CN103753469B - Percussion tool - Google Patents
Percussion tool Download PDFInfo
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- CN103753469B CN103753469B CN201310724372.4A CN201310724372A CN103753469B CN 103753469 B CN103753469 B CN 103753469B CN 201310724372 A CN201310724372 A CN 201310724372A CN 103753469 B CN103753469 B CN 103753469B
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- gear
- percussion tool
- output shaft
- torsion
- moment
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
- B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
- B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
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- Mechanical Engineering (AREA)
- Drilling And Boring (AREA)
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- Portable Power Tools In General (AREA)
Abstract
The invention provides a kind of percussion tool, this percussion tool is designed to be connected with matrix with given condition and provides the power tool of the rotary motion with periodically variable angular speed and/or moment of torsion.In addition, gear (1,2,3,4) has the radius r of pitch circle respectively
1(Θ), r
2(Θ), r
3(Θ) and r
4(Θ), Θ represents the angle position of the planet axis (7) be connected with gear (3) by gear (2), when the radius of gear (1,2,3,4) is in the angular range of at least 0≤Θ≤2 π, by meet r
1(Θ) r
3(Θ)/r
2(Θ) r
4(Θ) mode of the inequality of > 1 forms driving row, thus during at least certain part driving circulation, the direction of rotation of output shaft is reversed.By this structure, the percussion tool solving the problem in the past that high noisy, high vibration, high loss and height wear away can be provided.
Description
The divisional application that the application is application number is 201080016096.0, the applying date is on October 10th, 2011, denomination of invention is the application of " percussion tool ".
Technical field
The present invention relates to power tool, in particular to the percussion tool of the modified form of applying impulsive torque.
Background technology
The common power tool securing members such as nut, bolt, screw being applied to moment of torsion uses Continuous Drive or the interrupted mechanism driven.Compared with Continuous Drive, the percussion tool rotated by intermittently driving the output providing interrupted can apply higher peak torque to securing member, meanwhile, appropriateness can reduce the moment of torsion (reaction) brought user.In addition, this percussion tool has the compact advantage of tool size, and, realize the interrupted structure driven and be usually screwed in the purposes such as screw the effect played and maintain drive part (drill bit) and the engaging between driven portion (head of screw) to timber.This is because drive part (drill bit) engages again with driven portion (head of screw) in during the non-driven of drive part (drill bit).
As realizing the interrupted mechanism driven, usually use the rotating mechanism (with reference to Figure 16) be made up of hammer body 10 and anvil 11.Hammer body 10 is connected with power shaft via cam mechanism, and till rotating under the effect of motor and colliding with the anvil 11 that the securing member of itself and fastening object is connected.When being subject to impacting, output shaft rotates ormal weight according to the transmission of moment of momentum.When hammer body 10 slows down because colliding to anvil 11, under the effect of cam mechanism, hammer body 10 is separated from anvil 11, and thus, hammer body 10 can again accelerate and repeat crash-active.
It should be noted that, as disclose the percussion tool in the past that possesses above-mentioned hammer body 10 grade at first technical literature, such as have following patent document 1 etc.
At first technical literature
Patent document
Patent document 1: Japanese Unexamined Patent Publication 2000-42936 publication
Patent document 2: United States Patent (USP) No. 3424021 description
Brief summary of the invention
The problem that invention will solve
But the problem of the percussion tool of the mechanism that above-mentioned use intermittently drives is that described instrument is usually with high noisy, high vibration, high loss and the high problem worn away.
Summary of the invention
The existence that the present invention puts in view of the above problems completes, its object is to, by using the problem possessed described in the gear-box engagement type all the time of noncircular gear and alignment processing, wherein, described gear-box can carry out the output rotary motion of the change comprising stroboscopic motion and rotating campaign relative to constant input rotary motion.
For the means of dealing with problems
Below, the present invention is described.It should be noted that, for the ease of understanding the present invention, having drawn together by the reference marks of bracket by accompanying drawing, but therefore do not make the present invention be confined to illustrated form.
Percussion tool of the present invention is designed to be connected with matrix with given condition and to provide the rotary motion with periodically variable angular speed and/or moment of torsion, it is characterized in that, comprise: power shaft, its provide input angular velocity and/or moment of torsion during rotating a circle in constant in fact rotary motion; Output shaft, its Output speed as the angle of described power shaft function and change; Gear-box, it possesses as the above gear (1,2,3,4) of two couple of the driving row rotary motion of described power shaft transmitted to described output shaft, described two comprise the first gear mesh (1,2) be associated with described power shaft and the second gear mesh (3,4) be associated with described output shaft to above gear (1,2,3,4), and described gear (1,2,3,4) has the radius r of pitch circle respectively
1(Θ), r
2(Θ), r
3(Θ) and r
4(Θ), described Θ represents the angle position of planet axis (7) connecting gear (2) and gear (3), by with the radius of described gear (1,2,3,4) at least in the angular range of 0≤Θ≤2 π time meet following inequality and r
1(Θ) r
3(Θ)/r
2(Θ) r
4(Θ) mode of > 1 forms described driving row, thus during at least certain part driving circulation, the direction of rotation of described output shaft is reversed.
In percussion tool of the present invention, when using ζ as attenuation ratio, using wn as comprise percussion tool and percussion tool and matrix be connected to the rotation eigentone of interior system time, export cycling cycling vibration frequency larger than the computation cycles vibration frequency defined by sqrt (2 × (1-2 ζ)) wn.It should be noted that, " sqrt " in above formula represents square root (squareroot) (same below).
In addition, percussion tool of the present invention is designed to be connected with matrix with given condition and to provide the rotary motion with periodically variable angular speed and/or moment of torsion, it is characterized in that, comprise: power shaft, its provide described angular speed and/or moment of torsion during rotating a circle in constant in fact rotary motion, output shaft, angular speed described in it as the angle of described power shaft function and change, gear-box, it possesses as the above gear (1 of two couple of the driving row rotary motion of described power shaft transmitted to described output shaft, 2, 3, 4), described two to above gear (1, 2, 3, 4) the first gear mesh (1 be associated with described power shaft is comprised, 2) the second gear mesh (3 and with described output shaft be associated, 4), when using ζ as attenuation ratio, using wn as comprise percussion tool and percussion tool and matrix be connected to the rotation eigentone of interior system time, export cycling cycling vibration frequency larger than the computation cycles vibration frequency defined by sqrt (2 × (1-2 ζ)) wn.
In percussion tool of the present invention, the connection of described percussion tool and described matrix is provided by user, and described output cycling cycling vibration frequency is the vibration frequency being greater than 14Hz.
In addition, in percussion tool of the present invention, this percussion tool is used for trip bolt, the forward rotating movements (rotary motion to the fastening direction of screw) of described output shaft causes being separated of tool component and described screw, and return motion afterwards causes again engaging of described tool component and described screw.
And in percussion tool of the present invention, when described percussion tool is configured to use, cycling cycling vibration frequency is greater than in fact the eigentone of entire system.
Furthermore, in percussion tool of the present invention, can in order to reducing effect be in the moment of torsion of matrix (such as, the user held), the ratio of the time that the time that output shaft described in free setting rotates stops with described output shaft.
In addition, in percussion tool of the present invention, the mechanism of perception output torque indirectly can also be possessed, this mechanism be used for perception input side moment of torsion and use accordingly known gear ratio and about the angle position of system information and calculate the moment of torsion of outlet side.
In addition, in percussion tool of the present invention, this percussion tool is used for trip bolt, in order to avoid described tool component in during the driving be spaced during non-driven makes the anglec of rotation of described output shaft enough little from described screw separation.
In addition, in percussion tool of the present invention, this percussion tool is used for trip bolt, and the reverse angle of described output shaft is configured to described tool component in during driving makes described tool component again engage with described screw after being separated a little with described screw.
Furthermore, in percussion tool of the present invention, rotary body (186) included by described gear-box can possess counterweight portion (186a), and this counterweight portion (186a) is for obtaining the balance with the planet axis (7 (174)) being connected gear (2 (173)) and gear (3 (172)).
Invention effect
According to the present invention, can provide and solve high noisy, high vibration, high loss and the high percussion tool wearing away this problem in the past.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of the structure of noncircular gear case for illustration of present embodiment.
Fig. 2 is the curve map of gear ratio representing function as the angle Θ of input and change.
Fig. 3 is the figure exemplifying the form being configured with the noncircular gear of present embodiment with planetary gear box structure.
Fig. 4 is the figure representing the end face that common head of screw and screw-driven are bored.
Fig. 5 is the block diagram of the structure of the percussion tool exemplifying present embodiment.
Fig. 6 is the curve map of the relation between the eigentone of the entire system representing present embodiment and cycling cycling vibration frequency.
Fig. 7 is the figure representing the present invention's other embodiments adoptable.
Fig. 8 is the figure representing the adoptable other embodiment of the present invention.
Fig. 9 represents the figure realizing the right example of non-circular planetary gear of the present invention/non-circular central gear.
Figure 10 is the integrally-built vertical section right hand view of the percussion tool representing the present embodiment.
Figure 11 is the major part exploded perspective expanded view of the important part structure of percussion tool for illustration of the present embodiment.
Figure 12 is that (a) represented in non-circular planetary figure, the figure of the present embodiment represents side, rear, and (b) in figure represents section.
Figure 13 is the figure of the non-circular central gear of the band output shaft representing the present embodiment, and (a) in figure represents side, rear, and (b) in figure represents section.
Figure 14 is the figure for illustration of noise measuring method.
Figure 15 is the figure representing adoptable other embodiments another of the present invention.
Figure 16 exemplifies as the mechanism realizing intermittently driving and the figure of rotating mechanism that is normally used, that be made up of hammer body and anvil.
Detailed description of the invention
Below, accompanying drawing is utilized to illustrate for implementing suitable embodiment of the present invention.It should be noted that, the invention of following embodiment to each technical scheme is not construed as limiting, in addition, all combinations of the feature illustrated in embodiments differ establish a capital be invention necessary for technical solution problem.
Fig. 5 is the block diagram of the structure of the percussion tool illustrating present embodiment.In order to reach average torque characteristic and the average speed characteristic of expectation, the percussion tool of present embodiment such as possesses the motor (electromagnetism, air pressure or use the motor of other power) 14 be combined with gear-box 25 in the past by motor reel 16.
The power shaft 26 being arranged on gear-box 25 provides driving force to the noncircular gear case 18 comprising noncircular gear, then noncircular gear case 18 driver output axle 17.The input angular velocity of this noncircular gear case 18 can be expressed as the function of the angle of power shaft 26 with the ratio of Output speed.Output shaft 17 usually connects into can be separated with the tool component 22 such as mechanical type fastener such as nut or screw as the object transmitting impulsive torque.
Fig. 1 is the schematic diagram of the structure of noncircular gear case 18 for illustration of present embodiment.As shown in Figure 1, noncircular gear case 18 comprises input gear 23 and output gear 24, and described gear 23,24 has the radius changed along their complete cycles respectively.At this, define gear ratio as follows.
ω
2＝Rω
1
In above formula, ω
1be the input angular velocity that the power shaft 26 in the gear-box 25 by being arranged in the past provides, R is gear ratio, ω
2it is the Output speed of output shaft 17.In 2 gear drive row as shown in Figure 1, according to involutory two gears 23,24 in the radius ratio of the contact point in this moment, gear ratio can be drawn as follows.
R＝r
1/r
2
In above formula, r
1the joint radius of a circle of input gear 23, r
2it is the joint radius of a circle of output gear 24.Made a pair noncircular gear of radius change by the function possessed as angle Θ, the function as the angle Θ of input can be reached and the gear ratio (with reference to Fig. 2) that changes, therefore, by R, r
1and r
2entirety replaces with R (Θ), r
1(Θ) and r
2(Θ).
In structure described herein, the input of constant speed provides the output speed changed relative to angle and these both sides of time of power shaft 26.In addition, when with T
1as input torque, with T
2during as output torque, pass through T
2=T
1/ R (Θ) provide moment of torsion, thus the moment of torsion of change can be provided to export according to the gear ratio of this change.
Low in order to ensure the moment of torsion that the torque ratio transmitted to matrix 21 applies by exporting, export cycling cycling vibration frequency setting for larger than sqrt (2 × (1-2 ζ)) wn (being called " computation cycles vibration frequency range (CalculatedCycleFrequencyRange) ").In above formula, ζ is attenuation ratio, and wn is the rotation eigentone being connected to interior system comprising percussion tool and percussion tool and matrix 21.For the user of the percussion tool of present embodiment, this computation cycles vibration frequency range can be expressed as the vibration frequency larger than 14Hz.
The further improvement point of present embodiment is that above-mentioned noncircular gear 23,24 configures with planetary gear box structure.As shown in Figure 3, a pair circular gear 1,2 can combine with a pair noncircular gear 3,4.It should be noted that, as variation, also can be contrary with the structure shown in Fig. 3, a pair gear shown in symbol 1,2 is noncircular gear, and a pair gear shown in symbol 3,4 is circular gear.And, all gears also can be made to be noncircular gear.
Power shaft 5 and actuating arm 6 rigidity link, and consequently, when power shaft 5 rotates, actuating arm 6 rotates identical amount.Thus, planet axis 7 is turn-taked with the axle of constant radius around power shaft 5.When planet axis 7 is driven by actuating arm 6, its axle around self rotates freely.Linked with planet axis 7 rigidity by driving planetary gear 2.The angle of this planet axis 7 is called as Θ.When being moved around static central gear 1 by driving planetary gear 2, rotated relative to its axle thus by driving planetary gear 2, thus drive planet axis 7 to rotate.The driving planetary gear 3 that this rotary actuation and planet axis 7 rigidity link.Next, drive planetary gear 3 that output central gear 4 is rotated, driver output axle 27 rotates thus.
Gear arrangement shown in Fig. 3 is known by conventional art patent document 2 as escribed above.
The gear ratio of this system is as described below.
R(Θ)＝1-r
1(Θ)·r
3(Θ)/r
2(Θ)·r
4(Θ)
In above formula, Θ is the angle of planet axis 7.If gear 1,2,3 and 4 is circular, then r
1(Θ)=r
1=constant, r
2(Θ)=r
2=constant, r
3(Θ)=r
3=constant, r
4(Θ)=r
4=constant, therefore, gear ratio R (Θ)=R=is constant.But under a pair gear shape becomes non-circular situation as described above, R (Θ) changes usually used as the function of Θ.In addition, during scope sometime, r
1(Θ)=r
4(Θ) and r
2(Θ)=r
3(Θ) when, R (Θ)=0, exports and stops, and on the other hand, input continues to rotate.Interrupted driving can be obtained thus.
Inertia with power shaft 5 is middle during non-driven to accelerate, and slows down in during driving.Therefore, the moment of torsion of output shaft 27 is counteractive combinations of the driving torque that such as provided by motor and the deceleration relative to inertia.Therefore, this structure can apply the moment of torsion higher than the Direct driver of motor.
It should be noted that, the internal gear form had on static central gear 1 and/or the same system exporting the internal gear form on central gear 4 can also be realized.
And, the interdependent form r of pitch circle radius
n(Θ) (n=1,2,3,4) brings impact to the rate of change of output speed.In order to avoid the sharply change of speed, the interdependent form of pitch circle radius can be selected, speed is very slowly increased.By making speed more slowly increase, very high acceleration can be avoided, so consequently noise and vibration can be reduced.
As other adoptable change forms, also comprise with Θ=Θ in the circulating cycle
rev1to Θ=Θ
rev2(0≤Θ
rev1, Θ
rev2≤ 2 π) a certain angle or a certain angular range in become r
1(Θ) r
3(Θ) > r
2(Θ) r
4(Θ), several aspects become r
1(Θ) r
3(Θ) < r
2(Θ) mode of r4 (Θ), selects the situation of pitch radius (that is, when when the angular range of 0≤Θ≤2 π, to comprise r
1(Θ) r
3(Θ)/r
2(Θ) r
4(Θ) situation of > 1 and r
1(Θ) r
3(Θ)/r
2(Θ) r
4(Θ) situation of < 1).So, when meeting Θ
rev1< Θ < Θ
rev2time, the output that direction of rotation is reversed can be obtained all the time.This may be used for being screwed into the purposes such as screw to timber.Be screwed in process at screw, the situation that the Continuous Drive being screwed into screw causes the connection between output shaft interface (being often called as " drill bit ") and driven portion (head of screw) to be separated sometimes, this is the well known phenomenon being called " departing from occlusion (cam-out) " in this technical field.In the present invention, at first, only advancing a small amount of in circulation by driving at each, thus avoiding being separated of drill bit in given circulation and head of screw.And, in non-driven, by a certain angle of reversing, drill bit is engaged again with head of screw, thus limit or prevent the disengaging in multiple circulation to be engaged.This state is shown in Figure 4.In the diagram, the end view drawing of general head of screw 8 and screw-driven brill 9 is shown.They are in initial fully contraposition, and in driving, they start to be separated, and after during driving, are easily again engaged by reversion.
Motor 14 can consider to utilize someway such as electromagnetic field or air pressure to the structure of housing 15 transmitting torque.Described motor 14 drives the noncircular gear case 18 of the type in aforementioned type via a certain connection shaft (motor reel 16).This noncircular gear case 18 mechanically or other modes be connected with housing 15 and output shaft 17, be then connected with a certain tool component 22.
Consider the All Time spent to during the next one drives from during some drivings, the interests of " cycle period " (its inverse is " cycling cycling vibration frequency ") of the output shaft 17 of the peak torque transmitted to matrix 21 can be reached.This system is considered the system being similar to torsion spring 12 and torsional vibration damper 13, the wrist of such as people is utilized to be fixed on matrix 21, when having certain rotatory inertia, the relation between the eigentone of entire system and cycling cycling vibration frequency determines to be applied to the peak torque on matrix 21.In the extreme housing that cycling cycling vibration frequency is unlimited, matrix 21 bears the peak torque identical with the moment of torsion that tool component 22 bears.When limiting the eigentone of cycling cycling vibration frequency and system, the peak torque that matrix 21 bears increases further.But when cycling cycling vibration frequency increases above the eigentone of entire system, the torque ratio peak torque that matrix 21 bears is low.
Fig. 6 represents this effect under eigentone 14Hz, and y-axis represents and is defined as the power of output and " transport " of the ratio of the power of input, represents with dB.Therefore, by suitably selecting gear forms, can to reach the way selection cycling cycling vibration frequency of this favourable operating characteristic.And the ratio of the time that the time that the size of the moment of torsion transmitted is rotated by output shaft 17 stops with output shaft 17 decides.Because all impacts must be kept between matrix 21 and tool component 22, so when applying high moment of torsion with the short time to tool component 22, can be made it and balance each other through being for longer periods applied to the low-down moment of torsion on matrix 21.That is, in order to reducing effect is in the moment of torsion of matrix, the percussion tool of present embodiment by possessing the mechanism of the ratio that freely can set the time that time that output shaft 17 rotates stops with output shaft 17, thus can control the moment of torsion of outlet side.
As other advantages of above-mentioned embodiment, there is the situation reaching engagement between constrained input all the time.Different from the percussion tool in the past that there is not dependency relation between input torque and output torque, there is dependency relation in structure according to the present embodiment between input torque and output torque.Thereby, it is possible to the moment of torsion of perception input side, and use the gear ratio both known and the information about the angle position of system to calculate the moment of torsion of outlet side accordingly.That is, the percussion tool of present embodiment is by possessing the mechanism of indirect perception output torque further, can calculate the moment of torsion of outlet side.
These above-mentioned mechanisms are such as useful when controlling the moment of torsion be applied on securing member.When using electromagnetic motor, can according to the moment of torsion of the information acquisition motor about electric current and voltage.Therefore, as an example of present embodiment, the present invention comprises electronic torque sensing detection.
An advantage of above-mentioned present embodiment is, owing to eliminating beater mechanism and output shaft more gently accelerates, so compared with the percussion tool both deposited, can reduce noise.Equally, present embodiment can reduce the vibration because device produces.And by the collision of high loss and slidingly contact the Structure deformation replacing with gear, thus, present embodiment can realize low-loss.This can also bring the advantage of low abrasion, and and then the advantage of generation long service life.
As it will be appreciated by persons skilled in the art that the percussion tool of above-mentioned present embodiment can bring benefit to the power tool comprising driver drilling tool and impact driver at large.And, when needs rotate reciprocating action, such as, for brush cutting machine (trimmer), this system can be used.
In addition, such as, realize simple " rotation-straight line " conversion by using rack-and-pinion, present embodiment can also be applicable to other devices, is especially applicable to reciprocating action saw device.
And, other advantages of present embodiment are, in the equipment energy characteristic of present embodiment, for the given combination of motor and gear-box, the output torque higher than the direct drive unit of the conventional arts such as driver drilling tool can be realized, thus, the size of device can be reduced when moment of torsion is equal.When the use of the beater mechanism of present embodiment is again compared with the direct drive unit of driver drilling tool etc., for given output torque, the moment of torsion being applied to mechanical " matrix (such as user) " by device can be reduced.And, may lose in the purposes of contact (being screwed into of the screw using drill bit to carry out), again engaging between drill bit with head of screw can be realized by reversion, can avoid thus losing engaging.
Above, although be preferred embodiment illustrated of the present invention, technical scope of the present invention is not limited to the scope recorded in above-mentioned embodiment.In the above-described embodiment, numerous variations or improvement can be realized.
Such as, Fig. 7 shows following particular implementation, and this embodiment is suitable for comprising the multiple purposes as being known as the replacement instrument impacting the such power tool of driver and situation about using.Power shaft 71 driving rotating bodies 78, is provided with planet axis 74 in this rotary body 78, planet axis 74 around itself axle and rotate freely.Planet axis 74 is provided with circular planetary gear 73 and non-circular planetary gear 72.Described gear 72,73 is interconnected, and when needing to provide torque capability to a certain degree from gear-box, realizes connecting preferably by being integrally formed.Circular planetary gear 73 rotates under the effect of the circular central gear 76 be connected with mechanical device matrix.Therefore, non-circular planetary gear 72 is driven by circular planetary gear 73.Consequently, non-circular planetary gear 72 drives non-circular central gear 75.This non-circular central gear 75 is connected and driver output axle 77 with output shaft 77.
Embodiment shown in Fig. 7 has advantage to a certain degree compared with the structure shown in Fig. 3.Not mechanism power shaft 71 end and at output shaft 77 end, circular central gear 76 is connected with matrix, the two supports planet axis 74 in rotary body 78 can be realized.By the two supports planet axis 74 in rotary body 78, for the given moment be applied in planet axis 74, the normal load at planet axis 74 two ends can be reduced, thus the gear-box of more high strength can be formed, realize lighter compacter gear box structure.And this structure, without the need to accommodating bearing between described gear 72,73, can make circular planetary gear 73 and non-circular planetary gear 72 be formed as single part.Owing to transmitting moment of torsion to a certain degree between described gear 72,73, so utilize this structure can improve the intensity of this unit.
When needing to install the reduction gear box added, also there is the possibility that the size of entire system is reduced in power shaft.Other embodiments shown in Fig. 8 represent the reduction gear box added directly arranged on rotary body 86.Power shaft 85 drives central gear 81, and central gear 81 acts on one or more planetary gear 82, and planetary gear 82 is mobile in the circular internal gear 84 be connected with matrix.The axle 83 of planetary gear 82 provides rotary body 86 around the rotary actuation of axle.In addition, axle 83 can be suitably set on rotary body 86.Compared with the situation of installing the independently reduction gear box added with the importation of the structure shown in Fig. 3, this situation can realize simplification to a certain degree and reduce size.
When utilizing the impact driver of conventional art the screw of 4.5 × 90mm to be screwed into dry pine, known intermediate point being screwed into when about 45mm is screwed in timber (screw), general hammer body collides and makes for 1 time screw produce 90 degree of rotations.Time needed for 1 collision is 15ms, and therefore, the vibration frequency of this spike train is 67Hz.This eigentone than instrument/user's system is high a lot.In addition, the moment of torsion being delivered to user is the value of the torque time equalization by being applied to screw.Therefore, user can not bear the high torque pulse be applied on screw.And can know, the analysis of common impact driver generally makes drill bit relative to screw reversion 10 degree under the disengaging occlusion condition under the poorest situation.
By selecting suitable noncircular gear form and circular gear size, for the operating characteristic of the impact driver of aforesaid conventional art, use the present invention also can become same operating characteristic in (collisionless) gear-box that tooth remains engaging.Fig. 9 shows the right example of the non-circular central gear of non-circular planetary gear 91/ 92 of reaching above-mentioned situation.Described gear 91,92 has 14 teeth of module same in fact.Can by described gear 91,92 in the gear-box of Fig. 7 or Fig. 8 shown type and planet: the circular gear (such as, the circular planetary gear of pitch diameter 13mm and the circular central gear of pitch diameter 17mm) of the sun than=0.765 combines.This structure makes output shaft (symbol 77 of Fig. 7 and the symbol 87 of Fig. 8) rotate forward 95 degree, then makes described output shaft 77,87 reverse 10 degree.
It should be noted that, about positive gyration and the reverse angle of above-mentioned output shaft 77,87, be according to forming the structural condition etc. of gear train of the present invention and change.Such as, the situation that the reverse angle of output shaft 77,87 is generally about 10 degree is only the representational numerical value exemplified.By suitably changing structure member of the present invention in the scope of this invention thought, the change in various setting can be carried out to the operating characteristic of percussion tool of the present invention.
When utilizing the structure shown in Fig. 7 to implement these forms, when driving power shaft 71 with 1556rpm, the driving/reverse cycle of output shaft 77 carries out with the frequency of 34Hz.This structure carries out work when not carrying out the collision of the device in conventional art just can reach object, thus has reached lower noise level in operation.
Or, also can use the structure shown in Fig. 8.When the pitch diameter of circular central gear 81 be 5mm, the pitch diameter of circular planetary gear 82 is 17.5mm, the pitch diameter of circular internal gear 84 is 40mm, reach the speed reducing ratio of 9:1 between power shaft 85 and rotary body 86.Therefore, when making power shaft 85 rotate with the 14000rpm non-abnormal speed of motor (in the conventional art that same power tool adopts), driving/reverse cycle carries out with the frequency of 34Hz.
Therefore, compared with driver drill bit, the useful characteristic of impacting driver can be reached.These useful characteristics comprise: same screw is screwed into the time, few generation departs from occlusion, puts on the higher peak torque of screw and put on the lower peak torque of user and reduce size relative to the output of given moment of torsion.And, compared with impact driver, can realize significantly reducing noise, reducing vibration and raise the efficiency and reduce abrasion.
It should be noted that, in the above-described embodiment, utilize Fig. 4 etc. to restriction and prevent the mechanism of the disengaging scuffing occurred in multiple circulation to be illustrated.That is, in the present embodiment, at first, only carry out a small amount of forward rotating movements by driving in circulation at each, thus avoid drill bit in given circulation to be separated with head of screw.And, even if in driving they start be separated, also can during driving after utilize reverse easily make it again engage.In addition, the situation that described action is realized by the 2 gear drive row etc. engaged all the time be arranged in noncircular gear case 18 is described.But, in the above-described embodiment, can increase further suitable improvement, such as, in order to avoid tool component middle during driving is separated from screw, the anglec of rotation of the output shaft be spaced during being preferably configured to make non-driven is enough little.In addition, as other improvement example, the reverse angle of output shaft is preferably set to tool component in during driving makes tool component again engage with screw after being separated a little with screw.Utilize this improvement, can reliably prevent from departing from scuffing.
In addition, the structure utilizing Fig. 7 and Fig. 8 etc. to exemplify merely illustrates the adoptable form of the present invention.The present invention has above-mentioned basic structure, plays in the scope of same action effect, can adopt various deformation form.Such as, the variation as the embodiment shown in Fig. 7 is illustrated by Figure 15.In the embodiment represented by Figure 15, be with the difference of Fig. 7, non-circular planetary gear 72 and non-circular central gear 75 are configured in output shaft 77 side, and circular planetary gear 73 and circular central gear 76 are configured in power shaft 71 side this point.In the embodiment shown in Figure 15, the front end of power shaft 71 is provided with rotary body 78.When power shaft 71 driving rotating bodies 78, the planet axis 74 be arranged on rotary body 78 carries out planetary motion.This planet axis 74 around itself axle and freely rotate.In addition, planet axis 74 is provided with non-circular planetary gear 72 and circular planetary gear 73.These gears 72,73 are interconnected and fixed relative to planet axis 74.Circular planetary gear 73 rotates under the effect of the circular central gear 76 be connected with mechanical device matrix.Therefore, non-circular planetary gear 72 is driven in rotation along with the rotary motion of circular planetary gear 73.Consequently, non-circular planetary gear 72 drives non-circular central gear 75.Because the non-circular central gear 75 of output shaft 77 and this is connected, so output shaft 77 is driven in rotation along with the rotary actuation of non-circular central gear 75.It should be noted that, in the embodiment shown in Figure 15, because non-circular planetary gear 72 configures multiple in the mode being in symmetric position relative to non-circular central gear 75, so the advantage that the balance with rotary motion is good.
According to the record of technical scheme can it is clear that, the form of having carried out this change or improvement is also included in the technical scope of the present invention.
Next, use Figure 10 ~ Figure 13 that the embodiment embodiment utilizing Fig. 7 and Fig. 8 to exemplify specifically being applicable to percussion tool is described.At this, Figure 10 is the integrally-built vertical section right hand view of the percussion tool representing the present embodiment.In addition, Figure 11 is the exploded perspective expanded view of the major part of the important part structure of percussion tool for illustration of the present embodiment.And Figure 12 represents that non-circular planetary figure, Figure 13 of the present embodiment are the figure of the non-circular central gear with output shaft representing the present embodiment, and (a) in each figure represents side, rear, and (b) in figure represents section.
As shown in Figures 10 and 11, the percussion tool 100 of the present embodiment is the percussion tool 100 of battery type, and it possesses: accommodate the shell 110 of drive source such as motor 111 grade, be arranged to dismounting carries out driving the supply of electric power freely battery pack 130 to this motor 111 in the bottom of shell 110.
Shell 110 comprises: shell upper body 110a, its collecting motor 111 and be equivalent to the driving mechanism portion 115 of noncircular gear case 18 of above-mentioned present embodiment; Housing center body 110b, it is subject to the holding of user; Outer casing underpart body 110c, it possesses the bindiny mechanism be connected with battery pack 130.From outer casing underpart body 110c via housing center body 110b to shell upper body 110a, implement power wiring, the driving electric power be charged in battery pack 130 can supply to motor 111.In addition, above shell central body 110b, front face side is provided with console switch 112, and the user holding housing center body 110b can carry out suitable operation to this console switch 112.
The driving mechanism portion 115 being arranged on the front of motor 111 achieves the mechanism of the present invention utilizing Fig. 7 and Fig. 8 to illustrate particularly.That is, the driving mechanism portion 115 of the present embodiment possesses: the central gear 181 that the motor reel 111a possessed with motor 111 is connected, two planetary gears 182 be connected with a joggle around this central gear 181,182, surround the circular internal gear 184 of the periphery of two planetary gears 182,182.When making motor reel 111a rotate by supplying electric power to motor 111, motor reel 111a drives central gear 181, central gear 181 acts on two planetary gears 182,182, and planetary gear 182,182 is mobile in the circular internal gear 184 be connected with the shell upper body 110a as mechanical device matrix.
The front of two planetary gears 182,182 is provided with rotary body 186.The axle 183 of planetary gear 182 is connected with this rotary body 186, provides the rotary actuation around axle of rotary body 186.
In the position of the pivot bias from rotary body 186, planet axis 174 is set.This planet axis 174 is arranged with the form being contained in the inside of rotary body 186, and the shaft end of the both sides of planet axis 174 is supported by bearing 174a, 174b axles such as the needle bearings be arranged in rotary body 186.
In addition, in planet axis 174, be provided with circular planetary gear 173 at the shaft end of front side, the shaft end of side is provided with non-circular planetary gear 172 in the wings.Described gear 172,173 is rigidly connected to each other, and, freely can rotate around the axle of planet axis 174.
Circular planetary gear 173 engages with the circular central gear 176 be fixedly connected on as the shell upper body 110a of mechanical device matrix.Namely, when rotary body 186 utilizes the rotation of two planetary gears 182,182 and is driven in rotation, planet axis 174 is turn-taked around circular central gear 176, and consequently, circular planetary gear 173 also revolves round the sun while the surrounding edge rotation of this circular central gear 176 be fixedly installed.
Along with the above-mentioned rotary actuation of circular planetary gear 173, non-circular planetary gear 172 is driven in rotation similarly.Because the non-circular central gear 175 be connected with output shaft 177 engages with this non-circular planetary gear 172, so non-circular central gear 175 is driven in rotation accordingly with the rotary actuation of non-circular planetary gear 172, as its result, output shaft 177 is driven in rotation.It should be noted that, the rotating shaft center of the output shaft 177 connected with non-circular central gear 175 is overlapping with the rotary middle spindle of rotary body 186.In addition, the shaft end of the rear side of output shaft 177 is supported by the bearing be arranged in rotary body 186, and the shaft end of front side is connected with drill bit frame 179.Therefore, the rotary actuation being arranged on the instruments such as the driver in drill bit frame 179 and output shaft 177 rotates accordingly, thus can implement operation to outside.
It should be noted that, as mentioned above, rotary body 186 is driven in rotation with the planetary motion of planetary gear 182, but planet axis 174 eccentric setting arranged therein.In addition, planet axis 174 is provided with non-circular planetary gear 172 and this weight member of circular planetary gear 173.Therefore, in order to make rotary body 186 suitably be rotated, need to arrange for obtaining the counterweight balanced each other with weight member such as planet axis 174 grade.Therefore, in the rotary body 186 of the present embodiment, as shown in figure 11, have employed and the main body middle body of rotary body is formed as hemisect structure, arrange in the position opposed with the setting position of planet axis 174 by the structure of the counterweight portion 186a of hemisect Structure composing.By arranging this counterweight portion 186a, rotary body 186 can stably be rotated, thus can realize the percussion tool 100 with stable operation.
Next, the action of the percussion tool 100 of the present embodiment is described with reference to Figure 10.
In the percussion tool 100 of the present embodiment, utilize the driving of motor 111 and drive motor axle 111a rotates, the revolving force of this motor reel 111a makes central gear 181 rotate.When central gear 181 rotates, two planetary gears 182,182 be arranged between central gear 181 and circular internal gear 184 carry out planetary motion.The axle 183 had due to planetary gear 182 is connected with rotary body 186, so carry out planetary motion by two planetary gears 182,182 and driving rotating bodies 186 rotates.
When rotary body 186 is driven in rotation, under the effect of the circular central gear 176 be fixedly connected with shell upper body 110a, circular planetary gear 173 rotates, and carries out rotary actuation with the rigidly connected non-circular planetary gear 172 of this circular planetary gear 173 is also same with circular planetary gear 173.Because non-circular planetary gear 172 and circular planetary gear 173 are arranged in the planet axis 174 of the inside being located at rotary body 186, so these two gears 172,173 are while freely rotating around the axle of planet axis 174, the rotary middle spindle around rotary body 186 carries out circus movement.
The non-circular planetary gear 172 carrying out planetary motion is in the above-described manner engaged with non-circular central gear 175, and is connected with output shaft 177 on this non-circular central gear 175.In addition, rotate because non-circular central gear 175 corresponds to the planetary motion of non-circular planetary gear 172, so its rotary driving force can be delivered to output shaft 177, thus can externally provide given moment of torsion.
It should be noted that, as illustrated in the above-described embodiment, in the percussion tool 100 of the present embodiment, also be under the effect of two noncircular gears and non-circular planetary gear 172 and non-circular central gear 175, output shaft 177 carries out rotating forward and carries out reversion action in the cycle period of regulation.By this action, can obtain and prevent from departing from the good effects such as occlusion.
And the percussion tool 100 of the present embodiment is different from the percussion tool in the past possessing hammer body 10 grade, owing to possessing the structure utilizing the realization of multiple noncircular gear as the mechanism of percussion tool, so have this good advantage of low noise when load uses.This advantage can according to Figure 14 and table 1, the analysis result of the comparative measurements of the noise that uses the percussion tool 100 of percussion tool in the past and the present embodiment to produce and obtain clear and definite.At this, Figure 14 is the figure for illustration of noise measuring method.
The noise measuring method this time implemented is to fastening in the test film 190 be made up of dry U.S. pine (DryPine)
wood screw time the noise that produces carry out method for measuring.Noise locate be the rear of percussion tool, left, above and the position of below distance percussion tool 1m.It should be noted that, when measuring noise, being measured by additional A characteristic frequency weighting sound pressure level (Aweightedsoundpressurelevel).In addition, the percussion tool used in noise measuring is the percussion tool 100 of the present embodiment utilizing Figure 10 etc. to illustrate and the percussion tool possessing hammer body 10 etc. in the past that is representative with above-mentioned patent document 1.As shown in table 1 according to the measurement result of the noise of above condition mensuration.It should be noted that, table 1 is the table compared the measurement result of noise when having a load.
[table 1]
The comparison of noise during table 1 load
According to table 1 can it is clear that, compared with the percussion tool (impact driver) of conventional art, the percussion tool 100 of the present embodiment is low noise level all locating.In addition, even if the mean value of noise result that comparative measurements is arrived, also make the percussion tool 100 of the present embodiment realize low noise because difference 5.0dB (A), thus confirm superiority of the present invention.
Symbol description
1 static central gear, 2 by driving planetary gear, 3 drive planetary gear, 4 export central gear, 5 power shafts, 6 actuating arms, 7 planet axis, 8 head of screws, 9 screw-driven are bored, 10 hammer bodies, 11 anvils, 12 torsion springs, 13 torsional vibration dampers, 14 motor, 15 housings, 16 motor reels, 17 output shafts, 18 noncircular gear casees, 21 matrixes, 22 tool components, 23 input gears, 24 output gears, 25 (in the past) gear-box, 26 power shafts, 27 output shafts, 71 power shafts, 72 non-circular planetary gears, 73 circular planetary gears, 74 planet axis, 75 non-circular central gears, 76 circular central gears, 77 output shafts, 78 rotary bodies, 81 central gears, 82 planetary gears, 83 axles, 84 circular internal gears, 85 power shafts, 86 rotary bodies, 87 output shafts, 91 non-circular planetary gears, 92 non-circular central gears, 100 percussion tools, 110 shells, 110a shell upper body, 110b housing center body, 110c outer casing underpart body, 111 motor, 111a motor reel, 112 console switch, 115 driving mechanism portions, 130 battery pack, 172 non-circular planetary gears, 173 circular planetary gears, 174 planet axis, 174a, 174b bearing, 175 non-circular central gears, 176 circular central gears, 177 output shafts, 179 drill bit frame, 181 central gears, 182 planetary gears, 183 axles, 184 circular internal gears, 186 rotary bodies, 186a counterweight portion, 190 test films.
Claims (8)
1. a percussion tool, it is designed to be connected with matrix with given condition and to provide the rotary motion with periodically variable angular speed and/or moment of torsion, it is characterized in that, comprising:
Power shaft, its provide input angular velocity and/or moment of torsion during rotating a circle in constant in fact rotary motion;
Output shaft, its Output speed as the angle of described power shaft function and change;
Gear-box, it possesses as the above gear (1,2,3,4) of two couple of the driving row rotary motion of described power shaft transmitted to described output shaft, described two comprise the first gear mesh (1,2) be associated with described power shaft and the second gear mesh (3,4) be associated with described output shaft to above gear (1,2,3,4)
When using ζ as attenuation ratio, using wn as comprise percussion tool and percussion tool and matrix be connected to the rotation eigentone of interior system time,
Export cycling cycling vibration frequency larger than the computation cycles vibration frequency defined by sqrt (2 × (1-2 ζ)) wn.
2. percussion tool according to claim 1, is characterized in that,
The connection of described percussion tool and described matrix is provided by user,
Described output cycling cycling vibration frequency is the vibration frequency being greater than 14Hz.
3. percussion tool according to claim 1, is characterized in that,
This percussion tool is used for trip bolt,
The forward rotating movements of described output shaft causes being separated of tool component and described screw, and return motion afterwards causes again engaging of described tool component and described screw.
4. percussion tool according to claim 1, is characterized in that,
When described percussion tool is configured to use, cycling cycling vibration frequency is greater than in fact the eigentone of entire system.
5. percussion tool according to claim 1, is characterized in that,
In order to reducing effect is in the moment of torsion of matrix, the ratio of the time that the time that output shaft described in free setting rotates stops with described output shaft.
6. percussion tool according to claim 1, is characterized in that,
Also possess the mechanism of perception output torque indirectly, this mechanism be used for perception input side moment of torsion and use accordingly known gear ratio and about the angle position of system information and calculate the moment of torsion of outlet side.
7. percussion tool according to claim 3, is characterized in that,
This percussion tool is used for trip bolt,
Be separated from described screw in order to avoid described tool component in during the driving be spaced during non-driven and make the anglec of rotation of described output shaft enough little.
8. percussion tool according to claim 3, is characterized in that,
This percussion tool is used for trip bolt,
The reverse angle of described output shaft is configured to described tool component in during driving makes described tool component again engage with described screw after being separated a little with described screw.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB0908645.5 | 2009-05-20 | ||
| GBGB0908645.5A GB0908645D0 (en) | 2009-05-20 | 2009-05-20 | Impulse tool |
| GB0915483.2 | 2009-09-07 | ||
| GBGB0915483.2A GB0915483D0 (en) | 2009-09-07 | 2009-09-07 | Top up to impulse tool |
| CN201080016096.0A CN102387896B (en) | 2009-05-20 | 2010-05-12 | Impact tool |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201080016096.0A Division CN102387896B (en) | 2009-05-20 | 2010-05-12 | Impact tool |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103753469A CN103753469A (en) | 2014-04-30 |
| CN103753469B true CN103753469B (en) | 2015-12-30 |
Family
ID=43125989
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310724372.4A Expired - Fee Related CN103753469B (en) | 2009-05-20 | 2010-05-12 | Percussion tool |
| CN201080016096.0A Expired - Fee Related CN102387896B (en) | 2009-05-20 | 2010-05-12 | Impact tool |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201080016096.0A Expired - Fee Related CN102387896B (en) | 2009-05-20 | 2010-05-12 | Impact tool |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP5496190B2 (en) |
| CN (2) | CN103753469B (en) |
| WO (1) | WO2010134296A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| TW201406501A (en) * | 2013-10-31 | 2014-02-16 | Quan-Zheng He | Impact set of pneumatic tool |
| CN104546438B (en) * | 2015-02-12 | 2016-05-18 | 王丽媛 | Foot massager |
| JP6868851B2 (en) * | 2017-01-31 | 2021-05-12 | パナソニックＩｐマネジメント株式会社 | Impact rotary tool |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3424021A (en) * | 1967-05-23 | 1969-01-28 | Ferdinand Freudenstein | Intermittent motion mechanism employing non-circular gears |
| US4055091A (en) * | 1972-08-31 | 1977-10-25 | Ker-Train Systems N.V. | Variable output transmission |
| US4756203A (en) * | 1986-07-28 | 1988-07-12 | Yoshida Kogyo K. K. | Intermittent drive mechanism |
| CN101032814A (en) * | 2006-03-07 | 2007-09-12 | 日立工机株式会社 | Impact tool with vibration control mechanism |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4954123A (en) * | 1988-12-12 | 1990-09-04 | Eugens Kurywczak | Radial helix drive horse power amplifier |
| US5170757A (en) * | 1991-12-24 | 1992-12-15 | Damien Gamache | Variable horsepower output gearing for piston engine |
| JP3559174B2 (en) * | 1998-05-25 | 2004-08-25 | リョービ株式会社 | Impact tool impact structure |
| JP2000176851A (en) * | 1998-12-17 | 2000-06-27 | Mitsubishi Heavy Ind Ltd | Rotary working device |
| JP4008865B2 (en) * | 2003-08-01 | 2007-11-14 | 株式会社東洋空機製作所 | Fastener |
| JP4699316B2 (en) * | 2006-09-01 | 2011-06-08 | 株式会社エスティック | Impact type screw tightening device |
| JP4837498B2 (en) * | 2006-09-04 | 2011-12-14 | 株式会社エスティック | Planetary gear device and impact type screw fastening device |
| TWM311558U (en) * | 2006-12-01 | 2007-05-11 | Jungli Shing Jr | Multi-functional impact type electric tool |
-
2010
- 2010-05-12 CN CN201310724372.4A patent/CN103753469B/en not_active Expired - Fee Related
- 2010-05-12 CN CN201080016096.0A patent/CN102387896B/en not_active Expired - Fee Related
- 2010-05-12 WO PCT/JP2010/003224 patent/WO2010134296A1/en active Application Filing
- 2010-05-12 JP JP2011514319A patent/JP5496190B2/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3424021A (en) * | 1967-05-23 | 1969-01-28 | Ferdinand Freudenstein | Intermittent motion mechanism employing non-circular gears |
| US4055091A (en) * | 1972-08-31 | 1977-10-25 | Ker-Train Systems N.V. | Variable output transmission |
| US4756203A (en) * | 1986-07-28 | 1988-07-12 | Yoshida Kogyo K. K. | Intermittent drive mechanism |
| CN101032814A (en) * | 2006-03-07 | 2007-09-12 | 日立工机株式会社 | Impact tool with vibration control mechanism |
Also Published As
| Publication number | Publication date |
|---|---|
| JPWO2010134296A1 (en) | 2012-11-08 |
| JP5496190B2 (en) | 2014-05-21 |
| WO2010134296A1 (en) | 2010-11-25 |
| CN103753469A (en) | 2014-04-30 |
| CN102387896A (en) | 2012-03-21 |
| CN102387896B (en) | 2014-05-21 |
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Effective date of registration: 20180604 Address after: Hiroshima County Patentee after: KYOCERA Industrial Tools Co., Ltd. Address before: Hiroshima County, Japan Patentee before: Ryobi Ltd. |
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Granted publication date: 20151230 Termination date: 20190512 |