CN102441873B - Swing-type power tool - Google Patents
Swing-type power tool Download PDFInfo
- Publication number
- CN102441873B CN102441873B CN201010511574.7A CN201010511574A CN102441873B CN 102441873 B CN102441873 B CN 102441873B CN 201010511574 A CN201010511574 A CN 201010511574A CN 102441873 B CN102441873 B CN 102441873B
- Authority
- CN
- China
- Prior art keywords
- swing
- output shaft
- type power
- motor
- shift fork
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Landscapes
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
- Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
Abstract
A kind of swing-type power tool, comprise casing, the motor be arranged in casing, by motor-driven motor shaft, output shaft and the eccentric drive mechanism that is arranged between described motor shaft and output shaft.Described motor shaft drives described output shaft to do oscillating traverse motion around himself axis by described eccentric drive mechanism.Wherein, the pendulum angle of described output shaft is greater than 4 °.By increasing the pendulum angle of output shaft, improve the operating efficiency of swing-type power tool, and making the more application function of swing-type power tool easily extensible.
Description
Technical field
The present invention relates to a kind of power tool, specifically a kind of hand-held swing-type power tool.
Background technology
Multi Role Aircraft is the common hand-held swing-type power tool of industry, and to be output shaft do oscillating motion around self axial line for its operation principle.Therefore, after user is provided with different operating head attachment on output shaft, multiple different operating function can be realized.Common operating head attachment comprises straight blade, saw blade, triangle frosted dish, scraper etc., can realize as work requirements such as sawing, cut, grind, scrape.
Traditional swing-type power tool generally includes head capsule, the motor be arranged in head capsule, by motor-driven main shaft and the eccentric stiffener that is arranged on main shaft, the rotational motion of main shaft converted to the reciprocally swinging of driving shaft thus the oscillating motion of driven tool head by eccentric stiffener.
US Patent No. RE36909 discloses a kind of swing-type power tool, comprise head capsule, be arranged on motor in head capsule and by motor-driven main shaft, main shaft has the eccentric part of a rotation and the setting of offset rotation axis, one shift fork is by main shaft drives and manipulation is connected on working cell, the provided at one of shift fork connects on the driving shaft, the other end is formed with the fork shape of a pair branch and is stuck on the eccentric part on main shaft, driving shaft and main shaft rotation generallyperpendicular, eccentric part and shift fork have two contact portions, at least one contact portion has curved surface, main shaft converts the oscillating traverse motion of shift fork around the axis of driving shaft to around the rotation of rotation, thus drive driving shaft reciprocally swinging by shift fork and the work of driven tool head.
In above-mentioned swing-type power tool and at present occurred on the market swing-type power tool, because output shaft is directly connected with motor by transmission mechanism, the operations such as deceleration were not carried out in centre, and thus the hunting frequency of shift fork is larger.Like this, whole instrument is shaken in the course of the work comparatively large, seismaesthesia is comparatively strong, for the long-time use of user causes inconvenience.In order to make the vibrations in work relatively little, and reduce the wearing and tearing of part, in existing swing-type power tool, the pendulum angle of shift fork is less, is all less than 4 °, normally 3.2 °.Therefore, shift fork pendulum angle is less than 4 ° has become one of industry design reference when designing swing-type power tool.
Because pendulum angle is less, swing-type power tool in use operating efficiency is lower, and this is also people's insurmountable problems always.In addition, the little problem also bringing other of pendulum angle, when slotting as used straight blade working head, sawdust is not easily discharged, thus causes saw blade generate heat and wear and tear, and saw blade also can be made to be easy to be stuck.Pendulum angle is little, limits the application function of swing-type power tool simultaneously, is not easy to expansion working head to realize other more application function, as cut grass, boring, hammering etc.
For this reason, be really necessary the swing-type power tool that a kind of improvement is provided, to overcome the deficiency that above-mentioned swing-type power tool exists.
Summary of the invention
For the deficiencies in the prior art, the object of the present invention is to provide a kind of swing-type power tool had compared with high workload efficiency.
The technical solution adopted for the present invention to solve the technical problems is: a kind of swing-type power tool, comprise casing, the motor be arranged in casing, by motor-driven eccentric drive mechanism, and driven by described eccentric drive mechanism and do the output shaft of oscillating traverse motion around himself axis.Wherein, the pendulum angle of described output shaft is greater than 4 °, described eccentric drive mechanism is selectively at least changed between the first mode of operation and the second mode of operation, when described eccentric drive mechanism is positioned at different mode of operations, described output shaft has different pendulum angles, described swing-type power tool also comprises the adjusting device that described eccentric drive mechanism can be driven to change between the first mode of operation and the second mode of operation, described swing-type power tool is provided with the frequency matching device of the hunting frequency of the adjustable described output shaft when the pendulum angle change of described output shaft.
Preferably, the hunting frequency of described output shaft is greater than 10000 times per minute.
Preferably, described eccentric drive mechanism comprises shift fork and is connected to the eccentric part on described motor shaft, one end of described shift fork is connected on described output shaft, the other end of described shift fork matches with described eccentric part, and described eccentric part can coordinate with the diverse location of described shift fork under the drive of described adjusting device.
Preferably, described shift fork has the auxiliary section coordinated with described eccentric part, and described auxiliary section extends along the axis direction of described motor shaft, and described adjusting device drives described eccentric part to slide along the auxiliary section of the relatively described shift fork of axis of described motor shaft.
Preferably, described eccentric drive mechanism comprises shift fork and interval and is connected to the first eccentric part on the motor shaft of described motor and the second eccentric part, described shift fork is provided with first auxiliary section and the second auxiliary section that can coordinate with described first eccentric part and described second eccentric part respectively, described eccentric drive mechanism has the first mode of operation and the second mode of operation, when described eccentric drive mechanism is in the first mode of operation, described first eccentric part matches with the first auxiliary section of described shift fork; When described eccentric drive mechanism is in the second mode of operation, described second eccentric part matches with the second auxiliary section of described shift fork.
Preferably, described frequency matching device comprises shift adjusting circuit and controller, and when the pendulum angle of described output shaft changes, described controller regulates the rotating speed of described motor by described shift adjusting circuit.
Preferably, described adjusting device comprises the push button being arranged on described casing outside and the driving lever be connected with described push button, described driving lever can be driven to drive described eccentric part to move relative to described shift fork by described push button.
Preferably, described motor has at least one preset rotation speed, and described swing-type power tool is provided with the speed stabilizing control system making described motor constant rotation under described preset rotation speed.
Preferably, described speed stabilizing control system comprises: power supply; Controller, it monitors operating voltage and the load current of described motor, and calculates the target voltage of described motor according to the load current of described motor, then specifies the dutycycle of described operating voltage according to the difference of described operating voltage and described target voltage; And power switching unit, it connects described power supply and described motor, and the dutycycle of the described operating voltage that described controller is specified by described power switching unit is applied on described motor, makes the operating voltage of described motor be adjusted to described target voltage.
Preferably, the preset rotation speed of described motor is at more than 10000 turns per minute.
Preferably, when being provided with in described casing for reducing the work of described swing-type power tool produce the elastic component of vibrations.
Preferably, described casing comprises head capsule, and one end of described head capsule is extended with sidewall along the direction of described output shaft, and described elastic component is radially connected between described output shaft and described sidewall.
Preferably, described casing comprises head capsule, is provided with the pressing plate perpendicular to described output shaft in described head capsule, and described output the tip of the axis is provided with flange portion, and be axially set on described output shaft and two ends supports described flange portion and described pressing plate to described elastic component respectively.
Preferably, described eccentric drive mechanism comprises the eccentric part of shift fork and shift fork reciprocally swinging, described shift fork comprises the first end be connected with described output shaft and the second end coordinated with described eccentric part, described second end comprises two outer walls be oppositely arranged, between the outer wall of described shift fork and described casing, the swaying direction of described shift fork is respectively arranged with described elastic component.
Preferably, described output shaft connects support, between described support and described casing, be provided with elastic component.
Preferably, described elastic component is divided into the first elastic component and the second elastic component, described support has the first side wall relative with housing and the second sidewall, described first elastic component and the second elastic component are separately positioned on described the first side wall, between the second sidewall and described housing, described first elastic component and the second elastic component extrude described support in the opposite direction.
Preferably, the pendulum angle minimum of a value of described output shaft is the one in 5 °, 6 °, 7 °, 8 °, 9 ° or 10 °.
Preferably, the pendulum angle of described output shaft is greater than 10 °.
Preferably, described power input to a machine is greater than 500W.
Preferably, described casing is provided with operating grip.
Preferably, described eccentric drive mechanism comprises shift fork and drives described shift fork to rotate the eccentric part of reciprocally swinging, described eccentric part be bearing and the ratio of its external diameter and internal diameter more than 19/7.
The invention has the beneficial effects as follows: swing-type power tool of the present invention, by increasing the pendulum angle of output shaft, improves the operating efficiency of swing-type power tool, and makes the more application function of swing-type power tool easily extensible.
Accompanying drawing explanation
Be described in further detail below in conjunction with accompanying drawing and the preferred embodiments of the present invention.
Fig. 1 be the first embodiment of swing-type power tool in the present invention schematic perspective view.
Fig. 2 is the sectional view of swing-type power tool shown in Fig. 1.
Fig. 3 is the structural representation of eccentric drive mechanism in Fig. 2.
Fig. 4 is the using state reference diagram of swing-type power tool in Fig. 1, and now output shaft and saw blade are along counterclockwise swinging.
Fig. 5 is the using state reference diagram of swing-type power tool in Fig. 1, and now output shaft and saw blade and saw blade are positioned at initial position.
Fig. 6 is the using state reference diagram of swing-type power tool in Fig. 1, and now output shaft and saw blade swing clockwise.
Fig. 7 is the theory diagram of the speed stabilizing control system of swing-type power tool of the present invention.
Fig. 8 is the circuit diagram of speed stabilizing control system shown in Fig. 7.
Fig. 9 is the view that in second embodiment of the invention, eccentric gearing structure is positioned at the first mode of operation.
Figure 10 is positioned at the view of the second mode of operation for the structure of eccentric gearing shown in Fig. 9.
Figure 11 is the subelement perspective exploded view in eccentric drive mechanism shown in Fig. 9.
Figure 12 is the top view of the structure of eccentric gearing shown in Fig. 9.
Figure 13 is the top view of the structure of eccentric gearing shown in Figure 10.
Figure 14 is the view that in third embodiment of the invention, eccentric gearing structure is positioned at the first mode of operation.
Figure 15 is positioned at the view of the second mode of operation for the structure of eccentric gearing shown in Figure 14.
Figure 16 is the subelement perspective exploded view in Figure 14 institute eccentric gearing structure.
Figure 17 is the top view of the structure of eccentric gearing shown in Figure 14.
Figure 18 is the top view of the structure of eccentric gearing shown in Figure 15.
Figure 19 is the structural representation of four embodiment of the invention.
Figure 20 is the structural representation of fifth embodiment of the invention.
Figure 21 is the partial sectional view of sixth embodiment of the invention.
Figure 22 is the partial sectional view of seventh embodiment of the invention.
Figure 23 is the sectional view along B-B direction in Figure 22.
Wherein, related elements reference numeral is as follows:
100. Multi Role Aircraft 1. casing 2. output shafts
3. motor 4. motor shaft 41. eccentric shaft
5. eccentric drive mechanism 6. saw blade 7. shift fork
71. sleeve pipe 72. forked portion 721,722. adjutages
81. outer ring 82. inner rings 91, motor shaft
911, accepting groove 92, output shaft 93, adjusting device
931, push button 932, driving lever 933, the collar
94, auxiliary section, shift fork 941, first auxiliary section 942, second
943, the first madial wall 944, second madial wall 95, first eccentric part
96, the second eccentric part 97, eccentric shaft 971, flange portion
972, first paragraph 973, second segment 974, the 3rd section
10, power supply 101, battery temperature testing circuit 102, battery voltage detection circuit
111, continued flow tube 12, controller 13, power switching unit
131, metal-oxide-semiconductor 132, mosfet driver 14, main switch
15, reduction voltage circuit 16, differential amplifier circuit 17, current sample amplifying circuit
18, shift adjusting circuit 19, angular transducer 20, output shaft
21, motor shaft 22, eccentric drive mechanism 23, shift fork
231, sleeve pipe 232, forked portion 233, adjutage
234, auxiliary section 235, madial wall 24, eccentric part
241, outer ring 242, inner ring 25, adjusting device
251, driving lever 252, push button 253, the collar
26, eccentric shaft 261, flange portion 262, first paragraph
263, second segment 300, Multi Role Aircraft 31, head capsule
311, sidewall 312, receiving space 32, output shaft
33, elastic component 400, Multi Role Aircraft 41, head capsule
42, output shaft 43, elastic component 44, flange portion
45, pressing plate 51, output shaft 52, head capsule
521, the first stator 522, second stator 53, support
531, ring portion 532, supporting seat 533, the first side wall
534, the second sidewall 54, first elastic component 55, second elastic component
Detailed description of the invention
Below in conjunction with Fig. 1 to Fig. 6, first first embodiment of the invention is described.
Refer to Fig. 1 and Fig. 2, a kind of swing-type power tool, especially a kind of swing-type power tool of hand-held, i.e. Multi Role Aircraft 100, comprise casing 1 and extend in casing 1 and the output shaft 2 vertically extended.Wherein, in casing 1, be provided with motor 3, drive the motor shaft 4 rotated and the eccentric drive mechanism 5 be arranged between motor shaft 4 and output shaft 2 by motor.Motor shaft 4 is approximately perpendicular to output shaft 2, by eccentric drive mechanism 5, the rotation of motor shaft 4 is converted to the rotation reciprocally swinging of output shaft 2.The end of output shaft 2 is provided with operating head attachment-saw blade 6, and output shaft 2 can drive saw blade 6 to rotate reciprocally swinging around himself axis X together.
With reference to Fig. 2 and Fig. 3, eccentric drive mechanism 5 comprises shift fork 7 and the eccentric part 8 be connected on the motor shaft (4).One end of shift fork 7 is connected to the top of output shaft 2, and its other end matches with eccentric part 8.Shift fork 7 comprises and is set in sleeve pipe 71 on output shaft 2 and the forked portion 72 of vertically motor shaft 4 horizontal-extending from sleeve pipe 71 top.Eccentric part 8 is ball bearing, and it has outer ring 81 and inner ring 82, and wherein, outer ring 81 has spherical outer surface, and inner ring 82 is set in from motor shaft 4 terminal shaft on the eccentric shaft 41 extended.The axis of eccentric shaft 41 does not overlap with the axis of motor shaft 4, and radial deflection certain between to crouch D.The free end of the forked portion 72 of shift fork 7 is formed with generally u-shaped adjutage 721,722, and these two adjutages 721,722 are coated on the both sides of the outer ring 81 of eccentric part 8 and closely slidingly contact.
When motor 3 drive motors axle 4 rotates, eccentric shaft 41 rotates relative to the eccentric axis of motor shaft 4 under the drive of motor shaft 4, and then drives eccentric part 8 to rotate relative to the eccentric axis of motor shaft 4.When eccentric part 8 is when doing eccentric rotary, drive shift fork 7 being produced the rotation reciprocally swinging in horizontal direction, driving output shaft 2 to do rotation oscillating traverse motion around himself axial line X further.
Please refer to Fig. 4 to Fig. 6 below, introduce the process that output shaft 2 drives saw blade 6 reciprocating rotary to swing in detail.In present embodiment, saw blade 6 level is arranged on output shaft 2, and when static, the longitudinal centre line of saw blade 6 is parallel to the axis of above-mentioned motor shaft 4.Operationally, output shaft 2 can drive saw blade 6 to turn reciprocally swinging in certain anglec of rotation inward turning.As shown in Figure 4, the anglec of rotation that the axis of the relative motor shaft 4 of saw blade 6 is maximum is counterclockwise θ °.After saw blade 6 is rotated counterclockwise maximum angle θ °, start to reply swing clockwise, as shown in Figure 5, saw blade 6 can reply the position of the axis being parallel rotated to its center line and motor shaft 4.As shown in Figure 6, saw blade 6 continues to turn clockwise, until rotate after maximum equally angle θ °, starts to reply swing counterclockwise.Go round and begin again, output shaft 2 drives saw blade 6 to rotate reciprocally swinging, thus realizes the functions such as cutting, saw.From the above, the pendulum angle of output shaft 2 in whole oscillating stroke is 2 θ °, and namely the maximum angle scope of output shaft 2 single amplitude of fluctuation is 2 θ °.
In present embodiment, the pendulum angle of output shaft 2 is 7 °, and namely θ equals 3.5, and the hunting frequency of output shaft 2 is 18000 times per minute.By the pendulum angle of output shaft is set to 7 °, substantially increase the operating efficiency of saw blade 6, and when saw blade is worked, be convenient to the discharge of chip.
Below with reference to the experimental data in following table, further illustrate the raising situation of large pendulum angle lower swing power tool efficiency.Can find out from following table, when the pendulum angle of output shaft is 7 °, when using kahikatea plate or the intermediate density plate of accurate saw blade cutting same size, efficiency all improves more than 70% when comparatively pendulum angle is 4 °; And when using standard saw blade cutting intermediate density plate, efficiency also can improve 50% when comparatively pendulum angle is 4 °; In addition, when using double break saw blade cutting iron nail, efficiency then can improve 48%.
It is to be noted, swing-type power tool of the present invention, the pendulum angle of output shaft 2 is not limited to 7 ° in above-mentioned embodiment, can also be set to any value being greater than 4 °, can be the one in 5 °, 6 °, 8 °, 9 ° or 10 °, also can be greater than 10 °.The hunting frequency of output shaft 2 is also not limited to 18000 times per minute, is preferably greater than minute 10000 times.
The method increasing the pendulum angle of output shaft 2 has a lot, as increased the diameter of the outer ring 81 of eccentric part 8, needs the distance increased between the adjutage 721,722 of shift fork 7 simultaneously.Also can when not changing the size of eccentric part 8, crouch between the axis between increase eccentric shaft 82 and motor shaft 4 D.Crouch between can also reducing between the axis of output shaft 2 and eccentric part 8, certainly now will shorten the horizontal size of the clamp forks 72 of shift fork 7.Above method also can be with the use of, to obtain larger pendulum angle.
In addition, the eccentric part in the present invention is not limited to adopt the ball bearing in above-mentioned embodiment, also can adopt needle bearing.In order to ensure that eccentric part can carry larger load, in the present invention eccentric part adopt the external diameter of bearing and the ratio of internal diameter to be preferably 19/7 or 16/6, also can be greater than 19/7 other value.Eccentric part, by selecting the bearing of above-mentioned size, can bear higher load, and extends the service life of eccentric part.
Compared with prior art, instant invention overcomes the technology prejudice that the pendulum angle of swing-type power tool is set to less than 4 ° by people, by arranging the large pendulum angle being greater than 4 °, adopt the hunting frequency being greater than the minute 10000 times simultaneously, substantially increase the operating efficiency of swing-type power tool, solve the technical problem that people thirst for solving for a long time.
Be appreciated that, the present invention is not limited to the Multi Role Aircraft in above-mentioned embodiment, by arranging larger pendulum angle, the operate accessories head of other kind can be installed, thus the application function of expansion swing-type power tool, as cut grass, boring, hammering etc., thus the present invention is made to achieve unexpected technique effect.
In addition, it may be noted that in above-mentioned embodiment, the power of Multi Role Aircraft 100 is 250W, and the power of swing-type power tool of the present invention also can be other value.Be readily appreciated that, when the size of swing-type power tool is larger, if higher operating efficiency will be obtained, then need motor to have larger power output.Swing-type power tool of the present invention, power input to a machine is greater than 500W, has higher operating efficiency to make this swing-type power tool.Correspondingly, for the ease of operating large-sized swing-type power tool, the operating grip being convenient to grip can be installed on the casing of swing-type power tool.This operating grip can be arranged to annular, also can be rectilinear, can be one-body molded with casing, also can with casing removably split arrange.
In order to improve the operating efficiency of Multi Role Aircraft 100 in present embodiment further, this Multi Role Aircraft 100 has the speed stabilizing control system making the rotating speed of motor 3 keep constant.
Figure 7 shows that the theory diagram of speed stabilizing control system of the present invention, this speed stabilizing control system comprises controller 12 and power switching unit 13.Swing-type power tool comprises the power supply 10 for its power supply further, and motor 3 has some preset rotation speed n*, can rotate according to selection with certain concrete preset rotation speed n*.
Controller 12 monitors operating voltage Uc and the load current Ic at two ends when motor 3 works, and calculates motor 3 according to the load current Ic of motor 3 and will reach target voltage Uo needed for preset rotation speed n*; And then based on operating voltage Uc and target voltage Uo difference adjustment power supply 10 PWM dutycycle, and PWM dutycycle is applied to power switching unit 13 to regulate the operating voltage Uc of motor 3 to target voltage Uo, thus make motor 3 in preset rotation speed n* lower aprons ground constant rotation.
In present embodiment, power switching unit 13 comprises the metal-oxide layer-semiconductor-field-effect transistor MOSFET (referred to as metal-oxide-semiconductor) 131 be connected in series between power supply 10 and motor 3, metal-oxide-semiconductor 131 switches between on off operating mode, to change the pulse width of PWM dutycycle.
Figure 8 shows that the detailed circuit diagram of speed stabilizing control system in the present invention, the detailed operation principle of Multi Role Aircraft 100 control system of the present invention is described in further detail below in conjunction with Fig. 7 and Fig. 8.
This circuit comprises main switch 14, and main switch 14 is for controlling the disconnection of whole circuit and closing.Motor 3 is direct current generator, is specifically as follows direct current permanent magnet motor or DC brushless motor.Power supply 10 is chargeable 10.8 volts of batteries, and power supply 10 is connected with the input port VDD of controller 12 by reduction voltage circuit 15, for controller 12 provides 5 volts of stable power supplys.Motor 3, together with metal-oxide-semiconductor 131, is connected with power supply 10 and main switch 14.
Motor 3 two ends are parallel with differential amplifier circuit 16, to detect the operating voltage U at two ends when motor 3 works
c.The operating voltage U at motor 3 two ends that this differential amplifier circuit 16 will detect
camplify, then pass through input port VDD by operating voltage U
cnumerical value be passed to controller 12.
Current sample amplifying circuit 17 is in series with, for detecting load current I when motor 3 works between motor 3 and controller 12
c.Load current I when the motor 3 detected works by this current sample amplifying circuit 17
camplify, then pass through input port AN6 by load current I
cnumerical value is passed to controller 12.
Power switching unit 13 also comprises the mosfet driver 132 be connected with metal-oxide-semiconductor 131, carrys out the break-make of the PWM duty cycle adjustment metal-oxide-semiconductor of self-controller 12 for basis.The input of this mosfet driver 132 is connected with the output port PWM of controller 12, and its output is connected with the input of metal-oxide-semiconductor.
Introduce the operating voltage U that power switching unit 13 regulates motor 3 two ends below in detail
cprinciple.First, metal-oxide-semiconductor has the PWM dutycycle according to receiving, the effect of conducting rapidly, shutoff.In the present embodiment, controller 12 is with the rate-adaptive pacemaker PWM dutycycle of 2000HZ, and namely PWM duty cycle signals has cycle T=0.5 millisecond.This PWM duty cycle signals amplifies through mosfet driver 132, becomes 12 volts from 5 volts, with the conducting of driven MOS pipe or shutoff.In cycle T, pulse signal has a high level and a low level, and high level and the low level ratio of time duration in cycle T is transformable PWM dutycycle.Wherein, when pulse signal is high level, metal-oxide-semiconductor is in the state of conducting, and now the voltage of power supply 10 can be applied on motor 3 by metal-oxide-semiconductor; When pulse signal is low level, metal-oxide-semiconductor is in the state of closedown, and now the voltage of power supply 10 cannot be applied on motor 3 by metal-oxide-semiconductor, but can by the continued flow tube 111 at motor 3 two ends.Like this, by regulating the PWM dutycycle of metal-oxide-semiconductor, can effectively be applied to the time on motor 3 by the voltage of power supply 10 in regulating cycle T, namely can be transferred to the energy of motor 3 by power supply 10 in regulating cycle T, thus regulating the operating voltage U at motor 3 two ends
c.Because the cycle T duration is short, on operator's appreciable time, motor 3 is driven all the time.
This system also comprises the cell voltage U for detecting power supply 10
bbattery voltage detection circuit 102, be used for protection power source 10, prevent power supply 10 from crossing and put.The cell voltage U of power supply 10 that this battery voltage detection circuit 102 will detect
bcontroller 12 is exported to, as cell voltage U by input port AN3
bduring lower than certain predetermined value, controller 12 can disconnect whole system, cut off the electricity supply 10 power supply.
In order to protection power source 10, native system is provided with battery temperature testing circuit 101 further, to detect the battery temperature T at power supply 10 two ends
b, and by input port AN7, battery temperature is inputed to controller 12.As battery temperature T
bwhen exceeding certain preset value, controller 12 can disconnect whole system equally, cut off the electricity supply 10 power supply.
Swing-type power tool usually needs to arrange different rotating speeds and selects for user, and therefore, this speed stabilizing control system is also provided with shift adjusting circuit 18.Controller 12 controls rotational speed regulation circuit 18 by output port AN4, and the rotating speed of motor 3 can be changed between some different preset rotation speed n*.
The speed stabilizing control system introducing swing-type power tool of the present invention below regulates the detailed process of motor speed.
When main switch 14 is opened, control whole system power on circuitry, controller 12 is preset, the preset initialization of register comprised in controller 12, and timer reset adjustment.In this stage, the signal of controller 12 meeting reading speed setting section input, select setting preset rotation speed n* according to user, motor 3 starts to rotate with preset rotation speed n*.
Meanwhile, the operating voltage U of motor 3 that will detect of differential amplifier circuit 16
cpass to controller 12, the load current I of motor 3 that current sample amplifying circuit 17 then will detect
cbe passed to controller 12 equally.The preset rotation speed n* of controller 12 by the motor 3 and load current I of the motor 3 real-time monitored
c, go out at load current I according to corresponding formulae discovery
ctime, make the actual speed n of motor 3 remain target voltage U required for preset rotation speed n*
o.Controller 12 carrys out the duty-cycle of the PWM duty cycle signals of regulation output according to respective algorithms, thus is controlled the ON time of metal-oxide-semiconductor 131 by mosfet driver 132.When metal-oxide-semiconductor 131 conducting, the two ends of motor 3 just can be subject to the voltage of power supply 10; When not conducting, the two ends of motor 3 are not subject to voltage, like this, by regulating the duty-cycle of PWM duty cycle signals, the time scale being applied to motor 3 effective voltage in the certain hour cycle can be regulated, and then regulate the operating voltage U being applied to motor 3 two ends in macroscopically certain hour
c, and the energy that power supply 10 exports, and then regulate actual speed n.As the operating voltage U of motor 3
chigher than target voltage U
otime, controller 12 regulates the duty-cycle reducing PWM duty cycle signals, and the energy that motor 3 accepts reduces, the operating voltage U at motor 3 two ends
creduce and close to target voltage U
o, thus the actual speed n of motor 3 is minimized, make it close to preset rotation speed n*.Vice versa, as the operating voltage U of motor 3
clower than target voltage U
otime, controller 12 regulates the duty-cycle improving PWM duty cycle signals, and the energy that motor 3 accepts increases, the operating voltage U at motor 3 two ends
cincrease and close to target voltage U
o, thus the actual speed n of motor 3 is raised, make it close to preset rotation speed n*.
Concrete, controller 12 is by operating voltage U current for motor 1
cwith target voltage U
orelatively, draw the deviation △ U of voltage, controller 12 calculates current for reaching target voltage U according to deviation △ U
othe PWM duty cycle signals that should export, PWM duty cycle signals amplifies through mosfet driver 132 and is delivered to metal-oxide-semiconductor 131, to control the energy flowing to motor 3 in power supply 10 special time, makes the operating voltage U that motor 1 is current
creach target voltage U
o.
In the present embodiment, the algorithm that pulse signal duty-cycle that controller 12 calculates its output adopts is proportional-integral-differential algorithm (abbreviation pid algorithm).Pid algorithm is industrial common control algolithm, in pid algorithm, this algorithm can calculate ratio, integration, the response of differential and this three's and, calculate real output with this.
Further, the present embodiment adopts increment type PID algorithm.In adjustment process, the every 50 milliseconds of operating voltage U to motor 3 two ends of processor 12
ccarry out sampling to calculate, and stored, processor 12 is according to present operating voltage U
c1, previous operating voltage U
c2, previous operating voltage U again
c3carry out PID calculating, draw and export PWM duty cycle signals.
Concrete, the duty-cycle of pulse width modulating signal can calculate according to following method and obtain:
The first, differential amplifier circuit 16 measures the operating voltage U of motor 3
c, and output signal is to controller 12.
The second, controller 12 records the present operating voltage U of motor 3
c1, previous operating voltage U
c2, previous operating voltage U again
c3, and calculate their deviation.
Three, according to operating voltage U
cdeviation, adjustment PWM dutycycle (PWM dutycycle) signal.
Four, metal-oxide-semiconductor 131 regulates the operating voltage Uc at motor 3 two ends to reach target voltage Uo according to the PWM duty cycle signals received, thus regulates the actual speed n of motor 3 to approach preset rotation speed n*.
The control system of Multi Role Aircraft 100 of the present invention, by the operating voltage U at direct-detection motor 3 two ends
cand load current I
c, do not need to arrange velocity sensor to detect the rotating speed of motor 3, the motor 3 of Multi Role Aircraft 100 just can be made to keep the preset rotation speed n* of approximately constant, structure is simple, and performance is more stable.
In addition, as shown in Figure 7, the output shaft 2 due to Multi Role Aircraft 100 of the present invention can export different pendulum angle α, and when the pendulum angle α of output shaft 2 is different, corresponding produced vibrations size is also different.Therefore, Multi Role Aircraft 100 is provided with frequency matching device.When the pendulum angle α of output shaft 2 changes, the hunting frequency of this frequency matching device output shaft 2 capable of automatic changing.
Said frequencies coalignment comprises the angular transducer 99 be connected with controller 12 and the shift adjusting circuit 18 introduced and controller 2 above, the pendulum angle α of the output shaft 2 detected is passed to controller 12 by angular transducer 99, when the pendulum angle α of output shaft 2 changes, controller 2 changes the preset rotation speed n* of motor 3 automatically by shift adjusting circuit 18.Be readily appreciated that, owing to not arranging any deceleration device between motor 3 and output shaft 2, therefore change the preset rotation speed n* of motor 3, just the corresponding hunting frequency changing output shaft 2.
Lift body, the output shaft 2 of Multi Role Aircraft 100 has the pendulum angle α 1, α 2, the α 3 that increase successively, and motor 3 then has the preset rotation speed n increased successively
1, n
2, n
3.In present embodiment, pendulum angle α 1, α 2, α 3 and preset rotation speed n
1, n
2, n
3be corresponding in turn to.Namely when the pendulum angle α of output shaft 2 increases, the preset rotation speed n* of corresponding reduction motor 3, to make output shaft 2 when larger pendulum angle α, corresponding hunting frequency is less, thus make the vibrations of output shaft 2 relatively little, make Multi Role Aircraft 100 have good operating handle.
The specific works process of frequency matching device is as follows: the pendulum angle α of angular transducer 99 Real-Time Monitoring output shaft 2 is also passed to controller 12, when controller 12 finds that the pendulum angle α of output shaft becomes α 2 or α 3 from α 1, then regulate the preset rotation speed n* of motor 3 by n by shift adjusting circuit 18
1become n
2or n
3.
The component of present system is not limited to concrete form cited in above-mentioned embodiment, and as people in the industry easily knows, the selection of the concrete form of these elements is various.Such as, controller 12 also can be analog comparator; Also operating voltage Uc and the load current Ic at motor 3 two ends can be detected by other circuit; Power switching unit 13 also can adopt the field-effect transistor of other type except metal-oxide-semiconductor 131; The pendulum angle α of the output shaft 2 and preset rotation speed n* of motor 3 is also not limited to three kinds, also when pendulum angle α increases, can improve preset rotation speed n*, to have higher operating efficiency simultaneously.
Operationally, the load of saw blade 5 is not unalterable to Multi Role Aircraft 100 usually, but constantly change.By arranging speed stabilizing control system, when the load change of saw blade 5, also the rotating speed of motor 3 can not be changed, but make the rotating speed of motor 3 keep relative constancy all the time, thus make the hunting frequency relative constancy of output shaft 2, and then make saw blade 5 have the hunting frequency of relative constancy, thus substantially increase the operating efficiency of Multi Role Aircraft 100.
By arranging frequency matching device, when can make the swing change of the output shaft of swing-type power tool of the present invention, the correspondingly hunting frequency of regulation output axle, the pendulum angle of output shaft and hunting frequency are reasonably mated, thus make swing-type power tool reach the highest operating efficiency and operating handle, to meet the needs of user.
In above-described embodiment, frequency matching device is when the pendulum angle of output shaft changes, and automatically regulates hunting frequency.Be easy to expect, frequency matching device also can adopt manual mode, and namely user manually can regulate and be arranged on button on the casing of swing-type power tool or knob carrys out regulation stall regulating circuit.Concrete scheme is that people in the industry is easy to realize, and does not repeat them here.
Below in conjunction with Fig. 9 to Figure 13, specifically describe the second embodiment of the present invention.
In present embodiment, swing-type power tool of the present invention comprises the motor shaft 91 and the relative vertically disposed output shaft 92 of motor shaft 91 that are driven by motor (not shown) and the eccentric drive mechanism be arranged between motor shaft 91 and output shaft 92.Eccentric drive mechanism shown in Fig. 9 is positioned at the first mode of operation, and eccentric drive mechanism shown in Figure 10 is positioned at the second mode of operation.The eccentric drive mechanism of present embodiment is selectively changed between the first mode of operation and the second mode of operation, and when eccentric drive mechanism is positioned at different mode of operations, output shaft 92 exports different pendulum angles.Swing-type power tool also comprises the adjusting device 93 that eccentric drive mechanism can be driven to change between the first mode of operation and the second mode of operation.
The first eccentric part 95 and the second eccentric part 96 that eccentric drive mechanism comprises shift fork 94 and can coordinate with shift fork 94 respectively.Motor shaft 91 is connected with eccentric shaft 97, the axis of motor shaft 91 and eccentric shaft 97 does not overlap and offsets certain distance.Above-mentioned first eccentric part 95 and the second eccentric part 96 spacer sleeve are located on eccentric shaft 97, and the outside dimension of the first eccentric part 95 is less than the outside dimension of the second eccentric part 96.Shift fork 94 is U-shaped, which is provided with first auxiliary section 941 and second auxiliary section 942 that can coordinate with the first eccentric part 95 and the second eccentric part 96 respectively.First auxiliary section 941 has two the first madial wall 943, second auxiliary sections 942 relatively be arranged in parallel and has two the second madial walls 944 relatively be arranged in parallel, and the spacing between two first madial walls 943 is less than the spacing between two second madial walls 944.
Adjusting device 93 comprises the push button 931 that can manually promote and the driving lever 932 perpendicular to push button 931.Push button 931 is arranged on the outside of casing (not shown), and driving lever 932 one end is connected on push button 931, and the other end has the collar 933 be set on eccentric shaft 97.Push button 931 can coordinate at some different working modes with casing and lock, and when promoting push button 931, push button 931 can drive driving lever 932 to move together.One end of eccentric shaft 97 is axially stretched in motor shaft 91, and can relatively slide axially by motor shaft 91.By operating the push button 931 of adjusting device 93, drive driving lever 932 in the horizontal direction in move back and forth, and then promotion the first eccentric part 95, second eccentric part 96 moves relative to motor shaft 91 axial reciprocating together with eccentric shaft 97, thus eccentric drive mechanism is changed between different mode of operations.
As shown in figure 11, eccentric shaft 97 comprises flange portion 971, lays respectively at first paragraph 972 and the second segment 973 of flange portion 971 both sides, and in drawing, be positioned at the 3rd section 974 on the left of second segment 973.Motor shaft 91 axially offers deltiod accepting groove 911 towards one end of eccentric shaft 97, and the both sides of the first paragraph 972 of eccentric shaft 97 are cut and form deltiod, and are housed in slidably in the accepting groove 911 of motor shaft 3.First eccentric part 95 is arranged on the 3rd section 974 of eccentric shaft 97, and the second eccentric part 96 is arranged on the second segment 973 of eccentric shaft 97, and there is certain intervals between the first eccentric part 95 and the second eccentric part 96.The collar 933 of adjusting device 93 is between the second eccentric part 96 and the flange portion 971 of eccentric shaft 97, and the internal diameter of the collar 933 is much larger than the external diameter of second segment 973, when motor shaft 91 drives eccentric shaft 97 to rotate, the second segment 973 of eccentric shaft 97 can not interfere with the collar 933 of adjusting device 93.
Please refer to Figure 12, eccentric drive mechanism, under the driving of adjusting device 93, is positioned at the first mode of operation.Now, two second madial walls 944 of the both sides of the second eccentric part 96 and the second auxiliary section 942 of shift fork 94 are separated, and two first madial wall 943 close contacts of the first auxiliary section 941 of the both sides of the first eccentric part 95 and shift fork 94.The distance in the axle center of the first eccentric part 95 to output shaft 92 is D1, and output shaft 92 has the first pendulum angle α 1.
Please refer to Figure 13, eccentric drive mechanism under the driving of adjusting device 93, by the first working mode change to the second mode of operation.Now, two first madial walls 943 of the both sides of the first eccentric part 95 and the first auxiliary section 941 of shift fork 94 are separated, and two second madial wall 944 close contacts of the second auxiliary section 942 of the both sides of the second eccentric part 96 and shift fork 94.The distance in the axle center of the second eccentric part 96 to output shaft 92 is D2, and output shaft 92 has the second pendulum angle α 2.
Be appreciated that the outside dimension due to the first eccentric part 95 is less than the outside dimension of the second eccentric part 96, and the first eccentric part 95 is less than the distance D2 of the second eccentric part 96 to the axle center of output shaft 92 to the distance D1 in the axle center of output shaft 92.Pendulum angle due to, output shaft 92 is that the distance in the outside dimension by eccentric part and the axle center to output shaft is determined jointly, therefore, can make the first pendulum angle α 1 and the second pendulum angle α 2 not.Therefore, by operation adjusting device 93, eccentric drive mechanism can be driven to change between the first mode of operation and the second mode of operation, thus make output shaft 92 selectively export the first pendulum angle α 1 or the second pendulum angle α 2.
It is pointed out that the first eccentric part 95, second eccentric part 96 and eccentric shaft 96 relative motor shaft 91 slip setting together in present embodiment, also can otherwise realize.As: eccentric shaft 96 can be fixedly installed by motor shaft 91 relatively, and on eccentric shaft 96 arrange can relative eccentric axle 96 slide sleeve pipe, the first eccentric part 95 and the second eccentric part 96 are arranged on sleeve pipe.By the driving of adjusting device 93, the first eccentric part 95 relative eccentric axle 96 together with the second eccentric part 96 can be made to slide.In addition, eccentric drive mechanism is also not limited to change between two mode of operations, can be realized in the conversion more between multi-operation mode, thus make output shaft have more pendulum angle by the quantity increasing eccentric part.
Below in conjunction with Figure 14 and Figure 18, specifically describe the 3rd embodiment of the present invention, illustrate that the eccentric drive mechanism of swing-type power tool of the present invention can another structure of movement between multiple position.Present embodiment and the second embodiment difference are only eccentric drive mechanism, therefore mainly describe the eccentric drive mechanism 22 in present embodiment below.
With reference to Figure 14, the eccentric drive mechanism 22 of present embodiment comprises shift fork 23 and the eccentric part 24 be connected on motor shaft 21.One end of shift fork 23 is connected to the top of output shaft 20, and its other end matches with eccentric part 24.Shift fork 23 comprise be set in sleeve pipe 231 on output shaft 20 and from sleeve pipe 231 top towards the forked portion 232 of motor shaft 21 horizontal-extending.Eccentric part 24 is ball bearing, and it has outer ring 241 and inner ring 242, and wherein, outer ring 241 has spherical outer surface, and inner ring 242 is set in from motor shaft 21 terminal shaft on the eccentric shaft 211 extended.The axis of eccentric shaft 211 does not overlap with the axis of motor shaft 21, and radial deflection certain between crouch.The forked portion 232 of shift fork 23 is generally u-shaped, and it comprises two adjutages be oppositely arranged 233.These two adjutage 233 ends are respectively equipped with the auxiliary section 234 of the both sides of the outer ring 241 being coated on eccentric part 24, and this auxiliary section 234 has roughly in the madial wall 235 of plane, slidingly contact to the intimate of madial wall 235 and outer ring 241.
In the lump with reference to Figure 14 and Figure 15, present embodiment eccentric drive mechanism 22 is changed by shift fork 23 and being engaged between different mode of operations of eccentric part 24, when different mode of operations, output shaft 20 can be made to export different pendulum angle α.The swing-type power tool of present embodiment also comprises the adjusting device 25 be arranged on eccentric shaft 211, and this adjusting device 25 can drive above-mentioned eccentric drive mechanism 22 to change between different mode of operations.
The madial wall 235 of two auxiliary sections 234 of shift fork 23 parallels, and is extended with a segment distance in the horizontal direction.The push button 252 that adjusting device 25 comprises driving lever 251 and is connected with driving lever 251, wherein, driving lever 251 is positioned at the side of eccentric part 24 and comprises the collar 253 be set on eccentric shaft 26, and push button 252 is connected to the free end of driving lever 251 and substantially vertical with driving lever 251.Push button 252 is located at the outside of said machine casing 1, and can coordinate at some different working modes with casing and lock, and when manually promoting push button 252, push button 252 can drive driving lever 251 to move together.
As shown in figure 16, eccentric shaft 26 comprises flange portion 261 and lays respectively at first paragraph 262 and the second segment 263 of flange portion 261 both sides, and motor shaft 21 axially offers deltiod accepting groove 211 towards one end of eccentric shaft 26.The both sides of the first paragraph 262 of eccentric shaft 26 are cut and form deltiod, and are housed in slidably in the accepting groove 211 of motor shaft 21.Eccentric part 24 is arranged on the second segment 263 of eccentric shaft 26, and the collar 253 of adjusting device 25 is between eccentric part 7 and the flange portion 261 of eccentric shaft 26.The internal diameter of the collar 253 is much larger than the external diameter of second segment 263, and when motor shaft 21 drives eccentric shaft 26 to rotate, the second segment 263 of eccentric shaft 26 can not interfere with the collar 253 of adjusting device 25.
When in drawing, court moves left the push button 252 promoting adjusting device 25, push button 252 drives push rod 251 to move to left together, and pushed the right side of eccentric part 24 by the collar 253 of push rod 251, thus eccentric part 24 is driven to be moved to the left with eccentric shaft 26 together relative motor shaft 21.On the contrary, when in drawing, court moves right the push button 252 promoting adjusting device 25, push button 252 drives push rod 251 to move to right together, and pushed the left side of the flange portion 261 of eccentric shaft 26 by the collar 253 of push rod 251, thus eccentric shaft 26 is driven to move right with eccentric part 24 together relative motor shaft 21.Obviously, the movement of eccentric part 24, the madial wall 235 of the auxiliary section 234 of the relative shift fork 23 of the outer surface of its outer ring 241 is slided, thus shift fork 23 can be coordinated in some different positions from eccentric part 24, make eccentric drive mechanism 22 have some different mode of operations.
As shown in figure 17, eccentric drive mechanism 22 is positioned at the first mode of operation, and now eccentric part 24 coordinates with the right-hand member of the auxiliary section 234 of shift fork 23, and eccentric part 24 is D3 to the horizontal range in the axle center of output shaft 20, and now output shaft 20 has pendulum angle α 3.As shown in figure 18, eccentric drive mechanism 22 is positioned at the second mode of operation, and now eccentric part 24 coordinates with the left end of the auxiliary section 234 of shift fork 23, and eccentric part 24 is D4 to the horizontal range in the axle center of output shaft 20, and now output shaft 20 has pendulum angle α 4.Obviously, when driving eccentric drive mechanism 22 to move to the second mode of operation by the first mode of operation by adjusting device 25, eccentric part 24 is reduced to D4 to the horizontal range in the axle center of output shaft 20 gradually by D3, and correspondingly, the pendulum angle of output shaft 20 then increases to α 4 gradually by α 3.
It is to be noted, the push button 252 of adjusting device 25 can coordinate at some diverse locations with casing and lock, therefore, other mode of operation can be set between the first mode of operation and the second mode of operation, thus eccentric drive mechanism 22 can be changed between multiple mode of operation, can select to make output shaft 20 to export multiple different pendulum angle α.
Above-mentioned three detailed description of the invention have done detailed description to the present invention, and compared with prior art, swing-type power tool of the present invention, by increasing the pendulum angle of output shaft, substantially increases the operating efficiency of swing-type power tool.In addition, in order to reduce the vibrations increasing and bring after pendulum angle, also elastic component can be set in casing, as spring, rubber blanket etc., thus improve the use feel of user.
As shown in figure 19, four embodiment of the invention discloses a kind of Multi Role Aircraft 300, and it comprises head capsule 31 and from the output shaft 32 that head capsule 31 extends, is with first embodiment of the invention difference, elastic component 33 is provided with, specifically spring between head capsule 31 and output shaft 32.One end extension of head capsule 31 is provided with sidewall 311, and sidewall 311 is formed with the receiving space 312 of collecting output shaft 32.Elastic component 33 is radially arranged in receiving space 312, and is connected to output shaft 32 and sidewall 311.By arranging elastic component 33, no matter the vibrations that the swing of output shaft 32 produces, or the vibrations that the uneven annex (not shown) that output shaft 32 is installed causes, all can be absorbed by elastic component 33 and weaken, thus the vibrations be passed on head capsule 31 will reduce greatly, the operational comfort of user effectively can be improved.
As shown in figure 20, for the 5th embodiment of the present invention discloses a kind of Multi Role Aircraft 400, it output shaft 42 comprising head capsule 41 and extend from head capsule 41, similar to the invention described above the 4th embodiment, be provided with elastic component 43 equally between head capsule 41 with output shaft 42, difference is: elastic component 43 is axially set on output shaft 42.Wherein, the free end of output shaft 42 is provided with flange portion 44, head capsule 41 is provided with the pressing plate 45 be set on output shaft 42, and above-mentioned elastic component 43 is set on output shaft 42, and the two ends of elastic component 43 support the flange portion 44 at pressing plate 45 and output shaft 42 respectively.Operationally, this Multi Role Aircraft 400 mainly suppresses the rotary oscillation of output shaft 42 with the flange portion 44 of output shaft 42 and the end-face friction of pressing plate 45 respectively by elastic component 43 two ends, and then reduce the vibrations of output shaft 42, to reach the effect of absorbing vibration, its principle and torsion spring are very similar.
As shown in figure 21, for a partial sectional view of sixth embodiment of the invention, wherein, Multi Role Aircraft 500 comprises head capsule 51, be arranged on motor shaft 52 in head capsule 51 and output shaft 53, and is arranged on the eccentric drive mechanism 54 between motor shaft 52 and output shaft 53.Eccentric drive mechanism 54 comprises the shift fork 56 being arranged on eccentric part on motor shaft 52 55 and being arranged on output shaft 53, and coordinating by eccentric part 55 and shift fork 56 when motor shaft 52 rotates, drive output shaft 53 rotates reciprocally swinging.Be with above-mentioned 4th, the 5th embodiment difference, in present embodiment, two elastic components 57 are set between shift fork 56 and head capsule 51, thus directly reduce the vibrations produced when shift fork 56 swings.
Above-mentioned shift fork 56 comprises the first end 561 coordinated with output shaft 53 and the second end 562 coordinated with eccentric part 55, and wherein, the second end 562 is generally u-shaped, and has the outer wall 563 that two are oppositely arranged on eccentric part 55 both sides.Head capsule 51 is provided with two coordinating blocks 511 relative with the outer wall 563 of shift fork 56 respectively, above-mentioned elastic component 57 is arranged between the outer wall 563 of shift fork 56 and the coordinating block 511 of head capsule 51, and be positioned on the swaying direction of shift fork 56.Be readily appreciated that, by arranging elastic component 57 between shift fork 56 and head capsule 51, effectively can reduce the vibrations and noise that produce when shift fork 56 coordinates with eccentric part 55, Multi Role Aircraft 500 can be made to have better operating handle.
Another shock-damping structure of the swing-type power tool that the seventh embodiment of the invention that is depicted as Figure 22 and Figure 23 discloses, output shaft 51 is arranged in head capsule 52, and shift fork (not shown) is arranged on output shaft 51.Be with the difference of above-mentioned 6th embodiment, output shaft 51 is provided with support 53 in addition, between the madial wall of support 53 and head capsule 52, be respectively arranged with the first elastic component 54 and the second elastic component 55.Support 53 is adjacent with shift fork and be positioned at the below of shift fork, and it comprises the ring portion 531 be set on output shaft 51 and the supporting seat 532 extended towards output shaft 51 side from ring portion 531, and the bearing of trend of supporting seat 532 is identical with shift fork.Supporting seat 531 is provided with relative the first side wall 533 and the second sidewall 534, and on the madial wall of head capsule 52, correspondence is provided with the first stator 521 and the second stator 522.Above-mentioned first elastic component 54 compression is arranged between the first side wall 533 and the first stator 521, and the second elastic component 55 compression is arranged between the second sidewall 534 and the second stator 522.
By arranging the support 53 near shift fork on output shaft 51, and the first elastic component 54 and the second elastic component 55 is set between support 53 and head capsule 52.When swing-type power tool operationally, shift fork drives output shaft 51 when rotating reciprocally swinging, and output shaft 51 can drive support 53 to rotate reciprocally swinging.When output shaft 51 turns clockwise, support 53 compresses the first elastic component 54 by supporting seat 532; When output shaft 51 is rotated counterclockwise, 53, support compresses the second elastic component 55 by supporting seat 532.
By arranging the first elastic component 54 and the second elastic component 55, support 53 is made to be applied to momentum time of head capsule 52 elongated, thus the active force be applied on head capsule 52 reduces, thus make the vibrations of whole swing-type power tool be absorbed and weaken, improve user greatly and in use shake numb hand problem, improve the operational comfort of user.
Elastic component in above-mentioned all embodiments, except employing spring, can also adopt other can realize the flexible member of equivalent effect, as shell fragment, rubber blanket etc.
It may occur to persons skilled in the art that, the present invention can also have other implementation, as long as but its technical spirit adopted is identical with the present invention or close, or any change of making based on the present invention and replacing all within protection scope of the present invention.
Claims (21)
1. a swing-type power tool, comprise casing, be arranged on the motor in casing, by motor-driven eccentric drive mechanism, and to be driven by described eccentric drive mechanism and to do the output shaft of oscillating traverse motion around himself axis, it is characterized in that: the pendulum angle of described output shaft is greater than 4 °, described eccentric drive mechanism is selectively at least changed between the first mode of operation and the second mode of operation, when described eccentric drive mechanism is positioned at different mode of operations, described output shaft has different pendulum angles, described swing-type power tool also comprises the adjusting device that described eccentric drive mechanism can be driven to change between the first mode of operation and the second mode of operation, described swing-type power tool is provided with the frequency matching device of the hunting frequency of the adjustable described output shaft when the pendulum angle change of described output shaft.
2. swing-type power tool as claimed in claim 1, is characterized in that: the hunting frequency of described output shaft is greater than 10000 times per minute.
3. swing-type power tool as claimed in claim 1, it is characterized in that: described eccentric drive mechanism comprises shift fork and is connected to the eccentric part on the motor shaft of described motor, one end of described shift fork is connected on described output shaft, the other end of described shift fork matches with described eccentric part, and described eccentric part can coordinate with the diverse location of described shift fork under the drive of described adjusting device.
4. swing-type power tool as claimed in claim 3, it is characterized in that: described shift fork has the auxiliary section coordinated with described eccentric part, described auxiliary section extends along the axis direction of described motor shaft, and described adjusting device drives described eccentric part to slide along the auxiliary section of the relatively described shift fork of axis of described motor shaft.
5. swing-type power tool as claimed in claim 1, it is characterized in that: described eccentric drive mechanism comprises shift fork and interval and is connected to the first eccentric part on the motor shaft of described motor and the second eccentric part, described shift fork is provided with first auxiliary section and the second auxiliary section that can coordinate with described first eccentric part and described second eccentric part respectively, described eccentric drive mechanism has the first mode of operation and the second mode of operation, when described eccentric drive mechanism is in the first mode of operation, described first eccentric part matches with the first auxiliary section of described shift fork; When described eccentric drive mechanism is in the second mode of operation, described second eccentric part matches with the second auxiliary section of described shift fork.
6. swing-type power tool as claimed in claim 1, it is characterized in that: described frequency matching device comprises shift adjusting circuit and controller, when the pendulum angle of described output shaft changes, described controller regulates the rotating speed of described motor by described shift adjusting circuit.
7. swing-type power tool as claimed in claim 3, it is characterized in that: described adjusting device comprises the push button being arranged on described casing outside and the driving lever be connected with described push button, described driving lever can be driven to drive described eccentric part to move relative to described shift fork by described push button.
8. swing-type power tool as claimed in claim 1, it is characterized in that: described motor has at least one preset rotation speed, described swing-type power tool is provided with the speed stabilizing control system making described motor constant rotation under described preset rotation speed.
9. swing-type power tool as claimed in claim 8, it is characterized in that: described speed stabilizing control system comprises controller and the power switching unit for being connected power supply and described motor, the operating voltage of motor described in described monitoring control devices and load current, and calculate according to the load current of described motor the target voltage reached needed for preset rotation speed, adjust the operating voltage of described motor to described target voltage, make described motor constant rotation under preset rotation speed.
10. swing-type power tool as claimed in claim 9, is characterized in that: the preset rotation speed of described motor is at more than 10000 turns per minute.
11. swing-type power tools as claimed in claim 1, is characterized in that: when being provided with in described casing for reducing the work of described swing-type power tool produce the elastic component of vibrations.
12. swing-type power tools as claimed in claim 11, is characterized in that: described casing comprises head capsule, and one end of described head capsule is extended with sidewall along the direction of described output shaft, and described elastic component is radially connected between described output shaft and described sidewall.
13. swing-type power tools as claimed in claim 11, it is characterized in that: described casing comprises head capsule, the pressing plate perpendicular to described output shaft is provided with in described head capsule, described output the tip of the axis is provided with flange portion, and be axially set on described output shaft and two ends supports described flange portion and described pressing plate to described elastic component respectively.
14. swing-type power tools as claimed in claim 11, it is characterized in that: described eccentric drive mechanism comprises the eccentric part of shift fork and shift fork reciprocally swinging, described shift fork comprises the first end be connected with described output shaft and the second end coordinated with described eccentric part, described second end comprises two outer walls be oppositely arranged, between the outer wall of described shift fork and described casing, the swaying direction of described shift fork is respectively arranged with described elastic component.
15. swing-type power tools as claimed in claim 11, is characterized in that: described output shaft has connected support, are provided with elastic component between described support and described casing.
16. swing-type power tools as claimed in claim 15, it is characterized in that: described elastic component is divided into the first elastic component and the second elastic component, described support has the first side wall relative with housing and the second sidewall, described first elastic component and the second elastic component are separately positioned on described the first side wall, between the second sidewall and described housing, described first elastic component and the second elastic component extrude described support in the opposite direction.
17. swing-type power tools as claimed in claim 1, is characterized in that: the pendulum angle minimum of a value of described output shaft is the one in 5 °, 6 °, 7 °, 8 °, 9 ° or 10 °.
18. swing-type power tools as claimed in claim 1, is characterized in that: the pendulum angle of described output shaft is greater than 10 °.
19. swing-type power tools as claimed in claim 1, is characterized in that: described power input to a machine is greater than 500W.
20. swing-type power tools as claimed in claim 1, is characterized in that: casing is provided with operating grip.
21. swing-type power tools as claimed in claim 1, is characterized in that: described eccentric drive mechanism comprises shift fork and drives described shift fork to rotate the eccentric part of reciprocally swinging, described eccentric part be bearing and the ratio of its external diameter and internal diameter more than 19/7.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010511574.7A CN102441873B (en) | 2010-10-01 | 2010-10-01 | Swing-type power tool |
| PCT/CN2011/080193 WO2012041211A1 (en) | 2010-10-01 | 2011-09-27 | Oscillating power tool |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010511574.7A CN102441873B (en) | 2010-10-01 | 2010-10-01 | Swing-type power tool |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102441873A CN102441873A (en) | 2012-05-09 |
| CN102441873B true CN102441873B (en) | 2015-11-25 |
Family
ID=46005063
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201010511574.7A Active CN102441873B (en) | 2010-10-01 | 2010-10-01 | Swing-type power tool |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102441873B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104889944A (en) * | 2015-06-15 | 2015-09-09 | 覃桂才 | Hand-held electric tool |
Families Citing this family (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103465230B (en) * | 2012-06-06 | 2016-12-14 | 苏州宝时得电动工具有限公司 | Swing-type power tool |
| CN103836110B (en) * | 2012-11-23 | 2016-04-06 | 苏州宝时得电动工具有限公司 | Oscillation damping method and vibration insulating system |
| CN103963014B (en) * | 2013-02-06 | 2016-10-12 | 苏州宝时得电动工具有限公司 | Power tool |
| CN103144087B (en) * | 2013-02-26 | 2015-05-20 | 何腾源 | Rotation/swing switch connector for pneumatic grinder |
| CN104249341A (en) * | 2013-06-27 | 2014-12-31 | 苏州宝时得电动工具有限公司 | Swinging power tool |
| US10576652B2 (en) * | 2013-11-15 | 2020-03-03 | Robert Bosch Gmbh | Articulating oscillating power tool |
| DE102014224591A1 (en) * | 2014-05-07 | 2015-11-12 | Robert Bosch Gmbh | Tool attachment and tool system |
| CN105328647B (en) * | 2014-06-30 | 2017-08-29 | 南京德朔实业有限公司 | Multi-purpose power tool |
| CN107009327B (en) | 2016-01-27 | 2021-03-16 | 苏州宝时得电动工具有限公司 | Swing power tool |
| CN211890703U (en) * | 2017-01-10 | 2020-11-10 | 创科无线普通合伙 | Vibration power tool |
| CN107951529B (en) * | 2017-12-25 | 2021-05-11 | 芜湖锐进医疗设备有限公司 | Medical dissection saw |
| CN109396545A (en) * | 2018-11-30 | 2019-03-01 | 张家港市创基机械设备制造有限公司 | Electric swing saw |
| CN109954941B (en) * | 2018-11-30 | 2023-11-24 | 张家港市创基机械设备制造有限公司 | Mini swing saw |
| EP4025390A4 (en) | 2019-09-04 | 2024-03-20 | Milwaukee Electric Tool Corporation | Oscillating power tool with adjustable angular amplitude of oscillation |
| CN116607780B (en) * | 2023-07-18 | 2023-10-03 | 佛山市云雀振动器有限公司 | Concrete vibrator with adjustable vibration and use method |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0623422A1 (en) * | 1993-05-05 | 1994-11-09 | C. & E. FEIN GmbH & Co. | Electrical tool |
| US5533925A (en) * | 1993-02-05 | 1996-07-09 | Ryobi Limited | Structure of drive section of power tool |
| EP1358964A1 (en) * | 2002-04-30 | 2003-11-05 | C. & E. Fein Gmbh & Co. KG | Oscillations generator |
| CN1623739A (en) * | 2003-12-01 | 2005-06-08 | 罗伯特·博施有限公司 | Hand-held machine tool |
| CN1833834A (en) * | 2005-03-18 | 2006-09-20 | 德昌电机股份有限公司 | Driving circuit for hair dressing device |
| CN201471402U (en) * | 2009-07-03 | 2010-05-19 | 苏州宝时得电动工具有限公司 | Power tool |
| CN201471401U (en) * | 2009-07-06 | 2010-05-19 | 苏州宝时得电动工具有限公司 | Power tool |
| CN201511357U (en) * | 2009-09-15 | 2010-06-23 | 苏州宝时得电动工具有限公司 | Swing power tool |
| CN101837579A (en) * | 2009-03-18 | 2010-09-22 | C.&E.泛音有限公司 | Vibratory tool with damping device |
-
2010
- 2010-10-01 CN CN201010511574.7A patent/CN102441873B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5533925A (en) * | 1993-02-05 | 1996-07-09 | Ryobi Limited | Structure of drive section of power tool |
| EP0623422A1 (en) * | 1993-05-05 | 1994-11-09 | C. & E. FEIN GmbH & Co. | Electrical tool |
| EP1358964A1 (en) * | 2002-04-30 | 2003-11-05 | C. & E. Fein Gmbh & Co. KG | Oscillations generator |
| CN1623739A (en) * | 2003-12-01 | 2005-06-08 | 罗伯特·博施有限公司 | Hand-held machine tool |
| CN1833834A (en) * | 2005-03-18 | 2006-09-20 | 德昌电机股份有限公司 | Driving circuit for hair dressing device |
| CN101837579A (en) * | 2009-03-18 | 2010-09-22 | C.&E.泛音有限公司 | Vibratory tool with damping device |
| CN201471402U (en) * | 2009-07-03 | 2010-05-19 | 苏州宝时得电动工具有限公司 | Power tool |
| CN201471401U (en) * | 2009-07-06 | 2010-05-19 | 苏州宝时得电动工具有限公司 | Power tool |
| CN201511357U (en) * | 2009-09-15 | 2010-06-23 | 苏州宝时得电动工具有限公司 | Swing power tool |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104889944A (en) * | 2015-06-15 | 2015-09-09 | 覃桂才 | Hand-held electric tool |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102441873A (en) | 2012-05-09 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102441873B (en) | Swing-type power tool | |
| CN102441874B (en) | Swing-type power tool | |
| US11000934B2 (en) | Hand power tool having an electronically commutated electric motor | |
| CN106715053B (en) | System comprising at least an electronically commutated electric motor defining structural dimensions and at least one rechargeable battery of a voltage class | |
| CN102441875A (en) | Power tool and speed stabilizing control system thereof | |
| US5637034A (en) | Detail sander | |
| CN105619342B (en) | Electric tool | |
| WO2017173705A1 (en) | Brushless motor-based, controllable, detachable power apparatus | |
| WO2012041211A1 (en) | Oscillating power tool | |
| CN109612773A (en) | A kind of portable soil acquisition device | |
| JP2003145447A (en) | Electrically-driven tool | |
| US7395875B2 (en) | Rechargeable battery-operated hand machine tool | |
| CN205237996U (en) | Multifunctional electric tool | |
| CN208125417U (en) | A kind of portable soil acquisition device | |
| CN107355405A (en) | One kind can reciprocating electric fan on the wall | |
| CN209503701U (en) | Facing attachment is used in a kind of logical box body production | |
| CN201913273U (en) | Variable-speed electric drill | |
| CN220051714U (en) | Electric tool | |
| CN201700176U (en) | Gardening tool with self propelling device | |
| CN208051624U (en) | A kind of motor-driven angle grinder of power construction | |
| CN220197231U (en) | Grinding machine with constant rotating speed | |
| CN208387295U (en) | A kind of mono-lever control device of walking machine | |
| CN221003221U (en) | Fan capable of realizing air circulation | |
| CN220965613U (en) | Weeder for forestry engineering | |
| CN207770914U (en) | A kind of Novel electric drill |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |