WO2010134296A1 - Outil de percussion - Google Patents

Outil de percussion Download PDF

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Publication number
WO2010134296A1
WO2010134296A1 PCT/JP2010/003224 JP2010003224W WO2010134296A1 WO 2010134296 A1 WO2010134296 A1 WO 2010134296A1 JP 2010003224 W JP2010003224 W JP 2010003224W WO 2010134296 A1 WO2010134296 A1 WO 2010134296A1
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WO
WIPO (PCT)
Prior art keywords
impact tool
gear
shaft
output shaft
torque
Prior art date
Application number
PCT/JP2010/003224
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English (en)
Japanese (ja)
Inventor
ストーンエドウィン
ジョン ローリンズフィリップ
リー クロスリーピーター
田辺晴之
田頭康範
Original Assignee
リョービ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from GBGB0908645.5A external-priority patent/GB0908645D0/en
Priority claimed from GBGB0915483.2A external-priority patent/GB0915483D0/en
Application filed by リョービ株式会社 filed Critical リョービ株式会社
Priority to CN201080016096.0A priority Critical patent/CN102387896B/zh
Priority to JP2011514319A priority patent/JP5496190B2/ja
Publication of WO2010134296A1 publication Critical patent/WO2010134296A1/fr

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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

Definitions

  • the present invention relates to a power tool, and more particularly to an improved impact tool that applies impact torque.
  • a rotation mechanism including a hammer 10 and an anvil 11 is generally used.
  • the hammer 10 is connected to the input shaft via a cam mechanism, and is rotated by a motor until it collides with an anvil 11 connected to a fastener to be tightened.
  • the output shaft rotates by a predetermined amount due to the transmission of angular momentum.
  • the hammer 10 decelerates due to the collision with the anvil 11, the hammer 10 is separated from the anvil 11 by the cam mechanism, whereby the hammer 10 is accelerated again and can repeat the collision operation.
  • Patent Document 1 As a prior art document disclosing the conventional impact tool provided with the above-described hammer 10 or the like, for example, there is the following Patent Document 1 or the like.
  • the present invention has been made in view of the above-mentioned problems, and its purpose is to enable a variable output rotational motion including intermittent motion and forward / reverse motion for a constant input rotational motion.
  • the object is to address these problems by using a constantly meshing gearbox including non-circular gears.
  • An impact tool is an impact tool that provides a rotational motion having a periodically changing angular velocity and / or torque designed to be connected to a ground at a given condition, wherein the angular velocity and / or Or an input shaft providing a rotational motion in which the torque is substantially constant during one revolution, an output shaft in which the angular velocity varies as a function of the angle of the input shaft, and the rotational motion of the input shaft as the output shaft.
  • Two pairs including a first gear pair (1, 2) associated with the input shaft and a second gear pair (3, 4) associated with the output shaft.
  • a gear box including the above gears (1, 2, 3, 4), and the gears (1, 2, 3, 4) have radiuses r 1 ( ⁇ ) and r 2 ( ⁇ ) of pitch circles, respectively.
  • r (Theta), and r 4 have a (theta)
  • the theta is represents the angular position of the planetary shaft (7) connecting the gear (2) and a wheel (3)
  • the radius of 4 is at least an angle range of 0 ⁇ ⁇ ⁇ 2 ⁇
  • the output cycle frequency is sqrt (2 ⁇ (1-2 ⁇ )) wn Is preferably set to be larger than the calculation cycle frequency defined by Note that “sqrt” in the above equation indicates a square root (the same applies hereinafter).
  • the impact tool according to the present invention is an impact tool that provides a rotational motion having a periodically changing angular velocity and / or torque designed to be connected to a ground under a given condition, And / or an input shaft that provides a rotational motion in which the torque is substantially constant during one revolution, an output shaft in which the angular velocity varies as a function of the angle of the input shaft, and the rotational motion of the input shaft
  • a drive train for transmitting to the output shaft comprising: a first gear pair (1, 2) associated with the input shaft; and a second gear pair (3, 4) associated with the output shaft.
  • a gear box having two or more pairs of gears (1, 2, 3, 4), a rotational natural vibration of a system including a damping ratio ⁇ and a connection wn to an impact tool and ground
  • the output cycle frequency, sqrt (2 ⁇ (1-2 ⁇ )) wn It is set so that it may become larger than the calculation cycle frequency defined by.
  • the connection to the ground is provided by a user, and the output cycle frequency is a frequency greater than 14 Hz.
  • the impact tool is used for tightening a screw, and the forward rotation motion (rotational motion in the tightening direction of the screw) of the output shaft is caused by the tool member and the screw.
  • the forward rotation motion rotational motion in the tightening direction of the screw
  • the impact tool according to the present invention is configured such that, when in use, the cycle frequency is substantially larger than the natural frequency of the entire system.
  • the time during which the output shaft is rotating and the time during which the output shaft is stopped in order to reduce the torque acting on the ground can be set freely.
  • the output torque for sensing the torque on the input side and calculating the torque on the output side using the known gear ratio and information on the angular position of the system therefrom may be further provided.
  • the impact tool is used for tightening a screw, and avoids separating the tool member from the screw during a driving period between non-driving periods.
  • the rotation angle of the output shaft can be configured to be sufficiently small.
  • the impact tool is used for tightening a screw, and a reverse rotation angle of the output shaft is slightly separated between the tool member and the screw during a driving period. Thereafter, the tool member and the screw can be re-engaged.
  • the rotating body (186) included in the gear box has a planetary shaft (7 (174)) connecting the gear (2 (173)) and the gear (3 (172)).
  • the balance weight part (186a) for balancing with can be provided.
  • FIG. 1 is a conceptual diagram for explaining the configuration of a non-circular gearbox according to the present embodiment.
  • FIG. 2 is a graph showing the gear ratio as a function of the input angle ⁇ .
  • FIG. 3 is a diagram illustrating a form in which the non-circular gears of the present embodiment are arranged in a planetary gear box configuration.
  • FIG. 4 is a diagram showing a general screw head and an end face of a screw driving bit.
  • FIG. 5 is a block diagram illustrating the configuration of the impact tool according to this embodiment.
  • FIG. 6 is a graph showing the relationship between the natural frequency and the cycle frequency of the entire system according to this embodiment.
  • FIG. 7 is a diagram showing another example embodiment that can be taken by the present invention.
  • FIG. 1 is a conceptual diagram for explaining the configuration of a non-circular gearbox according to the present embodiment.
  • FIG. 2 is a graph showing the gear ratio as a function of the input angle ⁇ .
  • FIG. 3 is a diagram illustrating
  • FIG. 8 is a diagram showing still another embodiment example that the present invention can take.
  • FIG. 9 is a diagram showing an example of a non-circular planetary gear / non-circular sun gear pair for realizing the present invention.
  • FIG. 10 is a vertical cross-sectional right side view showing the overall configuration of the impact tool according to the present embodiment.
  • FIG. 11 is an exploded exploded perspective view of a main part for explaining a main part configuration of the impact tool according to the present embodiment.
  • FIG. 12 is a diagram showing a non-circular planetary gear according to the present embodiment, where (a) in the drawing shows a rear side surface, and (b) in the drawing shows a cross section.
  • FIG. 10 is a vertical cross-sectional right side view showing the overall configuration of the impact tool according to the present embodiment.
  • FIG. 11 is an exploded exploded perspective view of a main part for explaining a main part configuration of the impact tool according to the present embodiment.
  • FIG. 12 is a diagram showing a non-cir
  • FIG. 13 is a view showing a non-circular sun gear with an output shaft according to the present embodiment, in which (a) in the drawing shows a rear side surface and (b) in the drawing shows a cross section.
  • FIG. 14 is a diagram for explaining a noise measurement method.
  • FIG. 15 is a diagram showing still another embodiment example that can be taken by the present invention.
  • FIG. 16 is a diagram illustrating a rotation mechanism composed of a hammer and an anvil generally used as means for realizing intermittent drive.
  • FIG. 5 is a block diagram illustrating the configuration of the impact tool according to the present embodiment.
  • the impact tool according to this embodiment uses, for example, a motor (electromagnetic, pneumatic, or other power) coupled to a conventional gear box 25 by a motor shaft 16 to achieve desired average torque characteristics and average speed characteristics. Motor 14).
  • a motor electromagnettic, pneumatic, or other power
  • the input shaft 26 installed in the gear box 25 provides driving force to the non-circular gear box 18 including non-circular gears, and then the non-circular gear box 18 drives the output shaft 17.
  • the ratio between the input angular velocity and the output angular velocity of the non-circular gear box 18 can be expressed as a function of the angle of the input shaft 26.
  • the output shaft 17 is generally separably connected to a mechanical fastener such as a nut or screw that is a target for transmitting impact torque.
  • FIG. 1 is a conceptual diagram for explaining a configuration of a non-circular gear box 18 according to the present embodiment.
  • the non-circular gearbox 18 includes an input gear 23 and an output gear 24, each of which has a radius that varies over their entire circumference.
  • ⁇ 1 is the input angular velocity provided by the input shaft 26 installed in the conventional gearbox 25
  • R is the gear ratio
  • ⁇ 2 is the output angular velocity of the output shaft 17.
  • r 1 is the radius of the pitch circle of the input gear 23
  • r 2 is the radius of the pitch circle of the output gear 24.
  • a constant speed input provides an output speed that varies with both the angle and time of the input shaft 26.
  • the torque is T 1 as input torque and T 2 as output torque.
  • T 2 T 1 / R ( ⁇ ) This varying gear ratio makes it possible to provide a varying torque output.
  • the output cycle frequency is sqrt (2 ⁇ (1-2 ⁇ )) wn (“Calculated cycle frequency range (Calculated Cycle Frequency Range) ”) Is set to be larger than
  • ⁇ is the damping ratio
  • wn is the rotational natural frequency of the system including the impact tool and the connection to the ground 21.
  • this calculation cycle frequency range can be shown to be a frequency greater than 14 Hz.
  • a further improvement of this embodiment is that the above-described non-circular gears 23 and 24 are arranged in a planetary gear box configuration.
  • the pair of circular gears 1 and 2 can be combined with a pair of non-circular gears 3 and 4.
  • the configuration shown in FIG. 3 is reversed so that the pair of gears indicated by reference numerals 1 and 2 are non-circular gears and the pair of gears indicated by reference numerals 3 and 4 are circular gears. You can also. Further, all the gears can be non-circular gears.
  • the input shaft 5 is rigidly connected to the drive arm 6.
  • the drive arm 6 rotates by the same amount.
  • the planetary shaft 7 circulates around the axis of the input shaft 5 with a constant radius.
  • Planetary shaft 7 rotates freely about its own axis when driven by drive arm 6.
  • the driven planetary gear 2 is rigidly connected to the planetary shaft 7.
  • the angle of the planetary shaft 7 is called ⁇ .
  • the driven planetary gear 2 moves around the stationary sun gear 1
  • the driven planetary gear 2 thereby rotates about its axis, thereby driving the rotation of the planetary shaft 7.
  • This rotation drives the drive planetary gear 3 rigidly connected to the planetary shaft 7.
  • the drive planetary gear 3 then rotates the output sun gear 4 thereby driving the rotation of the output shaft 27.
  • the inertia associated with the input shaft 5 accelerates during the non-driving period and decelerates during the driving period.
  • the torque at the output shaft 27 is a combination of, for example, a drive torque provided by a motor and a reaction to inertia deceleration. Therefore, such a configuration makes it possible to apply a higher torque than direct driving by a motor.
  • the dependent form of the gear pitch circle radius can be chosen so that the speed increases slowly enough. By increasing the speed relatively slowly, very high accelerations are avoided, resulting in a reduction in noise and vibration.
  • the continuous drive of screwing may cause a disconnection of the connection between the output shaft interface (often referred to as “bit”) and the driven part (screw head), This is a phenomenon known in the art as “cam-out”.
  • bit and screw head separation in a given cycle is avoided by first advancing by a small amount during each drive cycle.
  • the bit and screw head re-engage, limiting or preventing camout over multiple cycles. This is shown in FIG. FIG. 4 shows an end view of a typical screw head 8 and screw drive bit 9. They are initially well aligned and during drive they begin to separate, and after the drive period, reverse rotation facilitates re-engagement.
  • the motor 14 can transmit torque to the case 15 by a certain method, for example, electromagnetic field or air pressure.
  • the motor 14 drives a non-circular gearbox 18 of one of the types described above via a connecting shaft (motor shaft 16).
  • This non-circular gearbox 18 is mechanically or otherwise connected to the case 15 and the output shaft 17 and from there to a certain tool member 22.
  • the “cycle period” of the output shaft 17 at the peak torque transmitted to the ground 21 (the reciprocal of this is the “cycle frequency”). ) Can be achieved.
  • this system is considered to be fixed to the ground 21 by a system approximate to the torsion spring 12 and the torsion damper 13, for example, a human arm, and has a certain rotational inertia
  • the natural frequency and cycle frequency of the entire system Determines the peak torque applied to ground 21.
  • the ground 21 receives the same peak torque that the tool member 22 receives.
  • the cycle frequency and the natural frequency of the system converge, the peak torque received by the ground 21 further increases. However, when the cycle frequency increases beyond the natural frequency of the entire system, the torque received by the ground 21 becomes lower than the peak torque.
  • FIG. 6 shows this effect at a natural frequency of 14 Hz
  • the y-axis shows the “transmission rate” defined as the ratio of the output force to the input force, and is shown in dB. Therefore, by appropriately selecting the gear type, the cycle frequency can be selected to achieve this advantageous behavior.
  • the magnitude of the transmitted torque is determined by the ratio of the time during which the output shaft 17 is rotating and the time during which the output shaft 17 is stopped. Since the entire impact must be stored between the ground 21 and the tool member 22, if a high torque is applied to the tool member 22 for a short time, this is applied to the ground 21 for a longer time. Can be balanced with the much lower torques that are available.
  • the impact tool according to the present embodiment has means for allowing the ratio of the time during which the output shaft 17 is rotating and the time during which the output shaft 17 is stopped to be freely set in order to reduce the torque acting on the ground. By providing, the torque on the output side can be controlled.
  • the configuration based on this embodiment has a correlation between input torque and output torque.
  • the input side torque can be sensed and the output side torque can be calculated therefrom using the known gear ratio and information about the angular position of the system.
  • the impact tool according to the present embodiment further includes means for indirectly sensing the output torque, whereby the output side torque can be calculated.
  • the present invention includes electronic torque sensing.
  • This embodiment described above is that it is less noisy than existing impact tools due to the removal of the impact mechanism and more gradual acceleration of the output shaft. Similarly, this embodiment reduces vibrations created by the device. Furthermore, this embodiment has a low loss by replacing the highly impaired collision and sliding contact with the rolling contact of the gear. This further provides the advantage of low wear and even longer life.
  • the impact tool according to this embodiment described above can provide benefits to power tools in general including a driver drill and an impact driver. Furthermore, such a system can be used when a rotary reciprocation is required, for example in the case of a hedge trimming machine.
  • the present embodiment can be applied to other devices, particularly a reciprocating saw device, by using a rack and pinion to realize a simple “rotation-linear” conversion.
  • another advantage of this embodiment is that the characteristics of the device based on this embodiment allow higher output torque than a prior art direct drive device such as a driver drill for a given combination of motor and gearbox.
  • the device size can be reduced when the torques are equal.
  • the use of the impact mechanism of this embodiment further reduces the torque applied by the device to the mechanical “ground (eg user)” for a given output torque when compared to a direct drive device such as a driver drill. Can be made.
  • contact may be lost (such as threading a screw using a bit)
  • this causes loss of engagement because reversal allows re-engagement between the bit and the screw head. Can be avoided.
  • FIG. 1 A specific embodiment suitable for many applications including, for example, use as a replacement tool for a type of power tool known as an impact driver is shown in FIG.
  • the input shaft 71 drives a rotator 78 in which the planetary shaft 74 is mounted, and the planetary shaft 74 is free to rotate about its own axis.
  • a circular planetary gear 73 and a non-circular planetary gear 72 are mounted on the planetary shaft 74. These gears 72 and 73 are connected to each other. When a considerable torque capacity from the gear box is required, the gears 72 and 73 are preferably connected by being integrally formed.
  • the circular planetary gear 73 is rotated by the action of a circular sun gear 76 connected to the mechanical ground.
  • the non-circular planetary gear 72 is driven by the circular planetary gear 73.
  • the non-circular planetary gear 72 drives the non-circular sun gear 75.
  • the non-circular sun gear 75 is connected to the output shaft 77 and drives the output shaft 77.
  • FIG. 7 has considerable advantages over the configuration shown in FIG.
  • the vertical load at both ends of the planetary shaft 74 is reduced for a given moment applied to the planetary shaft 74, forming a higher strength gearbox, and more Enables a lighter and more compact gearbox structure.
  • this configuration allows the circular planetary gear 73 and the non-circular planetary gear 72 to be formed as a single part without having to accommodate a bearing between these gears 72,73. Since a considerable torque is transmitted between the gears 72 and 73, the strength of the unit is increased by this configuration.
  • FIG. 8 shows an additional reduction gearbox constructed directly on the rotating body 86.
  • the input shaft 85 drives a sun gear 81, which acts on one or more planetary gears 82, which travel in a circular internal gear 84 connected to ground.
  • a shaft 83 of the planetary gear 82 provides rotational drive about the axis of the rotator 86. Further, the shaft 83 can be conveniently installed on the rotating body 86. This achieves considerable simplification and size reduction compared to installing an additional separate reduction gearbox at the input of the configuration shown in FIG.
  • each gear 91, 92 has 14 teeth of a substantially similar module.
  • the output shaft reference numeral 77 in FIG. 7 and reference numeral 87 in FIG. 8 is rotated forward by 95 degrees, and thereafter, the output shafts 77 and 87 are reversed by 10 degrees.
  • the forward rotation angle and the reverse rotation angle of the output shafts 77 and 87 described above vary depending on the configuration conditions of the gear group constituting the present invention.
  • the fact that the reverse angle of the output shafts 77 and 87 is generally about 10 degrees is merely an example of representative numerical values.
  • the configuration shown in FIG. 8 can be used.
  • the pitch circle diameter of the circular sun gear 81 is 5 mm
  • the pitch circle diameter of the circular planetary gear 82 is 17.5 mm
  • the pitch circle diameter of the circular internal gear 84 is 40 mm
  • the speed is reduced between the input shaft 85 and the rotating body 86.
  • a ratio of 9: 1 is achieved.
  • the input shaft 85 is rotated at 14,000 rpm (a non-anomalous speed of a prior art motor used with similar power tools)
  • the drive / reverse cycle occurs at 34 Hz.
  • the mechanism for limiting and preventing the cam-out phenomenon over a plurality of cycles has been described with reference to FIG. That is, in this embodiment, the bit and screw head separation in a given cycle is avoided by first rotating it forward by a small amount during each driving cycle. Furthermore, even if they begin to separate during driving, re-engagement can be facilitated by reverse rotation after the driving period. Further, it has been described that these operations are realized by a two-gear drive train or the like that is always meshed and installed in the non-circular gear box 18. However, further suitable improvements can be made to the above-described embodiments, for example, the output shaft between non-drive periods to avoid separating the tool member from the screw during the drive period.
  • the rotation angle is sufficiently small.
  • the reverse angle of the output shaft is configured to re-engage the tool member and the screw after a slight separation between the tool member and the screw during the driving period. is there. Such improvement makes it possible to reliably prevent the cam-out phenomenon.
  • FIG. 15 is shown as a modification of the embodiment shown in FIG.
  • the non-circular planetary gear 72 and the non-circular sun gear 75 are arranged on the output shaft 77 side, and the circular planetary gear 73 and the circular sun gear 76 are arranged on the input shaft 71 side.
  • a rotating body 78 is installed at the tip of the input shaft 71.
  • the planetary shaft 74 attached to the rotating body 78 performs planetary motion.
  • This planetary shaft 74 rotates freely about its own axis.
  • a non-circular planetary gear 72 and a circular planetary gear 73 are mounted on the planetary shaft 74. These gears 72 and 73 are connected and fixed to each other with respect to the planetary shaft 74.
  • the circular planetary gear 73 is rotated by the action of a circular sun gear 76 connected to the mechanical ground. Therefore, the non-circular planetary gear 72 is rotationally driven as the circular planetary gear 73 rotates. As a result, the non-circular planetary gear 72 drives the non-circular sun gear 75.
  • the output shaft 77 Since the output shaft 77 is connected to the non-circular sun gear 75, the output shaft 77 is rotationally driven as the non-circular sun gear 75 is rotationally driven. Note that the embodiment shown in FIG. 15 has the advantage that the balance of rotational motion is good because a plurality of non-circular planetary gears 72 are arranged so as to be symmetrical with respect to the non-circular sun gear 75. Yes.
  • FIG. 10 is a vertical cross-sectional right side view showing the overall configuration of the impact tool according to the present embodiment.
  • FIG. 11 is an exploded exploded perspective view of a main part for explaining a main part configuration of the impact tool according to the present embodiment.
  • FIG. 12 is a diagram showing a non-circular planetary gear according to the present embodiment
  • FIG. 13 is a diagram showing a non-circular sun gear with an output shaft according to the present embodiment. (B) in a figure has shown the cross section.
  • the impact tool 100 is a battery-type impact tool 100, and is detachably attached to a housing 110 that houses a drive source such as a motor 111 and a lower end portion of the housing 110. And a battery pack 130 for supplying driving power to the motor 111.
  • the housing 110 includes a housing upper body 110a that houses the drive mechanism 115 corresponding to the motor 111 and the non-circular gear box 18 according to the above-described embodiment, a housing central body 110b that receives a grip from the user, and a battery pack 130. And a housing lower body 110c having a connection mechanism. Power wiring is provided from the housing lower body 110 c to the housing upper body 110 a via the housing central body 110 b, so that driving power charged in the battery pack 130 can be supplied to the motor 111. Further, an operation switch 112 is provided on the upper front side of the housing central body 110b, and a user who holds the housing central body 110b can operate the operation switch 112 suitably.
  • the drive mechanism 115 installed in front of the motor 111 is a specific implementation of the mechanism of the present invention described with reference to FIGS. That is, the drive mechanism 115 according to the present embodiment includes a sun gear 181 connected to a motor shaft 111a included in the motor 111, two planetary gears 182 and 182 meshingly connected around the sun gear 181 and two planetary gears.
  • the gears 182 and 182 further include a circular internal gear 184 that surrounds the outer periphery.
  • the motor shaft 111a rotates by supplying electric power to the motor 111, the motor shaft 111a drives the sun gear 181.
  • the sun gear 181 acts on the two planetary gears 182 and 182, and the planetary gears 182 and 182 It moves in the circular internal gear 184 connected to the housing upper body 110a.
  • a rotating body 186 is installed in front of the two planetary gears 182 and 182.
  • the shaft 183 of the planetary gear 182 is connected to this rotating body 186 and provides rotational drive about the axis of the rotating body 186.
  • a planetary shaft 174 is installed at a position eccentric from the rotation center of the rotating body 186.
  • the planetary shaft 174 is installed in a form that is accommodated inside the rotating body 186, and both shaft ends of the planetary shaft 174 are bearings 174 a and 174 b such as needle bearings installed in the rotating body 186. It is pivotally supported by.
  • the planetary shaft 174 is provided with a circular planetary gear 173 at the front shaft end and a non-circular planetary gear 172 at the rear shaft end. These gears 172 and 173 are rigidly connected to each other, and can rotate freely around the axis of the planetary shaft 174.
  • the circular planetary gear 173 meshes with a circular sun gear 176 fixedly connected to the housing upper body 110a as a mechanical ground. That is, when the rotating body 186 is driven to rotate by the rotation of the two planetary gears 182 and 182, the planetary shaft 174 circulates around the circular sun gear 176, and as a result, the circular sun gear 176 that is fixedly installed.
  • the circular planetary gear 173 rotates and revolves around.
  • the non-circular planetary gear 172 is also rotated in the same manner. Since the non-circular planetary gear 172 meshes with the non-circular sun gear 175 connected to the output shaft 177, the non-circular sun gear 175 is rotationally driven in accordance with the rotational drive of the non-circular planetary gear 172, and as a result As a result, the output shaft 177 is rotationally driven. Note that the rotation axis center of the output shaft 177 connected to the non-circular sun gear 175 overlaps the rotation center axis of the rotating body 186.
  • the shaft end on the rear side of the output shaft 177 is supported by a bearing installed in the rotating body 186, and the shaft end on the front side is connected to the bit holder 179. Therefore, a tool such as a driver installed in the bit holder 179 rotates in accordance with the rotational drive of the output shaft 177 so that the work can be performed on the outside.
  • the rotating body 186 is rotationally driven in accordance with the planetary movement of the planetary gear 182, but the planetary shaft 174 installed therein is eccentrically installed. Further, the planetary shaft 174 is provided with weight members such as a non-circular planetary gear 172 and a circular planetary gear 173. Therefore, in order for the rotator 186 to preferably rotate, it is necessary to provide a balance weight for balancing with a weight member such as the planetary shaft 174. Therefore, in the rotating body 186 according to the present embodiment, as shown in FIG. 11, the balance body portion having a half structure at the center of the body of the rotating body and having a half structure at a position facing the installation position of the planetary shaft 174. The structure which provides 186a was employ
  • the motor shaft 111a is rotationally driven by the drive of the motor 111, and the rotational force of the motor shaft 111a rotates the sun gear 181.
  • the sun gear 181 rotates
  • the two planetary gears 182 and 182 installed between the sun gear 181 and the circular internal gear 184 perform planetary motion. Since the shaft 183 of the planetary gear 182 is connected to the rotating body 186, the rotating body 186 is rotationally driven by the planetary gears 182 and 182 performing planetary motion.
  • the circular planetary gear 173 is rotated by the action of the circular sun gear 176 fixedly connected to the housing upper body 110a. It is rotationally driven in the same manner as the planetary gear 173. Since the non-circular planetary gear 172 and the circular planetary gear 173 are installed with respect to the planetary shaft 174 installed inside the rotating body 186, the two gears 172 and 173 move around the axis of the planetary shaft 174. While rotating freely, the rotary body 186 rotates around the rotation center axis.
  • the non-circular planetary gear 172 that performs planetary movement is engaged with the non-circular sun gear 175, and the output shaft 177 is connected to the non-circular sun gear 175. Then, since the non-circular sun gear 175 rotates in accordance with the planetary motion of the non-circular planet gear 172, the rotational driving force is transmitted to the output shaft 177, and a predetermined torque can be applied to the outside. ing.
  • the output shaft 177 is caused by the action of the non-circular planetary gear 172 and the non-circular sun gear 175 which are two non-circular gears.
  • reverse operation is performed in a predetermined cycle period. By such an operation, a suitable effect such as prevention of come-out can be obtained.
  • the impact tool 100 has a configuration in which a mechanism as an impact tool is realized by a plurality of non-circular gears. It has the favorable advantage of low noise at times. This advantage is made clear by the analysis result of the comparative measurement of noise using the conventional impact tool and the impact tool 100 of the present embodiment shown in FIG. 14 and Table 1.
  • FIG. 14 is a diagram for explaining a noise measurement method.
  • the noise measurement method implemented this time is to measure the noise generated when a wood screw of ⁇ 4.5 ⁇ 90 mm is fastened to a test piece 190 made of dry rice pine (Dry Pine).
  • the measurement position of the noise was set to a position 1 m away from the impact tool with respect to the rear direction, left direction, upper direction, and lower direction of the impact tool.
  • an A characteristic frequency weighted sound pressure level (A weighted sound pressure level) is added.
  • the impact tool used for the noise measurement is an impact tool including the impact tool 100 according to the present embodiment described with reference to FIG. 10 and the like, the conventional hammer 10 represented by the above-mentioned Patent Document 1, and the like.
  • Table 1 shows the measurement results of noise measured based on the above conditions.
  • Table 1 is a table comparing noise measurement results under load.
  • the impact tool 100 according to the present example had a lower noise level at all measurement positions than the impact tool (impact driver) according to the prior art. Further, even when the average values of the measured noise results are compared, the impact tool 100 according to the present embodiment achieves lower noise with a difference of 5.0 dB (A), and the superiority of the present invention is achieved. confirmed.

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  • Portable Power Tools In General (AREA)

Abstract

La présente invention concerne un outil de percussion qui est un outil électrique conçu pour être relié à la terre dans une condition déterminée, et qui peut effectuer un mouvement rotatif dont la vitesse angulaire et/ou le couple varie(nt) périodiquement. L'outil de percussion est conçu de sorte que lorsque des engrenages (1, 2, 3, 4) ont respectivement des rayons de cercle primitif r1(ө), r2(ө), r3(ө) et r4(ө), ө représente la position angulaire d'un arbre planétaire (7) qui relie l'engrenage (2) et l'engrenage (3). Les rayons des engrenages (1, 2, 3, 4) se situent dans une plage angulaire d'au moins 0≤ө≤2Π. Une transmission est conçue de manière à satisfaire l'inégalité suivante : r1(ө).r3(ө)/r2(ө).r4(ө)>1, et par conséquent la direction de rotation d'un arbre de sortie est inversée pendant au moins une partie d'un cycle d'entraînement. L'outil de percussion permettant de résoudre les problèmes traditionnels, parmi lesquels un niveau de bruit élevé, des vibrations importantes, une grande perte et une abrasion importante, peut être fourni grâce à la configuration susmentionnée.
PCT/JP2010/003224 2009-05-20 2010-05-12 Outil de percussion WO2010134296A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201080016096.0A CN102387896B (zh) 2009-05-20 2010-05-12 冲击工具
JP2011514319A JP5496190B2 (ja) 2009-05-20 2010-05-12 インパクト工具

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
GBGB0908645.5A GB0908645D0 (en) 2009-05-20 2009-05-20 Impulse tool
GB0908645.5 2009-05-20
GB0915483.2 2009-09-07
GBGB0915483.2A GB0915483D0 (en) 2009-09-07 2009-09-07 Top up to impulse tool

Publications (1)

Publication Number Publication Date
WO2010134296A1 true WO2010134296A1 (fr) 2010-11-25

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PCT/JP2010/003224 WO2010134296A1 (fr) 2009-05-20 2010-05-12 Outil de percussion

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Country Link
JP (1) JP5496190B2 (fr)
CN (2) CN103753469B (fr)
WO (1) WO2010134296A1 (fr)

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CN104546438B (zh) * 2015-02-12 2016-05-18 王丽媛 足底按摩器
JP6868851B2 (ja) * 2017-01-31 2021-05-12 パナソニックＩｐマネジメント株式会社 インパクト回転工具

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JP2008055580A (ja) * 2006-09-01 2008-03-13 Estic Corp インパクト式のネジ締め装置

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JP2000176851A (ja) * 1998-12-17 2000-06-27 Mitsubishi Heavy Ind Ltd 回転作業装置
JP2008055580A (ja) * 2006-09-01 2008-03-13 Estic Corp インパクト式のネジ締め装置
JP2008057747A (ja) * 2006-09-04 2008-03-13 Estic Corp 遊星歯車装置およびインパクト式のネジ締め装置

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TWI461261B (fr) * 2013-10-31 2014-11-21

Also Published As

Publication number Publication date
CN103753469B (zh) 2015-12-30
CN102387896B (zh) 2014-05-21
JPWO2010134296A1 (ja) 2012-11-08
CN103753469A (zh) 2014-04-30
CN102387896A (zh) 2012-03-21
JP5496190B2 (ja) 2014-05-21

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