JP4746920B2 - Electric tool - Google Patents

Description

  In the present invention, when the tip tool is pressed against the workpiece, the tool holder for holding the tip tool moves backward in the direction away from the workpiece together with the tip tool. The present invention relates to a power tool in which a clutch is connected.

Utility model registration gazette No. 2570110 (Patent Document 1) discloses an electric hammer drill used for drilling a workpiece (for example, concrete). In the electric hammer drill described in Patent Document 1, when a drill bit as a tip tool is pressed against a workpiece, the tool holder that holds the drill bit is moved backward in a direction away from the workpiece, thereby causing the clutch to pivot. The drive shaft and the driven shaft are connected to move in the direction, and the power of the drive motor is transmitted to the drill bit, that is, the drill bit performs a striking operation in the major axis direction.
By the way, although not described in Patent Document 1, in the electric hammer drill, a drill mode that causes the drill bit to perform only a rotational operation in the circumferential direction, a rotational operation in the circumferential direction and a striking operation in the long axis direction of the drill bit. There is provided a mode switching operation member for switching the mode between the hammer drill mode and the hammer drill mode. The operation member is mounted in a manner that penetrates the inside and outside of the housing constituting the tool body so that the operator can perform switching operation, and moves inside the housing together with the tool holder or the tool holder. It has a locking piece that can be engaged and disengaged with respect to a member to be engaged, for example, a slide plate for clutch switching. When the operation member is switched to the drill mode side, the locking piece is locked to the tool holder or the slide plate, thereby restricting the backward movement of the tool holder. When the operation member is switched to the hammer drill mode side, the locking piece is It is the structure which cancels | releases latching and accept | permits the backward movement of a drill bit.
Utility Model Registration Gazette No. 2570110

  In the above configuration, when the operation member is switched to the drill mode side and the retraction operation of the drill bit is restricted by the locking piece, all the loads in the retraction operation direction of the tool holder acting on the drill bit are controlled by the operation member. It is a configuration to receive. For this reason, when a large impact load is applied to the drill bit, for example, when the electric hammer drill falls, the operation member including the locking piece may be damaged by the load. There is room for improvement.

  This invention is made in view of this point, and it aims at providing an effective technique in protecting an operation member from the load which acts through a front-end tool in an electric power tool.

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 tool for performing a predetermined machining operation on the workpiece, and holding the tool, and the workpiece together with the tool by pressing the workpiece against the tool. A tool holder that is moved backward in a direction away from the drive tool, a drive mechanism that drives the tip tool, and a drive side that is provided in the drive mechanism and meshes with each other or releases the mesh engagement. The transmission side and the driven side clutch members that intermittently transmit power between the driven side and the driven side, and the meshing engagement between the driving side clutch member and the driven side clutch member are released to cut off the transmission of power. An electric power tool having an urging member for urging so as to be in a cut-off state is configured. The drive-side or driven-side clutch member moves in the axial direction against the urging force of the urging member by the retreating operation of the tool holder, so that the driving-side and driven-side clutch members engage with each other. Together, the power is transmitted. As the “electric tool” in the present invention, typically, when the tip tool is pressed against the workpiece, the tool holder moves backward with the tip tool toward the side away from the workpiece (that is, the tool). This applies to impact work tools such as electric hammers, hammer drills, etc., in which the clutch tool is switched to a connected state in which power is transmitted by the tool being pushed into the tool body) To do. Further, the “biasing member” in the present invention typically corresponds to a spring, so that the meshing engagement between the driving side clutch member and the driven side clutch member is released and the power is cut off. The present invention suitably includes not only a mode of directly biasing the clutch member but also a mode of biasing a member different from the clutch member, that is, a tool holder or a member that moves backward together with the tool holder.

  The invention according to claim 1 has, as a characteristic configuration, an operation member that is moved and operated between an allowable position that allows the backward movement of the tool holder and a restriction position that restricts the backward movement of the tool holder. In addition, in a state where the operating member is moved to the restriction position, the load receiving member that acts on the operating member from the tip tool through the tool holder and receives the load in the backward movement direction of the tool holder is provided. In the present invention, “restricting the backward movement of the tool holder” typically means a mode in which the backward movement is restricted by directly engaging the tool holder, or the backward movement together with the tool holder. The aspect etc. which restrict | treat backward operation | movement by latching with respect to another member to perform suitably are included. Further, the “load receiving member” in the present invention is sufficient if it can receive a load acting on the operation member, and the operation member receives the operation member so that the operation member does not move from the restricting position, or the elasticity of the operation member. Any mode in which the operation member is received while allowing slight movement due to deformation (deflection) is suitably included. According to the present invention, when a load in the backward movement direction of the tool holder is applied to the operation member that has been moved to the restriction position, the load can be received by the load receiving member. For this reason, even when the operation member is moved to the regulation position, for example, when a shocking large load is applied to the operation member from the tip tool through the tool holder due to the fall of the electric tool. By receiving the load by the load receiving member, the operation member can be protected from damage and its durability can be improved.

(Invention of Claim 2)
According to the invention described in claim 2, the load receiving member in an electric tool according to claim 1, a configuration which is supported by a rigid member provided in a fixed form to the load weight of the working direction acting on the operating member Is done. According to the present invention, the load acting on the operation member can be supported by the rigid member fixed in the acting direction of the load.

(Invention of Claim 3)
According to a third aspect of the present invention, in the electric tool according to the second aspect, the power tool includes a tool body that houses the drive mechanism, and a rigid member that is disposed inside the tool body and supports the drive mechanism. The load receiving member is constituted by a long rod-shaped member provided on the rigid member. The “long bar-shaped member” in the present invention typically corresponds to an elongated pin member. According to the present invention, the load receiving member is constituted by a long rod-shaped member, so that it is possible to arrange using a limited narrow space in the tool body. In addition, since the load receiving member is provided on the fixed member disposed in the tool body, the tool body can be formed into a cylindrical integral shape using a forming die. For example, if a configuration in which a load receiving member is provided in the tool body, it becomes difficult to form the tool body into a cylindrical integral shape due to die cutting, and as a result, the tool body is formed in a halved shape. However, according to the present invention, since the problem of die cutting does not occur, the tool body can be formed into an integral cylindrical shape that is advantageous in strength compared to the half structure. it can.

  According to the present invention, a technique effective in protecting an operation member from a large load acting through a tip tool in an electric power tool is provided.

  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 an electric tool. The hammer drill according to the present embodiment is a two-mode type that can be switched between a drill mode in which the drill bit performs only a rotating operation and a hammer drill mode in which the drill bit performs a rotating operation and a striking operation. 2 and FIG. 2 are side sectional views showing the overall configuration of the hammer drill according to the present embodiment with the rear side (grip side) omitted. However, FIG. 1 shows the drill mode (and the idling state in the hammer drill mode), and FIG. 2 shows the actual operation in the hammer drill mode. 3 and 4 are cross-sectional views taken along line AA in FIG. 2, respectively. FIG. 3 shows a state where the change lever is switched to the drill mode, and FIG. 4 shows a state where the change lever is switched to the hammer drill mode. . FIG. 5 is an external view in which the housing is omitted from the direction of arrow B in FIG. 3, and FIG. 6 is an external view in which the housing is omitted from the direction of arrow C in FIG.

  As shown in FIGS. 1 and 2, a hammer drill 101 according to the present embodiment is generally viewed as a main body 103 as a tool main body forming an outline of the hammer drill 101, and a tip region of the main body 103 (illustrated). A drill bit 119 detachably attached to the left side via a tool holder 131 and a grip (not shown) gripped by an operator connected to the rear end side (opposite side of the drill bit 119) of the main body 103 are mainly used. It is configured. The drill bit 119 is gripped with respect to the tool holder 131 in a state in which relative movement in the major axis direction is possible and relative rotation in the circumferential direction is restricted. The drill bit 119 corresponds to the “tip tool” in the present invention, and the tool holder 131 corresponds to the “tool holder” in the present invention. For convenience of explanation, the drill bit 119 side is referred to as the front, and the grip side is referred to as the rear.

  The main body 103 includes a motor housing 105 that houses a drive motor 111 (the tip portion is shown in FIG. 2), and a gear housing 107 that houses a power transmission mechanism 113, a motion conversion mechanism 115, and a striking element 117. Yes. The power transmission mechanism 113, the motion conversion mechanism 115, and the striking element 117 correspond to the “drive mechanism” in the present invention. In the gear housing 107, an inner housing 106 that divides the inside of the gear housing 107 and the inside of the motor housing 105 is disposed on the joint side with the motor housing 105. The inner housing 106 corresponds to a “rigid member” in the present invention.

  The drive motor 111 is disposed such that the motor shaft 111a is parallel to the long axis direction of the main body 103 (that is, the long axis direction of the drill bit 119). The rotation output of the drive motor 111 is appropriately decelerated by the power transmission mechanism 113 and then transmitted to the tool holder 131, and the drill bit 119 mounted on the tool holder 131 is rotated in the circumferential direction. The rotation output of the drive motor 111 is appropriately converted into a linear motion by the motion converting mechanism 115 and then transmitted to the striking element 117 and acts as an impact force in the major axis direction on the drill bit 119 via the striking element 117. To do. That is, the power transmission mechanism 113 constitutes a first drive mechanism for causing the drill bit 119 to rotate around the long axis direction, and the motion conversion mechanism 115 and the striking element 117 are arranged in the long axis direction of the drill bit 119. The second drive mechanism for performing the hitting operation is configured. The tool holder 131 is formed in a cylindrical shape with a bit mounting portion 133 on which a drill bit 119 is mounted, and its outer peripheral portion is rotatable in a vertical plane via front and rear bearings 127 and 128, and The sleeve 135 is supported so as to be movable in the axial direction, and the intermediate cylinder portion 137 is disposed between the bit mounting portion 133 and the sleeve 135 and accommodates an impact bolt 152 described later. And these bit mounting part 133, sleeve 135, and intermediate | middle cylinder part 137 are set as the structure which moves integrally in a major axis direction. The drive motor 111 is energized and driven by a pulling operation of a trigger (not shown) disposed on the grip.

  The power transmission mechanism 113 rotates together with a driven gear 122 that meshes and engages with a pinion 121 provided on the motor shaft 111 a of the drive motor 111, an intermediate shaft 123 that rotates in the vertical plane together with the driven gear 122, and the intermediate shaft 123. The first transmission gear 124 to be driven and the second transmission gear 125 engaged with and engaged with the first transmission gear 124 are mainly configured. The second transmission gear 125 is attached to the outer periphery of the sleeve 135 in the tool holder 131.

  The motion conversion mechanism 115 is mainly composed of an intermediate shaft 123, a clutch cam 141, a rotating body 142, a swash plate 143, and a cylinder 147. The clutch cam 141 corresponds to the “driving side clutch member” in the present invention, and the rotating body 142 corresponds to the “driven side clutch member” in the present invention. The clutch cam 141 is attached to the intermediate shaft 123 via a spline so as to rotate together with the intermediate shaft 123 and to move relative to the axial direction. The rotating body 142 is mounted so as to be rotatable relative to the intermediate shaft 123 in a state where movement in the axial direction is restricted. The clutch cam 141 and the rotating body 142 are arranged in an opposing manner, and have clutch teeth 141a and 142a on the opposing surfaces. Then, the clutch cam 141 moves on the intermediate shaft 123 in a direction approaching the rotating body 142, so that the clutch teeth 141a of the clutch cam 141 are engaged with the clutch teeth 142a of the rotating body 142, and the clutch cam 141 is engaged with the rotating body 142. The meshing engagement is released by moving in a direction away from 142.

  The swash plate 143 is attached to the inclined outer peripheral surface of the rotating body 142 via a bearing 144 so as to be relatively rotatable, and is swung in the major axis direction of the drill bit 119 as the rotating body 142 rotates. The movement causes the cylinder 147 to reciprocate linearly in the cylindrical hole of the sleeve 135 in the tool holder 131. Note that the swash plate 143 and the cylinder 147 are joined to the swing rod 145 protruding from the swash plate 143 by engaging the engaging member 148 provided at the rear end of the cylinder 147 in a loose fit. .

  The striking element 117 is slidably disposed in the cylindrical hole of the intermediate cylindrical portion 137 in the tool holder 131 and the striker 151 as a striking element slidably disposed on the bore inner wall of the cylinder 147. The impact bolt 152 as a meson that transmits the kinetic energy of the drill to the drill bit 119 is mainly used. An air chamber 153 defined by a radial wall surface of the cylinder 147 and the striker 151 is formed in the cylinder 147. The striker 151 includes an air chamber 153 accompanying the reciprocating linear motion of the cylinder 147 in the sleeve 135. It is driven linearly through pressure fluctuations inside, that is, through an air spring. The striker 151 transmits the kinetic energy to the drill bit 119 by colliding with the impact bolt 152.

  In the motion conversion mechanism 115, the meshing engagement operation and the releasing operation of the clutch teeth 141a of the clutch cam 141 and the clutch teeth 142a of the rotating body 142 are performed as a slide plate as a clutch operating member that moves in the longitudinal direction together with the tool holder 131. 155. The slide plate 155 is relatively rotatable with respect to the outer peripheral portion of the tool holder 131 and is relatively movable in the axial direction, and has a bifurcated engagement piece 155a extending toward the clutch cam 141 (FIGS. 5 and 5). 6), and the engagement piece 155a is engaged with the outer peripheral portion of the clutch cam 141 in a state where the engagement piece 155a is relatively rotatable and the movement in the axial direction is restricted. The slide plate 155 is normally pressed forward by the urging force of the compression coil spring 157 and is held at a position regulated by a flange-like stopper plate 135 a provided on the outer periphery of the sleeve 135.

  The urging force of the compression coil spring 157 acts as a force for moving the tool holder 131 together with the slide plate 155. For this reason, in a state where the drill bit 119 is not pressed against the workpiece (not shown), that is, in an unloaded state where no pressing force is applied to the tool holder 131, the slide plate 155 is urged by the biasing force of the compression coil spring 157. The clutch cam 141 is moved forward and moved away from the rotating body 142, and the meshing engagement between the clutch teeth 141a of the clutch cam 141 and the clutch teeth 142a of the rotating body 142 is released (see FIG. 1). On the other hand, in the slide plate 155, the drill bit 119 is pressed against the workpiece, and the tool holder 131 is moved away from the workpiece, that is, moved backward (pressed) relative to the main body 103. When loaded, the tool holder 131 is moved backward against the compression coil spring 157 to move the clutch cam 141 toward the side close to the rotating body 142. As a result, the clutch teeth 141a of the clutch cam 141 are engaged with and engaged with the clutch teeth 142a of the rotating body 142 (see FIG. 2). The retraction operation of the tool holder 131 when the drill bit 119 is pressed against the workpiece is such that the large diameter portion 152a of the impact bolt 152 pressed by the drill bit 119 is the flange portion of the intermediate cylinder portion 137 of the tool holder 131. This is done by pushing 137a backward.

  The compression coil spring 157 is arranged in parallel with the bearing 128 in the outer peripheral region of the rear bearing 128 that supports the rear outer peripheral portion of the sleeve 135 of the tool holder 131. That is, the inner housing 106 described above is formed with a bearing holding cylindrical portion 158 fitted to the outer periphery of the bearing 128, and a compression coil spring 157 is disposed on the outer peripheral side of the cylindrical portion 158. The compression coil spring 157 is interposed such that one end in the axial direction is in contact with the front surface of the inner housing 106 connected to the cylindrical portion 158 and the other end is in contact with the change plate 156. The change plate 156 is disposed so as to overlap the rear surface of the slide plate 155, and, like the slide plate 155, is relatively rotatable with respect to the outer peripheral portion of the sleeve 135 of the tool holder 131 and is relatively movable in the axial direction. It is said that.

  As shown in FIGS. 5 and 6, the change plate 156 is formed with an engaging portion 156 a to which the stop pin 159 a of the mode change lever 159 that is rotated by the user is engaged or separated. The mode change lever 159 corresponds to the “operation member” in the present invention. As shown in FIGS. 3 and 4, the mode change lever 159 is mounted on the side surface of the gear housing 107 in a state of penetrating from the outside to the inside of the gear housing 107, and the locking claw 159b at the tip portion is the inner wall surface of the housing. It is prevented from coming off by being locked to. 5 and 6, the mode change lever 159 is indicated by a two-dot chain line. The mode change lever 159 has a rotation center P in a direction orthogonal to the major axis direction of the tool holder 131, and protrudes in parallel to the rotation center P at an eccentric position separated from the rotation center P by a predetermined distance. In addition, a stop pin 159a is provided so as to face the engaging portion 156a of the change plate 156. When the mode change lever 159 is switched to the drill mode side, the stop pin 159a comes into contact with the engaging portion 156a of the change plate 156, as shown in FIG. When the retracting operation of the holder 131 is restricted and the mode change lever 159 is turned about 90 degrees around the rotation center P from the drill mode position and switched to the hammer drill mode side, as shown in FIG. The slide plate 155 is allowed to move rearward by being pivotally displaced. The position of the stop pin 159a that contacts the engaging portion 156a corresponds to the “restricted position” in the present invention, and the position that moves away corresponds to the “allowable position” in the present invention.

  As shown in FIGS. 5 and 6, a rod-shaped member 161 made of an elongated round bar (pin) is installed behind the change plate 156. This rod-shaped member 161 is set to receive a load when a large load is applied to the mode change lever 159 in a state where the mode change lever 159 is switched to a drill mode that restricts the backward movement of the tool holder 131. ing. The rod-shaped member 161 corresponds to the “load receiving member” in the present invention. The rod-shaped member 161 is attached to the wall surface portion 106a of the inner plate 106 positioned behind the tool holder 131, that is, the wall surface portion 106a orthogonal to the longitudinal direction of the tool holder 131, and extends linearly toward the front. Exist. That is, the rod-shaped member 161 is formed in a long shape having a thick load receiving portion in the acting direction of the load acting on the mode change lever 159, and its axial direction is substantially the same as the long axis direction of the tool holder 131. And a configuration in which the tip of the mode change lever 159 faces the rear surface of the stop pin 159a of the mode change lever 159 with a slight gap when the mode change lever 159 is switched to the drill mode. Is done. The rod-shaped member 161 is fixed to the wall surface portion 106a of the inner housing 106 by press-fitting. However, the press-fitted portion is set as the large-diameter portion 161a, thereby reinforcing the rod-shaped member 161 itself. Yes.

  The hammer drill 101 according to the present embodiment is configured as described above. Next, the operation and usage method of the hammer drill 101 will be described. In the unloaded state where the drill bit 119 is not pressed against the workpiece, the change plate 156 and the slide plate 155 are pushed forward together with the tool holder 131 by the urging force of the compression coil spring 157 as shown in FIG. The clutch teeth 141 a of 141 are separated from the clutch teeth 142 a of the rotating body 142. In this state, when the mode change lever 159 is switched to the drill mode side, as shown in FIG. 5, the stop pin 159a is displaced forward and comes into contact with the rear surface of the engaging portion 156a of the change plate 156. The rearward movement (retracting operation) of the change plate 156 and the tool holder 131 is restricted.

  In this state, the rotational output of the drive motor 111 is transmitted as a rotational force to the tool holder 131 via the power transmission mechanism 113, and the drill bit 119 is rotated together with the tool holder 131. On the other hand, on the motion conversion mechanism 115 side, the clutch teeth 141a of the clutch cam 141 are separated from the clutch teeth 142a of the rotator 142, so the rotator 142 is not rotated. That is, in the state switched to the drill mode, the drill bit 119 is driven only by the rotating operation, and the operator can appropriately perform the drilling operation by pressing the drill bit 119 against the workpiece. At this time, although a pushing force is applied to the tool holder 131 by the pressing operation of the drill bit 119, the backward movement is restricted by the stop pin 159a of the mode change lever 159 as described above. Stable work in the mode is realized.

  On the other hand, when the mode change lever 159 is rotated approximately 90 degrees around the rotation center P and switched to the hammer drill mode side, the stop pin 159a of the mode change lever 159 is displaced rearward as shown in FIG. Then, the change plate 156 is moved away from the engaging portion 156a, and the movement restriction of the change plate 156 is released. When the drill bit 119 is pressed against the workpiece in this state, the tool holder 131, the slide plate 155, and the change plate 156 together with the drill bit 119 compress the compression coil spring 157 with respect to the main body 103 as shown in FIG. Move backwards relatively. As a result, the slide plate 155 moves the clutch cam 141 toward the rotating body 142, and the clutch teeth 141 a of the clutch cam 141 are engaged with and engaged with the clutch teeth 142 a of the rotating body 142. For this reason, a rotational force is transmitted to the rotating body 142 side, and the cylinder 147 moves linearly in the tool holder 131 through the swinging motion of the swash plate 143. As the cylinder 147 moves linearly, the striker 151 constituting the striking element 117 is moved via the air spring, and further, the linear movement is transmitted to the drill bit 119 via the impact bolt 152. That is, in the hammer drill mode, the drill bit 119 is driven by a rotating operation and a striking operation, so that a drilling operation can be performed on the workpiece.

  By the way, when the mode change lever 159 is switched to the drill mode side and the stop pin 159a of the mode change lever 159 is in contact with the engaging portion 156a of the change plate 156, the retreating operation of the tool holder 131 is restricted. When a load for moving the tool holder 131 backward acts on the holder 131, the entire load is received by the stop pin 159a. For this reason, for example, when the hammer drill 101 is inadvertently dropped and a large impact load is applied to the tool holder 131 through the drill bit 119, the mode change lever 159 may be damaged by the load. is there. According to the present embodiment, by disposing the rod-shaped member 161 so as to oppose the acting direction of the load on the stop pin 159a, the rod-shaped member 161 can receive a large impact load acting on the stop pin 159a. . As a result, the mode change lever 159 can be protected from damage and its durability can be improved.

  Further, according to the present embodiment, the long axis direction of the rod-shaped member 161 is provided so as to substantially coincide with the long axis direction of the tool holder 131, that is, the acting direction of the load acting on the stop pin 195a. For this reason, as a result of being able to receive in the major axis direction of the rod-shaped member 161 acting on the stop pin 195a, it is possible to configure a rational load support structure with high strength while forming the rod-shaped member 161 in a small shape.

  In the present embodiment, the rod-shaped member 161 is provided in the inner housing 106 disposed in the gear housing 107. That is, the rod-shaped member 161 is not provided in the gear housing 107, but is provided in the inner housing 106, which is a separate member fixedly arranged in the gear housing 107, and thus the gear housing 107 is provided. It is possible to form a cylindrical integral shape. For example, if the gear housing 107 is provided with a member that receives a load acting on the mode change lever 159, it is difficult to mold the gear housing 107 into a cylindrical integral shape because of the mold removal. As a result, the gear housing 107 must be formed in a halved shape. However, according to the present invention, such a problem of die cutting does not occur, and therefore the gear housing 107 is stronger than the halved shape. It is possible to form an integral cylindrical shape that is advantageous to the above. In addition, since the rod-shaped member 161 is provided in the inner housing 106, the rod-shaped member 161 can be formed by an elongated round bar or a square bar, and rationally using a limited narrow space in the gear housing 107. It becomes possible to arrange.

  In the above-described embodiment, the electric hammer drill 101 is described as an example of the working tool. However, the tool is not limited to the hammer drill 101, and the tool of the tip tool when the tip tool is pressed against the workpiece. Any power tool can be applied as long as the clutch is connected to the main body by a backward movement with respect to the main body and the power of the drive motor is transmitted to the tip tool.

It is a sectional side view which shows the whole structure of the hammer drill which concerns on embodiment of this invention in the state which a rear side (grip side) was abbreviate | omitted, and shows the time of drill mode (and idling state at the time of hammer drill mode). It is a sectional side view which shows the whole structure of a hammer drill in the state in which the rear side (grip side) was abbreviate | omitted, and shows the time of working of hammer drill mode. It is the sectional view on the AA line of FIG. 2, and has shown the state by which the change lever was switched to drill mode. It is the sectional view on the AA line of FIG. 2, and has shown the state by which the change lever was switched to hammer drill mode. It is the external view which abbreviate | omitted the housing from the B arrow direction of FIG. It is the external view which abbreviate | omitted the housing from the arrow C direction of FIG.

101 Hammer drill (electric tool)
103 Body 105 Motor housing 106 Inner housing (rigid member)
106a Wall surface portion 107 Gear housing 111 Drive motor 111a Motor shaft 113 Power transmission mechanism (drive mechanism)
115 Motion conversion mechanism (drive mechanism)
117 striking element (drive mechanism)
119 Drill bit (tip tool)
121 pinion 122 driven gear 123 intermediate shaft 124 first transmission gear 125 second transmission gear 127 bearing 128 bearing 131 tool holder 133 bit mounting part 135 sleeve 135a stopper plate 137 intermediate cylinder part 137a flange part 141 clutch cam (clutch member on the driving side) )
141a Clutch tooth 142 Rotating body (Clutch member on the driven side)
142a Clutch tooth 143 Swash plate 144 Bearing 145 Swing rod 147 Cylinder 148 Engaging member 151 Strike 152 Impact bolt 152a Large diameter part 153 Air chamber 155 Slide plate 155a Engaging piece 156 Change plate 156a Engaging part 157 Compression coil spring (biasing) Element)
158 Cylindrical part 159 Mode change lever (operation member)
159a Stop pin 159b Locking claw 161 Bar-shaped member (load receiving member)
161a Large diameter part

Claims (3)

A tip tool for performing a predetermined machining operation on the workpiece;
A tool holder that holds the tip tool and is retreated in a direction away from the workpiece together with the tip tool by a pressing operation of the tip tool against the workpiece;
A drive mechanism for driving the tip tool;
A driving-side and driven-side clutch member that is provided in the driving mechanism and that intermittently engages or disengages transmission of power between the driving side and the driven side by releasing the meshing engagement; ,
An urging member that urges the clutch member on the driving side and the clutch member on the driven side to disengage and disengage the power transmission,
The drive-side or driven-side clutch member moves in the axial direction against the urging force of the urging member by the retreating operation of the tool holder, whereby the driving-side and driven-side clutches are moved. An electric tool having a configuration in which members are engaged with each other to transmit power and transmit power,
An operation member that is moved between an allowable position that allows the tool holder to move backward and a restriction position that restricts the tool holder to move backward;
A load receiving member that receives a load in the backward movement direction of the tool holder, which acts on the operation member from the tip tool through the tool holder in a state where the operation member is moved to the restriction position. An electric tool characterized by that. “The power tool according to claim 1,
The load receiving member, the power tool characterized in that it is supported by a rigid member provided in a fixed form to the load weight of the working direction that acts on the operating member. " The electric tool according to claim 1 or 2,
A tool body that houses the drive mechanism;
A rigid member that is disposed inside the tool body and supports the drive mechanism;
The power tool, wherein the load receiving member is constituted by a long bar-like member provided on the rigid member.

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