EP2700476B1 - Schlagwerkzeug - Google Patents

Schlagwerkzeug Download PDF

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Publication number
EP2700476B1
EP2700476B1 EP12774797.0A EP12774797A EP2700476B1 EP 2700476 B1 EP2700476 B1 EP 2700476B1 EP 12774797 A EP12774797 A EP 12774797A EP 2700476 B1 EP2700476 B1 EP 2700476B1
Authority
EP
European Patent Office
Prior art keywords
tool
impact
cylinder
impact cylinder
handgrip
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.)
Active
Application number
EP12774797.0A
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English (en)
French (fr)
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EP2700476A4 (de
EP2700476A1 (de
Inventor
Takuro Konishi
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
Original Assignee
Makita Corp
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
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Publication of EP2700476A1 publication Critical patent/EP2700476A1/de
Publication of EP2700476A4 publication Critical patent/EP2700476A4/de
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Publication of EP2700476B1 publication Critical patent/EP2700476B1/de
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Classifications

    • 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
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/06—Means for driving the impulse member
    • B25D9/08—Means for driving the impulse member comprising a built-in air compressor, i.e. the tool being driven by air pressure
    • 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
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/245—Spatial arrangement of components of the tool relative to each other

Definitions

  • the invention relates to an impact tool according to the preamble of claim 1, which performs a predetermined operation on a workpiece by at least linear movement of a tool bit in an axial direction of the tool bit.
  • Such an impact tool is known from US 2011 / 0000693 A1 .
  • US patent No. 4751970 discloses an angular attachment that is attached to a front end of a hammer drill and can transmit rotation and linear movement of a hammer drill body to a tool bit which is oriented at a different angle at an output of the attachment.
  • the angular attachment is designed such that an output part of the tool bit intersects at 90 degrees with an output part of the hammer drill body.
  • EP 2 444 206 A1 (corresponds to JP 2011-000684 (A )) and US 2009/0020302 A1 and DE 10 2006 061 625 A1 (corresponds to US 2011-0000693 A1 ) each disclose an impact tool according to the preamble of claim 1.
  • an object of the invention to provide an impact tool having a tool body of which length in an axial direction of a tool bit is downsized.
  • the length of the tool body in the axial direction of the tool bit is defined by the tool holder and the impact cylinder.
  • the impact tool further has a compressed-air feeding cylinder for supplying compressed air to the air chamber of the cylinder.
  • the compressed-air feeding cylinder extends in a different direction from an extending direction of the impact cylinder.
  • the manner of "extending in a different direction” here represents the manner in which the compressed-air feeding cylinder extends in a direction perpendicular or angled to the extending direction of the impact cylinder.
  • a tool holder that holds a tool bit
  • an impact cylinder that houses a striking element for applying an impact force to the tool bit and has an air chamber for applying compressed air to the striking element
  • a piston that generates compressed air in the air chamber and a driving mechanism for the piston are arranged in series in the axial direction of the tool bit.
  • the impact tool has a handgrip which is connected to the tool body and designed to be held by a user in order to operate the impact tool, and a width direction of the handgrip preferably coincides with the extending direction of the impact cylinder.
  • the "width direction of the handgrip" here represents a direction transverse to the extending direction of a grip part of the handgrip to be held by the user's hand, for example, in the case of the handgrip which has the grip part having a linearly extending region.
  • the user's arm when holding the handgrip with the user's hand, extends in the extending direction of the impact cylinder or in a direction transverse to the axial direction of the tool bit. Specifically, the extending direction of the arm intersects with the axial direction of the tool bit. Therefore, when performing an operation, for example, on an inner wall surface of a U-shaped drainage ditch (made of concrete), the arm of the user holding the handgrip does not get in the way of the operation.
  • the axial direction of the tool bit, the extending direction of the compressed-air feeding cylinder and the extending direction of the handgrip intersect one another.
  • the impact tool can be compact as a whole.
  • the impact tool further has a motion converting mechanism that converts rotation into linear motion and thereby generates compressed air in the air chamber of the impact cylinder.
  • a rotating shaft of the motion converting mechanism is preferably disposed in parallel to the impact cylinder in a predetermined region along the extending direction of the impact cylinder. In this case, the rotating shaft of the motion converting mechanism preferably intersects with the extending direction of the impact cylinder.
  • the motion converting mechanism for generating compressed air in the air chamber is disposed in parallel to the impact cylinder. Therefore, the length of the impact tool in the axial direction of the tool bit can be shortened, compared with the known impact tool in which the motion converting mechanism is disposed outside a region of the impact cylinder in its longitudinal direction.
  • the impact tool has a handgrip designed to be held by a user in order to operate the impact tool, and the extending directions of the impact cylinder and the handgrip are preferably a parallel to each other.
  • the user's arm when holding the handgrip with the user's hand, extends in the extending direction of the impact cylinder or in a direction transverse to the axial direction of the tool bit. Specifically, the extending direction of the arm intersects with the axial direction of the tool bit. Therefore, when performing an operation, for example, on an inner wall surface of a U-shaped ditch, the arm of the user holding the handgrip does not get in the way of the operation.
  • an impact tool is provided with a tool body of which length in the axial direction of a tool bit is downsized.
  • a hammer drill 101 of this embodiment mainly includes a body 103 that forms an outer shell of the hammer drill 101, a hammer bit 119 detachably coupled to one end (front end region) of the body 103 in its longitudinal direction via a tool holder 137, and a handgrip 109 that is provided as a main handle on the opposite side of the body 103 from the hammer bit 119.
  • the hammer bit 119 is provided such that its axis extends in a direction transverse to the longitudinal direction of the body 103, and the hammer bit 119 is held by a tool holding member in the form of the hollow tool holder 137 such that it is allowed to linearly move in a longitudinal direction of the tool holder 137 with respect to the tool holder.
  • the tool holder 137 extends in a direction transverse to the longitudinal direction of the body 103 or in a width direction of the body 103.
  • the body 103 and the hammer bit 119 are features that correspond to the "tool body” and the "tool bit", respectively.
  • the body 103 mainly includes an outer housing 105 and an inner housing in the form of a gear housing 107 which is largely covered by the outer housing 105.
  • the outer housing 105 includes a motor housing that houses a driving motor 111, and the gear housing 107 houses a motion converting mechanism 113, a compression device 114, a striking mechanism 115 and a power transmitting mechanism 117.
  • the handgrip 109 is configured as a D-shaped handle having a grip 109a which is designed to be held by a user.
  • the grip 109a extends in a vertical direction transverse to the longitudinal direction of the body 103 and has upper and lower ends connected to the outer housing 105.
  • An axis of the hammer bit 119 extends in a horizontal direction transverse to the longitudinal direction of the body 103 and to the extending direction of the handgrip 109.
  • the hammer drill 101 has an auxiliary handle in the form of a side grip 110 separately from the above-described handgrip 109.
  • the side grip 110 is a rod-like member extending in a direction transverse to the axial direction of the hammer bit 119.
  • One axial end of the side grip 110 is removably mounted on a generally cylindrical barrel 107a which houses the tool holder 137, and a fixed position of the side grip 110 to the barrel 107a can be adjusted in a circumferential direction around the axis of the hammer bit 119.
  • the barrel 107a is provided as a region of the gear housing 107 which is exposed to the outside through the side surface of the outer housing 105.
  • the driving motor 111 is disposed such that its axis of rotation runs vertically in a direction (a vertical direction in FIG. 2 ) generally perpendicular to the longitudinal direction of the body 103.
  • Rotating power of the driving motor 111 is converted into linear motion via the motion converting mechanism 113 and then drives the compression device 114.
  • Compressed air generated by the compression device 114 is led to an impact cylinder 141 and drives the striking mechanism 115.
  • an impact force is generated in the axial direction (the vertical direction in FIG. 1 ) of the hammer bit 119 via the striking mechanism 115.
  • the power transmitting mechanism 117 reduces the speed of the rotating output of the driving motor 111 and then transmits it to the hammer bit 119 via the tool holder 137, so that the hammer bit 119 is caused to rotate in the circumferential direction.
  • the driving motor 111 is driven by depressing an operating member in the form of a trigger 147 which is disposed on the handgrip 109, and the direction of rotation of the driving motor 111 can be changed by sliding a normal/reverse selector switch 149 disposed adjacent to the trigger 147.
  • a direction in which the normal/reverse selector switch 149 is slid can be arbitrarily set.
  • the motion converting mechanism 113 mainly includes a driving gear 121 that is formed on a motor shaft 111a of the driving motor 111 and rotationally driven in a horizontal plane, a driven gear 123 that is engaged with the driving gear 121, a crank shaft 125 that rotates together with the driven gear 123, a crank pin 126 that is eccentrically disposed on the crank shaft 125, a crank arm 127 that is loosely connected to the crank pin 126 and a driving element in the form of a piston 129 that is mounted to the crank arm 127 via a connecting shaft 128.
  • the motor shaft 111 a and the crank shaft 125 are disposed side by side in parallel to each other.
  • the crank shaft 125, the crank pin 126, the crank arm 127 and the piston 129 which are described above, form the crank mechanism.
  • the piston 129 is slidably disposed within a bore of an air compression cylinder 131 and the piston 129 and the air compression cylinder 131 form the compression device 114.
  • the air compression cylinder 131 is a feature that corresponds to the "compressed-air feeding cylinder".
  • the air compression cylinder 131 has a compression chamber 131 a partitioned by the gear housing 107 and the piston 129.
  • the piston 129 generates compressed air by reducing (decreasing) a volume of the compression chamber 131a and supplies the compressed air to an air chamber 141a of the impact cylinder 141 through an air passage 133 formed in the gear housing 107.
  • the air compression cylinder 131 extends in a same direction as the longitudinal direction of the body 103 and in a direction transverse to both the axial direction of the hammer bit 119 and the extending direction of the handgrip 109. Specifically, the axial direction of the hammer bit 119, the extending direction of the air compression cylinder 131 and the extending direction of the handgrip 109 intersect one another.
  • the striking mechanism 115 mainly includes a striking element in the form of a striker 143 that is slidably disposed within a bore of the impact cylinder 141, and an intermediate element in the form of an impact bolt 145 that is slidably disposed within the tool holder 137 and serves to transmit kinetic energy of the striker 143 to the hammer bit 119.
  • the impact cylinder 141 has the air chamber 141 a extending in the axial direction of the hammer bit 119 and partitioned by the striker 143 and an inner wall surface 107b of the gear housing 107 which faces the striker 143. When compressed air is generated by movement of the piston 129 in a direction (to the left as viewed in FIGS.
  • the striker 143 is moved forward by this compressed air and then collides with (strikes) the impact bolt 145 and transmits an impact force to the hammer bit 119 via the impact bolt 145.
  • a negative pressure is formed in the air chamber 141a of the impact cylinder 141. Therefore, the striker 143 is sucked by this negative pressure, moved toward the inner wall surface 107b and returned to its retracted position.
  • a cushioning spring 144 is mounted on the inner wall surface 107b.
  • one end of the air passage 133 is open at the bottom of the compression chamber 131a of the air compression cylinder 131 and the other end is open at a head (a part facing the striker 143) of the air chamber 141 a of the impact cylinder 141.
  • compressed air is fed in the longitudinal direction of the impact cylinder 141 through the air passage 133.
  • the impact cylinder 141 is integrally formed by an extension of the tool holder 137 extending in its longitudinal direction. It may however be constructed such that the tool holder 137 and the impact cylinder 141 are separately formed and connected to each other.
  • the power transmitting mechanism 117 mainly includes a first intermediate gear 151 that engages with the driving gear 121 driven by the driving motor 111, a second intermediate gear 153 that engages with the first intermediate gear 151, a small bevel gear 155 that rotates together with the second intermediate gear 153 and a large bevel gear 157 that engages with the small bevel gear 155.
  • a first intermediate shaft 152 having the first intermediate gear 151 fitted thereon and a second intermediate shaft 154 having the second intermediate gear 153 and the small bevel gear 155 fitted thereon are disposed in parallel to the motor shaft 111a of the driving motor 111 and rotatably supported on the gear housing 107.
  • the large bevel gear 157 having a rotation axis perpendicular to that of the small bevel gear 155 is rotatably fitted on the impact cylinder 141 and connected to the impact cylinder 141 via a torque limiter 159 (see FIG. 1 ).
  • the torque limiter 159 has clutch teeth 159a which engage with clutch teeth 157a of the large bevel gear 157, and is normally biased in a direction of engagement between the clutch teeth 157a, 159a by a biasing spring (compression coil spring) 161.
  • a biasing spring compression coil spring
  • the torque limiter 159 moves in a direction away from the large bevel gear 157 against the biasing force of the biasing spring 161.
  • the clutch teeth 157a, 159a are disengaged from each other, which results in interrupting transmission of rotation from the large bevel gear 157 to the impact cylinder 141.
  • the motor shaft 111a, the crank shaft 125 and the first and second intermediate shafts 152, 154 are disposed on the same straight line P extending in the longitudinal direction of the body 103.
  • the hammer drill according to this embodiment is constructed as described above. Therefore, when the driving motor 111 is driven by depressing the trigger 147, the motion converting mechanism 113 is driven. Then, the piston 129 is rectilinearly slid within the air compression cylinder 131 and thus compresses the air in the compression chamber 131 a and supplies the compressed air to the air chamber 141 a of the impact cylinder 141 via the air passage 133. As a result, the striker 143 moves forward within the impact cylinder 141 and collides with the impact bolt 145, so that the kinetic energy of the striker 143 which is caused by the collision is transmitted to the hammer bit 119.
  • the rotating output of the driving motor 111 is transmitted to the impact cylinder 141 via the power transmitting mechanism 117. Therefore, the impact cylinder 141, the tool holder 137 and the hammer bit 119 held by the tool holder 137 are caused to rotate together. In this manner, the hammer bit 119 performs a drilling operation on a workpiece by linear motion in the axial direction and rotation in the circumferential direction.
  • the air compression cylinder 131 is provided separately from the impact cylinder 141 and the striker 143 is driven by supplying the compressed air generated in the compression chamber 131a of the air compression cylinder 131 to the air chamber 141a of the impact cylinder 141. Further, the air compression cylinder 131 is disposed such that it extends in a direction transverse to the extending direction of the impact cylinder 141.
  • the length of the body 103 in the striking direction or the axial direction of the hammer bit 119 is defined by the extending lengths of the tool holder 137 for holding the hammer bit 119 and the impact cylinder 141.
  • the impact cylinder 141 houses the striker 143 for applying the impact force to the hammer bit 119 and has the air chamber 141a for applying the compressed air to the striker 143.
  • the length of the body 103 in the striking direction of the hammer bit 119 can be shortened. Therefore, in performing a drilling operation, for example, on an inner wall surface of a U-shaped drainage ditch (made of concrete), the tool body 103 can be inserted into the U-shaped ditch with the axis of the hammer bit 119 extending in the width direction of the ditch.
  • the impact force of the striker 143 is linearly transmitted to the hammer bit 119.
  • the impact force of the striker 143 can be transmitted to the hammer bit 119 without loss.
  • the impact cylinder 141 is designed to extend in the width direction of the handgrip 109 or in a direction transverse to the extending direction of the grip 109a.
  • the user's arm extends in a direction transverse to the extending direction of the impact cylinder 141. Therefore, when performing an operation, for example, on an inner wall surface of a U-shaped ditch, the arm of the user holding the handgrip 109 does not get in the way of the operation.
  • a rear end region of the outer housing 105 in the striking direction is designed as an auxiliary grip 163 (see FIG. 1 ) which can be pressed with a user's whole palm in case that the side grip 110 is found to be hard to use, or that the side grip 110 is not provided.
  • the size (outer diameter) of the driving motor 111 determines the external dimensions of the motor housing 105a of the outer housing 105 which covers the driving motor 111.
  • the driving gear 121, the driven gear 123 of the motion converting mechanism 113 and the first intermediate gear 151 of the power transmitting mechanism 117 are disposed in series on a straight line P which extends in a radial direction through a center of the second intermediate gear 153 (the small bevel gear 155) and in parallel to a rear surface 105b of the outer housing 105 in the striking direction (to the longitudinal direction of the piston 129).
  • the motor housing 105a of the outer housing 105 may bulge rearward of the rear surface 105b of the outer housing 105 in the striking direction, so that such gear arrangement interferes with shortening the length of the body 103 in the striking direction. Therefore, a modification as shown in FIG. 4 is provided in order to avoid bulging of the motor housing 105a when the size (outer diameter) of the driving motor 111 is relatively large.
  • the driving gear 121, the driven gear 123 of the motion converting mechanism 113 and the first intermediate gear 151 of the power transmitting mechanism 117 are disposed on a straight line P1 which is displaced a predetermined distance E in the striking direction from the straight line P extending in a radial direction through the center of the second intermediate gear 153 (the small bevel gear 155) and in parallel to the rear surface 105b of the outer housing 105 in the striking direction.
  • the motor housing 105a can be prevented from bulging rearward of the rear surface 105b of the outer housing 105 in the striking direction.
  • FIGS. 5 and 6 A modification to a feeding passage of compressed air in this embodiment is now described with reference to FIGS. 5 and 6 .
  • compressed air is supplied into the air chamber 141a through the head of the impact cylinder 141.
  • the air passage 133 for supplying compressed air is formed through a sidewall of the impact cylinder 141 such that the compressed air is supplied into the air chamber 141a in the radial direction from the side or from a direction transverse to the longitudinal direction of the impact cylinder 141.
  • the length of the air passage 133 required can be shorter, and thus the length of the tool body 103 in the striking direction can be further shortened that much.
  • the air passage 133 is directly connected to the impact cylinder 141, so that the impact cylinder 141 cannot be rotated. Therefore, the impact cylinder 141 is formed separately from the tool holder 137 and fixed to the gear housing 107. Further, the tool holder 137 has an extension 137a which is fitted on the impact cylinder 141 and can rotate with respect to the impact cylinder 141, and the large bevel gear 157 is fitted on the extension 137a and can rotate together with the extension 137a.
  • the rotating output of the driving motor 111 can be transmitted to the tool holder 137 for holding the hammer bit 119.
  • a ring-like member 165 and a connecting pipe 167 form the air passage133.
  • the ring-like member 165 is fitted on the impact cylinder 141 such that it can rotate with respect to the impact cylinder 141, and has an annular groove 165a formed in its inner circumferential surface and extending in its circumferential direction.
  • the connecting pipe 167 serves to provide communication between the compression chamber 131a of the air compression chamber 131 and the annular groove 165a of the ring-like member 165.
  • the annular groove 165a communicates with the air chamber 141a via a plurality of vent holes 169 which are formed in the wall of the impact cylinder 141 and arranged in the circumferential direction. Therefore, according to this modification, in the construction in which the impact cylinder 141 rotates together (is integrally formed) with the tool holder 137, the compressed air of the air compression chamber 131 can be supplied to the air chamber 141a from the side or from a direction transverse to the longitudinal direction of the impact cylinder 141. Therefore, like the modification as viewed in FIG. 4 , the length of the tool body 103 in the striking direction can be further shortened.
  • the air compression cylinder 131 is obliquely disposed such that its longitudinal axis is inclined at a predetermined angle with respect to the longitudinal direction of the body 103. Further, a front end of a tubular part 171 protrudes from the bottom of the compression chamber 131a and is connected to the gear housing 107. Further, the head of the impact cylinder 141 is opposed to the inner wall surface of the gear housing 107 with a predetermined clearance such that the clearance forms an inner passage 173 to the air chamber 141 a. The inner passage 173 communicates with the compression chamber 131a of the air compression cylinder 131 via the tubular part 171 connected to the gear housing 107.
  • the compressed air of the air compression chamber 131 can be supplied to the air chamber 141a from the side or from a direction transverse to the longitudinal direction of the impact cylinder 141. Therefore, the length of the tool body 103 in the striking direction can be further shortened.
  • FIGS. 10 to 13 A second embodiment is now described with reference to FIGS. 10 to 13 . Further, the description of the second embodiment is focused on the points of difference in order to avoid overlapping descriptions with the first embodiment, and components in this embodiment which are substantially identical to those in the first embodiment are given like numerals as in the first embodiment.
  • the piston 129 which is one of components forming the motion converting mechanism 113 and performs linear movement is slidably disposed within the bore of the impact cylinder 141.
  • the striker 143 is driven via pressure fluctuations of the air chamber 141a which are caused by sliding movement of the piston 129, collides with (strikes) the impact bolt 145 which is slidably fitted in the tool holder 137 and transmits the impact force to the hammer bit 119 via the impact bolt 145.
  • the air compression cylinder in the first embodiment is not provided.
  • the impact cylinder 141 is separately formed from the tool holder 137.
  • the impact cylinder 141 is fitted in the tool holder 137 such that it can coaxially rotate with respect to the tool holder 137, and fixed to the gear housing 107.
  • the driving motor 111 is disposed such that the motor shaft 101a extends in the same direction as the longitudinal direction of the body 103 or in a direction transverse to the axial direction of the hammer bit 119 (the extending directions of the tool holder 137 and the impact cylinder 141).
  • the motion converting mechanism 113 for converting the rotating output of the driving motor 111 into linear motion is disposed in parallel to the impact cylinder 141 in a predetermined region along the longitudinal direction of the impact cylinder 141.
  • the motion converting mechanism 113 and the impact cylinder 141 are disposed to overlap each other when viewed from a direction (the longitudinal direction of the body 103) transverse to the axial direction of the hammer bit 119.
  • the rotation axis of the crank shaft 125 intersects with the extending direction of the impact cylinder 141.
  • the crank shaft 125 is a feature that corresponds to the "rotation axis”.
  • the motion converting mechanism 113 has a crank arm 181 formed by a generally U-shaped member.
  • An escape groove 183 is formed in a peripheral wall (side wall) of the impact cylinder 141 in order to install the crank arm 181.
  • a bottom region 181a of the U-shaped crank arm 181 (shown by a two-dot chain line in FIG. 12 ) has a circular section.
  • the crank arm 181 is installed with the bottom region 181 a through the escape groove 183, and in this state, one end of the crank arm 181 is connected to a connecting shaft 128 of the piston 129 and the other end is connected to the crank pin 126.
  • the escape groove 183 has such a width and an axial length that the crank arm 181 is allowed to move in the longitudinal direction of the impact cylinder 141 while swinging on the connecting shaft 128.
  • the crank arm 181 is U-shaped and allowed to move in the escape groove 183 formed in the peripheral wall of the impact cylinder 141.
  • the motion converting mechanism 113 can be disposed in parallel to the impact cylinder 141 in a region along the extending direction (the longitudinal direction) of the impact cylinder 141.
  • the length of the tool body 103 in the striking direction or the axial direction of the hammer bit 119 is defined by the extending lengths of the tool holder 137 for holding the hammer bit 119 and the impact cylinder 141 for housing the piston 129 and the striker 143. Therefore, the length of the tool body 103 in the striking direction can be shortened, compared with a known hammer drill in which the motion converting mechanism 113 is disposed in a rear position outside a region along the longitudinal direction of the impact cylinder 141.
  • the tool body 103 When performing a drilling operation with the hammer drill 101 constructed as described above, for example, on an inner wall surface of a U-shaped ditch, like the first embodiment, the tool body 103 can be inserted into the U-shaped ditch with the axis of the hammer bit 119 extending in the width direction of the ditch. In this case, the impact force of the striker 143 is linearly transmitted to the hammer bit 119. With this construction, compared with the construction in which the impact force of the striker is transmitted to the hammer bit via an angular attachment attached to the front end of the hammer drill, the impact force ofthe striker 143 can be transmitted to the hammer bit 119 without loss.
  • the handgrip 109 is configured as a D-shaped handle having the grip 109a designed to be held by a user.
  • the grip 109a extends in a direction transverse to the longitudinal direction of the body 103 and in parallel to the extending direction of the impact cylinder 141, and has upper and lower ends connected to the outer housing 105. With this construction, the handgrip 109 can be configured to extend within the length of the hammer drill 101 in the striking direction.
  • the trigger 147 for starting and stopping the driving motor 111 and the normal/reverse selector switch 149 are disposed on the handgrip 109.
  • the trigger 147 and the normal/reverse selector switch 149 are disposed in a front region (a lower region as viewed in FIG. 10 ) of the handgrip 109 in the striking direction (along the extending direction of the handgrip 109).
  • the handgrip 109 is designed and configured to be held such that the user's thumb and index finger are set on the front region of the handgrip 109 in the striking direction.
  • a rear end region of the outer housing 105 in the striking direction is designed as an auxiliary grip 163 which can be pressed with a user's whole palm.
  • the power transmitting mechanism 117 for transmitting the rotating output of the driving motor 111 to the hammer bit 119, rotation of an intermediate gear 185 which engages with the driving gear 121 driven by the driving motor 111 is transmitted to an intermediate shaft 186 via a torque limiter 187, and this rotation of the intermediate shaft 186 is transmitted from a small bevel gear 188 to the tool holder 137 via a large bevel gear 189 which engages with the small bevel gear 188.
  • the small bevel gear 188 is integrally formed with an axial end of the intermediate shaft 186.
  • the large bevel gear 189 is spline-fitted onto the tool holder 137 and rotates together with the tool holder 137.
  • the power transmitting mechanism 117 according to this embodiment has a single intermediate shaft, so that it is made simpler in structure compared with the power transmitting mechanism 117 of the first embodiment which has two intermediate shafts.
  • a crank arm 191 is formed by a linear rod-like member or a plate-like member.
  • the connecting shaft 128 of the piston 129 has an extension 128a which extends outward of the impact cylinder 141 through the escape groove 183, and the extension 128a is connected to a crank arm 191. Therefore, according to this modification, like in the second embodiment, the length of the tool body 103 in the striking direction can be shortened compared with the known hammer drill.
  • the trigger 147 for starting and stopping the driving motor 111 and the normal/reverse selector switch 149 are disposed in a rear region (an upper region as viewed in FIG. 14 ) of the handgrip 109 in the striking direction (along the extending direction of the handgrip 109).
  • the handgrip 109 is designed and configured to be held such that the user's thumb and index finger are set on the rear region of the handgrip 109 in the striking direction.
  • the hammer drill 101 is described as a representative example of an impact tool, but the teachings can be applied to a hammer in which the hammer bit 119 is caused to perform only linear movement in the axial direction.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Percussive Tools And Related Accessories (AREA)

Claims (7)

  1. Schlagwerkzeug zum Ausführen eines vorbestimmten Arbeitsvorganges an einem Werkstück durch zumindest lineare Bewegung eines Werkzeugbits, mit
    einem Antriebsmotor (111), der eine Drehachse aufweist,
    einem Werkzeughalter (137), der zum Halten eines Werkzeugbits (119) so angepasst ist, dass er eine relative Bewegung des Werkzeugbits in eine axiale Richtung des Werkzeugbits ermöglicht,
    einem Schlagelement (143), das dazu angepasst ist, sich linear in der axialen Richtung des Werkzeugbits zu bewegen und eine Schlagkraft dem Werkzeugbit aufzubringen,
    einem Schlagzylinder (141), der mit dem Werkzeughalter (137) verbunden ist, wobei der Schlagzylinder das Schlagelement (143) so aufnimmt, dass er eine relative Bewegung ermöglicht, und der Schlagzylinder eine Luftkammer (141a) aufweist, die zum Bewirken, dass komprimierte Luft auf das Schlagelement wirkt, angepasst ist,
    einem Bewegungsumwandlungsmechanismus (113), der dazu angepasst ist, eine Drehausgabe des Antriebsmotors (111) in eine lineare Bewegung umzuwandeln, und dabei komprimierte Luft in der Luftkammer (141a) des Schlagzylinders erzeugt,
    einem Handgriff (109, 109a), der so gestaltet ist, dass ihn ein Benutzer zum Betätigen des Schlagwerkzeugs halten kann,
    einem Werkzeugkörper (103), der ein vorderes Ende und ein hinteres Ende in seiner Längsrichtung aufweist, und der Werkzeugkörper (103) ein äußeres Gehäuse (105) aufweist, wobei das äußere Gehäuse (105) den Antriebsmotor (111) aufnimmt,
    bei dem der Werkzeughalter (137) in dem Bereich des vorderen Endes des Werkzeugkörpers (103) vorgesehen ist und der Handgriff (109, 109a) an dem hinteren Ende des Werkzeugkörpers (103) vorgesehen ist,
    bei dem sich sowohl der Werkzeughalter (137) als auch der Schlagzylinder (141) in der axialen Richtung des Werkzeugbits (119) erstrecken, wobei sich die axiale Richtung des Werkzeugbits (119) in eine Richtung transversal zur der Längsrichtung erstreckt,
    dadurch gekennzeichnet, dass
    der Werkzeugkörper (103) ein Getriebegehäuse (107) aufweist, das überwiegend durch das äußere Gehäuse (105) abgedeckt ist,
    bei dem das Getriebegehäuse (107) den Bewegungsumwandlungsmechanismus (113) und den Schlagzylinder (141) aufnimmt,
    bei dem die Länge des Werkzeugkörpers (103) in der axialen Richtung des Werkzeugbits (119) die Summe der Länge des Werkzeughalters (137), der Länge des Schlagzylinders (141), der Breite von Endwänden des äußeren Gehäuses (105) bzw. des Getriebegehäuses (107) an dem Ende des Schlagzylinders (141), das dem Werkzeugbit (119) gegenüberliegt, und optional der Breite einer Luftpassage (133) ist, die in der Endwand des Getriebegehäuses (107) ausgebildet ist.
  2. Schlagwerkzeug nach Anspruch 1, das weiter einen Kompressionsluftzuführungszylinder (131) zum Zuführen von komprimierter Luft zu der Luftkammer des Schlagzylinders aufweist, bei dem sich der Kompressionsluftzufiihrungszylinder in einer von einer Erstreckungsrichtung des Schlagzylinders (141) unterschiedlichen Richtung erstreckt.
  3. Schlagwerkzeug nach Anspruch 2, bei dem eine Breitenrichtung des Handgriffes mit der Erstreckungsrichtung des Schlagzylinders (141) zusammenfällt.
  4. Schlagwerkzeug nach Anspruch 3, bei dem die Erstreckungsrichtung des Kompressionsluftzuführungszylinders die axiale Richtung des Werkzeugbits kreuzt und die Erstreckungsrichtung des Kompressionsluftzuführungszylinders die Erstreckungsrichtung des Handgriffes kreuzt.
  5. Schlagwerkzeug nach Anspruch 1, bei dem der Bewegungsumwandlungsmechanismus (113) parallel zu dem Schlagzylinder (141) in einem vorbestimmten Bereich entlang der Erstreckungsrichtung des Schlagzylinders angeordnet ist.
  6. Schlagwerkzeug nach Anspruch 5, bei dem die Drehachse einer Drehwelle (125) des Bewegungsumwandlungsmechanismus (113) mit der Erstreckungsrichtung des Schlagzylinders (141) kreuzt.
  7. Schlagwerkzeug nach Anspruch 5 oder 6, bei dem die Erstreckungsrichtungen des Schlagzylinders (141) und des Handgriffs (109, 109a) parallel sind.
EP12774797.0A 2011-04-21 2012-04-19 Schlagwerkzeug Active EP2700476B1 (de)

Applications Claiming Priority (2)

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JP2011095090A JP2012223870A (ja) 2011-04-21 2011-04-21 打撃工具
PCT/JP2012/060635 WO2012144568A1 (ja) 2011-04-21 2012-04-19 打撃工具

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EP2700476A1 EP2700476A1 (de) 2014-02-26
EP2700476A4 EP2700476A4 (de) 2014-09-03
EP2700476B1 true EP2700476B1 (de) 2017-06-21

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JP7360891B2 (ja) * 2019-10-21 2023-10-13 株式会社マキタ ハンマドリル
JP7360892B2 (ja) * 2019-10-21 2023-10-13 株式会社マキタ 打撃工具
US11826891B2 (en) 2019-10-21 2023-11-28 Makita Corporation Power tool having hammer mechanism

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US1959458A (en) * 1928-03-19 1934-05-22 Christiansen Heinrich Tamping device for railway sleepers
DE1938738C3 (de) * 1969-07-30 1974-05-30 Daiichi Kikai Seisakusho Co. Ltd., Osaka Freikolben-Druckluftschlaggerät
JPS56126381U (de) * 1980-02-21 1981-09-25
DE3439475C2 (de) * 1984-10-27 1996-02-01 Bosch Gmbh Robert Winkelvorsatz für schlagend und rotierend arbeitende Werkzeugmaschinen
JP2541127Y2 (ja) * 1990-07-27 1997-07-09 日立工機株式会社 打撃穿孔機のアングルアタッチメント
JP3532504B2 (ja) * 1992-12-16 2004-05-31 株式会社マキタ 回転衝撃工具
JP2004114250A (ja) * 2002-09-27 2004-04-15 Hitachi Koki Co Ltd 打撃工具の潤滑機構
DE102006061625A1 (de) * 2006-12-27 2008-07-03 Robert Bosch Gmbh Elektrohandwerkzeugmaschine
DE102007000391A1 (de) * 2007-07-19 2009-01-22 Hilti Aktiengesellschaft Handwerkzeugmaschine mit Schlagwerk
JP4888329B2 (ja) * 2007-10-19 2012-02-29 日立工機株式会社 往復動工具
DE102007059896A1 (de) * 2007-12-12 2009-06-18 Robert Bosch Gmbh Handwerkzeugmaschinenschlagwerkeinheit
FR2938461B1 (fr) * 2008-11-19 2013-04-26 Inrs Inst Nat De Rech Et De Securite Pour La Prevention Des Accidents Du Travail Et Des Maladies Marteau anti-vibration
JP5395531B2 (ja) * 2009-06-19 2014-01-22 株式会社マキタ 作業工具
CN201565934U (zh) * 2009-11-06 2010-09-01 南京德朔实业有限公司 一种电动榔头

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WO2012144568A1 (ja) 2012-10-26
EP2700476A4 (de) 2014-09-03
EP2700476A1 (de) 2014-02-26

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