EP1980371A1 - Impact tool - Google Patents
Impact tool Download PDFInfo
- Publication number
- EP1980371A1 EP1980371A1 EP07707646A EP07707646A EP1980371A1 EP 1980371 A1 EP1980371 A1 EP 1980371A1 EP 07707646 A EP07707646 A EP 07707646A EP 07707646 A EP07707646 A EP 07707646A EP 1980371 A1 EP1980371 A1 EP 1980371A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- striking
- tool
- impact
- tool bit
- mechanisms
- 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
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Classifications
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- 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
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- 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
- B25D17/06—Hammer pistons; Anvils ; Guide-sleeves for pistons
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- 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
- B25D17/08—Means for retaining and guiding the tool bit, e.g. chucks allowing axial oscillation of the tool bit
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- 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
- B25D2216/00—Details of portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
- B25D2216/0007—Details of percussion or rotation modes
- B25D2216/0015—Tools having a percussion-only mode
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2216/00—Details of portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
- B25D2216/0007—Details of percussion or rotation modes
- B25D2216/0023—Tools having a percussion-and-rotation mode
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- 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
- B25D2217/0011—Details of anvils, guide-sleeves or pistons
- B25D2217/0023—Pistons
- B25D2217/0026—Double pistons
-
- 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
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
- B25D2250/275—Tools having at least two similar components
Definitions
- the present invention relates to an impact tool in which a tool bit performs a predetermined operation by striking movement in its axial direction.
- An impact tool in the form of an electric hammer in which a tool bit is driven by a motor and performs a predetermined operation by striking movement in its axial direction.
- Such an electric hammer is disclosed, for example, in Japanese non-examined laid-open Patent Publication No. 2005-335046 .
- a crank mechanism converts the rotating output of a motor into linear motion of a piston, and a striking element is caused to reciprocate by the action of an air spring or pressure fluctuations of air within an air chamber as a result of reciprocating movement of a piston and thereby strikes the tool bit.
- an object of the present invention to provide an effective technique for improving the working efficiency of an impact tool.
- the present invention provides an impact tool including a motor, a first motion converting mechanism, a first striking mechanism, a second motion converting mechanism, a second striking mechanism and a tool bit member.
- the first motion converting mechanism converts a rotating output of the motor into linear motion, and the first striking mechanism is driven by the first motion converting mechanism and thereby performs linear motion.
- the second motion converting mechanism converts a rotating output of the motor into linear motion, and the second striking mechanism is driven by the second motion converting mechanism and thereby performs linear motion.
- the tool bit member is struck by the first and second striking mechanisms and thereby reciprocates and performs a predetermined operation on a workpiece.
- the tool bit member is struck alternately by the striking mechanisms.
- the "impact tool” in this invention typically represents an electric hammer in which a tool bit member performs a hammering operation on a workpiece solely by linear striking movement in the axial direction, or an electric hammer drill in which a tool bit member performs a hammer drill operation on a workpiece by striking movement in the axial direction and rotation around its axis.
- the "first motion converting mechanism” and the “second motion converting mechanism” typically represent a mechanism that converts the rotating output of the motor into linear motion of a piston by a crank mechanism, but they are not limited to this.
- the first and second motion converting mechanisms also suitably include a mechanism that converts rotation of a rotating body rotated by the motor, into swinging motion of a swinging member and thereafter converts the swinging motion of the swinging member into linear motion of the piston, and a mechanism that converts rotation of the motor into linear motion of the piston by using a swash plate which is rotated by the motor.
- first striking mechanism and the “second striking mechanism” typically represent a construction that includes a striking element which is caused to reciprocate by pressure fluctuations of air within an air chamber as a result of reciprocating movement of a piston, and an intermediate element which transmits the reciprocating movement of the striking element to the tool bit member, but they also suitably includes a construction without the intermediate element.
- the impact tool includes the "first and second motion converting mechanisms". This means that the impact tool has at least two motion converting mechanisms. In addition to the first and second motion converting mechanisms, it may suitably include a third motion converting mechanism and further a fourth converting mechanism.
- the impact tool includes the "first and second striking mechanisms” in this invention, which means that the impact tool has at least two striking mechanisms. In addition to the first and second striking mechanisms, it may suitably include a third striking mechanism and further a fourth striking mechanism.
- the "tool bit member" in this invention may be suitably formed either by a single tool bit or by a plurality of tool bits.
- a single tool bit may be struck by a plurality of striking mechanisms, or a plurality of tool bits may be struck by the same number of striking mechanisms as the plurality of tool bits, or a plurality of tool bits may be struck by a larger number of striking mechanisms than the plurality of tool bits, or a plurality of tool bits may be struck by a smaller number of striking mechanisms than the plurality of tool bits. Either of these constructions is suitably applied in this invention.
- the tool bit member is struck by the first motion converting mechanism which is driven by the motor and the first striking mechanism and by the second motion converting mechanism which is driven by the motor and the second striking mechanism, and thereby performs a predetermined operation. Therefore, compared with a known impact tool in which a single motion converting mechanism and a single striking mechanism are used to drive the tool bit member, the operating efficiency is improved. In other words, if the number of strokes of the tool bit member per unit time is set to be equal to that of the known impact tool, the rotational speed of the motor and the driving speeds of the motion converting mechanisms and the striking mechanisms can be decreased. As a result, wear of a sliding part can be reduced and thus the durability can be improved without a decrease in operating efficiency.
- the first and second striking mechanisms are configured to perform linear motion in a direction opposite to each other. Therefore, when one striking mechanism strikes the tool bit member, the other striking mechanism linearly moves in a direction opposite to the one striking mechanism.
- the first and second striking mechanisms function as a counter weight with respect to each other.
- the first striking mechanism has a cylindrical first striking element that performs linear motion so as to drive the tool bit member.
- the second striking mechanism has a cylindrical second striking element that performs linear motion so as to drive the tool bit member, and the second striking element has generally the same mass as the first striking element.
- the first and second striking elements are configured to perform linear motion in a direction opposite to each other.
- the first and second striking mechanisms are disposed one above the other in parallel. With this construction, the driving balance of the impact tool can be further improved.
- FIG. 1 is a sectional side view schematically showing an entire electric hammer 101 as a first embodiment of the impact tool according to the present invention.
- the electric hammer 101 of this embodiment mainly includes a body 103 that forms an outer shell of the electric hammer 101, a single hammer bit 163 detachably coupled to the tip end region (on the left side as viewed in FIG.
- the hammer bit 119 is a feature that corresponds to the "tool bit member" according to the present invention.
- the side of the hammer bit 119 is taken as the front side and the side of the handgrip 109 as the rear side.
- the body 103 mainly includes a motor housing 105 that houses a driving motor 111, and a gear housing 107 that houses first and second crank mechanisms 113, 115 and first and second striking mechanisms 117, 119.
- the rotating output of the driving motor 111 is appropriately converted into linear motion via the first and second crank mechanisms 113, 115 and transmitted to the striking mechanisms 117, 119. Then, an impact force is generated in the axial direction of the hammer bit 163 via the striking mechanisms 117, 119.
- the driving motor 111 is a feature that corresponds to the "motor” according to this invention.
- the first and second crank mechanisms 113 and 115 are features that correspond to the "first motion converting mechanism” and the “second motion converting mechanism", respectively, according to this invention.
- the first and second striking mechanisms 117 and 119 are features that correspond to the "first striking mechanism” and the “second striking mechanism”, respectively, according to this invention.
- the driving motor 111 is driven when a trigger 109a on the handgrip 109 is de
- FIG. 2 shows an essential part of the hammer 101 in enlarged sectional view
- FIG. 3 is a sectional view taken along line A-A in FIG. 2
- the first and second crank mechanisms 113 and 115 are disposed one above the other in parallel within the gear housing 107.
- the first crank mechanism 113 includes a first crank plate 125 that can rotate in a horizontal plane, a first eccentric shaft 127 that is disposed in a position displaced from the center of rotation of the first crank plate 125, and a first crank arm 129 loosely connected at one end to the first eccentric shaft 127, and a first driving element in the form of a first piston 133 mounted to the other end of the first crank arm 129 via a first connecting shaft 131.
- the first crank plate 122 is circular and has a driven gear 125a on the outer peripheral surface.
- the driven gear 125a engages with a driving gear 121 that is rotationally driven by the driving motor 111.
- the first piston 133 is slidably disposed within a first bore 151 a of a cylinder 151, and when the driving motor 111 is driven, the first piston 133 reciprocates in the axial direction of the cylinder 151 (in the axial direction of the hammer bit).
- the second crank mechanism 113 includes a second crank plate 137 that can rotate in a horizontal plane, a second eccentric shaft 139 that is disposed in a position displaced from the center of rotation of the second crank plate 137, and a second crank arm 141 loosely connected at one end to the second eccentric shaft 139, and a second driving element in the form of a second piston 145 mounted to the other end of the second crank arm 141 via a second connecting shaft 143.
- the second piston 145 is slidably disposed within a second bore 151b of the cylinder 151.
- the axis of rotation of the first crank plate 125 coincides with the axis of rotation of the second crank plate 137. Further, the amount of displacement of the first eccentric shaft 127 from the center of rotation of the first crank plate 125 is equal to the amount of displacement of the second eccentric shaft 139 from the center of rotation of the second crank plate 137. Further, the first eccentric shaft 127 is connected to the second eccentric shaft 139 by a connecting member 147 with a phase difference of about 180° in the direction of rotation of the first crank plate 125. Specifically, the second crank mechanism 115 is driven via the connecting member 147 by the first crank mechanism 113 that is driven by the driving motor 111. The second piston 145 then reciprocates in a direction opposite to the first piston 133 with a delay of about 180° crank angle with respect to the first piston 133.
- the first and second striking mechanisms 117 and 119 are disposed one above the other in parallel.
- the first striking mechanism 117 includes a first striking element in the form of a first striker 153 that is slidably disposed within the first bore 151a of the cylinder 151 and reciprocates in the axial direction of the cylinder 151, and an intermediate element in the form of an impact bolt 157 that is slidably disposed within the cylindrical tool holder 161 and transmits the kinetic energy of the first striker 153 to the hammer bit 163.
- the first striker 153 is driven via the action of an air spring or pressure fluctuations of air within a first air chamber 151 c as a result of sliding movement of the first piston 133.
- the first striker 153 then collides with (strikes) the impact bolt 157 and transmits the striking force to the hammer bit 163 held by the tool holder 161, via the impact bolt 157. Specifically, the first striking mechanism 117 is driven by the first crank mechanism 113.
- the second striking mechanism 119 includes a second striking element in the form of a second striker 155 that is slidably disposed within the second bore 151b of the cylinder 151 and reciprocates in the axial direction of the cylinder 151, and the above-described impact bolt 157.
- the second striker 155 is driven via the action of an air spring within a second air chamber 151 d as a result of sliding movement of the second piston 145.
- the second striker 155 then collides with (strikes) the impact bolt 157 and transmits the striking force to the hammer bit 163 held by the tool holder 161, via the impact bolt 157.
- the second striking mechanism 119 is driven by the second crank mechanism 115.
- the impact bolt 157 has an axial rear end having a strike surface 157a that is large enough to receive the striking movement of the first striker 153 on its radially lower region and to receive the striking movement of the second striker 155 on its radially upper region.
- the cylinder 151 includes the circular first bore 151a in which the first piston 133 and the first striker 153 are slidably disposed, and the circular second bore 151b in which the second piston 145 and the second striker 155 are slidably disposed.
- the cylinder 151 is mounted to the gear housing 107 such that it is locked against movement in its axial and circumferential directions.
- the cross section structure of the cylinder 151 is shown in FIG. 3 .
- the tool holder 161 is mounted to the front end of the gear housing 107 such that it is locked against movement in its axial and circumferential directions.
- the hammer bit 163 is held by the tool holder 161 such that it is allowed to move in the axial direction with respect to the tool holder 161.
- the first striker 153 is caused to reciprocate within the cylinder 151 by pressure fluctuations of air or the action of the air spring within the first air chamber 151 c.
- the first striker 153 then collides with the impact bolt 157 and thereby transmits the kinetic energy (striking force) to the hammer bit 163.
- the hammer bit 163 slides within the tool holder 161 and performs a hammering operation on the workpiece.
- the second crank mechanism 115 when the first eccentric shaft 127 is caused to revolve by rotation of the first crank plate 125, the second eccentric shaft 139 is caused to revolve on the rotation axis of the second crank plate 137 via the connecting member 147. As a result, the second crank arm 141 is caused to swing, and the second piston 145 is caused to slide within the second bore 151 b of the cylinder 151. In this embodiment, a phase difference of about 180° crank angle is provided between the first eccentric shaft 127 and the second eccentric shaft 139. Therefore, the second piston 145 is caused to linearly slide within the second bore 151b of the cylinder 151 with a delay of about 180° crank angle with respect to the first piston 133.
- the second striker 155 When the second piston 145 slides from the non-compressing side to the hammer bit 163 side, the second striker 155 is caused to reciprocate within the cylinder 151 by the action of the air spring within the second air chamber 151d which is caused by the sliding movement of the second piston 145. The second striker 155 then collides with the impact bolt 157 and thereby transmits the kinetic energy (striking force) to the hammer bit 163.
- the hammer bit 163 slides within the tool holder 161 and performs a hammering operation on the workpiece.
- the single hammer bit 163 can perform two strokes of striking movement in one turn of the crank. Therefore, compared with a known electric hammer which provides one stroke of striking movement in one crank turn, the number of strokes of the hammer bit 163 is doubled if the number of revolutions of the driving motor 111 is set to be identical to that of the known hammer. Therefore, the operating efficiency is improved. From an alternative point of view, if the number of strokes of the hammer bit 163 per unit time is set to be equal to that of the known hammer, the rotational speed of the driving motor 111 and the driving speeds of the first and second crank mechanisms 113, 115 and the first and second striking mechanisms 117, 119 can be decreased. As a result, wear of a sliding member or a sliding part such as an O-ring can be reduced and thus the durability can be improved without a decrease in operating efficiency.
- the first piston 133 and the second piston 145 are driven with a phase difference of about 180° crank angle.
- the first striker 153 and the second striker 15 5 reciprocates in a direction opposite to each other. Therefore, when one striker or, for example, the first striker 153 linearly moves toward the hammer bit 163 (forward), the other striker or, for example, the second striker 155 linearly moves away from the hammer bit 163 (rearward).
- the first and second strikers 153, 155 function as a counter weight with respect to each other.
- the electric hammer 101 according to the second embodiment has two tool bits, or a first hammer bit 173 and a second hammer bit 175, as a tool bit member, and in the other points, it has the same construction as the first embodiment.
- Components or elements in the second embodiment which are substantially identical to those in the first embodiment are given like numerals as in the first embodiment and is not described or briefly described.
- the first hammer bit 173 and the second hammer bit 175 are features that correspond to the "first tool bit" and the "second tool bit", respectively, according to this invention.
- FIG. 4 shows the entire electric hammer 101
- FIG. 5 shows an essential part of the hammer 101
- FIGS. 6 and 7 are sectional views taken along line B-B and line C-C, respectively, in FIG. 5 .
- a tool holder 171 in the second embodiment has two bores for the first hammer bit 173 and the second hammer bit 175.
- the tool holder 171 is mounted to the front end of the gear housing 107 such that it is locked against movement in its axial and circumferential directions.
- the first and second hammer bits 173 and 175 are held by the tool holder 171 such that it is allowed to move in the axial direction with respect to the tool holder 171.
- the first striking mechanism 117 includes a first striking element in the form of the first striker 153 that reciprocates within the first bore 151a of the cylinder 151 in the axial direction of the hammer bit, and a first intermediate element in the form of a first impact bolt 177 that is slidably disposed within the tool holder 171 and transmits the kinetic energy of the first striker 153 to the first hammer bit 173.
- the first striker 153 is driven via the action of an air spring of the first air chamber 151c of the cylinder 151 as a result of sliding movement of the first piston 133.
- the first striker 153 then collides with (strikes) the first impact bolt 177 and transmits the striking force to the first hammer bit 173 held by the tool holder 171, via the first impact bolt 177.
- the first striking mechanism 117 is a feature that corresponds to the "first striking mechanism" according to this invention.
- the second striking mechanism 119 includes a second striking element in the form of the second striker 155 that reciprocates within the second bore 151b of the cylinder 151 in the axial direction of the hammer bit, and a second intermediate element in the form of a second impact bolt 179 that is slidably disposed within the tool holder 171 and transmits the kinetic energy of the second striker 155 to the second hammer bit 175.
- the second striker 155 is driven via the action of an air spring within the second air chamber 151 d of the cylinder 151 as a result of sliding movement of the second piston 145.
- the second striker 155 then collides with (strikes) the second impact bolt 179 and transmits the striking force to the second hammer bit 175 held by the tool holder 171, via the second impact bolt 179.
- the second striking mechanism 119 is a feature that corresponds to the "second striking mechanism" according to this invention.
- the first crank mechanism 113 for driving the first striking mechanism 117 and the second crank mechanism 115 for driving the second striking mechanism 119 have the same construction as in the first embodiment. Therefore, when the driving motor 111 is driven, the first striking mechanism 117 is driven by the first crank mechanism 113, and the second striking mechanism 119 is driven by the second crank mechanism 115. As a result, the first and second hammer bits 173 and 175 each perform one stroke of striking movement in one crank turn. In other words, a total of two strokes of striking movement are performed by the first and second hammer bits 173 and 175 in one crank turn. Therefore, like in the first embodiment, the operating efficiency can be improved.
- the rotational speed of the driving motor 111 and the driving speeds of the first and second crank mechanisms 113, 115 and the first and second striking mechanisms 117, 119 can be decreased.
- wear of a sliding member or a sliding part such as an O-ring can be reduced and thus the durability can be improved without a decrease in operating efficiency
- first piston 133 of the first crank mechanism 113 and the second piston 145 of the second crank mechanism 115 reciprocates within the cylinder 151 with a phase difference of about 180° crank angle. Therefore, like in the first embodiment, vibration which is caused in the axial direction of the hammer bit during hammering operation can be reduced in a rational manner. Thus, such a construction is also effective in reducing vibration of the electric hammer 101. Further, in this embodiment, with the construction using the two hammer bits 173, 175, a hammering operation can be performed on a wider area at the same time, compared with a construction using one hammer bit.
- crank mechanisms 113, 115 are used as a means for converting the rotating output of the driving motor 111 into linear motion of the pistons 133, 145.
- such means is not limited to them, but other mechanisms may also be used, including a mechanism that converts rotation of a rotating body rotated by the driving motor 111, into swinging motion of a swinging member and thereafter converts the swinging motion of the swinging member into linear motion of the pistons 133, 145, and a mechanism that converts rotation of the driving motor 111 into linear motion of the pistons 133, 145 by using a swash plate which is rotated by the driving motor 111.
- the two crank mechanisms 113, 115 and the two striking mechanisms 117, 119 are provided. However, these mechanisms may be further increased in number.
- the electric hammer 101 is described as a representative example of the impact tool.
- the present invention can also be applied to a hammer drill in which the hammer bits 163, 173, 175 perform not only the striking movement in the axial direction but rotation around its axis.
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Abstract
Description
- The present invention relates to an impact tool in which a tool bit performs a predetermined operation by striking movement in its axial direction.
- An impact tool in the form of an electric hammer is known in which a tool bit is driven by a motor and performs a predetermined operation by striking movement in its axial direction. Such an electric hammer is disclosed, for example, in Japanese non-examined laid-open Patent Publication No.
2005-335046 - In the above-described known impact tool, in order to increase working efficiency, the number of revolutions of the motor must be increased to drive the tool bit at high speed. However, the crank mechanism which is driven by the motor and a mechanical movement part such as a striking mechanism which is used for driving the tool bit are limited in following capability, for example, with respect to the rotational speed of the motor. Therefore, higher working efficiency cannot be realized by increasing the motor speed. In this point, further improvement is required.
- It is, accordingly, an object of the present invention to provide an effective technique for improving the working efficiency of an impact tool.
- The above-described problem can be solved by the features of claimed invention.
The present invention provides an impact tool including a motor, a first motion converting mechanism, a first striking mechanism, a second motion converting mechanism, a second striking mechanism and a tool bit member. The first motion converting mechanism converts a rotating output of the motor into linear motion, and the first striking mechanism is driven by the first motion converting mechanism and thereby performs linear motion. The second motion converting mechanism converts a rotating output of the motor into linear motion, and the second striking mechanism is driven by the second motion converting mechanism and thereby performs linear motion. The tool bit member is struck by the first and second striking mechanisms and thereby reciprocates and performs a predetermined operation on a workpiece. Preferably, the tool bit member is struck alternately by the striking mechanisms. The "impact tool" in this invention typically represents an electric hammer in which a tool bit member performs a hammering operation on a workpiece solely by linear striking movement in the axial direction, or an electric hammer drill in which a tool bit member performs a hammer drill operation on a workpiece by striking movement in the axial direction and rotation around its axis. - The "first motion converting mechanism" and the "second motion converting mechanism" typically represent a mechanism that converts the rotating output of the motor into linear motion of a piston by a crank mechanism, but they are not limited to this. The first and second motion converting mechanisms also suitably include a mechanism that converts rotation of a rotating body rotated by the motor, into swinging motion of a swinging member and thereafter converts the swinging motion of the swinging member into linear motion of the piston, and a mechanism that converts rotation of the motor into linear motion of the piston by using a swash plate which is rotated by the motor. Further, the "first striking mechanism" and the "second striking mechanism" typically represent a construction that includes a striking element which is caused to reciprocate by pressure fluctuations of air within an air chamber as a result of reciprocating movement of a piston, and an intermediate element which transmits the reciprocating movement of the striking element to the tool bit member, but they also suitably includes a construction without the intermediate element.
- In the present invention, the impact tool includes the "first and second motion converting mechanisms". This means that the impact tool has at least two motion converting mechanisms. In addition to the first and second motion converting mechanisms, it may suitably include a third motion converting mechanism and further a fourth converting mechanism. Similarly, the impact tool includes the "first and second striking mechanisms" in this invention, which means that the impact tool has at least two striking mechanisms. In addition to the first and second striking mechanisms, it may suitably include a third striking mechanism and further a fourth striking mechanism. Further, the "tool bit member" in this invention may be suitably formed either by a single tool bit or by a plurality of tool bits. In this case, a single tool bit may be struck by a plurality of striking mechanisms, or a plurality of tool bits may be struck by the same number of striking mechanisms as the plurality of tool bits, or a plurality of tool bits may be struck by a larger number of striking mechanisms than the plurality of tool bits, or a plurality of tool bits may be struck by a smaller number of striking mechanisms than the plurality of tool bits. Either of these constructions is suitably applied in this invention.
- According to this invention, the tool bit member is struck by the first motion converting mechanism which is driven by the motor and the first striking mechanism and by the second motion converting mechanism which is driven by the motor and the second striking mechanism, and thereby performs a predetermined operation. Therefore, compared with a known impact tool in which a single motion converting mechanism and a single striking mechanism are used to drive the tool bit member, the operating efficiency is improved. In other words, if the number of strokes of the tool bit member per unit time is set to be equal to that of the known impact tool, the rotational speed of the motor and the driving speeds of the motion converting mechanisms and the striking mechanisms can be decreased. As a result, wear of a sliding part can be reduced and thus the durability can be improved without a decrease in operating efficiency.
- In the impact tool, preferably, the first and second striking mechanisms are configured to perform linear motion in a direction opposite to each other. Therefore, when one striking mechanism strikes the tool bit member, the other striking mechanism linearly moves in a direction opposite to the one striking mechanism. Thus, the first and second striking mechanisms function as a counter weight with respect to each other. With such a construction, vibration which is caused in the axial direction of the tool bit member during operation can be reduced in a rational manner. Thus, such a construction is effective in reducing vibration of the impact tool.
- For example, preferably, the first striking mechanism has a cylindrical first striking element that performs linear motion so as to drive the tool bit member. The second striking mechanism has a cylindrical second striking element that performs linear motion so as to drive the tool bit member, and the second striking element has generally the same mass as the first striking element. In this case, preferably, the first and second striking elements are configured to perform linear motion in a direction opposite to each other. With this construction, the tool bit member is struck alternately by the first and second striking elements and reciprocates, so that the number of strokes of the tool bit member per unit time is increased and the first and second striking elements can further enhance the function as a counter weight with respect to each other.
- Further, in the impact tool, preferably, the first and second striking mechanisms are disposed one above the other in parallel. With this construction, the driving balance of the impact tool can be further improved.
- According to this invention, an effective technique for improving the working efficiency of an impact tool is provided.
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FIG. 1 is a sectional side view schematically showing an entire electric hammer according to a first embodiment of the invention. -
FIG. 2 is a sectional side view showing an essential part of the hammer. -
FIG. 3 is a sectional view taken along line A-A inFIG. 2 . -
FIG. 4 is a sectional side view showing an entire electric hammer according to a second embodiment of the invention.. -
FIG. 5 is a sectional side view showing an essential part of the hammer. -
FIG. 6 is a sectional view taken along line B-B inFIG. 5 . -
FIG. 7 is a sectional view taken along line C-C inFIG. 5 . - A first embodiment of the present invention is now described with reference to
FIGS. 1 to 3 . In this embodiment, an electric hammer is explained as a representative example of an impact tool according to the present invention.FIG. 1 is a sectional side view schematically showing an entireelectric hammer 101 as a first embodiment of the impact tool according to the present invention. As shown inFIG. 1 , theelectric hammer 101 of this embodiment mainly includes abody 103 that forms an outer shell of theelectric hammer 101, asingle hammer bit 163 detachably coupled to the tip end region (on the left side as viewed inFIG. 1 ) of thebody 103 via ahollow tool holder 161, and ahandgrip 109 that is connected to the other end of thebody 103 on the side opposite to thehammer bit 163 and designed to be held by a user. Thehammer bit 119 is a feature that corresponds to the "tool bit member" according to the present invention. For the sake of convenience of explanation, the side of thehammer bit 119 is taken as the front side and the side of thehandgrip 109 as the rear side. - The
body 103 mainly includes amotor housing 105 that houses a drivingmotor 111, and agear housing 107 that houses first andsecond crank mechanisms striking mechanisms driving motor 111 is appropriately converted into linear motion via the first andsecond crank mechanisms striking mechanisms hammer bit 163 via thestriking mechanisms motor 111 is a feature that corresponds to the "motor" according to this invention. The first and second crankmechanisms striking mechanisms motor 111 is driven when a trigger 109a on thehandgrip 109 is depressed. -
FIG. 2 shows an essential part of thehammer 101 in enlarged sectional view, andFIG. 3 is a sectional view taken along line A-A inFIG. 2 . As shown inFIG. 2 , the first and second crankmechanisms gear housing 107. Thefirst crank mechanism 113 includes afirst crank plate 125 that can rotate in a horizontal plane, a firsteccentric shaft 127 that is disposed in a position displaced from the center of rotation of the first crankplate 125, and afirst crank arm 129 loosely connected at one end to the firsteccentric shaft 127, and a first driving element in the form of afirst piston 133 mounted to the other end of thefirst crank arm 129 via a first connectingshaft 131. The first crank plate 122 is circular and has a drivengear 125a on the outer peripheral surface. The drivengear 125a engages with adriving gear 121 that is rotationally driven by the drivingmotor 111. Thefirst piston 133 is slidably disposed within afirst bore 151 a of acylinder 151, and when the drivingmotor 111 is driven, thefirst piston 133 reciprocates in the axial direction of the cylinder 151 (in the axial direction of the hammer bit). - The
second crank mechanism 113 includes asecond crank plate 137 that can rotate in a horizontal plane, a secondeccentric shaft 139 that is disposed in a position displaced from the center of rotation of the second crankplate 137, and asecond crank arm 141 loosely connected at one end to the secondeccentric shaft 139, and a second driving element in the form of asecond piston 145 mounted to the other end of thesecond crank arm 141 via a second connectingshaft 143. Thesecond piston 145 is slidably disposed within asecond bore 151b of thecylinder 151. - The axis of rotation of the first crank
plate 125 coincides with the axis of rotation of the second crankplate 137. Further, the amount of displacement of the firsteccentric shaft 127 from the center of rotation of the first crankplate 125 is equal to the amount of displacement of the secondeccentric shaft 139 from the center of rotation of the second crankplate 137. Further, the firsteccentric shaft 127 is connected to the secondeccentric shaft 139 by a connectingmember 147 with a phase difference of about 180° in the direction of rotation of the first crankplate 125. Specifically, thesecond crank mechanism 115 is driven via the connectingmember 147 by thefirst crank mechanism 113 that is driven by the drivingmotor 111. Thesecond piston 145 then reciprocates in a direction opposite to thefirst piston 133 with a delay of about 180° crank angle with respect to thefirst piston 133. - The first and second
striking mechanisms first striking mechanism 117 includes a first striking element in the form of afirst striker 153 that is slidably disposed within thefirst bore 151a of thecylinder 151 and reciprocates in the axial direction of thecylinder 151, and an intermediate element in the form of animpact bolt 157 that is slidably disposed within thecylindrical tool holder 161 and transmits the kinetic energy of thefirst striker 153 to thehammer bit 163. Thefirst striker 153 is driven via the action of an air spring or pressure fluctuations of air within afirst air chamber 151 c as a result of sliding movement of thefirst piston 133. Thefirst striker 153 then collides with (strikes) theimpact bolt 157 and transmits the striking force to thehammer bit 163 held by thetool holder 161, via theimpact bolt 157. Specifically, thefirst striking mechanism 117 is driven by thefirst crank mechanism 113. - The
second striking mechanism 119 includes a second striking element in the form of asecond striker 155 that is slidably disposed within thesecond bore 151b of thecylinder 151 and reciprocates in the axial direction of thecylinder 151, and the above-describedimpact bolt 157. Thesecond striker 155 is driven via the action of an air spring within asecond air chamber 151 d as a result of sliding movement of thesecond piston 145. Thesecond striker 155 then collides with (strikes) theimpact bolt 157 and transmits the striking force to thehammer bit 163 held by thetool holder 161, via theimpact bolt 157. Specifically, thesecond striking mechanism 119 is driven by thesecond crank mechanism 115. - The
impact bolt 157 has an axial rear end having a strike surface 157a that is large enough to receive the striking movement of thefirst striker 153 on its radially lower region and to receive the striking movement of thesecond striker 155 on its radially upper region. - The
cylinder 151 includes the circularfirst bore 151a in which thefirst piston 133 and thefirst striker 153 are slidably disposed, and the circularsecond bore 151b in which thesecond piston 145 and thesecond striker 155 are slidably disposed. Thecylinder 151 is mounted to thegear housing 107 such that it is locked against movement in its axial and circumferential directions. The cross section structure of thecylinder 151 is shown inFIG. 3 . Thetool holder 161 is mounted to the front end of thegear housing 107 such that it is locked against movement in its axial and circumferential directions. Thehammer bit 163 is held by thetool holder 161 such that it is allowed to move in the axial direction with respect to thetool holder 161. - Operation of the
electric hammer 101 constructed as described above is now explained. When the driving motor 111 (shown inFIG. 1 ) is driven, thedriving gear 121 is caused to rotate by the rotating output of the drivingmotor 111. When thedriving gear 121 rotates, the first crankplate 125 is caused to rotate via the driven gear 123 that engages with thedriving gear 121. Then, the firsteccentric shaft 127 on the first crankplate 125 is caused to revolve. As a result, thefirst crank arm 129 is caused to swing, and thefirst piston 133 mounted on the front end of thefirst crank arm 129 is caused to linearly slide within thecylinder 151. When thefirst piston 133 slides from the non-compressing side (the right side as viewed inFIGS. 1 and2 ) to thehammer bit 163 side, thefirst striker 153 is caused to reciprocate within thecylinder 151 by pressure fluctuations of air or the action of the air spring within thefirst air chamber 151 c. Thefirst striker 153 then collides with theimpact bolt 157 and thereby transmits the kinetic energy (striking force) to thehammer bit 163. Thus, thehammer bit 163 slides within thetool holder 161 and performs a hammering operation on the workpiece. - Meanwhile, in the
second crank mechanism 115, when the firsteccentric shaft 127 is caused to revolve by rotation of the first crankplate 125, the secondeccentric shaft 139 is caused to revolve on the rotation axis of the second crankplate 137 via the connectingmember 147. As a result, thesecond crank arm 141 is caused to swing, and thesecond piston 145 is caused to slide within thesecond bore 151 b of thecylinder 151. In this embodiment, a phase difference of about 180° crank angle is provided between the firsteccentric shaft 127 and the secondeccentric shaft 139. Therefore, thesecond piston 145 is caused to linearly slide within thesecond bore 151b of thecylinder 151 with a delay of about 180° crank angle with respect to thefirst piston 133. When thesecond piston 145 slides from the non-compressing side to thehammer bit 163 side, thesecond striker 155 is caused to reciprocate within thecylinder 151 by the action of the air spring within thesecond air chamber 151d which is caused by the sliding movement of thesecond piston 145. Thesecond striker 155 then collides with theimpact bolt 157 and thereby transmits the kinetic energy (striking force) to thehammer bit 163. Thus, thehammer bit 163 slides within thetool holder 161 and performs a hammering operation on the workpiece.. - As described above, according to this embodiment, the
single hammer bit 163 can perform two strokes of striking movement in one turn of the crank. Therefore, compared with a known electric hammer which provides one stroke of striking movement in one crank turn, the number of strokes of thehammer bit 163 is doubled if the number of revolutions of the drivingmotor 111 is set to be identical to that of the known hammer. Therefore, the operating efficiency is improved. From an alternative point of view, if the number of strokes of the hammer bit 163 per unit time is set to be equal to that of the known hammer, the rotational speed of the drivingmotor 111 and the driving speeds of the first and second crankmechanisms striking mechanisms - Further, in this embodiment, the
first piston 133 and thesecond piston 145 are driven with a phase difference of about 180° crank angle. Thus, thefirst striker 153 and the second striker 15 5 reciprocates in a direction opposite to each other. Therefore, when one striker or, for example, thefirst striker 153 linearly moves toward the hammer bit 163 (forward), the other striker or, for example, thesecond striker 155 linearly moves away from the hammer bit 163 (rearward). Thus, the first andsecond strikers electric hammer 101. - A second embodiment of the present invention is now described with reference to
FIGS. 4 to 7 . Theelectric hammer 101 according to the second embodiment has two tool bits, or afirst hammer bit 173 and asecond hammer bit 175, as a tool bit member, and in the other points, it has the same construction as the first embodiment. Components or elements in the second embodiment which are substantially identical to those in the first embodiment are given like numerals as in the first embodiment and is not described or briefly described. Thefirst hammer bit 173 and thesecond hammer bit 175 are features that correspond to the "first tool bit" and the "second tool bit", respectively, according to this invention. -
FIG. 4 shows the entireelectric hammer 101, andFIG. 5 shows an essential part of thehammer 101.FIGS. 6 and 7 are sectional views taken along line B-B and line C-C, respectively, inFIG. 5 . As shown inFIGS. 4 and5 , atool holder 171 in the second embodiment has two bores for thefirst hammer bit 173 and thesecond hammer bit 175. Thetool holder 171 is mounted to the front end of thegear housing 107 such that it is locked against movement in its axial and circumferential directions. The first andsecond hammer bits tool holder 171 such that it is allowed to move in the axial direction with respect to thetool holder 171. - The
first striking mechanism 117 includes a first striking element in the form of thefirst striker 153 that reciprocates within thefirst bore 151a of thecylinder 151 in the axial direction of the hammer bit, and a first intermediate element in the form of afirst impact bolt 177 that is slidably disposed within thetool holder 171 and transmits the kinetic energy of thefirst striker 153 to thefirst hammer bit 173. Thefirst striker 153 is driven via the action of an air spring of thefirst air chamber 151c of thecylinder 151 as a result of sliding movement of thefirst piston 133. Thefirst striker 153 then collides with (strikes) thefirst impact bolt 177 and transmits the striking force to thefirst hammer bit 173 held by thetool holder 171, via thefirst impact bolt 177. Thefirst striking mechanism 117 is a feature that corresponds to the "first striking mechanism" according to this invention. - The
second striking mechanism 119 includes a second striking element in the form of thesecond striker 155 that reciprocates within thesecond bore 151b of thecylinder 151 in the axial direction of the hammer bit, and a second intermediate element in the form of asecond impact bolt 179 that is slidably disposed within thetool holder 171 and transmits the kinetic energy of thesecond striker 155 to thesecond hammer bit 175. Thesecond striker 155 is driven via the action of an air spring within thesecond air chamber 151 d of thecylinder 151 as a result of sliding movement of thesecond piston 145. Thesecond striker 155 then collides with (strikes) thesecond impact bolt 179 and transmits the striking force to thesecond hammer bit 175 held by thetool holder 171, via thesecond impact bolt 179. Thesecond striking mechanism 119 is a feature that corresponds to the "second striking mechanism" according to this invention. - The
first crank mechanism 113 for driving thefirst striking mechanism 117 and thesecond crank mechanism 115 for driving thesecond striking mechanism 119 have the same construction as in the first embodiment. Therefore, when the drivingmotor 111 is driven, thefirst striking mechanism 117 is driven by thefirst crank mechanism 113, and thesecond striking mechanism 119 is driven by thesecond crank mechanism 115. As a result, the first andsecond hammer bits second hammer bits second hammer bits motor 111 and the driving speeds of the first and second crankmechanisms striking mechanisms - Further, the
first piston 133 of thefirst crank mechanism 113 and thesecond piston 145 of thesecond crank mechanism 115 reciprocates within thecylinder 151 with a phase difference of about 180° crank angle. Therefore, like in the first embodiment, vibration which is caused in the axial direction of the hammer bit during hammering operation can be reduced in a rational manner. Thus, such a construction is also effective in reducing vibration of theelectric hammer 101. Further, in this embodiment, with the construction using the twohammer bits - In the above-described embodiments, the
crank mechanisms motor 111 into linear motion of thepistons motor 111, into swinging motion of a swinging member and thereafter converts the swinging motion of the swinging member into linear motion of thepistons motor 111 into linear motion of thepistons motor 111. Further, in the above-described embodiments, the two crankmechanisms striking mechanisms
Further, in the above-described embodiments, theelectric hammer 101 is described as a representative example of the impact tool. However, the present invention can also be applied to a hammer drill in which thehammer bits -
- 101
- electric hammer (impact tool)
- 103
- body
- 105
- motor housing
- 107
- gear housing
- 109
- handgrip
- 109a
- trigger
- 111
- driving motor
- 113
- first crank mechanism
- 115
- second crank mechanism
- 117
- first striking mechanism
- 119
- second striking mechanism
- 121
- driving gear
- 125
- first crank plate
- 125a
- driven gear
- 127
- first eccentric shaft
- 129
- first crank arm
- 131
- first connecting shaft
- 133
- first piston
- 137
- second crank plate
- 139
- second eccentric shaft
- 141
- second crank arm
- 143
- second connecting shaft
- 145
- second piston
- 147
- connecting member
- 151
- cylinder
- 151a
- first bore
- 151b
- second bore
- 151c
- first air chamber
- 151d
- second air chamber
- 153
- first striker
- 155
- second striker
- 157
- impact bolt
- 157a
- strike surface
- 161
- tool holder
- 163
- hammer bit (tool bit member, tool bit)
- 171
- tool holder
- 173
- first hammer bit (tool bit member, first tool bit)
- 175
- second hammer bit (tool bit member, second tool bit)
- 177
- first impact bolt
- 179
- second impact bolt
Claims (6)
- An impact tool comprising:a motor,a first motion converting mechanism that converts a rotating output of the motor into linear motion,a first striking mechanism that is driven by the first motion converting mechanism and thereby performs linear motion,a second motion converting mechanism that converts a rotating output of the motor into linear motion,a second striking mechanism that is driven by the second motion converting mechanism and thereby performs linear motion, anda tool bit member that is struck by the first and second striking mechanisms and thereby reciprocates and performs a predetermined operation on a workpiece.
- The impact tool as defined in claim 1, wherein:the first striking mechanism has a first striking element that performs linear motion so as to drive the tool bit member,the second striking mechanism has a second striking element that performs linear motion so as to drive the tool bit member, the second striking element having generally the same mass as the first striking element,the first and second striking elements are configured to perform linear motion in a direction opposite to each other,the tool bit member comprises a single tool bit that performs a predetermined operation on a workpiece, and the tool bit member is struck alternately by the first and second striking elements and reciprocates, whereby the number of strokes of the tool bit member per unit time is increased and the first and second striking elements serve as a counter weight with respect to each other.
- The impact tool as defined in claim 2, wherein the first and second striking elements are cylindrically shaped having generally the same diameter.
- The impact tool as defined in claim 1, wherein the tool bit member comprises a first tool bit that is struck by the first striking mechanism, and a second tool bit that is struck by the second striking mechanism.
- The impact tool as defined in claim 4, wherein the first and second striking mechanisms are configured to perform linear motion in a direction opposite to each other.
- The power tool as defined in any one of claims 1 to 5, wherein the first and second striking mechanisms are disposed one above the other in parallel.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006022446A JP2007203388A (en) | 2006-01-31 | 2006-01-31 | Impact tool |
PCT/JP2007/051415 WO2007088821A1 (en) | 2006-01-31 | 2007-01-29 | Impact tool |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1980371A1 true EP1980371A1 (en) | 2008-10-15 |
EP1980371A4 EP1980371A4 (en) | 2010-06-16 |
EP1980371B1 EP1980371B1 (en) | 2014-03-19 |
Family
ID=38327394
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07707646.1A Expired - Fee Related EP1980371B1 (en) | 2006-01-31 | 2007-01-29 | Impact tool |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP1980371B1 (en) |
JP (1) | JP2007203388A (en) |
WO (1) | WO2007088821A1 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ITPN20110067A1 (en) * | 2011-10-11 | 2013-04-12 | Giovanni Zago | DRILLING EQUIPMENT-PLURI-CYLINDRICAL DEMOLITION FOR ELECTRO-PNEUMATIC ACTION |
US20180036842A1 (en) * | 2015-02-26 | 2018-02-08 | Ecoroll Ag Werkzeugtechnik | Hammering device for influencing workpieces and associated method |
US20230027574A1 (en) * | 2021-07-26 | 2023-01-26 | Makita Corporation | Striking tool |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2127820A1 (en) | 2008-05-26 | 2009-12-02 | Max Co., Ltd. | Driving tool |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE830332C (en) * | 1950-02-11 | 1952-02-04 | Moenninghoff Maschf | Pneumatically operated pick hammer |
DE967868C (en) * | 1955-03-31 | 1957-12-19 | Robel & Co G | Impact device |
JPS6033636A (en) * | 1983-08-04 | 1985-02-21 | Nec Corp | Inferential device |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS308287Y1 (en) * | 1953-01-17 | 1955-06-15 | ||
JPS4963601A (en) * | 1972-10-21 | 1974-06-20 | ||
JPS516583U (en) * | 1974-07-02 | 1976-01-17 | ||
JPS6033636B2 (en) * | 1979-07-04 | 1985-08-03 | 日立工機株式会社 | electric hammer |
-
2006
- 2006-01-31 JP JP2006022446A patent/JP2007203388A/en active Pending
-
2007
- 2007-01-29 WO PCT/JP2007/051415 patent/WO2007088821A1/en active Application Filing
- 2007-01-29 EP EP07707646.1A patent/EP1980371B1/en not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE830332C (en) * | 1950-02-11 | 1952-02-04 | Moenninghoff Maschf | Pneumatically operated pick hammer |
DE967868C (en) * | 1955-03-31 | 1957-12-19 | Robel & Co G | Impact device |
JPS6033636A (en) * | 1983-08-04 | 1985-02-21 | Nec Corp | Inferential device |
Non-Patent Citations (1)
Title |
---|
See also references of WO2007088821A1 * |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ITPN20110067A1 (en) * | 2011-10-11 | 2013-04-12 | Giovanni Zago | DRILLING EQUIPMENT-PLURI-CYLINDRICAL DEMOLITION FOR ELECTRO-PNEUMATIC ACTION |
US20180036842A1 (en) * | 2015-02-26 | 2018-02-08 | Ecoroll Ag Werkzeugtechnik | Hammering device for influencing workpieces and associated method |
US10549392B2 (en) * | 2015-02-26 | 2020-02-04 | ECOROLL AG Werkzengtechnik | Hammering device for influencing workpieces |
US20230027574A1 (en) * | 2021-07-26 | 2023-01-26 | Makita Corporation | Striking tool |
Also Published As
Publication number | Publication date |
---|---|
WO2007088821A1 (en) | 2007-08-09 |
EP1980371B1 (en) | 2014-03-19 |
EP1980371A4 (en) | 2010-06-16 |
JP2007203388A (en) | 2007-08-16 |
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