JP2015116616A - Placing tool - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a placing tool which is improved so as to exhibit predetermined placing performance.SOLUTION: A placing tool 100 comprises: a first piston 123 which is slidably disposed in a first cylinder 121, and having a long placing part 125 for placing a material to be placed; a second piston 133 which slides in a second cylinder 131; a crank 115 driven by a motor 111 to make the second piston 133 reciprocate in the second cylinder 131; a compressed air supply path 135 for communicating the second cylinder 131 with the first cylinder 121; a valve member 137 for opening and closing the compressed air supply path 135; and a cam member 151 which is coupled to the crank 115 and rotationally driven. The placing tool 100 further comprises an adjusting device 170 for adjusting opening timing so that the opening timing when the assembled valve member 137 is moved to an opening position to open the compressed air supply path 135 matches maximum compression timing when the second piston 133 is moved to a position where air in the second cylinder is in a maximum pressure state.

Description

  The present invention relates to an electro-pneumatic driving tool used for driving a workpiece such as a nail into a workpiece.

  Japanese Patent Laying-Open No. 2011-25363 (Patent Document 1) discloses an electro-pneumatic driving tool equipped with an electric motor driven by a battery and a compression device driven by the electric motor. This driving tool drives a compression device via a crank by a motor, and when the air in the compression chamber reaches the maximum compression state, the valve is opened by a cam connected to the crank to drive the compressed air in the compression chamber. The material to be driven is driven by supplying the air into the cylinder and operating the driving mechanism by the supplied compressed air.

JP 2011-25363 A

  In the driving tool described in Japanese Patent Application Laid-Open No. 2011-25363, the timing at which the valve opens when the air in the compression chamber reaches the maximum compression state is determined as the reference timing. On the other hand, in a mechanism that opens and closes a valve by converting the rotational motion of the cam to a linear motion, for example, when a gap occurs between the cam and a member that responds to the cam due to a manufacturing error in the mechanical parts. There is a possibility that the opening timing of the valve is deviated from the reference timing. Deviation in the opening timing of the valve adversely affects the driving performance of the driving tool.

  An object of this invention is to provide the driving tool improved so that predetermined | prescribed driving | operation performance could be exhibited in view of said problem.

  In order to solve the above-described problems, according to a preferred embodiment of the driving tool according to the present invention, the motor, the first cylinder, the sliding portion slidably accommodated in the first cylinder, and the sliding portion are connected. And a first piston provided with a long driving portion for driving a material to be driven, a second cylinder, a second piston that generates compressed air by reciprocating in the second cylinder, and a motor Driven by the crank for reciprocating the second piston in the second cylinder, the compressed air supply path communicating the first cylinder and the second cylinder, the open position for opening the compressed air supply path, and the closed position for closing A valve member that moves between the cam member, a biasing member that biases the valve member toward the closing position, and a cam member that is connected to the crank and is driven to rotate, and according to the cam lift amount of the cam member By valve member When the open / close control of the compressed air supply path is performed and the valve member is moved to the open position, the first piston is linearly formed by the compressed air sent from the second cylinder through the compressed air supply path into the first cylinder. The driving tool is configured to perform the driving operation of the driven material by the driving portion of the first piston. The “driving tool” in the present invention is typically a nail driver or a tacker, and the “placed material” is a straight bar with a sharpened tip, and an umbrella is placed on the head. Widely includes those with or without, U-shaped staples, etc.

  The driving tool according to the present invention has a predetermined position within a region in which the second piston moves and the air in the second cylinder is in a pressure state higher than a certain level necessary for driving the driven material by the first piston. An adjusting device that adjusts the opening timing of the valve member so that the opening timing at which the assembled valve member is moved to the opening position and the compressed air supply path is opened coincides with the compression timing when the valve member is moved to I have. The “compression timing when moved to a predetermined position” in the present invention is typically the maximum compression when the second piston is moved to a position where the air in the second cylinder is in a maximum pressure state. The timing, that is, the position at which the second piston has reached the top dead center of the crank angle that minimizes the volume of the second cylinder, but may be the position immediately before reaching the top dead center.

  According to the present invention, in the state where the cam member and the valve member are assembled, for example, due to a manufacturing error of the cam member and the valve member, a deviation occurs in the opening timing of the valve member with respect to the compression timing of the second piston. In this case, the opening timing can be adjusted by the adjusting device so that the opening timing matches the compression timing, and a predetermined driving performance of the driving tool can be obtained.

  According to a further aspect of the driving tool according to the present invention, the driving tool has an interposition member that connects the cam member and the valve member, the interposition member moves in contact with the cam member, and the moved interposition member contacts the valve member. The valve member is moved in contact with the valve member, and the compressed air supply path is opened by moving the valve member. The adjusting device includes a position adjusting member that can adjust the relative position between the cam member and the interposed member or the relative position between the valve member and the interposed member. Then, the relative position between the cam member and the interposition member or the relative position between the valve member and the interposition member is adjusted by the position adjustment member so that the interposition member contacts the cam member and the valve member. Is adjusted to match the compression timing. The “position adjusting member” in this embodiment includes a turn buckle that can adjust the connection length between members, a shim or a wedge that is disposed in an intervening manner between members and can adjust the relative position between members. Is applicable.

  In the configuration in which the cam member and the valve member are connected by the interposed member, it is conceivable that, for example, a gap (backlash) is generated between the cam member and the interposed member due to manufacturing errors of these members. According to this aspect, the position adjustment member adjusts the relative position of the cam member and the interposition member, or the relative position of the valve member and the interposition member, thereby eliminating the above-described gap and setting the opening timing of the valve member to the second piston. The release timing can be adjusted to coincide with the compression timing.

  According to the further form of the driving tool which concerns on this invention, the interposition member is comprised including the 1st member and 2nd member which can mutually move relatively. The position adjusting member is disposed between the first member and the second member so that the relative position between the first member and the second member can be adjusted by the position adjusting member. And the relative position of a cam member and an interposition member or the relative position of a valve member and an interposition member is adjusted by adjusting the relative position of a 1st member and a 2nd member by a position adjustment member.

  According to this aspect, the relative position between the cam member and the interposed member or the relative position between the valve member and the interposed member can be adjusted by adjusting the relative position between the first member and the second member by the position adjusting member.

  According to the further form of the driving tool which concerns on this invention, a position adjustment member has a wedge-shaped member. The wedge-shaped member is provided so as to be movable with respect to each of the first member and the second member, and the relative position between the first member and the second member can be adjusted according to the position of the wedge-shaped member. The “wedge-shaped member” in the present invention refers to a member that exhibits the effect of a wedge, and refers to a member that can firmly connect the first member and the second member.

  According to this aspect, the relative position between the cam member and the interposition member or the relative position between the valve member and the interposition member is adjusted by adjusting the relative position between the first member and the second member according to the position of the wedge-shaped member. be able to.

  According to the further form of the driving tool which concerns on this invention, a position adjustment member has the 2nd biasing member which biases a wedge-shaped member. The first member and the second member are held so that the interposing member abuts against each of the cam member and the valve member by the urging force of the second urging member.

  According to this aspect, even when the contact surface between the cam member and the interposition member is worn with use, the contact of the interposition member against the cam member and the valve member by the second biasing member that biases the wedge-shaped member. The contact state can be maintained. Thereby, it is possible to prevent occurrence of deviation of the opening timing of the valve member with respect to the compression timing of the second piston due to wear of the contact surface between the cam member and the interposition member.

  According to the further form of the driving tool which concerns on this invention, the 1st member and the 2nd member are attached so that it can rotate separately around the same axis, and the 1st member about the same axis according to the position of a wedge-shaped member And the relative position of the second member can be adjusted.

  According to this embodiment, the relative position between the cam member and the interposition member or the relative position between the valve member and the interposition member is adjusted by adjusting the relative position between the first member and the second member around the same axis according to the position of the wedge-shaped member. The position can be adjusted.

  According to the further form of the driving tool which concerns on this invention, a valve member is a structure which moves in a predetermined | prescribed axial direction, and opens and closes a compressed air supply path. The interposition member is disposed so as to be able to contact the cam member, and has a swinging member that is swung by the cam member in a rotation axis direction of the cam member with a predetermined rotation shaft as a fulcrum, and extends in a predetermined axial direction. And a transmission member that transmits the swing of the swing member to the valve member as a reciprocating motion. The transmission member includes a first transmission member and a second transmission member that are movable relative to each other with respect to a predetermined axial direction. The first transmission member is disposed so as to contact the valve member, and the second member swings. Connected to the member. The position adjustment member is disposed between the first transmission member and the second transmission member so that the relative position between the first transmission member and the second transmission member can be adjusted by the position adjustment member. The relative position between the first transmission member and the second transmission member is adjusted by the position adjustment member, so that the relative position of the swing member with respect to the cam member or the relative position of the first transmission member with respect to the valve member is adjusted. It was.

  According to this aspect, the relative position of the swing member relative to the cam member or the relative position of the first transmission member relative to the valve member is adjusted by adjusting the relative position between the first transmission member and the second transmission member by the position adjustment member. can do.

  According to the further form of the driving tool which concerns on this invention, a valve member is a structure which moves in a predetermined | prescribed axial direction, and opens and closes a compressed air supply path. The interposition member is disposed so as to be able to contact the cam member, and has a swinging member that is swung by the cam member in a rotation axis direction of the cam member with a predetermined rotation shaft as a fulcrum, and extends in a predetermined axial direction. And a transmission member that transmits the swing of the swing member to the valve member as a reciprocating motion. The position adjustment member is disposed between the transmission member and the valve member so that the relative position between the transmission member and the valve member can be adjusted by the position adjustment member.

  According to this aspect, the relative position between the cam member and the interposition member can be adjusted by adjusting the relative position between the transmission member and the valve member by the position adjusting member.

  According to the present invention, an improved driving tool is provided so as to exhibit a predetermined driving performance.

BRIEF DESCRIPTION OF THE DRAWINGS It is a whole block diagram which shows the electro-pneumatic type nailing machine which concerns on 1st Embodiment of this invention, and shows the state which the compression piston located in the bottom dead center. Similarly, it is a whole block diagram of an electro-pneumatic nailer, and shows a state where the compression piston is located at the top dead center. It is the fragmentary sectional view which expanded the head valve vicinity. It is a figure which shows a cam and a cam follower. It is an operation | movement figure of an electro-pneumatic type nailing machine, and shows the state which the cam follower contacted the cam pile. It is an operation | movement diagram of an electro-pneumatic nailing machine, A cam follower goes up to a cam mountain, and the opening | release initial state of the head valve which the seal | sticker of the head valve began to separate from a cylinder head is shown. It is an operation | movement diagram of an electro-pneumatic nailer, and shows the fully open state of a head valve. It is an operation | movement diagram of an electro-pneumatic nailer, and shows the initial stage of the return stroke which the compression piston started to move toward the bottom dead center from the top dead center. It is channel explanatory drawing explaining the flow of compressed air. FIG. 10 is a sectional view taken along line AA in FIG. 9. It is a perspective view which shows the error adjustment means which concerns on 1st Embodiment. It is a perspective view which decomposes | disassembles and similarly shows an error adjustment means. It is a schematic diagram explaining error adjustment by error adjustment means. It is a perspective view which shows the error adjustment means which concerns on 2nd Embodiment. It is a perspective view of the error adjustment means concerning a 3rd embodiment.

(First embodiment of the present invention)
Hereinafter, a first embodiment of the present invention will be described in detail with reference to FIGS. This embodiment will be described using an electro-pneumatic nailer as an example of a driving tool. As shown in FIG. 1, a nail driver 100 includes a main body housing 101 as a tool main body that forms an outline of the nail driver 100, and a nail as a material to be driven that is driven into a workpiece (not shown for convenience). Is loaded with a magazine 105. The main body housing 101 is formed by abutting and joining a pair of substantially symmetrical housings. The main body housing 101 accommodates a handle portion 103 held by an operator, a driving mechanism accommodating portion 101A for accommodating a nail driving mechanism 120, a compression device accommodating portion 101B for accommodating a compression device 130, and an electric motor 111. A motor housing 101C is integrally provided.

  As shown in FIGS. 1 and 2, the handle portion 103, the driving mechanism housing portion 101 </ b> A, the compression device housing portion 101 </ b> B, and the motor housing portion 101 </ b> C of the main body housing 101 are each formed in a substantially rectangular shape that forms each side. Has been placed.

  FIG. 1 shows a sideways state in which a driver guide 141 disposed at the distal end portion (right end in FIG. 1) of the nailing machine 100 is directed toward a workpiece. Therefore, in FIG. 1, the right direction is the nail driving direction by the nail driving mechanism 120 and the nail driving direction by the driver 125. For convenience of explanation, the front end side (right side in FIG. 1) of the nailing machine 100 is referred to as a front side, and the opposite side is referred to as a rear side. The connection side (upper side in FIG. 1) between the handle part 103 and the nail driving mechanism 120 is referred to as the upper side, and the connection side (lower side in FIG. 1) between the handle part 103 and the electric motor 111 is referred to as the lower side.

  The nail driving mechanism 120 housed in the driving mechanism housing portion 101A of the main body housing 101 is mainly composed of a driving cylinder 121 and a driving piston 123. A driving piston 123 for driving a nail is accommodated in the driving cylinder 121 so as to be slidable in the front-rear direction. The driving piston 123 includes a piston main body 124 slidably accommodated in the driving cylinder 121, and a long driver for driving a nail that is provided integrally with the piston main body 124 and extends forward. 125. The driving piston 123 is moved linearly in the major axis direction of the driving cylinder 121, that is, the front-rear direction, by the compressed air supplied to the cylinder chamber 121a. The driver 125 constitutes an operating member that moves forward in the driving path of the driver guide 141 and drives the nail. The driving cylinder 121 corresponds to the “first cylinder” in the present invention, and the driving piston 123 corresponds to the “first piston” in the present invention. The piston main body 124 corresponds to the “sliding portion” in the present invention, and the driver 125 corresponds to the “driving portion” in the present invention.

  The driver guide 141 is disposed at the tip (right side in FIG. 2) of the driving cylinder 121 and includes a driving passage as a nail injection port. The magazine 105 is a rectangular long member that accommodates a nail as a material to be driven in a straight line. The magazine 105 is arranged on the foremost side of the main body housing 101, and the nail supply side tip is connected to the driver guide 141. The magazine 105 is provided with a pusher plate (not shown) for pushing the nail in the supply direction (upward in FIG. 2). The pusher plate is configured to supply the nails linearly one by one from the direction intersecting the driving direction to the driving path of the driver guide 141. The driving path constitutes a path when the driver 125 drives in a straight line and drives a nail.

  As shown in FIG. 1, the compression device 130 accommodated in the compression device accommodating portion 101 </ b> B is configured mainly by a compression cylinder 131 and a compression piston 133 that is slidably disposed in the compression cylinder 131 in the vertical direction. The The compression cylinder 131 corresponds to the “second cylinder” in the present invention, and the compression piston 133 is an implementation configuration example corresponding to the “second piston” in the present invention.

  The compression cylinder 131 is arranged in parallel with the magazine 105 along the outer surface of the magazine 105 (the left side surface in FIG. 1). The upper end side of the compression cylinder 131 is integrally connected to the front end portion of the driving cylinder 121. The compression piston 133 is disposed so as to reciprocate in the vertical direction along the magazine 105. The compression piston 133 is configured such that the operation direction of the compression piston 133 is substantially orthogonal to the operation direction of the driving piston 123. As the compression piston 133 slides in the vertical direction, the volume of the compression chamber 131a that is the internal space of the compression cylinder 131 changes. The compression piston 133 compresses the air in the compression chamber 131a and generates compressed air during the forward movement that moves upward to reduce the volume of the compression chamber 131a. The compression chamber 131 a is formed on the upper side close to the driving cylinder 121 as a space surrounded by the inner wall surface of the compression cylinder 131 and the upper surface of the compression piston 133.

  As shown in FIG. 1, an electric motor 111 for driving the compression device 130 is accommodated in the motor accommodating portion 101C. This electric motor 111 is an implementation configuration example corresponding to the “motor” in the present invention. The electric motor 111 is arranged so that the rotation axis of the electric motor 111 is substantially parallel to the long axis of the driving cylinder 121. Therefore, the rotation axis of the electric motor 111 is orthogonal to the long axis extending in the operation direction of the compression piston 133. A rechargeable battery pack 110 serving as a power source for the electric motor 111 is detachably attached to the lower side of the motor housing 101C.

  The rotation of the electric motor 111 is transmitted to a planetary gear type reduction mechanism (not shown), and then converted into a linear motion via a crank mechanism 115 as a motion conversion mechanism and transmitted to the compression piston 133. The That is, in the present embodiment, a reciprocating type compression device mainly composed of the compression cylinder 131, the compression piston 133, and the crank mechanism 115 is used as the compression device 130. This crank mechanism 115 is an implementation configuration example corresponding to the “crank” in the present invention.

  As shown in FIG. 1, the crank mechanism 115 includes a crankshaft 115a rotated by a planetary gear type reduction mechanism, an eccentric pin 115b provided at a position eccentric from the rotation center of the crankshaft 115a, and an eccentric pin 115b. One end of the connecting rod 115c is connected to the compression piston 133, and the other end is connected to the compression piston 133. The crank mechanism 115 is disposed below the compression cylinder 131.

  The electric motor 111 pulls and operates the trigger 103 a provided on the handle portion 103 and is energized when a driver guide 141 that also functions as a contact arm provided in the front end region of the main body housing 101 is pressed against the workpiece. In addition, the trigger 103a is configured to be stopped by performing at least one of cancellation of the pulling operation of the trigger 103a and release of pressing of the driver guide 141 against the workpiece.

  The nailing machine 100 includes an air passage 135 (see FIG. 9) that communicates the compression chamber 131a of the compression cylinder 131 and the cylinder chamber 121a of the driving cylinder 121, and a head valve 137 that opens and closes the air passage 135 (FIG. 1, 3). As shown in FIG. 1, when the crank angle of the crankshaft 115a is 0 degrees (360 degrees), the driving piston 123 is located at the rear end position (left end position in FIG. 1) closest to the cylinder head 122 of the driving cylinder 121. The compression piston 133 is set to be located at the bottom dead center as the lower end position farthest from the cylinder head 132 of the compression cylinder 131. That is, the rear end position of the driving piston 123 is set as the initial position, and the bottom dead center of the compression piston 133 is set as the initial position.

  The air passage 135 includes a tubular member 135a, a communication port 135b on the compression cylinder side, a valve chamber 136, and a communication port 135c on the driving cylinder side. This air passage 135 is an implementation configuration example corresponding to the “compressed air supply path” in the present invention. As shown in FIG. 9, the tubular member 135 a extends linearly in the front-rear direction along the long axis direction of the driving cylinder 121. One end of the tubular member 135a communicates with a communication port 135b formed in the cylinder head 132 of the compression cylinder 131. The other end of the tubular member 135a communicates with a valve chamber 136 (see FIG. 3) formed in the cylinder head 122 of the driving cylinder 121. As shown in FIG. 3, a partition wall 127 is provided between the valve chamber 136 and the cylinder chamber 121a. A communication port 135c that connects the valve chamber 136 and the cylinder chamber 121a is formed in the partition wall 127.

  The valve chamber 136 is formed as a circular space in the cylinder head 122. A head valve 137 is disposed in the valve chamber 136 so as to be slidable in the front-rear direction. This head valve 137 is an implementation configuration example corresponding to the “valve member” in the present invention. The head valve 137 is provided as a columnar member. The head valve 137 is movable in the front-rear direction on the driving line of the driver 125 of the driving piston 123, that is, on the coaxial line with the hitting axis. One axial end surface of the head valve 137 facing the cylinder chamber 121a is set as a flat seal surface 137a. Opposite to the seal surface 137a, the partition wall 127 is provided with an O-ring 129 as a seal member. When the head valve 137 moves forward, the seal surface 137a contacts the O-ring 129 and closes the communication port 135c, and when the head valve 137 moves rearward, the seal surface 137a is separated from the O-ring 129 and connects the communication port 135c. Open. An O-ring 139 is provided on the outer periphery of the head valve 137 to prevent the air in the valve chamber 136 from leaking outside by contacting the inner peripheral surface of the valve chamber 136.

  As shown in FIG. 3, the head valve 137 is normally urged forward by a compression coil spring 138 as an urging member. For this reason, the sealing surface 137a is pressed against the O-ring 129 to close the communication port 135c. That is, in the head valve 137, the position where the communication port 135c is closed is set as the initial position. This compression coil spring 138 is an implementation structural example corresponding to the “biasing member” in the present invention. The head valve 137 is configured as a mechanical valve that is controlled to open and close via a link mechanism 155 by a cylindrical cam 151 that rotates in conjunction with the crank mechanism 115. The link mechanism 155 is provided as means for converting the rotational motion of the cylindrical cam 151 into a linear motion in the front-rear direction and transmitting it to the head valve 137.

  The cylindrical cam 151 according to the present embodiment is set as an end face cam in which a cam surface 153 is formed on one end face in the axial direction, and is attached to rotate integrally on the crankshaft 115a. This cylindrical cam 151 is an implementation configuration example corresponding to the “cam member” in the present invention. The cylindrical cam 151 is set as an initial position when the crank angle at which the compression piston 133 is located at the bottom dead center is 0 degrees (360 degrees). When the crank angle at which the compression piston 133 reaches the top dead center is 180 degrees, that is, when the compressed air in the compression chamber 131a is in the maximum compression state, the head valve 137 is moved rearward so that the communication port 135c is Configured to open. FIG. 4 shows a part of the cylindrical cam 151 in a developed view. As shown in the drawing, the cam surface 153 of the cylindrical cam 151 has a peak portion 153 a as an open region for opening the head valve 137 and a valley portion 153 b as a closed region for closing the head valve 137. For example, a region from 160 degrees to 340 degrees in crank angle is a peak portion 153a (including a slope), and the other region is a valley portion 153b.

  As shown in FIG. 1, the link mechanism 155 includes a link 157 and a push plate 159. The link 157 is arranged to extend in the vertical direction along the outer surface of the compression cylinder 131, and is attached to the main body housing 101 so as to be rotatable in the front-rear direction by the support shaft 156 at a substantially central portion in the extending direction. Yes. A cam follower 161 that responds to the movement of the cylindrical cam 151 is disposed at one end (lower end) of the link 157 so as to face the cam surface 153 of the cylindrical cam 151. The cam follower 161 is configured by a roller that can rotate around an axis that intersects the axis of the cylindrical cam 151.

  The push plate 159 extends in the front-rear direction along the outer surface of the driving cylinder 121. One end (front end) of the push plate 159 is connected to the other end (upper end) of the link 157 by a pin 163 so as to be relatively rotatable. The other end of the push plate 159 is provided with a long hole in the vertical direction in which the pin 163 is loosely fitted, and when the link 157 is rotated in the front-rear direction with the support shaft 156 as a fulcrum. The relative displacement between the link 157 and the push plate 159 in the vertical direction is allowed. The other end side (rear end side) of the push plate 159 is formed in an L shape in plan view (top view). The L-shaped end 159 a of the push plate 159 is connected to the head of the head valve 137 in a state of being inserted into the valve chamber 136 through the opening of the cylinder head 122 of the driving cylinder 121. Specifically, as shown in FIG. 3, the L-shaped end 159a has a circular hole. In the state where the head of the head valve 137 is inserted into the hole, the head valve 137 is clamped by a flange portion 137b provided on the head and a retaining ring 158 fitted and fixed to the head to prevent the head valve 137 from coming off. .

  Therefore, when the upper end side of the link 157 is rotated forward with the support shaft 156 as a rotation fulcrum, and the push plate 159 moves forward, the head valve 137 moves forward to close the communication port 135c, and the link 157 Is rotated rearward and the push plate 159 moves rearward, the head valve 137 moves rearward against the biasing force of the compression coil spring 138 to open the communication port 135c. FIG. 7 shows the fully opened state of the communication port 135c. The urging force of the compression coil spring 138 that urges the head valve 137 toward the closing side acts to press the cam follower 161 of the link 157 against the cam surface 153 of the cylindrical cam 151.

  In the nailing machine 100 configured as described above, the state where the compression piston 133 is located at the bottom dead center, that is, the position when the crank angle of the crankshaft 115a is 0 is set as the initial position of the compression piston 133. . On the other hand, the position at which the head valve 137 is moved most forward by the biasing force of the compression coil spring 138 to close the communication port 135c is set as the initial position of the head valve 137 (see FIG. 1). In this state, when the electric motor 111 is energized, the crank mechanism 115 is driven via the speed reduction mechanism, and the compression piston 133 starts moving toward the top dead center. During this forward movement, the cam follower 161 faces the valley 153b of the cylindrical cam 151. Therefore, the head valve 137 is pushed forward by the biasing force of the compression coil spring 138 to close the communication port 135c. Therefore, as shown in FIG. 5, the air trapped in the compression chamber 131a is compressed.

  Next, as shown in FIG. 6, the cylindrical cam 151 rotates, the cam follower 161 contacts the peak portion 153a, and the cam follower 161 starts to rise up the peak portion 153a. At this time, the compression piston 133 has not yet reached top dead center. When the cam follower 161 moves up the peak portion 153 a, the head valve 137 moves backward against the biasing force of the compression coil spring 138 via the link mechanism 155, and the seal surface 137 a of the head valve 137 is separated from the O-ring 129. . When the communication port 135c is opened even a little, the head valve 137 is pushed rearward by the pressure acting on the seal surface 137a of the head valve 137, and is fully opened. That is, when the cam follower 161 goes up the peak portion 153a, the crank angle reaches 180 degrees, the compression piston 133 reaches the top dead center, and the compressed air in the compression chamber 131a reaches the maximum compression state. 135c is fully opened. At this time, the cam follower 161 once leaves the peak portion 153a of the cylindrical cam 151, but then comes into contact with the peak portion 153a when the cylindrical cam 151 rotates and faces the top portion of the peak portion 153a. When the communication port 135c is opened, as shown in FIG. 7, compressed air is supplied into the cylinder chamber 121a via the valve chamber 136, and the driving piston 123 is moved forward by the compressed air. The driver 125 of the driving piston 123 moved forward hits the nail waiting in the driving passage of the driver guide 141, and drives the nail into the workpiece.

  In addition, after the compression operation of the compression piston 133, when the compression piston 133 moves backward toward the bottom dead center, the compression chamber 131a becomes negative pressure as the volume of the compression chamber 131a increases. Then, the driving piston 123 in the driving cylinder 121 is returned to the initial position by the negative pressure in the compression chamber 131a. During this time, the head valve 137 continues to open the communication port 135c as shown in FIG. Thus, in the nail driver 100 according to this embodiment, when the compression piston 133 reciprocates once, the driver 125 of the driving piston 123 performs a single nail driving operation.

  In the nail driver 100 configured and acting as described above, in this embodiment, the compression piston 133 is moved to a position where the air in the compression chamber 131a of the compression cylinder 131 is in a maximum pressure state. The opening timing at which the head valve 137 opens the communication port 135c coincides with the compression timing. However, in the case where the head valve 137 is a valve opening / closing mechanism that is opened and closed by the cylindrical cam 151 via the link mechanism 155, in the assembled state of each component constituting the valve opening / closing mechanism, due to manufacturing errors of each component, There may be a gap (backlash) between the cylindrical cam 151 and the cam follower 161, between the L-shaped end 159a of the push plate 159 and the retaining ring 158, or between the L-shaped end 159a and the flange 137b. There is. Such a gap causes a deviation in the opening timing for opening the communication port 135c of the head valve 137 with respect to the maximum compression timing, and as a result, the pressure supplied to the cylinder chamber 121a of the driving cylinder 121 becomes unstable, and the driving piston There is a possibility that 123 may not be able to drive the nail with a predetermined driving force. The above maximum compression timing corresponds to the “compression timing” in the present invention, and the release timing corresponds to the “release timing” in the present invention.

  Therefore, the nail driver 100 according to the present embodiment has the head valve 137 so that the opening timing for opening the communication port 135c of the head valve 137 coincides with the maximum compression timing when the components of the valve opening / closing mechanism are assembled. Timing adjusting means 170 is provided for adjusting the opening timing. This timing adjusting means 170 is an implementation configuration example corresponding to the “adjusting device” in the present invention.

  The timing adjustment unit 170 is mainly configured by a wedge-shaped member 171 disposed on the link 157 in the link mechanism 155. The structural members constituting the link mechanism 155 are an implementation structural example corresponding to the “intervening member” in the present invention. Hereinafter, the timing adjustment unit 170 will be described mainly with reference to FIGS. The link 157 on which the wedge-shaped member 171 is disposed is composed of two members, a first link element 165 to which the cam follower 161 is attached in the extending direction (vertical direction) and a second link element 167 connected to the push plate 159. It is composed of Then, in the extending direction of the link 157, a part of the first link element 165 and a part of the second link element 167 are arranged so as to overlap each other in the left-right direction (direction perpendicular to the paper surface of FIG. 1). The first link element 165 corresponds to the “first member” in the present invention, and the second link element 167 corresponds to the “second member” in the present invention. The wedge-shaped member 171 is disposed in an area where the first link element 165 and the second link element 167 overlap with each other, and moves in the extending direction of the link 157 to move the first link element 165 around the support shaft 156 in the front-rear direction. It is provided as a member to be rotated.

  In the region where the first link element 165 and the second link element 167 overlap each other, the first link element 165 has a circular first attachment hole 165a and a rectangular shape formed at a position above the first attachment hole 165a. A first engagement hole 165b for wedge engagement. The second link element 167 includes an oval second mounting hole 167a that is long in the front-rear direction, and a rectangular wedge engaging second engagement hole 167b that is formed at a position higher than the second mounting hole 167a. And have. The first link element 165 and the second link element 167 are rotatably attached to the main body housing 101 by the support shaft 156 inserted into the first mounting hole 165a and the second mounting hole 167a. Since the second mounting hole 167b is formed in an oval shape that is long in the front-rear direction, the second link element 167 is allowed to move in the front-rear direction with respect to the support shaft 156.

  As shown in FIG. 12, the wedge-shaped member 171 mainly includes a rectangular first engagement portion 173 and a rectangular second engagement portion 175 formed integrally with the first engagement portion 173. Has been. The first engaging portion 173 and the second engaging portion 175 are arranged side by side in the left-right direction. The first engagement portion 173 is engaged with the first engagement hole 165b of the first link element 165, and the front surface 173a of the first engagement portion 173 is in the first engagement hole in the first engagement hole 165b. The front surface of the joint hole 165b is contacted, and the rear surface 173b of the first engagement portion 173 is slidable in the vertical direction with the rear surface of the first engagement hole 165b being in contact. The second engagement portion 175 is engaged with the second engagement hole 167b of the second link element 167, and the front surface 175a of the second engagement portion 175 is the second engagement hole in the second engagement hole 167b. The first engagement portion 175 is in contact with the front surface of the second engagement portion 175, and the rear surface 175b of the second engagement portion 175 is in contact with the rear surface of the second engagement hole 167b.

  In FIG. 13, the first link element 165, the second link element 167, and the wedge-shaped member 171 are simply shown. In FIG. 13, for convenience, the first link element 165 and the first engaging portion 173 are indicated by broken lines, and the second link element 167 and the second engaging portion 175 are indicated by solid lines. The first engaging portion 173 and the first engaging hole 165b are formed substantially linearly in the extending direction (vertical direction) of the link 157. On the other hand, the second engagement portion 175 and the second engagement hole 167b pass above the center of the support shaft 156 as the rotation center of the link 157 and are upward with respect to a straight line orthogonal to the axis of the cylindrical cam 151. It is formed in an inclined shape that is inclined to the front (right side in FIG. 13). That is, the wedge-shaped member 171 constitutes an inverted V-shaped first wedge portion that is narrowed upward by the front surface 173a of the first engagement portion 173 and the rear surface 175b of the second engagement portion 175. The rear surface 173b of the joint portion 173 and the front surface 175a of the second engagement portion 175 constitute a V-shaped second wedge portion that narrows downward.

  Therefore, when the wedge-shaped member 171 is moved upward as indicated by the arrow F in FIG. 13, the first wedge portion acts as a wedge. That is, the front surface 173a of the first engagement portion 173 pushes the front surface of the first engagement hole 165b of the first link element 165 forward (rightward in FIG. 13), and the rear surface 175b of the second engagement portion 175 is the second. The rear surface of the second engagement hole 167b of the link element 167 is pushed backward (leftward in FIG. 13). For this reason, the first link element 165 rotates around the support shaft 156 in the direction indicated by the arrow P, that is, in the rear direction in which the cam follower 161 is brought into contact with the cylindrical cam 151. On the other hand, when the wedge-shaped member 171 is moved downward, the second wedge portion acts as a wedge. That is, the rear surface 173b of the first engagement portion 173 pushes the rear surface of the first engagement hole 165b of the first link element 165 rearward (leftward in FIG. 13), and the front surface 175a of the second engagement portion 175 is second. The front surface of the second engagement hole 167b of the link element 167 is pushed forward (rightward in FIG. 13). For this reason, the first link element 165 rotates around the support shaft 156 in the direction opposite to the direction indicated by the arrow P, that is, forward to separate the cam follower 161 from the cylindrical cam 151. Thus, the wedge-shaped member 171 is provided as a member that adjusts the relative position of the first link element 165 and the second link element 167 in accordance with the position of the wedge-shaped member 171. This wedge-shaped member 171 is an implementation structural example corresponding to the “position adjusting member” in the present invention.

  When the nailing machine 100 is driven, when the cam follower 161 rides on the peak portion 153a of the cylindrical cam 151, the front surface of the first engagement hole 165b of the first link element 165 is the front surface 173a of the first engagement portion 173. Is pushed rearward, and the rear surface of the second engagement hole 167b of the second link element 167 relatively pushes the rear surface 175b of the second engagement portion 175 forward. That is, when the nailing machine 100 is driven, a force is applied to the wedge-shaped member 171 to move the wedge-shaped member 171 downward through the inverted V-shaped first wedge portion. In the present embodiment, the frictional force generated on the sliding surface between the rear surface 175b of the second engagement portion 175 and the rear surface of the second engagement hole 167b exceeds the force for moving the wedge-shaped member 171 downward. The inclination angle of the second engagement portion 175 and the second engagement hole 167b with respect to a straight line passing through the center of the support shaft 156 and orthogonal to the axis of the cylindrical cam 151 is set. As a result, the wedge-shaped member 171 firmly connects the first link element 165 and the second link element 167.

  That is, the wedge-shaped member 171 can be moved with fingers, but is not moved by the force received from the cylindrical cam 151 side. When the timing is adjusted, the wedge-shaped member 171 rotates the first link element 165 around the support shaft 156, thereby intersecting the axis of the cylindrical cam 151 and passing through the rotation center of the link 157. The inclination angle of the first link element 165 with respect to is changed, thereby functioning to change the position of the cam follower 161 with respect to the axial direction of the cylindrical cam 151. On the other hand, the wedge-shaped member 171 is not moved by the force received from the cylindrical cam 151 when the nailing machine 100 is driven, and the vertical position with respect to the link 157 is fixed, and the first link element 165 and the second link element 167 It functions as a member that firmly connects the two.

  Further, the wedge-shaped member 171 of this embodiment has a cylindrical spring accommodating portion 177, and a compression coil spring 179 as an urging member is accommodated in the cylindrical space of the spring accommodating portion 177. This compression coil spring 179 is an implementation structural example corresponding to the “second urging member” in the present invention. The compression coil spring 179 has one end in the axial direction supported by the bottom surface of the cylindrical space of the spring accommodating portion 177 and the other end supported by the spring extending in a direction intersecting with the extending direction of the link 157 provided in the first link element 165. Supported by the portion 165c. For this reason, the urging force of the compression coil spring 179 is always applied to the wedge-shaped member 171 upward. Note that the wedge-shaped member 171 has a washer with a screw 169 in a state where the first engagement portion 173 is engaged with the first engagement hole 165b and the second engagement portion 175 is engaged with the second engagement hole 167b. It is attached so as not to fall off from the link 157 via 168.

  The timing adjustment unit 170 according to the present embodiment is configured as described above. In the assembled state of the valve opening / closing mechanism in which the head valve 137 is opened / closed by the cylindrical cam 151 via the link mechanism 155, the head valve 137 is pushed forward by the urging force of the compression coil spring 138 to a position where the communication port 135 c is closed. Is retained. In this state, as described above, the manufacturing error of each component constituting the valve opening / closing mechanism is, as described above, between the connecting portions of each component, specifically between the cam follower 161 and the cam surface 153 of the cylindrical cam 151. The gap appears between the link 157 and the push plate 159 and between the push plate 159 and the head valve 137. The generation of such a gap is an opening that opens the communication port 135c of the head valve 137 with respect to the maximum compression timing when the compression piston 133 is moved to a position where the compressed air in the compression chamber 131a is brought into a maximum compression state. The timing will shift.

  When the wedge-shaped member 171 is moved upward in order to adjust the deviation of the opening timing of the head valve with respect to the maximum compression timing due to such a manufacturing error, the first link above the support shaft 156 as shown in FIG. In the region where the element 165 and the second link element 167 overlap, the first wedge portion of the wedge-shaped member 171 acts as a wedge. That is, the front surface 173a of the first engagement portion 173 pushes the front surface of the first engagement hole 165b of the first link element 165 forward (rightward in FIG. 13), and the rear surface 175b of the second engagement portion 175 is the second. The rear surface of the second engagement hole 167b of the link element 167 is pushed backward (leftward in FIG. 13). For this reason, the first link element 165 rotates around the support shaft 156 in the rear direction indicated by the arrow P, and the cam follower 161 comes into contact with the cam surface 153 of the cylindrical cam 151. On the other hand, the second link element 167 is rotated forward around the support shaft 156. The push plate 159 is moved forward by the forward rotation of the second link element 167. This eliminates the gap between the cam follower 161 and the cam surface 153 of the cylindrical cam 151, the gap between the link 157 and the push plate 159, and the gap between the push plate 159 and the head valve 137. That is, the cam follower 161 and the cam surface 153 of the cylindrical cam 151 are in contact with each other, the link 157 and the push plate 159 are in contact with each other, and the push plate 159 and the head valve 137 are in contact with each other.

  According to the present embodiment, as described above, the cam follower 161 and the cam surface 153 of the cylindrical cam 151 are in contact with each other, the link 157 and the push plate 159 are in contact with each other, and the push plate 159 and the head valve 137 are in contact with each other. Thus, the opening timing for opening the communication port 135c of the head valve 137 is adjusted to coincide with the maximum compression timing of the compression piston 133. That is, when the compression piston 133 driven by the crank mechanism 115 reaches near the top dead center and the compressed air in the compression chamber 131a is in the maximum compression state, the head valve 137 driven by the cylindrical cam 151 is connected to the communication port. It is adjusted so that 135c is opened, and thereby it is possible to secure the planned driving performance of the nail driver 100. That is, the pressure supplied to the cylinder chamber 121a of the driving cylinder 121 is stabilized, and the driving piston 123 can drive the nail with a predetermined driving force.

  Further, in the present embodiment, the wedge-shaped member 171 is configured such that the urging force of the compression coil spring 179 always acts upward. For this reason, even when the cam surface 153 of the cylindrical cam 151 and the cam follower 161 are worn due to long-term use, the wedge-shaped member 171 is moved upward by the biasing force of the compression coil spring 179, and the cylindrical cam 151 is caused by the wear. The cam surface 153 and the cam follower 161 can be automatically adjusted so that no gap is generated. The automatic adjustment by the compression coil spring 179 can be said not only at the time of wear but also at the time of assembly. That is, the urging force of the compression coil spring 179 that urges the wedge-shaped member 171 causes the cam follower 161 and the cam surface 153 of the cylindrical cam 151 to contact each other, the link 157 and the push plate 159 contact each other, and the push plate 159 and the head valve The relative positions of the first link element 165 and the second link element 167 are positioned so that the 137 abuts each other. Therefore, unlike manual adjustment, positioning can be performed with a constant force (spring load) determined by the compression coil spring 179 without excess or deficiency.

(Second embodiment of the present invention)
Next, a second embodiment of the present invention will be described in detail with reference to FIG. This embodiment is a modification of the timing adjustment unit 170 of the first embodiment, and the configuration other than the timing adjustment unit 170 is the same as that of the first embodiment. The timing adjustment means 170 of the present embodiment is provided on the push plate 159 among the constituent members of the link mechanism 155 disposed between the cylindrical cam 151 and the head valve 137, and the extension direction of the push plate 159 It is comprised by the turnbuckle 187 which adjusts the length of. In the present embodiment, the link 157, which is another constituent member of the link mechanism 155, is composed of a single long plate-like member. The constituent members of the link mechanism 155 correspond to the “interposition member” in the present invention, the link 157 corresponds to the “swing member” in the present invention, and the push plate 159 corresponds to the “transmission member” in the present invention. It is an implementation structural example.

  As shown in FIG. 14, the push plate 159 extends in the front-rear direction along the driving cylinder 121 and is configured by two members of a first plate element 181 and a second plate element 183 in the extending direction. ing. The first plate element 181 corresponds to the “first member” and the “first transmission member” in the present invention, and the second plate element corresponds to the “second member” and the “second transmission member” in the present invention. It is an implementation configuration example. The first plate element 181 has a rear L-shaped end 181a and a front L-shaped end 181b each formed in an L shape. The rear L-shaped end 181 a is inserted into the valve chamber 136 through the opening of the cylinder head 122 of the driving cylinder 121 and is connected to the head of the head valve 137. A screw hole is formed in the front L-shaped end 181b.

  The front end side of the second plate element 183 is connected to the upper end portion of the link 157 by a pin 185 so as to be relatively rotatable. The second plate element 183 has an L-shaped end 183a at the rear end, and the L-shaped end 183a faces the front L-shaped end 181b of the first plate element 181 with a predetermined distance.

  The turnbuckle 187 is mainly composed of an adjustment screw 189 extending through the front L-shaped end 181b of the first plate element 181 and the L-shaped end 183a of the second plate element 183. The adjustment screw 189 is attached to one end side in the axial direction so as to be rotatable around the axis line in a state where movement in the axial direction is restricted with respect to the L-shaped end portion 183a of the second plate element 183, and a hand tool such as a spanner The end portion 189a is formed in a square shape in order to enable the rotation operation using the. A male screw 189 b is formed on the other axial end side of the adjustment screw 189, and this male screw 189 b is screwed into a screw hole of the front L-shaped end 181 b of the first plate element 181. A lock nut 188 is screwed into the male screw 189 b of the adjustment screw 189.

  The turnbuckle 187 of the present embodiment is configured as described above. Therefore, in the state where the lock nut 188 is loosened, the adjustment screw 189 is rotated to narrow the distance between the front L-shaped end 181b of the first plate element 181 and the L-shaped end 183a of the second plate element 183. . As a result, the length of the push plate 159 extends, and the distance from the connection point with the link 157 to the connection point with the head valve 137 increases. By extending the length of the link 157, the link 157 rotates around the support shaft 156 in a direction in which the cam follower 161 contacts the cam surface 153 of the cylindrical cam 151. That is, the turnbuckle 187 adjusts the length of the push plate 159 by adjusting the relative position of the first plate element 181 and the second plate element 183, and corresponds to the “position adjusting member” in the present invention. It is an implementation configuration example.

  As described above, according to the present embodiment, the adjusting screw 189 of the turnbuckle 187 is rotated, the length of the push plate 159 is adjusted, and the cam follower 161 is brought into contact with the cam surface 153 of the cylindrical cam 151. As in the case of the first embodiment described above, the clearance between the cam follower 161 and the cam surface 153 of the cylindrical cam 151 due to the manufacturing error, the clearance between the link 157 and the push plate 159, the push plate 159 And the head valve 137 can be eliminated.

(Third embodiment of the present invention)
Next, a third embodiment of the present invention will be described in detail with reference to FIG. This embodiment is a modification of the timing adjustment unit 170 of the first embodiment, and the configuration other than the timing adjustment unit 170 is the same as that of the first embodiment. The timing adjustment means 170 of the present embodiment is mainly configured by a shim (thin plate) 191 interposed at a connection portion between the head valve 137 and the push plate 159. Further, in the present embodiment, as in the case of the second embodiment, the link 157 among the constituent members of the link mechanism 155 is configured by a single long plate-shaped member. The constituent members of the link mechanism 155 correspond to the “interposition member” in the present invention, the link 157 corresponds to the “swing member” in the present invention, and the push plate 159 corresponds to the “transmission member” in the present invention. It is an implementation structural example.

  As shown in FIG. 15, the head valve 137 has a flange portion 137b on the outer periphery of the head portion, and includes a screw shaft portion 137c formed with a male screw behind the flange portion 137b. On the other hand, an L-shaped end portion 159a having a through hole into which the screw shaft portion 137c can be inserted is formed at the rear end portion of the push plate 159. After inserting the screw shaft portion 137c of the head valve 137 into the through hole of the L-shaped end portion 159a, a lock nut 193 is screwed into the screw shaft portion 137c, and the L-shaped end portion 159a is connected by the lock nut 193 and the flange portion 137b. The head valve 137 and the push plate 159 are connected by sandwiching them.

  In the connection structure as described above, in this embodiment, an annular shim 191 that can be fitted to the screw shaft portion 137c is disposed between the flange portion and the L-shaped end portion 159a so as to perform so-called shim adjustment. Thus, the relative position of the head valve 137 and the push plate 159 is adjusted. As a result, the length from the connection center of the push plate 159 to the head valve 137 to the connection center of the push plate 159 with the link 157 (the center of the pin 163) is adjusted. This shim 191 is an implementation configuration example corresponding to the “position adjusting member” in the present invention.

  According to this embodiment, the length adjustment described above is performed, the link 157 is rotated around the support shaft 156, and the cam follower 161 is brought into contact with the cam surface 153 of the cylindrical cam 151. As in the case of the configuration, a gap between the cam follower 161 and the cam surface 153 of the cylindrical cam 151 due to a manufacturing error, a gap between the link 157 and the push plate 159, and between the push plate 159 and the head valve 137. The gap can be eliminated.

  In the above-described embodiment, the opening timing of the head valve 137 is made to coincide with the maximum compression timing at which the compression piston 133 is moved to the position where the compressed air in the compression chamber 131a is in the maximum compression state. It is not limited to the compression timing. That is, with respect to the compression timing when the compression piston 133 is moved and the air in the compression chamber 131a is driven in and the pressure state is higher than a certain level necessary for driving the nail by the piston 123, the compression timing is moved to a predetermined position. Thus, the opening timing of the head valve 137 may be configured to match.

  The timing adjusting means 170 may be provided on the cylindrical cam 151 side. Specifically, a shim as timing adjusting means 170 is disposed between the cylindrical cam 151 and the crankshaft 115a so that the position of the cylindrical cam 151 in the axial direction with respect to the crankshaft 115a can be adjusted. The relative position between the cam 151 and the cam follower 161 may be adjustable.

  In each of the above-described embodiments, the link mechanism 155 is described as including the link 157 and the push plate 159, but the push plate 159 that is one of the components of the link mechanism 155 is omitted. May be. That is, the link 157 is provided so as to be rotatable around the support shaft 156. Then, a cam follower 161 capable of contacting the cam surface 153 of the cylindrical cam 151 may be provided on one end side of the link 157, and the other end side of the link 155 may be directly connected to the head valve 137.

  In addition, the timing adjusting unit 170 according to each of the above-described embodiments has been described in the case where the driving cylinder 121 and the compression cylinder 131 are applied to a nail driver in which the driving cylinder 121 and the compression cylinder 131 are orthogonally arranged. May be applied to a valve opening and closing mechanism of a driving machine having a configuration in which are arranged in parallel. In that case, the cylindrical cam is changed to a plate cam, and the head valve is configured to open and close via a bar-shaped interposed member that linearly moves according to the rotation of the plate cam. For example, the length may be adjusted by a turnbuckle, or a shim may be interposed at a connection portion between the interposed member and the head valve.

  Moreover, although embodiment mentioned above demonstrated the nail driver 100 as an example as a driving tool, you may apply to driving tools called a tucker other than a nail driver and a stapler.

(Correspondence between each component of the embodiment and the component of the present invention)
The relationship between each component in the present embodiment and the invention-specific matters of the component in the present invention is as follows. Of course, each component in the present embodiment is only one example of the configuration related to the specific matters of the present invention, and each component of the present invention is not limited to this.
The nailing machine 100 is an example of a configuration corresponding to the “driving tool” of the present invention.
The electric motor 111 is an example of a configuration corresponding to the “motor” in the present invention.
The driving cylinder 121 is an example of a configuration corresponding to the “first cylinder” of the present invention.
The driving piston 123 is an example of a configuration corresponding to the “first piston” of the present invention.
The piston main body portion 124 is an example of a configuration corresponding to the “sliding portion” of the present invention.
The driver 125 is an example of a configuration corresponding to the “driving unit” of the present invention.
The compression cylinder 131 is an example of a configuration corresponding to the “second cylinder” of the present invention.
The compression piston 133 is an example of a configuration corresponding to the “second piston” of the present invention.
The crank mechanism 115 is an example of a configuration corresponding to the “crank” of the present invention.
The air passage 135 is an example of a configuration corresponding to the “compressed air supply path” of the present invention.
The head valve 137 is an example of a configuration corresponding to the “valve member” of the present invention.
The cylindrical cam 151 is an example of a configuration corresponding to the “cam member” of the present invention.
The compression coil spring 138 is an example of a configuration corresponding to the “biasing member” of the present invention.
The timing adjustment unit 170 is an example of a configuration corresponding to the “adjustment device” in the present invention.
The structural member of the link mechanism 155 is an example of the structure corresponding to the “interposition member” of the present invention.
The first link element 165 is an example of a configuration corresponding to the “first member” of the present invention.
The second link element 167 is an example of a configuration corresponding to the “second member” of the present invention.
The wedge-shaped member 171, the turnbuckle 187 and the shim 191 are an example of a configuration corresponding to the “position adjusting member” of the present invention.
The compression coil spring 179 is an example of a configuration corresponding to the “second biasing member” of the present invention.
The link 157 is an example of a configuration corresponding to the “swing member” of the present invention.
The push plate 159 is an example of a configuration corresponding to the “transmission member” of the present invention.
The first plate element 181 is an example of a configuration corresponding to the “first member” and the “first transmission member” of the present invention.
The 2nd plate element 183 is an example of the structure corresponding to the "2nd member" and "2nd transmission member" of this invention.

100 nailing machine (driving tool)
101 body housing 101A driving mechanism housing portion 101B compression device housing portion 101C motor housing portion 103 handle portion 103a trigger 105 magazine 110 battery pack 111 electric motor (motor)
115 Crank mechanism (crank)
115a Crankshaft 115b Eccentric pin 115c Connecting rod 120 Nail driving mechanism 121 Driving cylinder (first cylinder)
121a Cylinder chamber 122 Cylinder head 123 Driving piston (first piston)
124 Piston body (sliding part)
125 driver (driving part)
127 Partition wall 129 O-ring 130 Compressor 131 Compression cylinder (second cylinder)
131a Compression chamber 132 Cylinder head 133 Compression piston (second piston)
135 Air passage (Compressed air supply route)
135a Tubular member 135b Communication port 135c Communication port 136 Valve chamber 137 Head valve (valve member)
137a Seal surface 137b Flange portion 137c Screw shaft portion 138 Compression coil spring (biasing member)
139 O-ring 141 Driver guide 151 Cylindrical cam 153 Cam surface 153a Mountain portion 153b Valley portion 155 Link mechanism (intervening member)
156 Support shaft 157 Link (interposition member, swing member)
159 Push plate (transmission member)
159a L-shaped end portion 161 Cam follower 163 Pin 165 First link element (first member)
165a First mounting hole 165b First engagement hole 165c Spring support 167 Second link element (second member)
167a Second mounting hole 167b Second engagement hole 168 Washer 169 Screw 170 Timing adjustment means (adjustment device)
171 Wedge-shaped member (position adjustment member)
173 First engagement portion 173a Front surface 173b Rear surface 175 Second engagement portion 175a Front surface 175b Rear surface 177 Spring accommodating portion 179 Compression coil spring (second biasing member)
181 First plate element (first member, first transmission member)
181a Rear L-shaped end 181b Front L-shaped end 183 Second plate element (second member, second transmission member)
183a L-shaped end 185 Pin 187 Turnbuckle (position adjustment member)
188 Lock nut 189 Adjustment screw 189a End 189b Male screw 191 Shim (Position adjustment member)
193 Lock nut

Claims (8)

A motor,
A first cylinder;
A first piston having a sliding portion accommodated in the first cylinder so as to be slidable, and a long driving portion that is connected to the sliding portion and drives a material to be driven;
A second cylinder;
A second piston that generates compressed air by reciprocating in the second cylinder;
A crank driven by the motor to reciprocate the second piston in the second cylinder;
A compressed air supply path communicating the first cylinder and the second cylinder;
A valve member that moves between an open position for opening the compressed air supply path and a closed position for closing the compressed air supply path;
A biasing member that biases the valve member toward the closed position;
A cam member connected to the crank and driven to rotate,
Opening / closing control of the compressed air supply path by the valve member is performed according to the cam lift amount of the cam member,
When the valve member is moved to the open position, the first piston is moved linearly by the compressed air sent from the second cylinder to the first cylinder through the compressed air supply path, A driving tool for performing a driving operation of the driven material by the driving portion of the first piston,
The second piston is moved and moved to a predetermined position within a region where the air in the second cylinder is in a pressure state higher than a certain level necessary for driving the material to be driven by the first piston. An adjusting device for adjusting the opening timing of the valve member so that the opening timing of the assembled valve member being moved to the opening position and opening the compressed air supply path coincides with the compression timing at that time A driving tool characterized by comprising. The driving tool according to claim 1,
An interposition member connecting the cam member and the valve member;
The interposed member moves in contact with the cam member, the moved interposed member contacts the valve member and moves the valve member, and the compressed air supply path is opened by moving the valve member. Configuration
The adjusting device is configured by a position adjusting member capable of adjusting a relative position between the cam member and the interposed member, or a relative position between the valve member and the interposed member,
The relative position between the cam member and the interposition member or the relative position between the valve member and the interposition member is adjusted by the position adjustment member so that the interposition member contacts the cam member and the valve member. The driving tool is characterized in that the opening timing is adjusted to coincide with the compression timing. The driving tool according to claim 2,
The interposition member includes a first member and a second member that can move relative to each other,
The position adjusting member is disposed in an intervening manner between the first member and the second member,
The relative position of the first member and the second member is configured to be adjustable by the position adjusting member,
The relative position between the first member and the second member is adjusted by the position adjusting member, so that the relative position between the cam member and the interposed member or the relative position between the valve member and the interposed member is adjusted. A driving tool characterized by A driving tool according to claim 3, wherein
The position adjusting member has a wedge-shaped member,
The wedge-shaped member is provided to be movable with respect to each of the first member and the second member,
A driving tool characterized in that the relative position of the first member and the second member can be adjusted according to the position of the wedge-shaped member. The driving tool according to claim 4,
The position adjusting member has a second biasing member that biases the wedge-shaped member,
The driving tool characterized in that the first member and the second member are held so that the interposition member abuts on each of the cam member and the valve member by the biasing force of the second biasing member. The driving tool according to claim 4 or 5,
The first member and the second member are attached so as to be individually rotatable around the same axis,
A driving tool characterized in that a relative position between the first member and the second member with respect to the same axis can be adjusted according to the position of the wedge-shaped member. The driving tool according to claim 2,
The valve member is configured to open and close the compressed air supply path by moving in a predetermined axial direction,
The interposition member is disposed so as to be able to contact the cam member and swings by the cam member in the rotation axis direction of the cam member with a predetermined rotation shaft as a fulcrum, and the predetermined shaft A transmission member that extends in a direction and transmits the swing of the swing member to the valve member as a reciprocating motion;
The transmission member includes a first transmission member and a second transmission member that are movable relative to each other with respect to the predetermined axial direction.
The first transmission member is disposed so as to be able to contact the valve member, and the second transmission member is connected to the swing member;
The position adjusting member is disposed between the first transmission member and the second transmission member,
The relative position of the first transmission member and the second transmission member is configured to be adjustable by the position adjustment member,
The relative position between the first transmission member and the second transmission member is adjusted by the position adjustment member, so that the relative position of the swing member relative to the cam member or the relative position of the first transmission member relative to the valve member. A driving tool characterized in that is adjusted. The driving tool according to claim 2,
The valve member is configured to open and close the compressed air supply path by moving in a predetermined axial direction,
The interposition member is disposed so as to be able to contact the cam member and swings by the cam member in the rotation axis direction of the cam member with a predetermined rotation shaft as a fulcrum, and the first piston And a transmission member that transmits the swing of the swing member to the valve member as a reciprocating motion.
The position adjustment member is disposed in an interposed manner between the transmission member and the valve member,
A driving tool characterized in that a relative position between the transmission member and the valve member can be adjusted by the position adjusting member.

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