CN102441873A - Swinging power tool - Google Patents
Swinging power tool Download PDFInfo
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- CN102441873A CN102441873A CN2010105115747A CN201010511574A CN102441873A CN 102441873 A CN102441873 A CN 102441873A CN 2010105115747 A CN2010105115747 A CN 2010105115747A CN 201010511574 A CN201010511574 A CN 201010511574A CN 102441873 A CN102441873 A CN 102441873A
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Abstract
The invention discloses a swinging power tool, which comprises a shell, a motor, a motor shaft, an output shaft and an eccentric transmission mechanism, wherein the motor is arranged in the shell; the motor shaft is driven by the motor; the eccentric transmission mechanism is arranged between the motor shaft and the output shaft; the motor shaft is used for driving the output shaft to swing around the axis of the output shaft in a reciprocating way through the eccentric transmission mechanism; and the swinging angle of the output shaft is greater than 4 degrees. The swinging angle of the output shaft is increased, so that the working efficiency of the swinging power tool is increased, and more application functions can be extended for the swinging power tool.
Description
Technical field
The present invention relates to a kind of power tool, specifically is a kind of hand-held swing power tool.
Background technology
Multi Role Aircraft is the common hand-held of an industry swing power tool, and its operation principle is that the axial line that output shaft centers on self is done oscillating motion.Therefore, when the user is being equipped with a different working annex on the output shaft after, can realize multiple different operation function.Common working head annex comprises straight blade, saw blade, triangle frosted dish, scraper etc., can realize like work requirements such as sawing, cut, grind, scrape.
Traditional swing power tool generally includes head capsule, be arranged on motor in the head capsule, by motor-driven main shaft and be arranged on the eccentric stiffener on the main shaft, thereby the rotational motion of main shaft is converted to a reciprocally swinging driven tool oscillating motion of driving shaft through eccentric stiffener.
U.S. Pat RE36909 discloses a kind of swing power tool; The motor that comprises head capsule, is arranged in the head capsule reaches by motor-driven main shaft; Main shaft has the eccentric part of a rotation and the setting of offset rotation axis, and a shift fork is connected on the working cell by main shaft drives and manipulation, and an end pivoting of shift fork is connected on the driving shaft; The other end is formed with the fork shape of a pair of branch and is stuck on the eccentric part on the main shaft; Driving shaft is vertical substantially with the main axis rotation axis, and eccentric part and shift fork have two contact portions, and 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, thereby drives driving shaft reciprocally swinging and the work of driven tool head through shift fork.
In above-mentioned swing power tool and the present swing power tool that is occurred on the market, because output shaft directly is connected with motor through transmission mechanism, operations such as deceleration were not carried out in the centre, thereby the hunting frequency of shift fork is bigger.Like this, it is bigger to make that entire tool shakes in the course of the work, and seismaesthesia is stronger, for user's long-time use has caused inconvenience.In order to make the vibrations in the work less relatively, and reduce the wearing and tearing of part, in the existing swing power tool, the pendulum angle of shift fork is less, all less than 4 °, and normally 3.2 °.Therefore, the shift fork pendulum angle has become one of industry design reference when power tool is swung in design less than 4 °.
Because pendulum angle is less, operating efficiency is lower in use for the swing power tool, and this also is the insurmountable always problems of people.In addition, the little problem that also can bring other of pendulum angle, when using straight blade working head fluting, sawdust is difficult for discharging, thereby causes the saw blade heating and wear and tear, and also can make saw blade be easy to be stuck.Pendulum angle is little, has limited the application function of swing power tool simultaneously, is not easy to expand working head realizing other more applications function, as cuts grass, boring, hammering etc.
For this reason, be necessary to provide a kind of improved swing power tool really, to overcome the deficiency that above-mentioned swing power tool exists.
Summary of the invention
To the deficiency of prior art, the object of the present invention is to provide a kind of swing power tool with higher operating efficiency.
The technical solution adopted for the present invention to solve the technical problems is: a kind of swing power tool; Comprise casing, be arranged on motor in the casing, by motor-driven eccentric drive mechanism, and the output shaft that drives and do oscillating traverse motion by said eccentric drive mechanism around himself axis.Wherein, the pendulum angle of said output shaft is greater than 4 °.
Preferably, the hunting frequency of said output shaft is greater than per minute 10000 times.
Preferably; Said eccentric drive mechanism is selectively changed between first mode of operation and second mode of operation at least; When said eccentric drive mechanism is positioned at the different working pattern; Said output shaft has different pendulum angles, and said swing power tool also comprises can drive the adjusting device that said eccentric drive mechanism is changed between first mode of operation and second mode of operation.
Preferably; Said eccentric drive mechanism comprises shift fork and is connected the eccentric part on the said motor shaft; One end of said shift fork is connected on the said output shaft; The other end of said shift fork matches with said eccentric part, and said eccentric part can cooperate with the diverse location of said shift fork under the drive of said adjusting device.
Preferably, said shift fork has the auxiliary section that cooperates with said eccentric part, and extend along the axis direction of said motor shaft said auxiliary section, and said adjusting device drives said eccentric part and slides along the auxiliary section of the said relatively shift fork of axis of said motor shaft.
Preferably; Said eccentric drive mechanism comprises shift fork and is connected at interval first eccentric part and second eccentric part on the motor shaft of said motor; Said shift fork is provided with first auxiliary section and second auxiliary section that can cooperate with said first eccentric part and said second eccentric part respectively; Said eccentric drive mechanism has first mode of operation and second mode of operation, and when said eccentric drive mechanism was in first mode of operation, said first eccentric part matched with first auxiliary section of said shift fork; When said eccentric drive mechanism was in second mode of operation, said second eccentric part matched with second auxiliary section of said shift fork.
Preferably, said swing power tool is provided with the frequency matching device of the hunting frequency of the said output shaft of scalable when the pendulum angle of said output shaft changes.
Preferably, said frequency matching device comprises shift adjusting circuit and controller, and when the pendulum angle of said output shaft changed, said controller was regulated said rotating speed of motor through said shift adjusting circuit.
Preferably, said adjusting device comprises and is arranged on said casing outside push button and the driving lever that is connected with said push button, can drive said driving lever through said push button and drive said eccentric part and move relative to said shift fork.
Preferably, said motor has at least one preset rotation speed, and said swing power tool is provided with the speed stabilizing control system that makes said motor constant rotation under said preset rotation speed.
Preferably, said speed stabilizing control system comprises: power supply; Controller, it monitors the operating voltage and the load current of said motor, and calculates the target voltage of said motor according to the load current of said motor, specifies the dutycycle of said operating voltage then according to the difference of said operating voltage and said target voltage; And the power switch unit, it connects said power supply and said motor, and said power switch unit is applied to the dutycycle of the said operating voltage of said controller appointment on the said motor, makes the operating voltage of said motor be adjusted to said target voltage.
Preferably, the preset rotation speed of said motor is more than per minute 10000 changes.
Preferably, be provided with in the said casing and be used to reduce said swing power tool work time and produce the elastic component that shakes.
Preferably, said casing comprises head capsule, and an end of said head capsule is extended with sidewall along the direction of said output shaft, and said elastic component radially is connected between said output shaft and the said sidewall.
Preferably, said casing comprises head capsule, is provided with the pressing plate perpendicular to said output shaft in the said head capsule, and said output the tip of the axis is provided with flange portion, and said elastic component axially is set on the said output shaft and two ends support said flange portion and said pressing plate respectively.
Preferably; Said eccentric drive mechanism comprises the eccentric part of shift fork and shift fork reciprocally swinging; Said shift fork comprises first end that is connected with said output shaft and second end that cooperates with said eccentric part; Said second end comprises two outer walls that are oppositely arranged, between the outer wall of said shift fork and the said head capsule, on the swaying direction of said shift fork, is respectively arranged with said elastic component.
Preferably, connect support on the said output shaft, be provided with elastic component between said support and the said housing.
Preferably; Said elastic component is divided into first elastic component and second elastic component; Said support has the first side wall relative with housing and second sidewall; Said first elastic component and second elastic component are separately positioned between said the first side wall, second sidewall and the said housing, and said first elastic component and second elastic component push said support in the opposite direction.
Preferably, the pendulum angle minimum of a value of said output shaft is a kind of in 5 °, 6 °, 7 °, 8 °, 9 ° or 10 °.
Preferably, the pendulum angle of said output shaft is greater than 10 °.
Preferably, said power input to a machine is greater than 500W.
Preferably, said casing is provided with operating grip.
Preferably, said eccentric drive mechanism comprises shift fork and the eccentric part that drives said shift fork rotation reciprocally swinging, and said eccentric part is that the ratio of bearing and its external diameter and internal diameter is more than 19/7.
The invention has the beneficial effects as follows: swing power tool of the present invention has improved the operating efficiency of swing power tool through increasing the pendulum angle of output shaft, and makes the swing power tool can expand the more applications function.
Description of drawings
Do further explain below in conjunction with accompanying drawing and the preferred embodiments of the present invention.
Fig. 1 for first embodiment of swing power tool among the present invention schematic perspective view.
Fig. 2 is the cutaway view of swing power tool shown in Figure 1.
Fig. 3 is the structural representation of eccentric drive mechanism among Fig. 2.
Fig. 4 is the user mode reference diagram of swing power tool among Fig. 1, and this moment, output shaft and saw blade were along swing counterclockwise.
Fig. 5 is the user mode reference diagram of swing power tool among Fig. 1, and this moment, output shaft and saw blade and saw blade were positioned at initial position.
Fig. 6 is the user mode reference diagram of swing power tool among Fig. 1, and this moment, output shaft and saw blade were swung along clockwise direction.
Fig. 7 swings the theory diagram of the speed stabilizing control system of power tool for the present invention.
Fig. 8 is the circuit diagram that speed stabilizing shown in Figure 7 is controlled system.
Fig. 9 is positioned at the view of first mode of operation for eccentric gearing structure in the second embodiment of the invention.
Figure 10 is positioned at the view of second mode of operation for eccentric gearing structure shown in Figure 9.
Figure 11 is the subelement perspective exploded view in the eccentric drive mechanism shown in Figure 9.
Figure 12 is the vertical view of eccentric gearing structure shown in Figure 9.
Figure 13 is the vertical view of eccentric gearing structure shown in Figure 10.
Figure 14 is positioned at the view of first mode of operation for eccentric gearing structure in the third embodiment of the invention.
Figure 15 is positioned at the view of second mode of operation for eccentric gearing structure shown in Figure 14.
Figure 16 is the subelement perspective exploded view in Figure 14 institute eccentric gearing structure.
Figure 17 is the vertical view of eccentric gearing structure shown in Figure 14.
Figure 18 is the vertical view of eccentric gearing structure 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 along the cutaway view of B-B direction among Figure 22.
Wherein, the related elements reference numeral is following:
100. Multi Role Aircraft 1. casings 2. output shafts
3. motor 4. motor shafts 41. eccentric shafts
5. eccentric drive mechanism 6. saw blades 7. shift forks
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, shift fork 941, first auxiliary section 942, second auxiliary section
943, first madial wall 944, second madial wall 95, first eccentric part
96, second eccentric part 97, eccentric shaft 971, flange portion
972, first section 973, second sections 974, the 3rd sections
10, power supply 101, battery temperature testing circuit 102, battery voltage detection circuit
111, continued flow tube 12, controller 13, power switch 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 section
263, second section 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, first stator 522, second stator 53, support
531, ring portion 532, supporting seat 533, the first side wall
534, second sidewall 54, first elastic component 55, second elastic component
The specific embodiment
Below in conjunction with Fig. 1 to Fig. 6, at first first embodiment of the invention is described.
See also Fig. 1 and Fig. 2, a kind of swing power tool, especially a kind of swing power tool of hand-held, promptly Multi Role Aircraft 100, the output shaft 2 that comprises casing 1 and in casing 1, extend and vertically extend.Wherein, in casing 1, be provided with motor 3, by motor-driven motor rotating axle 4 and be arranged on motor shaft 4 and output shaft 2 between eccentric drive mechanism 5.Motor shaft 4 is approximately perpendicular to output shaft 2, through eccentric drive mechanism 5, the rotation of motor shaft 4 is converted into the rotation reciprocally swinging of output shaft 2.The end of output shaft 2 is equipped with working head annex-saw blade 6, and output shaft 2 can drive saw blade 6 together around himself axis X rotation reciprocally swinging.
With reference to Fig. 2 and Fig. 3, eccentric drive mechanism 5 comprises shift fork 7 and is connected the eccentric part 8 on the motor shaft 4.One end of shift fork 7 is connected the top of output shaft 2, and its other end matches with eccentric part 8.Shift fork 7 comprises that the sleeve pipe 71 that is set on the output shaft 2 reaches from sleeve pipe 71 tops vertically towards motor shaft 4 horizontally extending forked portion 72.Eccentric part 8 is a 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 shafts on extended eccentric shaft 41.The axis of eccentric shaft 41 does not overlap with the axis of motor shaft 4, and radial deflection certain between the D that crouches.The free end of the forked portion 72 of shift fork 7 is formed with the adjutage 721,722 that roughly is the U type, and these two adjutages 721,722 are coated on the both sides and the closely sliding-contact of the outer ring 81 of eccentric part 8.
When motor 3 drive motors axles 4 rotate, the eccentric axis rotation of 41 relative motor shafts 4 under the drive of motor shaft 4 of eccentric shaft, and then the eccentric axis rotation of drive eccentric part 8 relative motor shafts 4.When eccentric part 8 when doing eccentric rotation, with driving the rotation reciprocally swinging that shift fork 7 produces on the horizontal directions, drive output shaft 2 further and do the rotation oscillating traverse motion around himself axial line X.
Please refer to Fig. 4 to Fig. 6 below, introduce the process that output shaft 2 drives saw blade 6 reciprocal rotary oscillations in detail.In this embodiment, saw blade 6 levels are installed on the 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.When work, it is moving that output shaft 2 meeting drive saw blades 6 transfer physical pendulum in certain anglec of rotation inward turning.As shown in Figure 4, the maximum counterclockwise anglec of rotation of the axis of saw blade 6 relative motor shafts 4 is θ °.Be rotated counterclockwise angle θ ° of maximum when saw blade 6 after, swing is replied in beginning clockwise, and is as shown in Figure 5, and saw blade 6 can be replied the position of the parallel axes that rotates to its center line and motor shaft 4.As shown in Figure 6, saw blade 6 continues to turn clockwise, and after the angle θ that rotates to same maximum °, swing is replied in beginning counterclockwise.Go round and begin again, output shaft 2 drives saw blade 6 rotation reciprocally swingings, thereby realizes functions such as cutting, saw.From the above, the pendulum angle of output shaft 2 in whole oscillating stroke is 2 θ °, and promptly the maximum angle scope of output shaft 2 single amplitudes of fluctuation is 2 θ °.
In this embodiment, the pendulum angle of output shaft 2 is 7 °, and promptly θ equals 3.5, and the hunting frequency of output shaft 2 is per minute 18000 times.Pendulum angle through output shaft is set to 7 °, has improved the operating efficiency of saw blade 6 greatly, and makes saw blade when work, is convenient to the discharge of chip.
With reference to the experimental data in the following table, further specify the raising situation of big pendulum angle lower swing power tool efficient below.Can find out that from following table when the pendulum angle of output shaft was 7 °, when kahikatea plate that uses accurate saw blade cutting same size or intermediate density plate, efficient all improved more than 70% when being 4 ° than pendulum angle; And when the standard of use saw blade cutting intermediate density plate, improve 50% when efficient also can be 4 ° than pendulum angle; In addition, when using double break saw blade cutting iron nail, efficient then can improve 48%.
It is to be noted; The present invention swings power tool, and the pendulum angle of output shaft 2 is not limited to 7 ° in the above-mentioned embodiment, can also be set to any value greater than 4 °; Can be a kind of in 5 °, 6 °, 8 °, 9 ° or 10 °, also can be greater than 10 °.The hunting frequency of output shaft 2 also is not limited to per minute 18000 times, is preferably greater than minute 10000 times.
The method that increases the pendulum angle of output shaft 2 has a lot, and the diameter like the outer ring 81 that can increase eccentric part 8 need increase the adjutage 721 of shift fork 7, the distance between 722 simultaneously.Also can under the situation of the size that does not change eccentric part 8, increase the D that crouches between the axis between eccentric shaft 82 and the motor shaft 4.Can also reduce between axis and the eccentric part 8 of output shaft 2 between crouch, to shorten the horizontal size of the clamp forks 72 of shift fork 7 this moment certainly.Above method also can be used, so that obtain bigger pendulum angle.
In addition, the eccentric part among the present invention is not limited to adopt the ball bearing in the above-mentioned embodiment, also can adopt needle bearing.In order to guarantee that eccentric part can carry bigger load, the external diameter of eccentric part institute employing bearing and the ratio of internal diameter are preferably 19/7 or 16/6 among the present invention, also can be other values greater than 19/7.Eccentric part can bear higher load through selecting the bearing of above-mentioned size for use, and prolongs the service life of eccentric part.
Compared with prior art; The present invention has overcome the pendulum angle that people swing power tool and has been set to the technological prejudice below 4 °; Through the big pendulum angle greater than 4 ° is set; Adopt hunting frequency simultaneously, improved the operating efficiency of swing power tool greatly, solved people and thirsted for the technical problem that solves for a long time greater than the minute 10000 times.
Be appreciated that; The present invention is not limited to the Multi Role Aircraft in the above-mentioned embodiment; Through bigger pendulum angle is set, the annex working head of other kind can be installed, thus the application function of expansion swing power tool; As cut grass, boring, hammering etc., thereby make the present invention obtain unexpected technique effect.
In addition, it may be noted that in the above-mentioned embodiment that the power of Multi Role Aircraft 100 is 250W, the power that the present invention swings power tool also can be other value.Be readily appreciated that, when the size of swinging power tool is big,, then need motor to have bigger power output if obtain higher operating efficiency.Swing power tool of the present invention, power input to a machine are greater than 500W, so that this swing power tool has higher operating efficiency.Correspondingly, for the ease of operating large-sized swing power tool, the operating grip of being convenient to grip can be installed on the casing of swing power tool.This operating grip can be arranged to the annular, also can be rectilinear, can be one-body molded with casing, also can with removably split setting of casing.
In order further to improve the operating efficiency of Multi Role Aircraft 100 in this embodiment, this Multi Role Aircraft 100 has the rotating speed that makes motor 3 and keeps constant speed stabilizing control system.
Shown in Figure 7 is the theory diagram that speed stabilizing of the present invention is controlled system, and this speed stabilizing control system comprises controller 12 and power switch unit 13.The swing power tool further is included as the power supply 10 of its power supply, and motor 3 has the plurality of preset rotation speed n
*, can be according to selecting with certain concrete preset rotation speed n
*Rotate.
The operating voltage Uc and the load current Ic at two ends during 3 work of controller 12 monitoring motors, and calculate motor 3 according to the load current Ic of motor 3 and will reach preset rotation speed n
*Required target voltage Uo; And then based on the PWM dutycycle of the difference of operating voltage Uc and target voltage Uo adjustment power supply 10, and with the PWM dutycycle impose on power switch unit 13 with the operating voltage Uc that regulates motor 3 to target voltage Uo, thereby make motor 3 at preset rotation speed n
*Following constant rotation approx.
In this embodiment; Power switch unit 13 comprises the metal-oxide layer-semiconductor-field-effect transistor MOSFET (abbreviating metal-oxide-semiconductor as) 131 that is connected in series between power supply 10 and the motor 3; Metal-oxide-semiconductor 131 switches between on off operating mode, to change the pulse width of PWM dutycycle.
Detailed circuit diagram for speed stabilizing control system among the present invention shown in Figure 8 describes in further detail the detailed operation principle that Multi Role Aircraft 100 of the present invention is controlled systems below in conjunction with Fig. 7 and Fig. 8.
This circuit comprises main switch 14, and main switch 14 is used to control the disconnection and the closure of entire circuit.Motor 3 is a direct current generator, specifically can be direct current permanent magnet motor or dc brushless motor.Power supply 10 is chargeable 10.8 volts of batteries, and power supply 10 links to each other with the input port VDD of controller 12 through reduction voltage circuit 15, for controller 12 provides 5 volts of stable power supplys.Motor 3 and metal-oxide-semiconductor 131 are connected with power supply 10 and main switch 14 together.
Be in series with current sample amplifying circuit 17 between motor 3 and the controller 12, the load current I when being used to detect motor 3 work
cLoad current I when this current sample amplifying circuit 17 is worked detected motor 3
cAmplify, pass through input port AN6 then load current I
cNumerical value is passed to controller 12.
Introduce power switch unit 13 below in detail and regulate the operating voltage U at motor 3 two ends
cPrinciple.At first, metal-oxide-semiconductor has according to the PWM dutycycle that receives, the effect of conducting rapidly, shutoff.In the present embodiment, controller 12 is with the frequency of 2000HZ output PWM dutycycle, and promptly the PWM duty cycle signals has cycle T=0.5 millisecond.This PWM duty cycle signals amplifies through mosfet driver 132, becomes 12 volts by 5 volts, with conducting of driven MOS pipe or shutoff.In cycle T, pulse signal has a high level and a low level, and the ratio of high level and low level duration length in cycle T is transformable PWM dutycycle.Wherein, when pulse signal was high level, metal-oxide-semiconductor was in the state of conducting, and this moment, the voltage of power supply 10 can be applied on the motor 3 through metal-oxide-semiconductor; When pulse signal was low level, metal-oxide-semiconductor was in closing state, and this moment, the voltage of power supply 10 can't be applied on the motor 3 through metal-oxide-semiconductor, but can be through the continued flow tube 111 at motor 3 two ends.Like this, through regulating the PWM dutycycle of metal-oxide-semiconductor, can regulating cycle T in the voltage of power supply 10 effectively be applied to the time on the motor 3, promptly can regulating cycle T in power supply 10 be transferred to the energy of motor 3, thereby regulate the operating voltage U at motor 3 two ends
cBecause the cycle T duration is short, the operator on the appreciable time motor 3 be driven all the time.
This system also comprises the cell voltage U that is used for detecting power supply 10
bBattery voltage detection circuit 102, be used for protecting power supply 10, prevent that power supply 10 from crossing to put.This battery voltage detection circuit 102 is with the cell voltage U of detected power supply 10
b Export controller 12 to through input port AN3, as cell voltage U
bWhen being lower than certain predetermined value, controller 12 can break off whole systems, 10 the power supply of cutting off the electricity supply.
In order to protect power supply 10, native system further is provided with battery temperature testing circuit 101, to detect the battery temperature T at power supply 10 two ends
b, and battery temperature is inputed to controller 12 through input port AN7.As battery temperature T
bWhen surpassing certain preset value, controller 12 can break off whole system equally, 10 the power supply of cutting off the electricity supply.
The swing power tool need be provided with different rotating speed usually and supply the user to select, and therefore, this speed stabilizing control system also is provided with shift adjusting circuit 18.Controller 12 can be through output port AN4 control rotational speed regulation circuit 18, makes the rotating speed of motor 3 can be in some different preset rotation speed n
*Between the conversion.
Introduce the detailed process that the present invention swings the speed stabilizing control system adjusting motor speed of power tool below.
When main switch 14 is opened, control whole system power on circuitry, controller 12 is preset, and presets the initialization of register that comprises in the controller 12, and the timer adjustment that resets.In this stage, the signal of controller 12 meeting reading speed setting section inputs selects to set a preset rotation speed n according to the user
*, motor 3 beginnings are with preset rotation speed n
*Rotate.
Meanwhile, differential amplifier circuit 16 is with the operating voltage U of detected motor 3
cPass to controller 12, current sample amplifying circuit 17 is then with the load current I of detected motor 3
cBe passed to controller 12 equally.Controller 12 is through the preset rotation speed n of motor 3
*Load current I with the motor that real-time monitors 3
c, calculate at load current I according to corresponding formulas
cThe time, make the actual speed n of motor 3 remain preset rotation speed n
*Needed target voltage U
oThe duty-cycle that controller 12 is regulated the PWM duty cycle signals of output according to respective algorithms, thus the ON time that mosfet driver 132 is controlled metal-oxide-semiconductors 131 passed through.When metal-oxide-semiconductor 131 conductings, the two ends of motor 3 just can receive the voltage of power supply 10; When not conducting; The two ends of motor 3 do not receive voltage, like this, and through regulating the duty-cycle of PWM duty cycle signals; Can regulate certain hour and impose on the time scale of motor 3 effective voltages in the cycle, and then be adjusted in macroscopical operating voltage U that is applied to motor 3 two ends in the certain hour that goes up
c, and the energy of power supply 10 outputs, and then regulate actual speed n.Operating voltage U when motor 3
cBe higher than target voltage U
oThe time, controller 12 is regulated the duty-cycle that reduces the PWM duty cycle signals, and the energy that motor 3 is accepted reduces the operating voltage U at motor 3 two ends
cReduce and approach target voltage U
oThereby, the actual speed n of motor 3 is minimized, make it to approach preset rotation speed n
*Vice versa, as the operating voltage U of motor 3
cBe lower than target voltage U
oThe time, controller 12 is regulated the duty-cycle that improves the PWM duty cycle signals, and the energy that motor 3 is accepted increases the operating voltage U at motor 3 two ends
cIncrease and approach target voltage U
oThereby, make the actual speed n of motor 3 be able to raise, make it to approach preset rotation speed n
*
The operating voltage U concrete, that controller 12 is current with motor 1
cWith target voltage U
oRelatively, draw the deviation delta U of voltage, controller 12 calculates current for reaching target voltage U according to deviation delta U
oThe PWM duty cycle signals that should export, the PWM duty cycle signals amplifies and is delivered to metal-oxide-semiconductor 131 through mosfet driver 132, to flow to the energy of motor 3 in control power supply 10 special times, makes the current operating voltage U of motor 1
cReach target voltage U
o
In the present embodiment, to calculate the algorithm that the pulse signal duty-cycle of its outputs adopted be proportional-integral-differential algorithm (abbreviation pid algorithm) for controller 12.Pid algorithm is that common control algolithm is gone up in industry, in pid algorithm, this algorithm can calculate ratio, integration, differential response and this three's and, calculate real output with this.
Further, present embodiment adopts increment type PID algorithm.In adjustment process, processor 12 per 50 milliseconds of operating voltage U to motor 3 two ends
cThe calculating of taking a sample, and with its storage, processor 12 is according to the work at present voltage U
C1, operating voltage U last time
C2, operating voltage U last time again
C3Carry out PID and calculate, draw output PWM duty cycle signals.
Concrete, the duty-cycle of pulse width modulating signal can be calculated according to following method and obtain:
The first, differential amplifier circuit 16 is measured the operating voltage U of motor 3
c, and the output signal is to controller 12.
The second, the work at present voltage U of controller 12 record motors 3
C1, operating voltage U last time
C2, operating voltage U last time again
C3, and calculate their deviation.
Three, according to operating voltage U
cDeviation, adjustment PWM dutycycle (PWM dutycycle) signal.
Four, metal-oxide-semiconductor 131 reaches target voltage Uo according to the operating voltage Uc at PWM duty cycle signals adjusting motor 3 two ends that receive, thereby the actual speed n of regulating motor 3 approaches preset rotation speed n
*
The control system of Multi Role Aircraft 100 of the present invention is through the operating voltage U at direct detection motor 3 two ends
cAnd load current I
c, the rotating speed that velocity sensor detects motor 3 need be set, just can make the preset rotation speed n of the motor 3 maintenance approximately constants of Multi Role Aircraft 100
*, simple in structure, performance is more stable.
In addition, as shown in Figure 7, because the output shaft 2 of Multi Role Aircraft 100 of the present invention can be exported different pendulum angle α, and the pendulum angle α of output shaft 2 is not simultaneously, and the corresponding vibrations size that produces 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.
The said frequencies coalignment comprises the shift adjusting circuit 18 and the controller 2 of the angular transducer that is connected with controller 12 99 and preceding text introduction; Angular transducer 99 is passed to controller 12 with the pendulum angle α of detected output shaft 2; When the pendulum angle α of output shaft 2 changed, controller 2 changed the preset rotation speed n of motor 3 automatically through shift adjusting circuit 18
*Be readily appreciated that,, therefore change the preset rotation speed n of motor 3 owing between motor 3 and the output shaft 2 any deceleration device is not set
*, with regard to the corresponding hunting frequency that changes output shaft 2.
Lift body, the output shaft 2 of Multi Role Aircraft 100 has pendulum angle α 1, α 2, the α 3 that increases successively, and motor 3 then has the preset rotation speed n that increases successively
1, n
2, n
3In this embodiment, pendulum angle α 1, α 2, α 3 and preset rotation speed n
1, n
2, n
3Corresponding successively.Promptly when the pendulum angle α of output shaft 2 increases, the preset rotation speed n of corresponding reduction motor 3
*, so that output shaft 2 is when bigger pendulum angle α, corresponding hunting frequency is less, thereby makes the vibrations of output shaft 2 less relatively, makes Multi Role Aircraft 100 have operating handle preferably.
The concrete course of work of frequency matching device is following: angular transducer 99 is monitored the pendulum angle α of output shaft 2 in real time and is passed to controller 12; When controller 12 finds that the pendulum angle α of output shaft becomes α 2 or α 3 by α 1, then regulate the preset rotation speed n of motor 3 through shift adjusting circuit 18
*By n
1Become n
2Or n
3
The component of system of the present invention is not limited to concrete form cited in the above-mentioned embodiment, knows easily that like the people in the industry selection of the concrete form of these elements is various.For example, controller 12 also can be analog comparator; Also can detect the operating voltage Uc and the load current Ic at motor 3 two ends through other circuit; Power switch unit 13 also can adopt the field-effect transistor of other type except that metal-oxide-semiconductor 131; The pendulum angle α of output shaft 2 and the preset rotation speed n of motor 3
*Also be not limited to three kinds, also can when pendulum angle α increases, improve preset rotation speed n simultaneously
*, to have higher operating efficiency.
Through frequency matching device is set; When the swing that can make the present invention swing the output shaft of power tool changes; Correspondingly regulate the hunting frequency of output shaft; The pendulum angle and the hunting frequency of output shaft are reasonably mated, thereby make the swing power tool reach the highest operating efficiency and operating handle, to satisfy user's needs.
In the foregoing description, frequency matching device is when the pendulum angle of output shaft changes, and regulates hunting frequency automatically.Be easy to expect that frequency matching device also can adopt manual mode, promptly the user can come the regulation stall regulating circuit through button or the knob that manual adjustments is arranged on the casing of swinging power tool.Concrete scheme is that the people in the industry is easy to realize, repeats no more at this.
Below in conjunction with Fig. 9 to Figure 13, specifically describe second embodiment of the present invention.
In this embodiment, the present invention swing power tool comprise the motor shaft 91 that drives by motor (not shown) and relatively motor shaft 91 vertically disposed output shafts 92 and be arranged on motor shaft 91 and output shaft 92 between eccentric drive mechanism.Eccentric drive mechanism shown in Fig. 9 is positioned at first mode of operation, and eccentric drive mechanism shown in Figure 10 is positioned at second mode of operation.The eccentric drive mechanism of this embodiment is selectively changed between first mode of operation and second mode of operation, when eccentric drive mechanism is positioned at the different working pattern, and the different pendulum angle of output shaft 92 outputs.The swing power tool also comprises can drive the adjusting device 93 that eccentric drive mechanism is changed between first mode of operation and second mode of operation.
Eccentric drive mechanism comprises shift fork 94 and first eccentric part 95 and second eccentric part 96 that can cooperate with shift fork 94 respectively.Be connected with eccentric shaft 97 on the motor shaft 91, the axis of motor shaft 91 and eccentric shaft 97 certain distance that do not overlap and squint.Above-mentioned first eccentric part 95 and second eccentric part, 96 spacer sleeves are located on the eccentric shaft 97, and the outside dimension of first eccentric part 95 is less than the outside dimension of second eccentric part 96.Shift fork 94 is the U type, which is provided with first auxiliary section 941 and second auxiliary section 942 that can cooperate with first eccentric part 95 and second eccentric part 96 respectively.First auxiliary section 941 has first madial wall, 943, the second auxiliary sections 942 that two opposing parallel are provided with and has spacing between second madial wall, 944, two first madial walls 943 that two opposing parallel are provided with less than the spacing between two second madial walls 944.
Adjusting device 93 comprises the push button 931 that can manually promote and perpendicular to the driving lever 932 of push button 931.Push button 931 is arranged on the outside of casing (not shown), and driving lever 932 1 ends are connected on the push button 931, and the other end has the collar 933 that is set on the eccentric shaft 97.Push button 931 and casing can cooperate and lock at some different working modes, and when promoting push button 931, push button 931 can drive driving levers 932 and move together.One end of eccentric shaft 97 axially stretches in the motor shaft 91, and motor shaft 91 endwisely slips relatively.Push button 931 through adjusted device 93; Driving driving lever 932 moves back and forth in the horizontal direction; And then promote first eccentric part 95, second eccentric part 96 and eccentric shaft 97 together relatively motor shaft 91 axially move back and forth, thereby eccentric drive mechanism is changed between the different working pattern.
Shown in figure 11, eccentric shaft 97 comprises flange portion 971, lays respectively at first section 972 and second sections 973 of flange portion 971 both sides, and in drawing, is positioned at the 3rd section 974 of second section 973 left side.Motor shaft 91 axially offers deltiod accepting groove 911 towards an end of eccentric shaft 97, and first section 972 both sides of eccentric shaft 97 are formed deltiod by excision, and are housed in slidably in the accepting groove 911 of motor shaft 3.First eccentric part 95 is installed on the 3rd section 974 of eccentric shaft 97, and second eccentric part 96 is installed on second section 973 of eccentric shaft 97, and has certain intervals between first eccentric part 95 and second eccentric part 96.The collar 933 of adjusting device 93 is between the flange portion 971 of second eccentric part 96 and eccentric shaft 97; And the internal diameter of the collar 933 is much larger than second section 973 external diameter; When motor shaft 91 drives eccentric shaft 97 rotations, second section 973 collar 933 that can not interfere with adjusting device 93 of eccentric shaft 97.
Please refer to Figure 12, eccentric drive mechanism is positioned at first mode of operation under the driving of adjusting device 93.At this moment, two second madial walls 944 of second auxiliary section 942 of the both sides of second eccentric part 96 and shift fork 94 are separated, and the both sides of first eccentric part 95 closely contact with two first madial walls 943 of first auxiliary section 941 of shift fork 94.The distance in the axle center of first eccentric part 95 to the output shaft 92 is D1, and output shaft 92 has the first pendulum angle α 1.
Please refer to Figure 13, eccentric drive mechanism is under the driving of adjusting device 93, by first working mode change to the second mode of operation.At this moment, two first madial walls 943 of first auxiliary section 941 of the both sides of first eccentric part 95 and shift fork 94 are separated out, and the both sides of second eccentric part 96 closely contact with two second madial walls 944 of second auxiliary section 942 of shift fork 94.The distance in the axle center of second eccentric part 96 to the output shaft 92 is D2, and output shaft 92 has the second pendulum angle α 2.
Be appreciated that since the outside dimension of first eccentric part 95 less than the outside dimension of second eccentric part 96, and first eccentric part 95 to the distance B 1 in the axle center of output shaft 92 less than the distance B 2 of second eccentric part 96 to the axle center of output shaft 92.Because the pendulum angle of output shaft 92 is by the outside dimension of eccentric part and common definite to the distance in the axle center of output shaft, therefore, the first pendulum angle α 1 and the second pendulum angle α 2 is not waited.Therefore,, can drive eccentric drive mechanism and between first mode of operation and second mode of operation, change, thereby make output shaft 92 selectively export the first pendulum angle α 1 or the second pendulum angle α 2 through adjusted device 93.
It is pointed out that in this embodiment first eccentric part 95, second eccentric part 96 and eccentric shaft 96 together relatively motor shaft 91 slide and be provided with, also can otherwise realize.As: eccentric shaft 96 motor shaft 91 relatively fixedly installs, and the sleeve pipe of eccentric shaft 96 slips relatively is set on eccentric shaft 96, and first eccentric part 95 and second eccentric part 96 are installed on the sleeve pipe.Through the driving of adjusting device 93, can make eccentric shaft 96 slips relatively together of first eccentric part 95 and second eccentric part 96.In addition, eccentric drive mechanism also is not limited between two mode of operations, change, and can be implemented in the more conversion between the multi-operation mode through the quantity that increases eccentric part, thereby make output shaft have more pendulum angle.
Below in conjunction with Figure 14 and Figure 18, specifically describe the 3rd embodiment of the present invention, explain that the present invention swings another structure that the eccentric drive mechanism of power tool can move between a plurality of positions.This embodiment only is eccentric drive mechanism with the second embodiment difference, the therefore following main eccentric drive mechanism of describing in this embodiment 22.
With reference to Figure 14, the eccentric drive mechanism 22 of this embodiment comprises shift fork 23 and is connected the eccentric part 24 on the motor shaft 21.One end of shift fork 23 is connected the top of output shaft 20, and its other end matches with eccentric part 24.Shift fork 23 comprises that the sleeve pipe 231 that is set on the output shaft 20 reaches from sleeve pipe 231 tops towards motor shaft 21 horizontally extending forked portion 232.Eccentric part 24 is a 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 shafts on extended eccentric shaft 211.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 roughly is the U type, and it comprises two adjutages that are 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 that is coated on eccentric part 24, and this auxiliary section 234 has the madial wall 235 that roughly is the plane, the intimate ground sliding-contact of madial wall 235 and outer ring 241.
With reference to Figure 14 and Figure 15, this embodiment eccentric drive mechanism 22 can be changed through being engaged between the different working pattern of shift fork 23 and eccentric part 24 in the lump, when the different working pattern, can make the different pendulum angle α of output shaft 20 outputs.The swing power tool of this embodiment also comprises the adjusting device 25 that is arranged on the eccentric shaft 211, and this adjusting device 25 can drive above-mentioned eccentric drive mechanism 22 and between the different working pattern, change.
The madial wall 235 of two auxiliary sections 234 of shift fork 23 parallels, and along continuous straight runs is extended with a segment distance.Adjusting device 25 comprises driving lever 251 and the push button 252 that is connected with driving lever 251, and wherein, driving lever 251 is positioned at a side of eccentric part 24 and comprises the collar 253 that is set on the eccentric shaft 26, push button 252 be connected in driving lever 251 free end and with driving lever 251 approximate vertical.Push button 252 is located at the outside of said machine casing 1, and can cooperate and lock at some different working modes with casing, and when manually promoting push button 252, push button 252 can drive driving levers 251 and move together.
Shown in figure 16, eccentric shaft 26 comprises flange portion 261 and lays respectively at first section 262 and second sections 263 of flange portion 261 both sides that motor shaft 21 axially offers deltiod accepting groove 211 towards an end of eccentric shaft 26.First section 262 both sides of eccentric shaft 26 are formed deltiod by excision, and are housed in slidably in the accepting groove 211 of motor shaft 21.Eccentric part 24 is installed on second section 263 of eccentric shaft 26, and the collar 253 of adjusting device 25 is between the flange portion 261 of eccentric part 7 and eccentric shaft 26.The internal diameter of the collar 253 is much larger than second section 263 external diameter, when motor shaft 21 drives eccentric shafts 26 and rotates, and second section 263 collar 253 that can not interfere with adjusting device 25 of eccentric shaft 26.
When the push button 252 that promotes adjusting device 25 in drawing when moving left; Push button 252 drives push rod 251 and moves to left together; And the right side of the 253 pushing eccentric parts 24 of the collar through push rod 251, thereby drive eccentric part 24 and eccentric shaft 26 together relatively motor shaft 21 be moved to the left.On the contrary; When the push button 252 that promotes adjusting device 25 in drawing when moving right; Push button 252 drives push rod 251 and moves to right together; And the left side of the flange portion 261 of the 253 pushing eccentric shafts 26 of the collar through push rod 251, thereby drive eccentric shaft 26 and eccentric part 24 together relatively motor shaft 21 move right.Obviously; Moving of eccentric part 24; The madial wall 235 of auxiliary section 234 of the relative shift fork 23 of outer surface of its outer ring 241 is slided, thereby make shift fork 23 can make eccentric drive mechanism 22 have some different working patterns in the cooperation of some different positions with eccentric part 24.
Shown in figure 17, eccentric drive mechanism 22 is positioned at first mode of operation, and this moment, eccentric part 24 cooperated 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 this moment, output shaft 20 had pendulum angle α 3.Shown in figure 18, eccentric drive mechanism 22 is positioned at second mode of operation, and this moment, eccentric part 24 cooperated 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 this moment, output shaft 20 had pendulum angle α 4.Obviously; When moving to second mode of operation by first mode of operation through adjusting device 25 driving eccentric drive mechanisms 22; Eccentric part 24 is reduced to D4 to the horizontal range in the axle center of output shaft 20 by D3 gradually, and correspondingly, the pendulum angle of output shaft 20 then increases to α 4 by α 3 gradually.
It is to be noted; The push button 252 of adjusting device 25 and casing can cooperate and lock at some diverse locations; Therefore; Output shaft 20 can between first mode of operation and second mode of operation, other mode of operation be set, thereby eccentric drive mechanism 22 can be changed between a plurality of mode of operations, so that can select to export a plurality of different pendulum angle α.
Above-mentioned three specific embodiment have been done detailed description to the present invention, and compared with prior art, swing power tool of the present invention has improved the operating efficiency of swing power tool greatly through increasing the pendulum angle of output shaft.In addition, increase the vibrations that brought behind the pendulum angle, also elastic component can be set in casing,, thereby improve user's use feel like spring, rubber blanket etc. in order to reduce.
Shown in figure 19; Four embodiment of the invention has disclosed a kind of Multi Role Aircraft 300, and it comprises head capsule 31 and from head capsule 31 extended output shafts 32, is with the first embodiment of the invention difference; Being provided with elastic component 33 between head capsule 31 and the output shaft 32, specifically is spring.The one end extension of head capsule 31 is provided with sidewall 311, and sidewall 311 is formed with the receiving space 312 of accommodating output shaft 32.Elastic component 33 radially is arranged in the receiving space 312, and is connected to output shaft 32 and sidewall 311.Through elastic component 33 is set; No matter be the vibrations of the swing generation of output shaft 32; Or the vibrations that the uneven annex (not shown) that output shaft 32 is installed causes; All can and weaken, thereby the vibrations that are passed on the head capsule 31 will reduce greatly, can effectively improve user's operational comfort through elastic component 33 absorptions.
Shown in figure 20; For the 5th embodiment of the present invention has disclosed a kind of Multi Role Aircraft 400; It comprises that head capsule 41 reaches from head capsule 41 extended output shafts 42; Similar with the invention described above the 4th embodiment, be provided with elastic component 43 equally between head capsule 41 and the output shaft 42, difference is: elastic component 43 is axially to be set on the output shaft 42.Wherein, the free end of output shaft 42 is provided with flange portion 44, and the pressing plate 45 that is set on the output shaft 42 is installed on the head capsule 41, and above-mentioned elastic component 43 is set on the 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.When work; This Multi Role Aircraft 400 mainly is the rotary oscillation that suppresses output shaft 42 by elastic component 43 two ends respectively with the end-face friction of flange portion of output shaft 42 44 and pressing plate 45; And then reduce the vibrations of output shaft 42, to reach the effect of absorbing vibration, its principle and torsion spring are very similar.
Shown in figure 21; A partial sectional view for sixth embodiment of the invention; Wherein, Multi Role Aircraft 500 comprises head capsule 51, is arranged on motor shaft 52 and output shaft 53 in the head capsule 51, and is arranged on the eccentric drive mechanism 54 between motor shaft 52 and the output shaft 53.Eccentric drive mechanism 54 comprises the eccentric part that is installed on the motor shaft 52 55 and is installed in the shift fork 56 on the output shaft 53, through the cooperating of eccentric part 55 and shift fork 56, drives output shaft 53 and rotates reciprocally swingings when motor shaft 52 rotates.Be with above-mentioned the 4th, the 5th embodiment difference, in this embodiment, two elastic components 57 be set between shift fork 56 and the head capsule 51, thereby directly reduce the vibrations that produced when shift fork 56 is swung.
Above-mentioned shift fork 56 comprises first end 561 that cooperates with output shaft 53 and second end 562 that cooperates with eccentric part 55, and wherein, second end 562 roughly is the U type, and has two outer walls 563 that are oppositely arranged on eccentric part 55 both sides.Head capsule 51 is provided with two relative with the outer wall of shift fork 56 563 respectively coordinating blocks 511, and above-mentioned elastic component 57 is arranged between the coordinating block 511 of outer wall 563 and head capsule 51 of shift fork 56, and is positioned on the swaying direction of shift fork 56.Be readily appreciated that,, can effectively reduce the vibrations and the noise that are produced when shift fork 56 cooperates with eccentric part 55, can make Multi Role Aircraft 500 have better operating handle through between shift fork 56 and head capsule 51, elastic component 57 being set.
Figure 22 and shown in Figure 23 is other a kind of shock-damping structure of the swing power tool that seventh embodiment of the invention disclosed, and output shaft 51 is arranged in the head capsule 52, and shift fork (not shown) is installed on the output shaft 51.Be with the difference of above-mentioned the 6th embodiment, be provided with support 53 on the output shaft 51 in addition, be respectively arranged with first elastic component 54 and second elastic component 55 between the madial wall of support 53 and head capsule 52.Support 53 is adjacent with shift fork and be positioned at the below of shift fork, and it comprises ring portion 531 that is set on the output shaft 51 and the supporting seat 532 that extends towards output shaft 51 1 sides from ring portion 531, and the bearing of trend of supporting seat 532 is identical with shift fork.Supporting seat 531 is provided with the relative the first side wall 533 and second sidewall 534, and correspondence is provided with first stator 521 and second stator 522 on the madial wall of head capsule 52.54 compressions of above-mentioned first elastic component are arranged between the first side wall 533 and first stator 521, and 55 compressions of second elastic component are arranged between second sidewall 534 and second stator 522.
Through the support 53 near shift fork is set, and first elastic component 54 and second elastic component 55 are set between support 53 and head capsule 52 on output shaft 51.When swinging power tool in work, when shift fork drove output shaft 51 rotation reciprocally swingings, output shaft 51 can drive support 53 rotation reciprocally swingings.When output shaft 51 turned clockwise, support 53 was through supporting seat 532 compressions first elastic component 54; When output shaft 51 was rotated counterclockwise, 53 on support passed through supporting seat 532 compressions second elastic component 55.
Through first elastic component 54 and second elastic component 55 are set; It is elongated to make support 53 be applied to momentum time of head capsule 52; Thereby the active force that affacts on the head capsule 52 reduces; Thereby the vibrations that make whole swing power tool are absorbed and weaken, and have improved the user greatly and have in use shaken numb hand problem, have improved user's operational comfort.
Elastic component in above-mentioned all embodiments can also adopt other flexible member that can realize equivalent effect, like shell fragment, rubber blanket etc. except that adopting spring.
What it may occur to persons skilled in the art that is, the present invention can also have other implementation, but as long as its technical spirit that adopts is identical with the present invention or close, perhaps any variation of making based on the present invention and replacing all within protection scope of the present invention.
Claims (23)
1. swing power tool for one kind; Comprise casing, be arranged on motor in the casing, by motor-driven eccentric drive mechanism; And drive and do the output shaft of oscillating traverse motion around himself axis by said eccentric drive mechanism, it is characterized in that: the pendulum angle of said output shaft is greater than 4 °.
2. swing power tool as claimed in claim 1 is characterized in that: the hunting frequency of said output shaft is greater than per minute 10000 times.
3. swing power tool as claimed in claim 1; It is characterized in that: said eccentric drive mechanism is selectively changed between first mode of operation and second mode of operation at least; When said eccentric drive mechanism is positioned at the different working pattern; Said output shaft has different pendulum angles, and said swing power tool also comprises can drive the adjusting device that said eccentric drive mechanism is changed between first mode of operation and second mode of operation.
4. swing power tool as claimed in claim 3; It is characterized in that: said eccentric drive mechanism comprises shift fork and is connected the eccentric part on the said motor shaft; One end of said shift fork is connected on the said output shaft; The other end of said shift fork matches with said eccentric part, and said eccentric part can cooperate with the diverse location of said shift fork under the drive of said adjusting device.
5. swing power tool as claimed in claim 4; It is characterized in that: said shift fork has the auxiliary section that cooperates with said eccentric part; Extend along the axis direction of said motor shaft said auxiliary section, and said adjusting device drives said eccentric part and slides along the auxiliary section of the said relatively shift fork of axis of said motor shaft.
6. swing power tool as claimed in claim 3; It is characterized in that: said eccentric drive mechanism comprises shift fork and is connected at interval first eccentric part and second eccentric part on the motor shaft of said motor; Said shift fork is provided with first auxiliary section and second auxiliary section that can cooperate with said first eccentric part and said second eccentric part respectively; Said eccentric drive mechanism has first mode of operation and second mode of operation; When said eccentric drive mechanism was in first mode of operation, said first eccentric part matched with first auxiliary section of said shift fork; When said eccentric drive mechanism was in second mode of operation, said second eccentric part matched with second auxiliary section of said shift fork.
7. swing power tool as claimed in claim 3 is characterized in that: said swing power tool is provided with the frequency matching device of the hunting frequency of the said output shaft of scalable when the pendulum angle of said output shaft changes.
8. swing power tool as claimed in claim 7; It is characterized in that: said frequency matching device comprises shift adjusting circuit and controller; When the pendulum angle of said output shaft changed, said controller was regulated said rotating speed of motor through said shift adjusting circuit.
9. swing power tool as claimed in claim 3; It is characterized in that: said adjusting device comprises and is arranged on said casing outside push button and the driving lever that is connected with said push button, can drive said driving lever through said push button and drive said eccentric part and move relative to said shift fork.
10. swing power tool as claimed in claim 1 is characterized in that: said motor has at least one preset rotation speed, and said swing power tool is provided with the speed stabilizing control system that makes said motor constant rotation under said preset rotation speed.
11. swing power tool as claimed in claim 10; It is characterized in that: said speed stabilizing control system comprises controller and the power switch unit that is used to be connected said power supply and said motor; The operating voltage and the load current of the said motor of said monitoring control devices; And calculate according to the load current of said motor and to reach the required target voltage of preset rotation speed, adjust operating voltage to the said target voltage of said motor, make said motor constant rotation under preset rotation speed.
12. swing power tool as claimed in claim 11 is characterized in that: the preset rotation speed of said motor is more than per minute 10000 changes.
13. swing power tool as claimed in claim 1 is characterized in that: be provided with in the said casing and be used to reduce said swing power tool work time and produce the elastic component that shakes.
14. swing power tool as claimed in claim 13 is characterized in that: said casing comprises head capsule, an end of said head capsule is extended with sidewall along the direction of said output shaft, and said elastic component radially is connected between said output shaft and the said sidewall.
15. swing power tool as claimed in claim 13; It is characterized in that: said casing comprises head capsule; Be provided with pressing plate in the said head capsule perpendicular to said output shaft; Said output the tip of the axis is provided with flange portion, and said elastic component axially is set on the said output shaft and two ends support said flange portion and said pressing plate respectively.
16. swing power tool as claimed in claim 13; It is characterized in that: said eccentric drive mechanism comprises the eccentric part of shift fork and shift fork reciprocally swinging; Said shift fork comprises first end that is connected with said output shaft and second end that cooperates with said eccentric part; Said second end comprises two outer walls that are oppositely arranged, between the outer wall of said shift fork and the said head capsule, on the swaying direction of said shift fork, is respectively arranged with said elastic component.
17. swing power tool as claimed in claim 13 is characterized in that: connected support on the said output shaft, be provided with elastic component between said support and the said housing.
18. swing power tool as claimed in claim 17; It is characterized in that: said elastic component is divided into first elastic component and second elastic component; Said support has the first side wall relative with housing and second sidewall; Said first elastic component and second elastic component are separately positioned between said the first side wall, second sidewall and the said housing, and said first elastic component and second elastic component push said support in the opposite direction.
19. swing power tool as claimed in claim 1 is characterized in that: the pendulum angle minimum of a value of said output shaft is a kind of in 5 °, 6 °, 7 °, 8 °, 9 ° or 10 °.
20. swing power tool as claimed in claim 1 is characterized in that: the pendulum angle of said output shaft is greater than 10 °.
21. swing power tool as claimed in claim 1 is characterized in that: said power input to a machine is greater than 500W.
22. swing power tool as claimed in claim 19, it is characterized in that: casing is provided with operating grip.
23. swing power tool as claimed in claim 1 is characterized in that: said eccentric drive mechanism comprises shift fork and the eccentric part that drives said shift fork rotation reciprocally swinging, and said eccentric part is that the ratio of bearing and its external diameter and internal diameter is 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 |
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| Publication Number | Publication Date |
|---|---|
| CN102441873A true CN102441873A (en) | 2012-05-09 |
| CN102441873B CN102441873B (en) | 2015-11-25 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201010511574.7A Active CN102441873B (en) | 2010-10-01 | 2010-10-01 | Swing-type power tool |
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| CN103144087A (en) * | 2013-02-26 | 2013-06-12 | 何腾源 | Rotation/swing switch connector for pneumatic grinder |
| CN103465230A (en) * | 2012-06-06 | 2013-12-25 | 苏州宝时得电动工具有限公司 | Swinging power tool |
| CN103836110A (en) * | 2012-11-23 | 2014-06-04 | 苏州宝时得电动工具有限公司 | Vibration reduction method and vibration reduction system |
| CN103963022A (en) * | 2013-02-06 | 2014-08-06 | 苏州宝时得电动工具有限公司 | Power tool |
| CN104249341A (en) * | 2013-06-27 | 2014-12-31 | 苏州宝时得电动工具有限公司 | Swinging power tool |
| CN105082082A (en) * | 2014-05-07 | 2015-11-25 | 罗伯特·博世有限公司 | Tool attachment and tool system |
| CN105328647A (en) * | 2014-06-30 | 2016-02-17 | 南京德朔实业有限公司 | Multipurpose power tool |
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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 (24)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103465230A (en) * | 2012-06-06 | 2013-12-25 | 苏州宝时得电动工具有限公司 | Swinging power tool |
| 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 |
| CN103836110A (en) * | 2012-11-23 | 2014-06-04 | 苏州宝时得电动工具有限公司 | Vibration reduction method and vibration reduction system |
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| CN103963022A (en) * | 2013-02-06 | 2014-08-06 | 苏州宝时得电动工具有限公司 | Power tool |
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| CN105082082A (en) * | 2014-05-07 | 2015-11-25 | 罗伯特·博世有限公司 | Tool attachment and tool system |
| CN105082082B (en) * | 2014-05-07 | 2020-01-17 | 罗伯特·博世有限公司 | Tool attachment and tool system |
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| US10808818B2 (en) | 2016-01-27 | 2020-10-20 | Positec Power Tools (Suzhou) Co., Ltd. | Oscillating power tool |
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| 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 |
| CN116607780A (en) * | 2023-07-18 | 2023-08-18 | 佛山市云雀振动器有限公司 | Concrete vibrator with adjustable vibration and use method |
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