JP4456559B2 - Work tools - Google Patents

Description

  The present invention relates to a work tool that performs a predetermined machining operation by linearly moving a tip tool in a long axis direction.

  German Patent No. 19716976 (Patent Document 1) discloses a hammer drill. In the hammer drill described in Patent Document 1, a switching member for clutch switching is arranged on the upper surface of the work tool main body. In the crank chamber of the work tool main body, a crank mechanism that strikes a hammer bit as a tip tool, and a power transmission state that transmits driving force to the crank mechanism and a power cutoff state that interrupts transmission of the driving force. A clutch mechanism that can be switched at is arranged. The switching operation of the switching member by the user is transmitted as a vertical motion to the clutch switching member via the switching motion transmission member disposed in the crank chamber, and the clutch mechanism portion slides in the long axis direction (vertical direction) by this vertical motion. It is configured to be operated and switched to a power transmission state or a power cut-off state. In the configuration in which the switching member is disposed on the upper surface of the work tool main body as in Patent Document 1, the switching is performed regardless of the user's handedness as compared with the method in which the switching member is disposed on the side surface of the work tool main body. It is easy to operate the member and is easy to use, and when the hammer drill is placed on the ground or table, the switching member is less likely to interfere with the ground or table, and the switching member can be prevented from unexpectedly switching. Is advantageous.

By the way, the crank mechanism housed in the crank chamber, the gear mechanism for transmitting the rotational driving force of the motor to the crank mechanism, the clutch mechanism, and the like each require lubrication of sliding portions. In order to improve the lubrication (grease) around the sliding portion and improve the lubricity, it is important to set the volume of the crank chamber as small as possible and eliminate useless space. However, in the hammer drill described in Patent Document 1, a switching operation transmitting member for transmitting the switching operation of the switching member to the clutch switching member is arranged in the crank chamber. This inevitably increases the volume of the crank chamber and requires an operation space for the switching operation transmitting member, and as a result, there is still room for improvement in that the lubricity is lowered.
German Patent No. 19716976

  In view of this point, the present invention provides a technique that contributes to a reduction in the volume of a crank chamber while utilizing the upper surface arrangement of a switching member in a work tool in which a tip tool linearly moves in a long axis direction to perform a predetermined machining operation. For the purpose.

In order to achieve the above object, the invention described in each claim is configured.
According to the first aspect of the present invention, the working tool is configured in which the tip tool linearly moves in the long axis direction to perform a predetermined machining operation. As the “work tool” in the present invention, typically, an electric hammer in which the tip tool performs a striking operation in the long axis direction, or the tip tool performs a striking operation in the long axis direction, and a rotation operation around the long axis direction. An impact-type work tool such as a hammer drill corresponds to this, but any tool other than an impact-type work tool is suitably included as long as the tip tool is of a type that linearly moves in the long axis direction.
The work tool of the present invention includes a work tool main body, a crank chamber, a crank mechanism, and a clutch mechanism for a crank mechanism. The crank chamber is formed in the work tool main body, and is preferably set in a hermetically sealed manner, and is configured to contain a lubricant for lubrication of each mechanism portion accommodated in the crank chamber. The crank mechanism is arranged in the crank chamber and linearly moves the tip tool. The crank mechanism clutch mechanism is disposed in the crank chamber and is switched between a power transmission state in which driving force is transmitted to the crank mechanism and a power cutoff state in which transmission of the driving force is interrupted.

  The work tool of the present invention has a switching member, an opening, a rotating member, a switching operation transmission mechanism, and an operation means as a characteristic configuration. The switching member is disposed on the upper surface of the work tool main body, and allows the work tool user to switch the operating state of the clutch mechanism by manual operation. The opening is provided to connect the crank chamber and the outside. The rotating member is provided so as to be able to rotate while closing the opening. The switching operation transmission mechanism is disposed outside the crank chamber, connects the switching member and the rotating member, and transmits the switching operation of the switching member by the manual operation of the work tool user to the rotating member. The rotating member has an operating means extending in the direction of the crank chamber, and the operating means switches the state between the power transmission state and the power shut-off state of the clutch mechanism using the rotating operation of the rotating member. It is configured to do. In the present invention, “using the rotating motion of the rotating member” typically corresponds to an aspect in which an operating component in a direction intersecting the rotational axis direction of the rotating member is used. Further, as a mode of using a motion component in a direction crossing the rotational axis direction, typically, an arc motion corresponds to this, but a mode in which the motion means moves linearly in the vertical direction, for example, a rack and pinion. A gear mechanism is preferably included.

  According to the present invention, the switching member for switching the operating state of the clutch mechanism is arranged on the upper surface of the work tool main body. Therefore, regardless of the user's dominant hand, the switching member can be easily operated, and when the hammer drill is placed on the ground or a table, the switching member is not easily interfered with the ground or the table, and the switching member is unpredictable. It has the advantage that it can prevent switching. In the present invention, the switching operation transmission mechanism as means for transmitting the switching operation of the switching member to the rotating member is arranged outside the crank chamber, so that the volume of the crank chamber is transmitted to the switching operation. It is possible to reduce the amount corresponding to the mechanism. As a result, the lubricant easily rotates around the mechanism portion arranged in the crank chamber, and the lubrication effect is improved. In addition, since the clutch mechanism is switched using the rotation operation of the rotating member, the state in which the opening is closed by the rotating member can be maintained. For this reason, it is possible to rationally realize the switching of the clutch mechanism while avoiding the problem of leakage from the opening of the lubricant in the crank chamber, although the switching operation transmission mechanism is arranged outside the crank chamber. As described above, according to the present invention, while taking advantage of the upper surface arrangement of the work tool main body of the switching member, the volume of the crank chamber is reduced while preventing leakage of the lubricant in the crank chamber to the outside. It became possible to improve the lubricity of the indoor mechanism.

(Invention of Claim 2)
According to the second aspect of the present invention, the operating means in the work tool according to the first aspect is constituted by an eccentric pin provided at a position eccentric from the rotation axis of the rotating member, and the eccentric pin is formed by the rotating member. When rotating, the state of the clutch mechanism is switched by the vertical component due to the eccentric rotation operation around the rotation axis of the rotating member. According to the present invention, since the switching of the state of the clutch mechanism can be realized with a simple configuration in which a pin is provided on the rotating member, it is effective in simplifying the structure and reducing the cost.

(Invention of Claim 3)
According to the third aspect of the present invention, the switching operation transmission mechanism in the work tool according to the first or second aspect has the rotary shaft member that is rotatable about the rotation axis perpendicular to the rotation axis of the rotation member. The rotating shaft member and the rotating member are connected to each other by a plurality of bevel gears that mesh and engage with each other. According to the present invention, the rotation shaft member and the rotation member are configured to rotate around the rotation axis within the arrangement space, and the rotation shaft member and the rotation member are connected to each other by a plurality of bevel gears that mesh and engage with each other. Therefore, the space for accommodating these is small.

(Invention of Claim 4)
According to the fourth aspect of the present invention, the switching operation transmission mechanism in the work tool according to the first or second aspect is a swing member that is swingable about a swing axis that intersects the rotation axis of the rotary member. Have The swing member has a gear extending in the swing direction of the swing member. The rotating member has a circular gear. The swinging member and the rotating member are connected to each other through meshing engagement between the gear and the circular gear. According to the present invention, the rotating member is rotated using the swinging motion of the swinging member, and the swinging member can be formed thin in the direction intersecting the swinging direction. For this reason, the accommodation space of the rocking member set in the work tool main body is reduced in the direction crossing the rocking direction, which is effective in reducing the size of the work tool main body in the crossing direction.

(Invention of Claim 5)
According to the invention described in claim 5, the tip tool in the work tool according to any one of claims 1 to 4 is configured by a tool bit that performs linear motion in the major axis direction and rotational motion around the major axis. ing. The work tool includes a rotary drive mechanism that rotates the tool bit, and a clutch mechanism for the rotary drive mechanism that is switched between a power transmission state that transmits driving force to the rotary drive mechanism and a power cutoff state that blocks transmission of the driving force. And having. The switching member is a mode between a hammer drill mode in which the tool bit is driven by a combination of a linear motion and a rotational motion, a hammer mode in which the tool bit is driven only in a linear motion, and a drill mode in which the tool bit is driven only in a rotational motion. It is configured as a mode switching member that performs switching.
The work tool also has a clutch switching mechanism that switches between a power transmission state and a power cut-off state of the clutch mechanism for the rotational drive mechanism based on the switching operation of the mode switching member, and the switching member enters the hammer drill mode. When switched, both the crank mechanism clutch mechanism and the rotational drive mechanism clutch mechanism are switched to the power transmission state. When the switching member is switched to the hammer mode, the crank mechanism clutch mechanism is switched to the power transmission state. When the clutch mechanism for the rotational drive mechanism is switched to the power cutoff state and the switching member is switched to the drill mode, the clutch mechanism for the crank mechanism is switched to the power cutoff state and the clutch mechanism for the rotary drive mechanism is transmitted power. It is configured to be switched to a state.
According to the present invention, in the work tool configured to arrange the mode switching member for switching the drive mode of the tool bit on the upper surface of the work tool main body portion, three types among the hammer drill mode, the hammer mode, and the drill mode are provided. It became possible to switch modes.

  According to the present invention, there is provided a technique that contributes to a reduction in the volume of the crank chamber while utilizing the upper surface arrangement of the switching member in the work tool in which the tip tool linearly moves in the long axis direction to perform a predetermined machining operation. became.

  Hereinafter, embodiments of the present invention will be described in detail with reference to FIGS. This embodiment will be described using an electric hammer drill as an example of a work tool. FIG. 1 is a side sectional view showing the overall configuration of the electric hammer drill according to the present embodiment. As shown in FIG. 1, the hammer drill 101 according to the present embodiment is generally not shown for convenience in the main body portion 103 that forms the outline of the hammer drill 101 and the tip region (left side in the drawing) of the main body portion 103. A hammer bit 119 detachably attached via a hollow tool holder and a hand grip 109 gripped by a user connected to the opposite side of the main body 103 to the hammer bit 119 are mainly configured. The hammer bit 119 is held by a tool holder in a state in which relative linear movement in the major axis direction is possible and relative rotation in the circumferential direction is restricted. The main body 103 corresponds to the “work tool main body” in the present invention, and the hammer bit 119 corresponds to the “tip tool” in the present invention. For convenience of explanation, the hammer bit 119 side is referred to as the front, and the hand grip 109 side is referred to as the rear.

  The main body 103 includes a motor housing 105 that houses the drive motor 111, and a gear housing 107 that houses the motion conversion mechanism 113, the striking element 115, and the power transmission mechanism 117. The rotational output of the drive motor 111 is appropriately converted into a linear motion by the motion conversion mechanism 113 and then transmitted to the striking element 115, and the major axis direction of the hammer bit 119 (the left-right direction in FIG. 1) via the striking element 115. Generates an impact force on. The rotational output of the drive motor 111 is appropriately decelerated by the power transmission mechanism 117 and then transmitted to the hammer bit 119, and the hammer bit 119 is rotated in the circumferential direction. The drive motor 111 is energized and driven by a pulling operation of a trigger 109 a disposed on the hand grip 109. The power transmission mechanism 117 corresponds to a “rotation drive mechanism” in claim 5 of the present invention.

  2 to 4 are enlarged sectional views showing the main part of the hammer drill 101. The motion conversion mechanism 113 is mainly composed of a drive gear 121, a driven gear 123, a crankshaft 122, a crank plate 125, a crank arm 127, and a piston 129 as a driver, which are driven to rotate in a horizontal plane by a drive motor 111. The crank shaft 114, the crank plate 125, the crank arm 127, and the piston 129 constitute a crank mechanism 114. The crank mechanism 114 corresponds to the “crank mechanism” in the present invention. The piston 129 is slidably disposed in the cylinder 141 and performs a linear motion along the cylinder 141 as the drive motor 111 is driven to energize.

  The crankshaft 122 is disposed so that the major axis direction of the crankshaft 122 is a vertical direction (vertical direction) intersecting the major axis direction of the hammer bit 119, and a clutch is interposed between the crankshaft 122 and the driven gear 123. A member 124 is disposed. The clutch member 124 corresponds to the “clutch mechanism for the crank mechanism” in the present invention. The clutch member 124 is formed in a cylindrical shape having an overhanging flange portion 124b at one end (upper end) in the long axis direction, and is relatively movable in the long axis direction on the crankshaft 122, and in the circumferential direction. It is attached to rotate integrally, and has clutch teeth 124a on the outer periphery. On the other hand, the driven gear 123 is provided with a circular recess, and clutch teeth 123a are formed on the inner periphery of the circular recess. The clutch member 124 is configured such that the clutch tooth 124a of the clutch member 124 meshes with the clutch tooth 123a of the driven gear 123 or the meshing engagement is released by moving in the major axis direction on the crankshaft 122. It is said. That is, the clutch member 124 is between a power transmission state (see FIGS. 2 and 3) in which the driving force of the driven gear 123 is transmitted to the crankshaft 122 and a power cutoff state (see FIG. 4) in which the transmission of the driving force is interrupted. The clutch teeth 124a are normally urged by the urging spring 126 in a direction in which the clutch teeth 124a are engaged with and engaged with the clutch teeth 123a of the driven gear 123. The switching of the operating state of the clutch member 124 will be described later.

  The striking element 115 is a striker 143 that is slidably disposed on the bore inner wall of the cylinder 141, and is slidably disposed on the tool holder, and transmits the kinetic energy of the striker 143 to the hammer bit 119. An impact bolt 145 (see FIG. 1) as a meson is mainly used. The striker 143 is driven via an air spring in the air chamber 141a of the cylinder 141 in accordance with the sliding motion of the piston 129, and collides with (impacts) an impact bolt 145 that is slidably disposed on the tool holder. The striking force is transmitted to the hammer bit 119 via 145.

  The power transmission mechanism 117 meshes with the intermediate gear 132 that meshes with and engages with the drive gear 121, the intermediate shaft 133 that rotates with the intermediate gear 132, the small bevel gear 134 that is rotationally driven in the horizontal plane with the intermediate shaft 133, and the small bevel gear 134. A large bevel gear 135 that engages and rotates in a vertical plane and a slide sleeve 147 that meshes with and engages with the large bevel gear 135 and is driven to rotate are mainly configured. The rotational driving force of the slide sleeve 147 is transmitted to the tool holder via the cylinder 141 that rotates together with the slide sleeve 147, and further transmitted to the hammer bit 119 held by the tool holder. The slide sleeve 147 is configured to be relatively movable on the cylinder 141 in the long axis direction of the hammer bit and to rotate integrally in the circumferential direction.

  The slide sleeve 147 constitutes a clutch mechanism in the power transmission mechanism 117, and has a clutch tooth 147a at one end outer peripheral portion in the major axis direction, and is relatively moved rearward (hand grip side) with respect to the cylinder 141. In some cases, when the clutch teeth 135a formed on the large bevel gear 135 are engaged with each other and moved forward (hammer bit side), the engagement engagement is released. That is, the slide sleeve 147 has a power transmission state (see FIGS. 3 and 4) that transmits the rotational driving force of the large bevel gear 135 to the cylinder 141 and a power cutoff state (see FIG. 2) that interrupts transmission of the driving force. It is possible to switch between them. The slide sleeve 147 is normally urged by the urging spring 148 in a direction in which the clutch teeth 147a are engaged with and engaged with the clutch teeth 135a of the large bevel gear 135. The slide sleeve 147 corresponds to the “rotary drive mechanism clutch mechanism” in the present invention. The switching of the operating state of the slide sleeve 147 will be described later.

  Further, the slide sleeve 147 has rotation lock teeth 147b on the other end side (front end side) in the long axis direction. When the slide sleeve 147 is moved forward and switched to the power cut-off state (when the hammer bit 119 is driven in the hammer mode), the lock ring 149 provided in a fixed state in the circumferential direction with respect to the gear housing 107. This makes it possible to perform a so-called variolock that restricts free movement in the circumferential direction of the cylinder 141, the tool holder, and the hammer bit 119.

  The motion conversion mechanism 113 and the power transmission mechanism 117 described above are accommodated in a crank chamber 151 that is an internal space of the gear housing 107, and the sliding portion is lubricated by a lubricant (grease) enclosed in the crank chamber 151. The

  Next, the mode switching mechanism 153 that switches the driving mode of the hammer bit 119 will be described with reference to FIGS. The mode switching mechanism 153 includes a hammer mode in which the hammer bit 119 performs only a striking operation, a hammer drill mode in which the hammer bit 119 performs a striking operation and a rotation operation, and a drill mode in which the hammer bit 119 performs only a rotation operation. It is possible to switch at.

  2 to 4, the mode switching mechanism 153 includes a mode switching member 155, a first switching mechanism 157 that switches the clutch member 124 of the crank mechanism 114 based on the switching operation of the mode switching member 155, The second switching mechanism 159 that switches the slide sleeve 147 of the transmission mechanism 117 is mainly configured. The mode switching member 155 corresponds to the “switching member” in the present invention. The mode switching member 155 is disposed outside the upper surface of the gear housing 107 (upper side in FIG. 1). That is, the mode switching member 155 is disposed above the crank mechanism 114. As shown in FIGS. 5 to 7, the mode switching member 155 includes a disk 155 a with an operation grip 155 b and is attached to the gear housing 107 so as to be rotatable in a horizontal plane. On the side of the gear housing 107, marks indicating the three mode positions, the hammer mode position, the hammer drill mode position, and the drill mode position, are marked at intervals of 120 degrees in the circumferential direction. The mode switching member 155 can be switched to a predetermined mode position by matching the pointer of the grip 155b. FIG. 5 shows a state where the mode switching member 155 is switched to the hammer mode, FIG. 6 shows a state where the mode switching member 155 is switched to the hammer drill mode, and FIG. 7 shows that the mode switching member 155 is drilled. The state switched to the mode is shown.

  When the mode switching member 155 is rotated for mode switching, the first switching mechanism 157 rotates the first eccentric pin 167 around the rotation axis of the rotating member 166 (eccentric rotation) so that the clutch of the crank mechanism 114 The member 124 is configured to be switched. The first switching mechanism 157 mainly includes a first gear 161, a second gear 162, a rotation transmission shaft 163, a third gear 164, a fourth gear 165, a rotating member 166, and a first eccentric pin 167.

  The first gear 161 is provided to rotate in the horizontal plane together with the mode switching member 155 when the mode switching member 155 is rotated in the horizontal plane. The second gear 162 meshes with and engages with the first gear 161 and is integrally formed with one end (upper end) in the long axis direction of the rotation transmission shaft 163. The rotation transmission shaft 163 is arranged so that the major axis direction thereof is parallel to the major axis direction of the crankshaft 122, that is, the vertical direction. A third gear 164 is formed integrally with the other end (lower end) in the major axis direction of the rotation transmission shaft 163, and the third gear 164 is formed integrally with the rotating member 166. The gear 165 is meshed and engaged. The rotation member 166 is disposed on the lower side of the rotation transmission shaft 163 so that the major axis direction thereof is orthogonal to the rotation transmission shaft 163, that is, the horizontal direction. The third gear 164 and the fourth gear 165 are each constituted by a bevel gear, and are engaged with each other.

  Therefore, when the mode switching member 155 is switched, the rotation transmission shaft 163 is rotated in the horizontal plane via the first gear 161 and the second gear 162, and the rotation operation of the rotation transmission shaft 163 is further increased. The rotation is transmitted to the rotating member 166 through the third gear 164 and the fourth gear 165 as a rotating motion in the vertical plane. The first eccentric pin 167 is provided on the axial end surface of the rotation member 166 at a position eccentric from the rotation axis of the rotation member 166 by a predetermined amount. The first eccentric pin 167 is disposed so as to face the lower surface of the flange portion 124 b of the clutch member 124. Therefore, the first eccentric pin 167 has an up-down direction component (long-axis direction component of the crankshaft 122) when the rotating member 166 is rotated in the vertical plane and eccentrically rotates around the rotation axis of the rotating member 166. The clutch member 124 is moved up and down along the crankshaft 122 while being engaged with the flange portion 124b of the clutch member 124, thereby switching the clutch member 124 between the power transmission state and the power cut-off position. Operate. The first gear 161, the second gear 162, the rotation transmission shaft 163, the third gear 164, and the fourth gear 165 constitute a switching operation transmission mechanism 169. This switching operation transmission mechanism 169 corresponds to the “switching operation transmission mechanism” in the present invention. The rotating member 166 corresponds to the “rotating member” in the present invention, and the first eccentric pin 167 corresponds to the “operation means” in the present invention.

  Among the constituent members constituting the first switching mechanism 157, the first gear 161 and the second gear 162 are disposed in the crank chamber 151, but the rotation transmission shaft 163, the third gear 164, the fourth gear 165, and The rotating member 166 is disposed outside the crank chamber 151. That is, a housing space 152 is formed in the gear housing 107 so as to accommodate the switching operation transmission mechanism 169, and the rotation transmission shaft 163, the third gear 164, the fourth gear 165, and the rotating member are accommodated in the housing space 152. 166 is arranged. The accommodation space 152 corresponds to “external” in the present invention. The crank chamber 151 and the accommodation space 152 are communicated with each other through a circular opening 168. The opening 168 corresponds to the “opening” in the present invention. The rotating member 166 is disposed in a state in which the circular outer peripheral portion is closely fitted to the opening 168 so that the circular outer periphery closes the opening 168, and can rotate in this fitted state. The eccentric pin 167 extends substantially horizontally into the crank chamber 151 through the opening 168 and is disposed so as to face the lower surface of the flange portion 124 b of the clutch member 124.

  When the mode switching member 155 is switched to the hammer mode or the hammer drill mode, the first eccentric pin 167 is positioned at the same position as or below the rotation axis of the rotating member 166 in the vertical direction as shown in FIG. 2 or FIG. Moved to. At this time, the clutch member 124 is moved downward by the biasing spring 126, and the clutch teeth 124 a are engaged with the clutch teeth 123 a of the driven gear 123. That is, the clutch member 124 is switched to the power transmission state. On the other hand, when the mode switching member 155 is switched to the drill mode, the first eccentric pin 167 is moved to a position above the rotation axis of the rotating member 166 in the vertical direction as shown in FIG. At this time, the clutch member 124 is moved upward against the biasing force of the biasing spring 126 by the eccentric pin 167, and the meshing engagement of the clutch teeth 124a and 123a is released. That is, the clutch member 124 is switched to the power cut-off state.

  Next, the second switching mechanism 159 will be described mainly with reference to FIGS. The second switching mechanism 159 is configured such that when the mode switching member 155 is operated for mode switching, the U-shaped frame member 173 moves linearly in the long axis direction of the cylinder 141 to slide the power transmission mechanism 117. 147 is configured to perform a switching operation. The second switching mechanism 159 is mainly composed of a substantially U-shaped frame member 173 arranged in the crank chamber 151 in a plan view. The frame member 173 corresponds to a “clutch switching mechanism” in claim 5 of the present invention.

  As shown in FIGS. 8 to 10, the frame member 173 passes through a base plate portion 173 a that extends horizontally in a direction intersecting the major axis direction of the cylinder 141, and an outer space portion of the large bevel gear 135. It consists of two left and right leg portions 173b that extend horizontally in the long axis direction. The base plate part 173a has a connecting pin 173c at each end in the extending direction, and the base pin part 173a and the leg part 173b are in the major axis direction of the cylinder 141 by engaging the connecting pin 173c with the recess of the leg part 173b. It is set as the structure which moves integrally. An oblong hole 173d is formed in the substrate portion 173a, and a second eccentric pin 175 (shown in cross section in FIGS. 8 to 10) is engaged with the oblong hole 173d. The second eccentric pin 175 is provided on the lower surface of the first gear 161 of the first switching mechanism 157 described above at a position eccentric from the rotation axis of the first gear 161 by a predetermined amount. When rotating around the axis, the frame member 173 is configured to move in the long axis direction of the cylinder 141 by the front-rear direction component (long axis direction component of the cylinder 141).

  Therefore, when the mode switching member 155 is switched, the frame member 173 is linearly moved in the major axis direction of the cylinder 141 by the second eccentric pin 175 engaged with the oblong hole 173c. The leg portion 173 b extends through the outer surface area of the large bevel gear 135, and its extending direction end reaches the outside of the slide sleeve 147. An engaging end 173e that can be engaged with the step 147c of the slide sleeve 147 in the extending direction is provided at the end in the extending direction. The engagement end portion 173e is formed by bending the end portion of the leg portion 173b inward (slide sleeve 147 side).

  When the mode switching member 155 is switched to the hammer mode, the frame member 173 is moved forward (to the left in the drawing) by the second eccentric pin 175, as shown in FIGS. The stepped portion 147c of the slide sleeve 147 is pushed forward against the biasing spring 148 by the end portion 173e. As a result, the slide sleeve 147 is moved forward away from the large bevel gear 135, and the clutch teeth 147a of the slide sleeve 147 are separated from the clutch teeth 135a of the large bevel gear 135 to release the meshing engagement. That is, the slide sleeve 147 is switched to the power cut-off state. On the other hand, when the mode switching member 155 is switched to the hammer drill mode or the drill mode, the frame member 173 is rearward (rightward in the drawing) by the second eccentric pin 175, as shown in FIG. 3 and FIG. 9 or FIG. 4 and FIG. The engagement end 173e at the tip of the leg is moved away from the step 147c of the slide sleeve 147. Then, the slide sleeve 147 is moved rearward toward the large bevel gear 135 by the urging force of the urging spring 148, and the clutch teeth 147a of the slide sleeve 147 are engaged with and engaged with the clutch teeth 135a of the large bevel gear 135. That is, the slide sleeve 147 is switched to the power transmission state.

  When the mode switching member 155 is switched to the hammer mode, the slide sleeve 147 is placed in the power cut-off state, and at the same time, the rotation locking tooth 147b is engaged with the tooth 149a of the lock ring 149, thereby causing the circumferential direction. Movement is regulated. That is, the variolock is activated.

Next, an operation and usage method of the hammer drill 101 configured as described above will be described. When the user switches the mode switching member 155 from the hammer drill mode or the drill mode to the hammer mode shown in FIG. 5, in the first switching mechanism 157, the first gear 161, the second gear 162, the rotation transmission shaft 163, The rotating member 166 is rotated through the third and fourth gears 164 and 165. Accordingly, as shown in FIG. 2, the first eccentric pin 167 rotates about 120 degrees around the rotation axis of the rotating member 166 and moves downward when viewed from the position in the hammer drill mode or the drill mode. The clutch member 124 is separated from the flange portion 124b. For this reason, the clutch member 124 is moved downward close to the driven gear 123 by the urging spring 126, and the clutch teeth 124a of the clutch member 124 are engaged with the clutch teeth 123a of the driven gear 123 to enter the power transmission state. Can be switched.
On the other hand, in the second switching mechanism 159, the second eccentric pin 175 rotates about 120 degrees around the rotation axis of the first gear 161 when viewed from the position in the hammer drill mode or the drill mode, and the frame member 173 is moved forward ( To the hammer bit 115 side). As shown in FIGS. 2 and 8, the frame member 173 that moves forward pushes the slide sleeve 147 forward by the engaging portion end portion 173 e of the leg portion 173 b, and the clutch teeth 147 a of the slide sleeve 147 has the large bevel gear 123. The slide sleeve 147 is separated from the clutch teeth 123a and switched to the power cut-off state. Further, the rotation locking tooth 147b of the slide sleeve 147 is engaged with and engaged with the tooth 147b of the lock ring 149, and the vario lock is activated.

  In the case where the hammer bit 119 is driven in the hammer mode, the hammer bit 119 is adjusted (positioned) so as to be in a predetermined direction in the circumferential direction. This adjustment operation is performed by moving the mode switching member 155 to the hammer mode position. And a hammer drill mode position, or an intermediate position (neutral position) not shown for convenience between the hammer mode position and the drill mode position. That is, in this intermediate position, the meshing engagement between the clutch teeth 147a of the slide sleeve 147 and the clutch teeth 135a of the large bevel gear 135 is released, and the rotation locking teeth 147b of the slide sleeve 147 and the lock ring 149 The meshing engagement with the tooth 149a is released. After adjusting the direction of the hammer bit 119 in this neutral state, when the mode switching member 155 is switched to the hammer mode, the above-described bariolock state is established, and the hammering operation can be performed with the orientation of the hammer bit 119 held constant. It becomes.

  In this manner, when the mode switching member 155 is switched to the hammer mode and the trigger 109a is pulled and the drive motor 111 is energized and driven, the rotational motion of the drive motor 111 is converted into linear motion by the crank mechanism 114. The piston 129 is slid linearly along the cylinder 141. The striker 143 linearly moves in the cylinder 141 and collides with the impact bolt 145 due to a change in air pressure in the air chamber 141a of the cylinder 141 accompanying the sliding movement of the piston 129, that is, the action of an air spring. The kinetic energy is transmitted to the hammer bit 119. At this time, since the slide sleeve 147 of the power transmission mechanism 117 is switched to the power cut-off state, the hammer bit 115 does not rotate. For this reason, in the hammer mode, it is possible to perform a predetermined hammer operation only by the hammering operation (hammer operation) of the hammer bit 115.

  Next, when the mode switching member 155 is switched from the hammer mode to the hammer drill mode shown in FIG. 6, as shown in FIG. 3, the first eccentric pin 167 of the first switching mechanism 157 is viewed from the position in the hammer mode. It rotates about 120 degrees around the rotation axis of the rotating member 166, and approaches the flange portion 124b of the clutch member 124, but only abuts or faces the flange portion 124b with a slight gap. It does n’t come. For this reason, the clutch member 124 is maintained in a power transmission state. On the other hand, the second eccentric pin 175 of the second switching mechanism 159 rotates about 120 degrees around the rotation axis of the first gear 161 when viewed from the position in the hammer mode, and the frame member 173 is moved as shown in FIG. Move backwards. As a result, the engagement end portion 173c of the frame member 173 is separated from the slide sleeve 147, so that the slide sleeve 147 is moved toward the large bevel gear 135 by the urging force of the urging spring 148, and the clutch teeth 147a are moved to the large bevel gear 135. The clutch teeth 135a are engaged with each other and switched to the power transmission state.

  In this state, when the drive motor 111 is energized and driven by pulling the trigger 109a of the handgrip 109, the crank mechanism 114 is driven, as in the hammer mode, via the striker 143 and the impact bolt 145 constituting the striking element 115. Thus, kinetic energy is transmitted to the hammer bit 115. On the other hand, the rotational output of the drive motor 111 is transmitted as a rotational motion to the cylinder 141 via the power transmission mechanism 117, and further held in a state where relative rotation is restricted by the tool holder connected to the cylinder 141 and the tool holder. Is transmitted to the hammer bit 119 as a rotational motion. That is, in the hammer drill mode, the hammer bit 119 is driven by a combined operation of a hammering operation (hammer operation) and a rotation operation (drilling operation), whereby a predetermined hammer drill operation can be performed on the workpiece.

  Next, when the mode switching member 155 is switched from the hammer drill mode to the drill mode shown in FIG. 7, as shown in FIG. 4, the first eccentric pin 167 of the first switching mechanism 157 is viewed from the position in the hammer drill mode. Then, it rotates about 120 degrees around the rotation axis of the rotating member 166, moves to the highest position in the vertical direction, and pushes up the flange portion 124b of the clutch member 124 upward. That is, the clutch member 124 is moved upward away from the driven gear 123, the clutch teeth 124a of the clutch member 124 are separated from the clutch teeth 123a of the driven gear 123, and the meshing engagement is released. Thus, the clutch member 124 is switched to the power cut-off state. On the other hand, the second eccentric pin 175 of the second switching mechanism 159 rotates about 120 degrees around the rotation axis of the first gear 161 when viewed from the position in the hammer drill mode, but at this time, as shown in FIG. The second eccentric pin 175 moves in the arc region of the oval hole 173d of the base plate part 173a in the frame member 173, and the front-rear direction component during the rotation operation is not transmitted to the frame member 173. For this reason, the frame member 173 is maintained at the same position as in the hammer drill mode, and the slide sleeve 147 is held in the power transmission state.

  In this state, when the drive motor 111 is energized by pulling the trigger 109a of the handgrip 109, the clutch member 124 is switched to the power cut-off state, so that the crank mechanism 114 is not driven and the hammer bit 119 is hit. No action is taken. On the other hand, in the power transmission mechanism 117, since the slide sleeve 147 is in a power transmission state, the rotational output of the drive motor 111 is transmitted to the hammer bit 119 as a rotational motion. That is, in the drill mode, the hammer bit 119 is driven only by a rotation operation (drill operation), and thereby a predetermined drill operation can be performed on the workpiece.

  In the electric hammer drill 101 according to the present embodiment, the mode switching member 155 is arranged on the outer upper surface of the gear housing 107, that is, on the upper surface side of the main body 103. According to this configuration, when the hand grip 109 is held with one hand, the mode switching member 155 can be easily operated even if the other hand is either the left hand or the right hand. That is, compared with the configuration in which the mode switching member 155 is disposed on the side surface of the main body 103, the switching operation of the mode switching mechanism 161 can be easily performed regardless of the user's dominant hand, and convenience is improved. . Further, the mode switching member 155 disposed on the upper surface of the main body 103 is less likely to interfere with the ground or table when the hammer drill 101 is placed on the ground or table. This can prevent a problem that the mode switching member 155 is unexpectedly switched.

Further, according to the present embodiment, the rotation transmission shaft 163, the third and fourth gears 164 as the constituent members constituting the switching operation transmission mechanism 169 for transmitting the switching operation of the mode switching member 155 to the rotation member 166. , 165 and the rotating member 166 are arranged outside the crank chamber 151. For this reason, it becomes possible to reduce the volume of the crank chamber 151 by an amount not accommodating these components. This means that the lubricant enclosed in the crank chamber 151 can easily go to the sliding portions of the crank mechanism 114 and the motion transmission mechanism 117 accommodated in the crank chamber 151, and the lubrication performance of each mechanism portion is improved. . Further, as the volume of the crank chamber 151 decreases, the amount of lubricant enclosed in the crank chamber 151 can be reduced.
In the present embodiment, the state of the clutch member 124 is switched using the rotational operation of the rotating member 166. For this reason, the opening 168 connecting the crank chamber 151 and the accommodation space 152 can be always closed by the rotating member 166. As a result, although the switching operation transmission mechanism 169 is arranged outside the crank chamber 151, the switching of the clutch member 124 can be rationally realized while avoiding the problem of lubricant leakage in the crank chamber 151.

  Further, according to the present embodiment, in the configuration in which the mode switching member 155 and the clutch member 124 are vertically arranged with the crank mechanism 114 interposed therebetween, the rotation transmission shaft 163 extending in the vertical direction and the rotation transmission shaft are provided. By using a rotating member 166 with an eccentric pin 167 arranged in a crossing manner at 163, the clutch member 124 can be switched to a power transmission state or a power cutoff state while avoiding interference with the crank mechanism 114. A rational switching means is established. In this case, the rotation transmission shaft 163 and the rotation member 166 are configured to rotate at the arranged positions, and the rotation transmission shaft 163 and the rotation member 166 are moved by the third and fourth gears 164 and 165 formed of bevel gears. Because of the concatenated structure, there is little space to accommodate them.

  Further, in the present embodiment, the operation means for switching the clutch member 124 to the power transmission state or the power cutoff state is constituted by the eccentric pin 167 provided at a position eccentric from the rotation axis of the rotation member 166, so that the configuration is simple. However, the switching of the state of the clutch member 124 can be realized, which is effective in simplifying the structure and reducing the cost.

Further, according to the present embodiment, the rotation transmission shaft 163 and the rotation member 166 are arranged outside the crank chamber 151, so that the crank chamber 151 is connected to the crank mechanism 144 with the bearing 128 supporting the crank shaft 122 as a boundary. Can be divided into a lower chamber (gear chamber) in which various gears and a clutch member 124 are accommodated. The pressure in the upper chamber of the crank chamber 151 varies due to the linear motion of the piston 129 when the crank mechanism 114 is driven.
By the way, in a hammer drill having a configuration in which the main body 103 is provided with a dynamic vibration absorber in order to reduce the vibration in the long axis direction of the hammer bit generated by the hammering operation of the hammer bit 119, the fluctuating pressure generated in the crank chamber 151 is used. In some cases, a so-called forced vibration method is employed in which the weight of the dynamic vibration absorber is actively driven to suppress vibration. According to the present embodiment, as the crank chamber 151 is divided into the upper chamber and the lower chamber as described above, the pressure fluctuation range in the upper chamber can be increased. It can be used as a pressure for forced vibration to enhance the vibration suppression function of the dynamic vibration absorber.

(Second embodiment of the present invention)
Next, a second embodiment of the present invention will be described with reference to FIGS. This embodiment relates to a change of switching means for switching the clutch member 124 of the crank mechanism 114 between the power transmission state and the power cutoff state in the hammer drill 101 according to the first embodiment. Therefore, components substantially equivalent to those of the first embodiment described above are denoted by the same reference numerals as those of the first embodiment, and description thereof is omitted.

  11 and 12 are sectional views showing the main part of the hammer drill 101 provided with the first switching mechanism 181 according to the present embodiment. 13 shows the first switching mechanism 181 as a plan view, and FIG. 14 shows the first switching mechanism 181 as a side view. The first switching mechanism 181 according to the present embodiment is mainly composed of a swing member 183 and a rotation member 185. The swing member 183 constitutes a switching operation transmission mechanism that transmits the switching operation of the mode switching member 155 to the rotating member 185. The swing member 183 is configured by a plate-like member having a substantially L-shaped cross-section formed by a horizontal plate portion 183a and a vertical plate portion 183b. The horizontal plate portion 183a is disposed at a position below the mode switching member 155, and a front end portion (hammer bit side) of the horizontal plate portion 183a is attached to be swingable in a horizontal plane with a pin portion 107a provided on the gear housing 107 as a fulcrum. . Further, the horizontal plate portion 183a has a long hole 183c extending in the front-rear direction (long axis direction of the cylinder 141), and the eccentric portion 155c provided in the mode switching member 155 is engaged with the long hole 183c. . Thereby, when the mode switching member 155 is rotated, the swing member 183 is swung horizontally clockwise or counterclockwise with the pin portion 107a as a fulcrum. The long hole 183c may be provided in the mode switching member 155, and the eccentric portion 155c may be provided in the horizontal plate portion 183a.

  The vertical plate portion 183 b of the swing member 183 is disposed outside the crank chamber 151, that is, in the accommodation space 152 formed in the gear housing 107. The vertical plate portion 183b is formed in an arc shape centering on the pin portion 107a, and extends downward from a connecting portion with the horizontal plate portion 183a, and extends in the swinging direction at the lower end portion thereof. A gear 183d is formed. The gear 183d meshes with and engages with a circular gear 185a formed on the rotating member 185. The rotating member 185 has a first eccentric pin 187, and the first eccentric pin 187 extends from the opening 188 into the crank chamber 151 and can be engaged with the lower surface of the flange portion 124b of the clutch member 124. This is the same as in the first embodiment. A guide groove 183e extending in the swinging direction is formed in the vertical plate portion 183b, and a guide pin 107b provided in the gear housing 107 and projecting in the horizontal direction is engaged with the guide groove 183e. For this reason, the swing member 183 swings while being guided by the guide pin 107b, and the swing operation is stabilized.

  The first switching mechanism 181 according to the present embodiment is configured as described above. Therefore, when the mode switching member 155 is switched for mode switching, the swinging member 183 is swung clockwise or counterclockwise around the pin portion 107a by the eccentric portion 155c of the mode switching member 155. Accordingly, the rotating member 185 is rotated via the gears 183d and 185a. When the rotation member 185 is rotated, the vertical position of the first eccentric pin 187 that rotates around the rotation axis of the rotation member 185 changes, and thereby the clutch member 124 moves in the longitudinal direction of the crankshaft 122. Then, similarly to the case of the first embodiment, the operation is switched to the power transmission state or the power cutoff state. FIG. 12 shows a state where the mode switching member 155 is switched to the hammer drill mode and the clutch member 124 is switched to the power transmission state, and FIG. 13 shows that the mode switching member 155 is switched to the drill mode and the clutch member 124 is switched. The state switched to the power cut-off state is shown.

  According to the present embodiment, the rotating member 185 having the eccentric pin 187 for switching the operating state of the clutch member 124, and the swinging member 183 for transmitting the switching operation of the mode switching member 155 to the rotating member 185, Each of them is arranged outside the crank chamber 151. Therefore, as in the case of the first embodiment described above, the volume of the crank chamber 151 is reduced while avoiding the problem of lubricant leakage in the crank chamber 151, and the crank mechanism 114 or the motion transmission mechanism 117 is lubricated by the lubricant. It became possible to increase the effect.

  In this embodiment, the rotating member 185 is rotated by using the swinging motion of the swinging member 183. The swinging member 183 is moved in the direction intersecting the swinging direction, that is, the front-rear direction. It can be formed thin. For this reason, the accommodation space 152 set in the gear housing 107 can be reduced in the front-rear direction, and as a result, the main body 103 can be reduced in the front-rear direction.

It is a sectional side view showing the whole hammer drill composition concerning a 1st embodiment of the present invention. It is a sectional side view which shows the principal part of a hammer drill, and shows the state switched to hammer mode. It is a sectional side view which shows the principal part of a hammer drill, and shows the state switched to hammer drill mode. It is a sectional side view which shows the principal part of a hammer drill, and shows the state switched to drill mode. It is a top view which shows a mode switching member, and shows the state switched to hammer mode. It is a top view which shows a mode switching member, and shows the state switched to hammer drill mode. It is a top view which shows a mode switching member, and shows the state switched to drill mode. It is a plane sectional view showing the 2nd change mechanism, and shows the state changed to hammer mode. It is a plane sectional view showing the 2nd change mechanism, and shows the state changed to hammer drill mode. It is a plane sectional view showing the 2nd change mechanism, and shows the state changed to drill mode. It is a sectional side view which shows the principal part of the hammer drill which concerns on 2nd Embodiment of this invention, and shows the state switched to hammer drill mode. It is a sectional side view which shows the principal part of the hammer drill which concerns on 2nd Embodiment of this invention, and shows the state switched to drill mode. It is a top view which shows a rocking | swiveling member. It is a side view which shows a rocking | swiveling member and a rotation member.

Explanation of symbols

101 Hammer drill (work tool)
103 Main body (work tool main body)
105 Motor housing 107 Gear housing 107a Pin portion 107b Guide pin 109 Hand grip 109a Trigger 111 Drive motor 113 Motion conversion mechanism 114 Crank mechanism 115 Stroke element 117 Power transmission mechanism 119 Hammer bit (tip tool)
121 Drive gear 122 Crankshaft 123 Driven gear 123a Clutch tooth 124 Clutch member 124a Clutch tooth 124b Flange portion 125 Crank plate 126 Energizing spring 127 Crank arm 128 Bearing 129 Piston 132 Intermediate gear 133 Intermediate shaft 134 Small bevel gear 135 Large bevel gear 135a Clutch tooth 141 Cylinder 141a Air chamber 143 Strike 145 Impact bolt 147 Slide sleeve 147a Clutch tooth 147b Rotation lock tooth 147c Stepped portion 148 Biasing spring 149 Lock ring 149a Teeth 151 Crank chamber 152 Housing space 153 Mode switching mechanism 155 Mode switching member (switching member )
155a Disc 155b Operation grip 155c Eccentric part 157 First switching mechanism 159 Second switching mechanism 161 First gear 162 Second gear 163 Rotation transmission shaft (switching operation transmission mechanism)
164 Third gear 165 Fourth gear 166 Rotating member 167 First eccentric pin (operation means)
168 Opening portion 169 Switching operation transmission mechanism 173 Frame member 173a Substrate portion 173b Leg portion 173c Connection pin 173d Oval hole 173e Engagement end portion 175 Second eccentric pin 181 First switching mechanism 183 Swing member (switching operation transmission mechanism)
183a Horizontal plate portion 183b Vertical plate portion 183c Long hole 183d Gear 183e Guide groove 185 Rotating member 185a Circular gear 187 First eccentric pin

Claims (5)

A work tool that performs a predetermined machining operation by moving the tip tool in a linear direction in the long axis direction,
A work tool body,
A crank chamber formed in the work tool body,
A crank mechanism that is disposed in the crank chamber and linearly moves the tip tool;
A crank mechanism clutch mechanism disposed in the crank chamber and switched between a power transmission state for transmitting a driving force to the crank mechanism and a power cutoff state for interrupting the transmission of the driving force;
A switching member that is disposed on the upper surface of the work tool main body, and that allows the work tool user to switch the operating state of the clutch mechanism by manual operation;
An opening connecting the crank chamber and the outside;
A rotating member capable of rotating while closing the opening;
A switching operation transmission mechanism disposed outside the crank chamber for connecting the switching member and the rotating member and transmitting a switching operation of the switching member by a manual operation of a work tool user to the rotating member; And
The rotating member has operating means extending in the crank chamber direction,
The operation tool is configured to switch a state between a power transmission state and a power cut-off state of the clutch mechanism by using a rotation operation of the rotating member. The work tool according to claim 1,
The operating means is constituted by an eccentric pin provided at a position eccentric from the rotational axis of the rotating member, and the eccentric pin is caused by an eccentric rotational operation around the rotational axis of the rotating member when the rotating member rotates. A work tool characterized in that the state of the clutch mechanism is switched by a vertical component. The work tool according to claim 1 or 2,
The switching operation transmission mechanism includes a rotation shaft member that is rotatable about a rotation axis orthogonal to the rotation axis of the rotation member, and a plurality of bevel gears that mesh with and engage with the rotation shaft member and the rotation member. A work tool characterized by being connected. The work tool according to claim 1 or 2,
The switching operation transmission mechanism includes a swinging member that is swingable about a swinging axis that intersects the rotation axis of the rotating member,
The swing member has a gear extending in the swing direction of the swing member,
The rotating member has a circular gear;
The working tool characterized in that the swinging member and the rotating member are connected to each other through meshing engagement of the gear and the circular gear. The work tool according to any one of claims 1 to 4,
The tip tool is constituted by a tool bit that performs a linear motion in the major axis direction and a rotational motion around the major axis,
A rotation drive mechanism for rotating the tool bit;
A rotational drive mechanism clutch mechanism that is switched between a power transmission state for transmitting a driving force to the rotational drive mechanism and a power cutoff state for interrupting the transmission of the driving force;
The switching member includes a hammer drill mode in which the tool bit is driven by a combination of a linear motion and a rotational motion, a hammer mode in which the tool bit is driven only in a linear motion, and a drill mode in which the tool bit is driven only in a rotational motion. It is configured as a mode switching member that switches modes between
A clutch switching mechanism that switches a state between a power transmission state and a power cut-off state of the rotary drive mechanism clutch mechanism based on a switching operation of the mode switching member;
When the switching member is switched to the hammer drill mode, both the clutch mechanism for the crank mechanism and the clutch mechanism for the rotational drive mechanism are switched to the power transmission state, and when the switching member is switched to the hammer mode, the crank mechanism When the clutch mechanism for the rotation is switched to the power transmission state, the clutch mechanism for the rotational drive mechanism is switched to the power cutoff state, and the switching member is switched to the drill mode, the clutch mechanism for the crank mechanism is switched to the power cutoff state. A work tool characterized by being configured to be switched and the clutch mechanism for the rotational drive mechanism to be switched to a power transmission state.

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