EP1637289A1 - Verfahren zur Herstellung eines Kraftwerkzeugs - Google Patents

Verfahren zur Herstellung eines Kraftwerkzeugs Download PDF

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Publication number
EP1637289A1
EP1637289A1 EP04021706A EP04021706A EP1637289A1 EP 1637289 A1 EP1637289 A1 EP 1637289A1 EP 04021706 A EP04021706 A EP 04021706A EP 04021706 A EP04021706 A EP 04021706A EP 1637289 A1 EP1637289 A1 EP 1637289A1
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EP
European Patent Office
Prior art keywords
vibration
counter weight
power tool
driving conditions
electric hammer
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP04021706A
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English (en)
French (fr)
Other versions
EP1637289B1 (de
Inventor
Takuo c/o Makita Corporation Arakawa
Hiroki c/o Makita Corporation Ikuta
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Makita Corp
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Makita Corp
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Filing date
Publication date
Application filed by Makita Corp filed Critical Makita Corp
Priority to DE200460003383 priority Critical patent/DE602004003383T8/de
Priority to EP20040021706 priority patent/EP1637289B1/de
Publication of EP1637289A1 publication Critical patent/EP1637289A1/de
Application granted granted Critical
Publication of EP1637289B1 publication Critical patent/EP1637289B1/de
Active legal-status Critical Current
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/24—Damping the reaction force
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/12—Means for driving the impulse member comprising a crank mechanism
    • B25D11/125—Means for driving the impulse member comprising a crank mechanism with a fluid cushion between the crank drive and the striking body
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/003—Crossed drill and motor spindles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0073—Arrangements for damping of the reaction force
    • B25D2217/0076—Arrangements for damping of the reaction force by use of counterweights
    • B25D2217/0088—Arrangements for damping of the reaction force by use of counterweights being mechanically-driven

Definitions

  • the present invention relates to a technique of manufacturing a power tool such as a hammer and a hammer drill to drive a tool bit at a predetermined cycle.
  • Japanese laid-open utility model publication No. 51-6583 discloses an electric hammer with a vibration reducing device.
  • This known electric hammer includes a motion converting mechanism that converts a rotating output of a driving motor in order to drive a tool bit that performs a hammering operation on a workpiece, and a striker that reciprocates via the motion converting mechanism. Further, in order to reduce vibration acting on the electric hammer, a counter weight is provided and driven in a direction opposite to the reciprocating direction of the striker.
  • the counter weight is thus designed to reduce vibration of the electric hammer by moving in a direction opposite to the moving direction of the striker.
  • the properties of vibration exerted to the electric hammer under loaded driving conditions in which the tool bit receives a load by performing the operation are different from those under unloaded driving conditions in which the tool bit does not receive a load. Due to such difference, the counter weight designed to perform a vibration reducing function under loaded driving conditions, may not be able to perform an appropriate vibration reducing function under unloaded driving conditions. It is therefore desired to reduce vibration of an electric hammer as much as possible under each operating condition.
  • an object of the invention to provide a technique for optimizing a vibration reducing mechanism of a power tool.
  • Such power tool may include a tool bit, a driving motor, driving force transmitting mechanism and a counter weight.
  • the tool bit performs a predetermined processing operation to a workpiece by a reciprocating movement.
  • the driving motor drives the tool bit.
  • the driving force transmitting mechanism converts a rotating output of the driving motor to a reciprocating movement and transmits the reciprocating movement to the tool bit.
  • the counter weight reduces a vibration caused in the power tool by reciprocating in a direction opposite to a component of linear motion of the driving force transmitting mechanism.
  • the representative method may include a step of determining the mass and travel of the counter weight based on the magnitudes of vibration caused in the power tool under loaded driving conditions in which the tool bit receives a load by performing the processing operation and under unloaded driving conditions in which the tool bit does not receive a load by performing the processing operation.
  • the representative method according to the invention is configured to determine the mass and travel of the counter weight based on the magnitudes of vibration caused in the power tool under loaded driving conditions in which the tool bit receives a load by performing the operation and under unloaded driving conditions in which the tool bit does not receive a load by performing the operation.
  • vibration reducing mechanism of the power tool can be optimized.
  • the "loaded driving conditions” in this invention typically corresponds to the conditions in which the operation is performed by a tool bit being pressed against a workpiece.
  • the “unloaded driving conditions” in this invention typically corresponds to the conditions in which the tool bit is not in contact with the workpiece and the power tool is idled.
  • the "magnitude of vibration" caused in the power tool may widely include indexes relating to vibration caused in the power tool, such as acceleration and stress that act on the power tool, as well as frequency of vibration.
  • a coordinate system such as three X-, Y-, Z-axis, cylindrical or polar coordinates system, can be appropriately used.
  • the counter weight is typically driven to reciprocate by a crank mechanism.
  • the "kinetic energy of the counter weight” in this invention is obtained based on the value of the mass of the counter weight being multiplied by the travel of the counter weight.
  • the "travel of the counter weight” in this case can be defined by the eccentricity between the center of rotation of the counter weight and the counter weight mounting point.
  • the manner in which a difference between the magnitudes of vibration under loaded and unloaded driving conditions is "within a predetermined range" includes the manner in which the magnitudes of vibration are substantially the same therebetween, as well as the manner in which the difference is smaller than a predetermined amount
  • an electric hammer 121 to be manufactured in this representative embodiment mainly comprises a body 123 that defines the contours of the electric hammer 101.
  • the body 123 includes a motor housing 125, a gear housing 127 and a tool holder 129.
  • a hammer bit 137 is disposed in the tip end region of the body 123.
  • the hammer bit 137 is a feature that corresponds to the "tool bit" according to the invention.
  • the motor housing 125 houses a driving motor 131
  • the gear housing 127 houses a motion converting mechanism 133 and a striking mechanism 135.
  • the motion converting mechanism 133 is adapted to convert the rotating output of the driving motor 131 to linear motion.
  • the motion converting mechanism 113 mainly includes a crank arm 134 that converts the rotation of an output shaft 132 of the driving motor 131 to linear motion in the axial direction of the hammer bit 137.
  • a driver 135b slidingly reciprocates within a cylinder 135a.
  • a striker 138 is caused to reciprocate within the cylinder 135a at a speed higher than the sliding speed of the driver 135b by the action of an air spring which is caused within the cylinder 135a by sliding movement of the driver 135b.
  • an impact force is applied to the hammer bit 137 so that the hammer bit 137 performs a hammering operation.
  • the driving mechanism of the hammer bit 137 is well known and therefore will not be explained in greater detail.
  • a counter weight 139 is connected to the motion convecting mechanism 133.
  • the counter weight 139 reciprocates with a 180° phase shift with respect to the reciprocating movement of the striker 138.
  • a mounting portion 139a of the counter weight 139 is located a predetermined distance apart from the center of a driving shaft 140 of the counter weight 139.
  • the radius of the revolving movement is identical to the horizontal distance between the center of a driving shaft 134a of the crank arm 134 and the mounting portion 139a of the counter weight 139, which is set to be a distance "r".
  • the crank arm 134 rotates around the driving shaft 134a
  • the counter weight 139 linearly moves the distance "2r” in the axial direction of the hammer bit 137.
  • the counter weight 139 reciprocates in a direction opposite to the reciprocating direction of the striker 138 which reciprocates to cause the hammer bit 137 to perform the hammering operation.
  • a computer-aided manufacturing system for the electric hammer 121 mainly includes a controller 103, and a ROM 105, a RAM 107, an acceleration detector 109, a correlation output section 111 and an optimum value output section 113 which are connected to the controller 103.
  • a first driving condition is defined as loaded driving conditions (designated by (A) in FIG. 2) in which the hammer bit 137 is in contact with the workpiece W and the user provides pushing force to press the electric hammer 121 toward the workpiece W, so that the hammer bit 137 receives a load, in the form of a reaction force Fw, from the workpiece W by performing a hammering operation.
  • a second driving condition is defined as unloaded driving conditions (designated by (B) in FIG. 2) in which the hammer bit 137 is not in contact with the workpiece W and the hammer bit 137 does not receive a load in the hammering operation.
  • a gauge for measuring acceleration on appropriate X, Y and Z axes is provided in the body of the electric hammer 121.
  • the detected value of the acceleration is inputted into the controller 103 via the acceleration detector 109.
  • the controller 103 combines the accelerations in the direction of each axis and executes a predetermined frequency correction, and then produces three-axis combined frequency-corrected acceleration data (in m/sec 2 ).
  • the ROM 105 stores index data relating to the mass value (in gram) and the travel (in mm) of the counter weight 139. Further, the ROM 105 stores a program for determining an optimum value for the counter weight 139 based on the index data and the above-mentioned acceleration data.
  • the correlation between the acceleration caused in the electric hammer 121 under loaded and unloaded driving conditions and the kinetic energy of the counter weight 139 is outputted to the correlation output section 111 in the form of a graph, of which example is shown in FIG. 3. Further, based on such correlation, an optimum design which can ensure the vibration reducing function of the electric hammer 121 as much as possible is outputted to the optimum value output section 113.
  • acceleration of vibration caused by the reciprocating movement of the counter weight 139 is defined as; ( mc / M ) ⁇ r w 2 sin ( wt + ⁇ )
  • acceleration of vibration caused in the electric hammer 121 in the axial direction of the hammer bit 137 under unloaded driving conditions is defined as; ( mc / M ) ⁇ r w 2 sin ( wt + ⁇ ) + ANL ( t ; ) wherein ANL (t) represents acceleration in the axial direction of the hammer bit 137 caused by the reciprocating movement of the crank arm 134, the driving motor 131 or the connecting rod under unloaded driving conditions.
  • acceleration of vibration which is caused by the reciprocating movement of the striker 135b is defined as; ( 1 / M ) ⁇ d / dt ( ms ⁇ vs )
  • acceleration of vibration which is caused in the electric hammer 121 in the axial direction of the hammer bit 137 under loaded driving conditions: ( 1 / M ) ⁇ d / dt ( ms ⁇ vs ) + ( mc / M ) ⁇ r w 2 sin ( wt + ⁇ ) + AL ( t ) ; wherein AL (t) represents acceleration in the axial direction of the hammer bit 137 caused by the reciprocating movement of the crank ann 134, the driving motor 131 or the connecting rod under loaded driving conditions.
  • the electric hammer 121 under loaded driving conditions and the electric hammer 121 under unloaded driving conditions are connected to the acceleration detector 109 of the computer-aided manufacturing system 101 shown in FIG. 2.
  • Two electric hammers 121 under the different driving conditions may be prepared and connected.
  • one electric hammer 121 may be connected and switched between the driving conditions as necessary.
  • one electric hammer 121 is connected to the computer-aided manufacturing system 101 and measurements are made on the hammer by switching it between loaded and unloaded driving conditions.
  • step S1 a value of "mc ⁇ r", or a value of the mass "mc" of the counter weight 139 of the electric hammer 121 multiplied by the radius "r" (corresponding half the distance "2r” between the driving shaft 140 of the counter weight 139 and the mounting portion 139a) of the revolving movement of the driving shaft 140 of the counter weight 139, is obtained from the ROM 105.
  • the value is used as an index relating to the kinetic energy of the counter weight 139.
  • the acceleration of vibration which is caused in the electric hammer 121 by the reciprocating movement of the counter weight 139 can be defined as "(mc/M) ⁇ rw 2 sin (wt + ⁇ )", and further, mass “M” of the electric hammer 121 is defined as steady-state value. Therefore, in this embodiment, the value of "mc ⁇ r" is used as an index relating to the kinetic energy of the counter weight 139. As shown in FIG. 3, in this embodiment, the value of "mc ⁇ r" is stored in the ROM 105 as a variable ranging from 0.0 to 4000.0.
  • step S2 the value of acceleration of vibration in the electric hammer 121 under loaded driving conditions is obtained (step S2).
  • the vibration acceleration value is obtained based on the measured value via the acceleration detector 10 shown in FIG. 2.
  • step S3 the value of acceleration of vibration in the electric hammer 121 under unloaded driving conditions is obtained (step S3).
  • the index (mass and eccentricity) relating to the kinetic energy of the counter weight 139 obtained in step S1 is adopted in the electric hammer 121, and accelerations caused by vibration of the electric hammer 121 under loaded and unloaded driving conditions are measured.
  • accelerations caused by vibration of the electric hammer 121 under loaded and unloaded driving conditions are measured with respect to each of the varied values of "mc ⁇ r" relating to the kinetic energy of the counter weight 139.
  • the acceleration values are stored in the RAM 107 one after another. This process is repeatedly continued until the value of "mc ⁇ r" reaches 4000.0 (step S4).
  • the change of accelerations of the electric hammer 121 under loaded and unloaded driving conditions with respect to the value of "mc ⁇ r" which is appropriately changed from 0.0 to 4000.0 is outputted to the correlation output section 111 (see FIG. 2) in the form of a graph shown in FIG. 3.
  • the plot (shown in the form of a set of plotted rhombic points in FIG. 3) of change of acceleration of the electric hammer 121 under unloaded driving conditions is shown uprising generally linearly when the value of "mc ⁇ r" is gradually increased.
  • a set value of acceleration is determined in step S5 of the program shown in FIG. 4.
  • the "set value of acceleration” is related to the acceleration value at the intersection of the plot FL of change of acceleration of the electric hammer 121 under loaded driving conditions and the plot FNL of change of acceleration of the electric hammer 121 under unloaded driving conditions, which plots are obtained by varying the value of "mc ⁇ r". This intersection is shown by S in FIG. 3.
  • the region of the intersection of the two plots can be defined as a region in which the vibration acceleration of the electric hammer 121 under loaded and unloaded driving conditions can be minimized in a manner of obtaining a greatest common divisor.
  • the controller 103 determines the set value of acceleration to be approximately 8.0 m/sec 2 and the value "mc ⁇ r" in the region of the intersection to be approximately 1000.0 g ⁇ mm.
  • optimum mass and the optimum eccentricity of the counter weight 139 are determined. Specifically, on the premises that the set value of acceleration and the value "mc ⁇ r" at the set acceleration value have been determined as mentioned above, the optimum mass and the optimum eccentricity of the counter weight 139 which satisfy the value "mc ⁇ r" are determined.
  • the optimum mass and the optimum eccentricity of the counter weight 139 are appropriately determined considering design constraints relating to the distance between the center of the driving shaft 140 of the counter weight 139 and the mounting portion 139a of the counter weight 139 in the electric hammer 121 (or the radius of revolution of the driving shaft 140 of the counter weight 139).
  • the optimum mass is 115 g and the optimum eccentricity is 9 mm, based on the value "mc ⁇ r" which has been determined to be approximately 1000.0 g ⁇ mm.
  • the optimum values of the mass "mc" of the counter weight 139 and the "eccentricity" of the clank arm 134 with respect to the counter weight 139 are determined based on the magnitude of vibrations caused in the electric hammer 121 under loaded and unloaded driving conditions.
  • Such system can facilitate optimized designing of the vibration reducing mechanism of the electric hammer 121.
  • the set value of acceleration is defined as an acceleration value in the region in which the vibration acceleration which acts on the electric hammer 121 under loaded driving conditions is about the same as that under unloaded driving conditions.
  • the set value of acceleration may be determined to be a value in the region in which a difference between the accelerations under loaded and unloaded driving conditions is within a predetermined range.
  • the set value of acceleration may be determined to be a value in the region which is slightly shifted to the side where acceleration under loaded driving conditions is lower than in the region in which acceleration is about the same as that under unloaded driving conditions. For example, in the case as shown in FIG. 3, acceleration under loaded driving conditions is further reduced in the region in which the value "mc ⁇ r" is slightly larger than that at the intersection S. Therefore, the set value of acceleration can be determined to be a value in this region.
  • the manufacturing method of this invention is applied to an electric hammer, but it may also be applied to other power tools, such as a reciprocating saw.
  • mean vibration caused in the electric hammer 121 is determined based on the plot FL reflecting the change of acceleration of the electric hammer 121 under loaded driving conditions and the plot FNL reflecting the change of acceleration of the electric hammer 121 under unloaded driving conditions.
  • the sum of a value obtained by multiplying the acceleration of the electric hammer 121 under loaded driving conditions by a first constant A and a value obtained by multiplying the acceleration of the electric hammer 121 under unloaded driving conditions by a second constant B is defined as the mean vibration MV in the electric hammer 121.
  • minimum zone in which the mean vibration MV is substantially at the minimum on the curve is determined.
  • the range of about 1200 to 1600 g ⁇ mm of the set value "mc ⁇ r" of acceleration is specifically defined as the minimum zone.
  • the mean vibration MV of the electric hammer 121 is at the minimum of about 7.7 to 7.8 m/sec 2 .
  • the optimum set value of acceleration is determined to be within the minimum zone of the value "mc ⁇ r" of about 1200 to 1600 g - mm, and specifically to be 1400 g - mm. Based on such determination, the optimum mass and optimum eccentricity of the counter weight 139 in manufacturing the electric hammer are determined to be 140 g and 10 mm, respectively. It is explicitly stated that all features disclosed in the description and/or the claims are intended to be disclosed separately and independently from each other for the purpose of original disclosure as well as for the purpose of restricting the claimed invention independent of the composition of the features in the embodiments and/or the claims. It is explicitly stated that all value ranges or indications of groups of entities disclose every possible intermediate value or intermediate entity for the purpose of original disclosure as well as for the purpose of restricting the claimed invention, in particular as limits of value ranges.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
EP20040021706 2004-09-13 2004-09-13 Verfahren zur Herstellung eines Kraftwerkzeugs Active EP1637289B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE200460003383 DE602004003383T8 (de) 2004-09-13 2004-09-13 Verfahren zur Herstellung eines Kraftwerkzeugs
EP20040021706 EP1637289B1 (de) 2004-09-13 2004-09-13 Verfahren zur Herstellung eines Kraftwerkzeugs

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Application Number Priority Date Filing Date Title
EP20040021706 EP1637289B1 (de) 2004-09-13 2004-09-13 Verfahren zur Herstellung eines Kraftwerkzeugs

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EP1637289A1 true EP1637289A1 (de) 2006-03-22
EP1637289B1 EP1637289B1 (de) 2006-11-22

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1832394A1 (de) * 2006-03-07 2007-09-12 Hitachi Koki Co., Ltd. Schlagwerkzeug mit Mechanismus zur Vibrationskontrolle
WO2008140030A3 (en) * 2007-05-01 2008-12-31 Hitachi Koki Kk Reciprocating tool
CN102161196A (zh) * 2010-02-23 2011-08-24 罗伯特·博世有限公司 外部减振器
CN101646529B (zh) * 2007-05-01 2013-06-26 日立工机株式会社 往复运动工具
EP3184259A1 (de) * 2015-12-25 2017-06-28 Makita Corporation Schlagwerkzeug
CN111300347A (zh) * 2018-12-12 2020-06-19 南京德朔实业有限公司 往复锯

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2464158C2 (ru) * 2007-05-01 2012-10-20 Хитачи Коки Ко., Лтд. Ручная машина с возвратно-поступательным движением рабочего органа

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1994002755A1 (de) * 1992-07-23 1994-02-03 Kaufmann, Peter Schwingungsdämpfer
EP1415768A1 (de) * 2002-10-31 2004-05-06 Atlas Copco Electric Tools GmbH Schwingungstilger
EP1439038A1 (de) * 2003-01-16 2004-07-21 Makita Corporation Elektrischer Hammer

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1994002755A1 (de) * 1992-07-23 1994-02-03 Kaufmann, Peter Schwingungsdämpfer
EP1415768A1 (de) * 2002-10-31 2004-05-06 Atlas Copco Electric Tools GmbH Schwingungstilger
EP1439038A1 (de) * 2003-01-16 2004-07-21 Makita Corporation Elektrischer Hammer

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1832394A1 (de) * 2006-03-07 2007-09-12 Hitachi Koki Co., Ltd. Schlagwerkzeug mit Mechanismus zur Vibrationskontrolle
US7513317B2 (en) 2006-03-07 2009-04-07 Hitachi Koki Co., Ltd. Impact tool with vibration control mechanism
WO2008140030A3 (en) * 2007-05-01 2008-12-31 Hitachi Koki Kk Reciprocating tool
AU2008250208B2 (en) * 2007-05-01 2012-02-16 Hitachi Koki Co., Ltd. Reciprocating tool
US8261854B2 (en) 2007-05-01 2012-09-11 Hitachi Koki Co., Ltd Reciprocating tool
TWI393615B (zh) * 2007-05-01 2013-04-21 Hitachi Koki Kk 往復動工具
CN101646529B (zh) * 2007-05-01 2013-06-26 日立工机株式会社 往复运动工具
CN102161196A (zh) * 2010-02-23 2011-08-24 罗伯特·博世有限公司 外部减振器
EP3184259A1 (de) * 2015-12-25 2017-06-28 Makita Corporation Schlagwerkzeug
CN111300347A (zh) * 2018-12-12 2020-06-19 南京德朔实业有限公司 往复锯
CN111300347B (zh) * 2018-12-12 2023-11-07 喜利得股份公司 往复锯

Also Published As

Publication number Publication date
DE602004003383D1 (de) 2007-01-04
DE602004003383T2 (de) 2007-10-04
EP1637289B1 (de) 2006-11-22
DE602004003383T8 (de) 2008-01-17

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