mode.

As shown in FIG. 58, the power tool 100 can also have a fourth operation interface, which is the same as the mode switching sequence of the third operation interface, except that the torque adjustment adopts an electronic torque adjustment, and when the load increases, the current of the motor increases. When the predetermined threshold is reached, the motor is stopped.

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 power tool that includes:

case;

Working shaft

a power unit for generating rotational power;

a hydraulic impact unit for intermittently rotating the working shaft, comprising a rotating member sleeved on the working shaft and rotatable by the power device, and an enclosed space is formed between the rotating member and the working shaft, the closed space Hydraulic oil is disposed therein, the oil pressure impact unit further includes a piston member located in the closed space, the working shaft is provided with a guiding groove, and the piston member is radially movable in the guiding groove, and the feature thereof Yes,

The working shaft has a first end located in the enclosed space and a second end for connecting the working head, and the second end extends out of the enclosed space away from the power device; the power tool further includes a clutch member, and The clutch member is switchable between a first position in which the working shaft can be driven to rotate continuously, and a second position in which the clutch member is in the second position The working shaft can be driven to rotate intermittently.
The power tool according to claim 1, wherein the rotating member is fixedly coupled to the power unit, and the clutch member connects the rotating member and the clutch member when the clutch member is in the first position. a working shaft; the clutch member is disengaged from at least one of the working shaft and the rotating member when the clutch member is in the second position.
The power tool according to claim 2, wherein a fitting member is fixed to the working shaft, and the clutch member is fixedly coupled to the adapter member when the clutch member is in the first position.
The power tool according to claim 3, wherein the clutch member is switched between a first position and a second position by axial movement, and the clutch is located in the second position, the clutch The piece is disengaged from the working shaft and coupled to the rotating member.
The power tool according to claim 2, wherein said power unit comprises a motor and a gear mechanism coupled to the output end of the motor, said gear mechanism comprising a carrier, said oil pressure impact unit being disposed adjacent one end of the motor a first sealed end cap, the carrier being fixedly coupled to the first sealed end cap.
The power tool according to claim 5, wherein said carrier and said first seal The end cap is integrally formed.
The electric power tool according to claim 1, wherein said closed space includes a high pressure chamber capable of sealing a portion of hydraulic oil, said high pressure chamber being formed between said working shaft and said piston member.
The power tool according to claim 2, wherein the first end of the working shaft in the closed space is provided with an axial hole, and the guiding groove is symmetrically disposed on both sides of the axial hole and An axial hole communicating, wherein the axial hole is provided with a movable member fixed relative to the rotating member, and when the clutch member is in the second position, the movable member is driven to rotate relative to the working shaft to seal the piston member The oil pressure of the hydraulic oil between the working shaft and the working shaft can vary.
The power tool according to claim 1, wherein said power tool further comprises a control assembly, said control assembly comprising an operating member for triggering a work command and a control circuit for executing a work command, said clutch member being In one position, the operating member can trigger the control assembly to selectively place the power tool in a screwdriver mode or an electric drill mode, and the operating member can trigger the control assembly to place the power tool when the clutch is in the second position Impact wrench mode.
The electric power tool according to claim 9, wherein the operating member is movably disposed relative to the housing, the operating member being capable of being in a first stroke of the corresponding screwdriver mode, a second stroke corresponding to the electric drill mode, and corresponding Move in the third stroke of the impact wrench mode.
The power tool according to claim 10, wherein the housing is respectively provided with at least one gear position corresponding to the first, second, and third strokes, when the operating member moves to the gear position The corresponding position is indicated, and the power tool performs an output corresponding to the gear position indication in the corresponding working mode.
The electric power tool according to claim 1, wherein said closed space includes a high pressure chamber capable of generating a high oil pressure, said high pressure chamber being formed on said rotary member, said working shaft and said piston member between.
The power tool according to claim 12, wherein the inner wall of the rotating member is provided with a plurality of sealing portions, and the surface of the working shaft is provided with a radial portion, and during the rotating of the rotating member, when The high pressure chamber is formed when the radial portion and the piston member simultaneously contact the sealing portion.
The power tool according to claim 1, wherein one end of said clutch member is The power unit is coupled and axially moved to selectively connect the other end to one of the rotating member and the working shaft outside the enclosed space, and in the first position, the other end of the clutch member is outside the enclosed space The working shaft is coupled, and in the second position, the other end of the clutch member is coupled to the rotating member.
A power tool that includes:

case;

a working shaft for driving the working head;

a power unit for generating rotational power;

a hydraulic impact unit for intermittently rotating the working shaft, comprising a rotating member sleeved on the working shaft, an opening space formed between the rotating member and the working shaft, and hydraulic oil in the closed space The oil pressure impact unit further includes a piston member located in the closed space, the working shaft is provided with a guiding groove, and the piston member is radially movable in the guiding groove, characterized in that the rotating member and The output end of the power device is fixedly connected, and the power tool further includes a clutch member, wherein the clutch member is switchable between a first position and a second position, and in the first position, the clutch member is connected The rotating member and the working shaft can be driven to rotate continuously; in the second position, the working shaft can be driven to rotate intermittently.
The power tool according to claim 15, wherein said power unit comprises a motor, and said one end of said oil pressure striking unit adjacent to said motor is provided with a first sealed end cap, said working shaft being adjacent to said first A first end of the sealed end cap is located within the enclosed space.
A power tool characterized by comprising:

case;

a motor for generating power;

a working shaft for driving the working head;

a hydraulic impact unit for intermittently rotating the working shaft, comprising a rotating member sleeved on the working shaft, an enclosed space of hydraulic oil in the rotating member, and a radial movement in the closed space a piston member assembled in a guide groove of the working shaft;

a switching assembly, comprising a clutch member, wherein the clutch member is switchable between a first position and a second position, wherein the clutch member connects the working shaft and the rotating member when the clutch member is in the first position; When the clutch member is in the second position, the clutch member is separated from at least one of the working shaft and the rotating member The working shaft can be driven to generate intermittent rotation, wherein the clutching position of the clutch member is located on a side of the oil pressure impact unit away from the motor.
The electric power tool according to claim 17, wherein said closed space includes a high pressure chamber capable of sealing a portion of hydraulic oil, said high pressure chamber being formed between said working shaft and said piston member.
The electric power tool according to claim 18, wherein one end of the working shaft is for connecting the working head, and the other end of the working shaft is provided with an axial hole, and the axial hole has a built-in following a movable member that rotates together with the rotating member, the guiding groove communicates with the axial hole through a radial hole, and a ball is disposed between the guiding groove and the axial hole, and the rotating piece is internally disposed to be used to force An urging portion of the piston member moving radially toward the movable member;

When the clutch member is in the second position, the thrust portion is not in radial contact with the piston member, the axial hole communicates with the closed space, and hydraulic oil in the closed space can enter the An axial hole; when the abutting portion abuts against the piston member in the radial direction, the axial hole forms a partition space with the closed space, and the piston member moves radially along the guiding groove toward the axial hole The partition space is reduced in volume to form the high pressure chamber;

a process in which the piston member abuts against the abutting portion in a radial direction to abut against the abutting portion, the rotating member impacts the piston member, and the piston member moves in a radial direction while being circumferentially Impacting the working shaft.
The electric power tool according to claim 19, wherein the urging portion has a climbing surface and an abutting surface, and the top of the piston member has a transition surface and a contact surface, and the urging portion climbs during the rotation The slope slides along the transition surface and forces the piston member to move radially until the abutment surface abuts the contact surface in the radial direction.
The electric power tool according to claim 17, wherein said closed space includes a high pressure chamber capable of generating a high oil pressure, said high pressure chamber being formed in said rotary member, said working shaft and said piston member between.
The electric power tool according to claim 21, wherein an inner wall of the rotary member is provided with a plurality of sealing portions, and a surface of the working shaft is provided with a radial portion, and the sealing member rotates during the rotation The portion simultaneously forms a high pressure chamber in contact with the radial portion and the piston member.
The power tool according to claim 17, wherein said clutch member is in the first In a position, the operating member can be operatively controlled to change the output torque of the motor.
The power tool according to claim 17, wherein said operating member is operable to control an output rotational speed of said motor when said clutch member is in the second position.
The power tool according to claim 17, wherein the switching assembly further comprises an operating unit for driving the clutch member, the operating unit for driving the clutch member to switch between the first position and the second position,

The power tool further includes a control assembly including an operating member and a control circuit triggered by the operating member, the operating member being operative to change an output torque of the motor when the clutch is in the first position .
The electric power tool according to claim 17, wherein a gear mechanism is provided between the motor and the rotary member, and the rotary member is driven to rotate by the gear mechanism, and the gear mechanism is a primary reduction gear.