JP2008213105A - Screw driving machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a screw driving machine capable of switching driving forces and also securing sufficient displacement by solving the problem wherein a screw driving machine of driving a screw while rotating the screw by means of compressed air as a power source sometimes has an insufficient exhaust flow rate when the intake flow rate is reduced, when a structure which switches the driving forces according to cases of driving into a steel plate and a wooden plate is employed. <P>SOLUTION: A valve body 42 is provided vertically movably in the axial direction of a cylinder 21 on a valve seat 41 and the valve body 42 is elevated by the compressed air in a cylinder upper chamber 24 generated by elevating a piston 22, thereby exhausting through both a large vent hole 42a and a small vent hole 42b. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention is a so-called air tool that uses compressed air as a power source, and is screwed into a screw driving material by driving a screwdriver bit having a screw set at the tip end in an axial direction while rotating the screwdriver. Related to the machine.

For example, when a gypsum board as an upper material is screwed to a wooden board as a base, a screw driving machine capable of continuously tightening a large number of screws is used. This screw driving machine is configured to move the driver bit in the axial direction by rotating the driver bit by the thrust (driving force) of the piston using compressed air as the power source and the rotational force (screw tightening force) of the air motor. According to the above, in the movement process of the driver bit, the tip of the driver bit is fitted to the screw head of the screw connection band in which a large number of screws are connected in parallel, and the screw is detached from the screw connection band. The upper material can be screwed to the ground by penetrating the upper material into the ground while being rotated.
As a technique related to this screw driving machine, for example, a technique disclosed in Patent Document 1 below has been known. This prior art is configured to include a mechanism (intake flow rate switching mechanism) that switches the thrust of the piston in two stages by switching the intake flow rate to the cylinder that houses the piston for screw striking in two stages. According to such a configuration, the piston thrust is changed in two stages by switching the intake air flow rate to the cylinder when the base is a relatively soft wood board (wood boarding) and when it is a harder steel board (steel boarding). In the former case, the screw is driven with a relatively small driving force, and in the latter case, the screw is driven with a larger driving force. And an appropriate tightening force (fastening force) of the screw can be obtained.
Japanese Patent No. 3520443 JP-A 64-45580 JP-A-8-141931

  However, according to the above-described conventional intake flow rate switching mechanism, when the intake flow rate is reduced to the low flow rate side for striking the wood board, the exhaust flow rate when the piston moves up is also reduced, so the exhaust efficiency is reduced. There was a problem to do. The present invention has been made in view of this problem, and it is possible to switch the thrust of the piston depending on the tightening target, and maintain high exhaust efficiency even when the intake flow rate to the cylinder is reduced by this switching. The purpose is to be able to.

For this reason, the present invention is a screw driving machine having the configuration described in each claim.
According to the screw driving machine of the first aspect, the air is sucked into the cylinder upper chamber through the flow rate switching valve provided in the upper part of the cylinder. This intake flow rate can be switched between a large flow rate for steel plate driving and a small flow rate for wood plate driving by switching the flow rate switching valve.
In addition, according to the screw driving machine of the first aspect, the switching valve is automatically switched by the pressure of the cylinder upper chamber generated by the upward movement of the piston, and the exhaust flow rate through the flow rate switching valve is higher than the intake flow rate. Also grows. For this reason, for example, even when the flow rate switching valve is switched to the small flow rate side in order to strike a wood board, the flow rate switching valve automatically switches when the piston moves up, and the exhaust gas is exhausted at a flow rate greater than the intake flow rate. Therefore, high exhaust efficiency can be ensured. Further, for example, even when the flow rate switching valve is switched to the high flow rate side to make a steel plate, when the piston moves up, the flow rate switching valve automatically switches to exhaust at a flow rate greater than the intake flow rate. Therefore, high exhaust efficiency can be ensured even in the case of the steel plate hitting.
Thus, according to the screw driving machine of the first aspect, it is possible to switch to a driving force appropriate for each of the steel plate driving and the wooden plate driving without impairing the exhaust efficiency.
According to the screw driving machine of the second aspect, the intake flow rate is switched by rotating the valve body around the cylinder axis. This switching can be performed manually by the user of the screw driving machine. Further, when the piston moves up, the valve main body automatically moves in the cylinder axial direction by the pressure in the cylinder upper chamber to ensure a large exhaust flow rate.
According to the screw driving machine of claim 3, when the valve body is rotated around the cylinder axis and the large ventilation hole is aligned with the reference ventilation hole, for example, a large intake flow rate can be secured. A force (piston thrust) can be generated to reliably perform steel plate punching.
On the other hand, if the valve body is rotated around the cylinder axis and the small ventilation hole is aligned with the reference ventilation hole, the intake flow rate can be reduced. Can be driven into the wood board by an appropriate amount. For this reason, it is possible to perform wood board driving with high pull-out resistance while reducing reaction during screw driving.
According to the screw driving machine of the fourth aspect, the valve body moves in a direction away from the valve seat against the spring biasing force by the air pressure in the cylinder upper chamber, and a large exhaust flow rate is secured. When the upward movement of the piston is completed and the pressure in the cylinder upper chamber is reduced, the valve body is returned to the state in contact with the valve pedestal by the urging force of the compression spring.
According to the screw driving machine of the fifth aspect, it is possible to prevent the inadvertent movement by holding the switching operation lever at the switching position.
According to the screw driving machine of the sixth aspect, it is possible to enhance the functionality of the valve pedestal portion and thus the flow rate switching valve, thereby reducing the number of parts, the assembly cost, and making the driving machine compact. Can do.

Next, an embodiment of the present invention will be described with reference to FIGS. FIG.1 and FIG.2 has shown the non-operation state (initial state) of the screw driving machine 1 which concerns on this embodiment. The screw driving machine 1 includes a main body portion 2 having a substantially cylindrical body shape, and a handle portion 3 provided so as to protrude sideways from substantially the center in the longitudinal direction of the main body portion 2. A trigger valve 4 is disposed near the base of the handle portion 3. The trigger valve 4 is opened and closed by a trigger 5 that is pulled by a user with a fingertip. Since the trigger valve 4 itself is the same as that conventionally known and does not require any particular change in the present embodiment, a detailed description of its configuration and operation is omitted.
When the user pulls the trigger 5, one screw S is driven into the screw driving material W from the tip (lower end in FIG. 1) of the main body 2. The screw driving material W has a two-layer structure of an upper material W1 and a base W2. The upper material W1 is, for example, a gypsum board, and the base W2 is a wooden board or a steel plate.
An air hose 6 for supplying compressed air serving as a power source of the screw driving machine 1 is connected to the tip of the handle portion 3. Compressed air is supplied from the air hose 6 to the pressure accumulating chamber 7 inside the handle portion 3. Further, an exhaust pipe 8 is attached inside the handle portion 3 along the longitudinal direction thereof. One end side (exhaust port 8 a) of the exhaust pipe 8 is opened at the distal end portion of the handle portion 3. The other end of the exhaust pipe 8 communicates with an exhaust chamber 8 b provided in the main body 2.
Between the lower part of the main body part 2 and the tip part of the handle part 3, a magazine 11 for accommodating a screw connection band (not shown) holding a number of screws S to S in parallel, and a screw pulled out from the magazine 11 A screw connection band feed mechanism 12 for pitch-feeding the connection band to the main body 2 side is provided.

The main body 2 includes an impact mechanism 20, an air motor 50, and a speed reduction mechanism 70 in order from the upper side in FIG. 1. As shown in the drawing, the striking mechanism portion 20 is disposed on the upper side with respect to the handle portion 3, and the air motor 50 and the speed reducing mechanism portion 70 are disposed on the lower side.
The striking mechanism 20 includes a cylinder 21 and a piston 22 accommodated therein. The piston 22 is accommodated in the cylinder 21 so as to reciprocate up and down in the drawing. Hereinafter, an upper chamber that is an air chamber inside the cylinder 21 and is hermetically partitioned by the piston 22 is referred to as a cylinder upper chamber 24, and a lower chamber is referred to as a cylinder lower chamber 25.
The cylinder 22 is held immovably inside the holding sleeve 27. The holding sleeve 27 is fixed to the main body housing 2 a of the main body 2.
At the center of the lower surface of the piston 22, an upper end portion of the driver bit 23 is coupled so as to be rotatable around its axis and not movable in the axial direction. The driver bit 23 extends from the center of the lower surface of the piston 22 downward (in the screw driving direction) and reaches the vicinity of the tip of the main body 2.
A cylindrical head valve 30 is disposed on the outer periphery of the holding sleeve 27. Details of the head valve 30 and its surroundings are shown in FIG. FIG. 3 shows a state in which the trigger 5 is started to be pulled from the initial state shown in FIGS. 1 and 2, the head valve 30 starts to open, the air motor 50 starts to rotate, and the damper 26 is moved upward. Operations from these initial positions will be described later.
Compression springs 31 to 31 are interposed between the head valve 30 and the head housing 2b. The head valve 30 is always urged downward (closed side) by the compression springs 31-31. In addition, on the upper surface side (head valve upper chamber 30a) of the head valve 30, the state is switched between a state where the compressed air in the pressure accumulating chamber 7 acts via the trigger valve 4 and a state where the compressed air is released to the atmosphere and does not act. . The air pressure action state of the head valve upper chamber 30a is switched by the operation of the trigger 5 and the operation of the trigger valve 4.

On the other hand, an outer pressure receiving surface 30e and an inner pressure receiving surface 30f, which are inclined in the direction of decreasing the thickness, are respectively provided at the lower part of the head valve 30 over the entire circumference. The compressed air of the pressure accumulating chamber 7 always flows into the head valve lower chamber 30d defined below the pressure receiving surface 30e on the outer peripheral side. For this reason, the air pressure of the compressed air always acts on the pressure receiving surface 30e. The compressed air pressure acting on the pressure receiving surface 30e acts in a direction to move the head valve 30 upward.
When the trigger valve 4 is turned on by pulling the trigger 5, the compressed air in the head valve upper chamber 30a is exhausted and released to the atmosphere. The urging force of the compression springs 31 to 31 is set to be smaller than the pressure of the compressed air acting on the pressure receiving surface 30e of the head valve 30. For this reason, when the trigger valve 4 is turned on, the head valve 30 is moved up against the compression springs 31 to 31 by the compressed air pressure acting on the pressure receiving surface 30e.
When the head valve 30 is moved upward, the inner peripheral side vent chamber 30b is changed to the outer peripheral side head valve lower chamber 30d at an initial stage (half-open state) where the lower end of the head valve 30 starts to open between the upper surface of the valve seat portion 35. As a result, compressed air flows into the ventilation chamber 30b. The ventilation chamber 30 b communicates with the air motor 50 through the ventilation chamber 32. For this reason, at the initial stage when the head valve 30 starts to open, the air motor 50 starts to rotate first. Details of the air motor 50 will be described later.
The compressed air that has flowed into the ventilation chamber 30b acts on the pressure-receiving surface 30f on the inner peripheral side of the head valve 30, so that the head valve 30 moves up at once and is fully opened. FIG. 7 shows a state where the head valve 30 is fully opened. When the head valve 30 is fully opened, an air passage is opened with the seal ring 27a attached to the outer periphery of the upper portion of the holding sleeve 27, and the air chamber 30c on the inner peripheral side of the head valve 30 is communicated with the air chamber 30b. Compressed air flows into the ventilation chamber 30c. The compressed air that has flowed into the ventilation chamber 30 c flows into the cylinder upper chamber 24 through the flow rate switching valve 40 mounted on the upper portion of the cylinder 21. Thus, when compressed air flows into the cylinder upper chamber 24, the piston 22 moves downward. When the piston 22 moves downward, the driver bit 23 moves downward along its axial direction.
When the driver bit 23 moves downward, its tip is engaged with the head of one screw S of the screw connection band supplied from the magazine 11, and after removing the screw S from the screw connection band as it is, the screw driving material W is driven into. The driving force of the driver bit 23 (the thrust of the piston 22) can be switched between large and small by switching the intake flow rate to the cylinder upper chamber 24 by a flow rate switching valve 40 described below.

Details of the flow rate switching valve 40 are also shown in FIGS. The flow rate switching valve 40 includes a generally disc-shaped valve pedestal portion 41 that is fixed in a state where the upper end portion of the cylinder 21 is airtightly closed, a valve main body 42, and a switching lever 43 that changes the relative position of both. .
The valve pedestal portion 41 is fitted into the upper end portion of the cylinder 21 opened in a mortar shape, and is not movable in the axial direction and is pivoted around the shaft while being sandwiched between the upper end portion of the cylinder 21 and the head housing 2b. It is fixed in a non-rotatable state. The valve pedestal portion 41 has moderate elasticity and functions as a damper (cushion body) that regulates the upper moving end (top dead center) of the piston 22 and absorbs an impact when moving upward. Also have. The valve pedestal 41 is provided with reference vent holes 41a to 41a penetrating in the plate thickness direction. In the present embodiment, the three reference vent holes 41a to 41a are arranged at circumferentially equally divided positions (120 ° intervals). As shown in FIGS. 12 and 15, each reference vent hole 41a is opened in a fan shape, and the opening area thereof is relatively large.
The valve main body 42 has a substantially disk shape facing the upper surface of the valve pedestal portion 41, and a support shaft portion 42c is integrally provided at the center of the upper surface. The valve main body 42 is supported by the head housing 2b via the support shaft portion 42c so as to be rotatable about its axis and parallelly movable within a certain range in the axial direction. The support shaft portion 42c passes through the head housing 2b and protrudes into a recess 2c provided on the outer surface of the head housing 2b. A switching lever 43 is attached to the protruding portion. The switching lever 43 is fixed to the tip of the support shaft part 42c with a screw 45. The position of the valve body 42 around the support shaft portion 42 c can be easily switched from the outside by the turning operation of the switching lever 43. As shown in FIGS. 10 and 13, the recess 2 c of the head housing 2 b is formed in a fan shape that opens at about 60 ° in plan view. The switching lever 43 is accommodated so as not to protrude from the recess 2b. For this reason, the switching lever 43 is tilted within a range of about 60 °. The valve body 42 is rotated in a range of about 60 ° by tilting the switching lever 43 by about 60 °.

The valve main body 42 is provided with three large vent holes 42a to 42a and three small vent holes 42b to 42b penetrating in the plate thickness direction. The three large vent holes 42a to 42a are arranged at the three-way positions in the circumferential direction around the support shaft portion 42c. In the present embodiment, each large vent 42a is formed in a fan shape having the same size as the reference vent 41a on the valve seat 41 side. The three small ventilation holes 42b to 42b are also arranged at the three-way positions in the circumferential direction around the support shaft portion 42c. Each small vent 42b is arranged at the center between two large vents 42a, 42a adjacent in the circumferential direction. Accordingly, the three large vent holes 42a to 42a and the three small vent holes 42b to 42b are alternately arranged at intervals of 60 ° on substantially the same circumference. For this reason, when the switching lever 43 is tilted within a range of about 60 °, the large ventilation hole 42a is aligned with each of the three reference ventilation holes 41a to 41a of the valve seat 41 (shown in FIG. 12). State) and a state where the small vents 42b are aligned (state shown in FIG. 15).
In the state in which the large ventilation holes 42 a to 42 a are aligned with the reference ventilation holes 41 a to 41 a of the valve seat 41 and the state in which the small ventilation holes 42 b to 42 b are aligned, the inner circumference side of the head valve 30 is arranged. The flow path areas between the ventilation chamber 30c and the cylinder upper chamber 24 are greatly different. The flow path area is smaller in the latter case than in the former case. In the former case, the total area of the three large vent holes 42a to 42a (in this embodiment, approximately equal to the total area of the three reference vent holes 41a to 41a) is the flow path area, and in the latter case, the three small vent holes The total area of the pores 42b to 42b is the flow path area.
For this reason, in the former case, the amount of compressed air flowing into the cylinder upper chamber 24 per unit time increases, and the thrust of the piston 22 increases, so that the driving force of the screw S increases. As will be described later, this case is suitable when the base W2 is a steel plate (steel plate mode).

On the other hand, in the latter case, the flow passage area is reduced, and the amount of compressed air flowing into the cylinder upper chamber 24 per unit time becomes smaller, and as a result, the thrust of the piston 22 is smaller than in the former case. Therefore, the driving force of the screw S is reduced. This case is suitable when the base W2 is a wood board (wood board mode).
As described above, the screw driving machine 1 of the present embodiment includes the flow rate switching valve 40 for adjusting the driving force of the screw S. According to this flow rate switching valve 40, the amount of compressed air flowing into the cylinder upper chamber 24 can be switched in two stages, so that an optimum driving force can be achieved for both so-called steel plate driving and wood plate driving. It is possible to perform the driving work. FIG. 10 shows a state in which the switching lever 43 is switched to a steel plate mode suitable for steel plate driving, and FIG. 11 shows a state in which the switching lever 43 is switched to a wood board mode suitable for wood board driving.
Position holding convex portions 2d and 2e for holding the switching lever 43 at the steel plate mode position and the wood plate mode position are provided at the bottom of the concave portion 2c. On the other hand, the valve body 42 is urged in a direction (downward in the drawing) to be pressed against the valve pedestal portion 41 by a compression spring 44 interposed between the valve body 42 and the head housing 2b. For this reason, the lever 43 integrally attached to the support shaft part 42c of the valve body 42 is in a state of being urged in a direction to be pressed against the position holding convex parts 2d and 2e of the concave part 2c by the urging force of the compression spring 44. ing. Due to the urging force of the compression spring 44, the elastic engagement state of the lever 43 with respect to the position holding convex portions 2d and 2e is held, and an appropriate movement resistance is given. By giving this movement resistance, the switching lever 43 is elastically held at the respective positions to prevent inadvertent movement.

Next, the valve main body 42 is urged by the compression spring 44 in a direction in which the valve main body 42 is pressed against the valve pedestal portion 41. In the case of the steel plate mode, since the large vent holes 42a to 42a having substantially the same opening area are aligned with the three reference vent holes 41a to 41a of the valve seat 41, the piston 22 is moved upward. The compressed air pressure in the cylinder upper chamber 24 hardly acts on the valve body 42. For this reason, when the piston moves up in the steel plate mode, the valve main body 42 is maintained in a state of being pressed against the upper surface of the valve pedestal 41, and accordingly, inflow of compressed air into the cylinder upper chamber 24 and exhaust from the cylinder upper chamber 24. In any case, the total area of the three reference vent holes 41a to 41a is used as the flow path area.
On the other hand, in the case of the wood board mode shown in FIGS. 13 to 16, the small vent holes 42 b to 42 b have a sufficiently smaller opening area than the three reference vent holes 41 a to 41 a of the valve seat 41. 42b is aligned. Therefore, as shown in FIG. 14, the lower surface of the valve main body 42 is exposed in the cylinder upper chamber 24 in each reference vent hole 41 a. This exposed portion acts as a pressure receiving surface 42d that receives the compressed air pressure in the cylinder upper chamber 24 when the piston moves up, so that the compressed air pressure in the cylinder upper chamber 24 acts on the valve body 42. In this case, the compressed air pressure in the cylinder upper chamber 24 acts in a direction in which the valve body 42 is moved up against the compression spring 44. The urging force of the compression spring 44 is appropriately set so that the valve main body 42 can move up by the compressed air pressure in the cylinder upper chamber 24 when the piston 22 moves up.
As shown in FIG. 16, when the valve main body 42 moves up against the compression spring 44, the valve main body 42 is separated from the upper surface of the valve pedestal 41 and a gap 42e is generated between them. Through this gap 42e, the piston upper chamber 24 communicates with three large vent holes 42a to 42a in addition to the three small vent holes 42b to 42b of the valve body 42.
Thus, in the case of the steel plate mode shown in FIGS. 10 to 12, the large vent hole 42 a of the valve body 42 is aligned with each of the reference vent holes 41 a to 41 a of the valve pedestal portion 41. The intake flow rate per unit time to the cylinder upper chamber 24 during operation increases and a large driving force is obtained, and a sufficient amount of exhaust per unit time from the cylinder upper chamber 24 during piston movement is ensured. Thus, high exhaust efficiency can be ensured and a smooth upward movement of the piston 22 can be obtained.
On the other hand, in the wood board mode shown in FIGS. 13 to 16, the intake flow rate per unit time to the cylinder upper chamber 24 when the piston moves downward is reduced to obtain a weak driving force suitable for wood board driving. On the other hand, when the piston moves up, the valve body 42 moves against the compression spring 44, so that the flow passage area is automatically expanded and high exhaust efficiency is ensured. Smooth upward movement is ensured.

Exhaust gas is returned to the ventilation chamber 30 c on the inner peripheral side of the head valve 30 through the flow rate switching valve 40. In this case, since the head valve 30 is moved downward and closed with respect to the holding sleeve 27, the ventilation chamber 30c is airtightly blocked from the ventilation chamber 30b and the head valve lower chamber 30d. Therefore, the exhaust is exhausted to the exhaust chamber 30 h on the outer peripheral side of the head valve 30 through the exhaust holes 30 g to 30 g provided in the head valve 30. The exhaust chamber 30 h communicates with the exhaust chamber 8 b through an exhaust path (not shown), and thus communicates with the exhaust pipe 8 in the handle portion 3. Exhaust gas (compressed air) flowing into the exhaust pipe 8 is exhausted to the atmosphere through the exhaust port 8a.
A plurality of exhaust holes 21 a to 21 a are provided on the peripheral surface of the upper side of the cylinder 21. The exhaust holes 21a to 21a are airtightly closed only in one direction (intake side) by a seal ring 28 mounted on the outer peripheral side (check valve). Therefore, the cylinder upper chamber 24 is exhausted by the exhaust holes 21a to 21a in addition to the flow rate switching valve 40 when the piston moves up. The compressed air exhausted from the exhaust holes 21a to 21a flows into the ventilation chamber 30c in the same manner as the exhaust gas having passed through the flow rate switching valve 40, and is then exhausted to the exhaust chamber 30h through the exhaust holes 30g to 30g.
When the piston moves downward, the cylinder lower chamber 25 is exhausted through a plurality of return holes 21 b to 21 b provided on the lower peripheral surface of the cylinder 21. The return holes 21 b to 21 b are opened in a return air chamber 29 that is airtightly partitioned between the cylinder 21 and the holding sleeve 27. As will be described later, compressed air flows into the return air chamber 29 from the vent chamber 33 through the return holes 21b to 21b when the piston 22 reaches the bottom dead center and the damper 26 is opened. The compressed air flowing into the return air chamber 29 is returned to the cylinder lower chamber 25 through the return hole 21b again when the piston 22 moves upward, and is used as an operating source for moving the piston 22 upward.

Next, the lower end position (bottom dead center) of the piston 22 is regulated by the damper 26. Details of the configuration of the damper 26 and its periphery are shown in FIGS. The damper 26 is an elastic body that hermetically closes the lower end portion of the cylinder 21 and is supported so as to be displaceable in the piston movement direction (vertical direction in FIG. 4) within a certain range in this embodiment. An insertion hole 26 a is provided through the center of the damper 26. The driver bit 23 is inserted into the insertion hole 26a so as to be movable in the axial direction.
The damper 26 includes a substantially truncated cone-shaped main body portion 26b and a support shaft portion 26c extending downward from the center of the lower surface of the main body portion 26b. The upper part of the main body part 26b is formed in a truncated cone shape that is inclined in a direction of a smaller diameter as the peripheral surface thereof reaches the upper side. The cylinder lower chamber 25 is hermetically sealed from a later-described vent chamber 33 by pressing the peripheral surface of the main body 26b against the inclined surface 21c formed in the lower opening of the cylinder 21.
The support shaft portion 26c of the damper 26 passes through the insertion hole 61a of the first frame body 61 fixed to the main body housing 2a, and below the support hole 60a of the second frame body 60 fixed to the main body housing 2a. It is inserted and supported so that it can move in the direction. On the second frame 60, a rotary shaft 51 on the upper side of an air motor 50 described later is rotatably supported via a bearing 53.
As shown in FIG. 9, the damper 26 is displaced downward by the thrust of the piston 22 while absorbing the impact when the piston 22 reaches the lower moving end position. In the present embodiment, the position displaced downward is the initial position of the damper 26. As will be described later, when the piston 22 reaches the bottom dead center and the damper 26 is displaced downward, the cylinder lower chamber 25 communicates with the vent chamber 33, whereby compressed air is supplied to the cylinder lower chamber 25 from the vent chamber 33. This flows into the return air chamber 29 through the return hole 21b.
A convex portion 26d having a semicircular cross section is provided on the entire lower surface of the main body portion 26b and around the support shaft portion 26c. The upper surface 61b of the first frame 61 is located below the convex portion 26d. As the trigger 5 is pulled, the damper 26 is displaced upward as shown in FIG. 4, so that the convex portion 26 d is separated from the upper surface 61 b of the first frame 61. In this state, the ventilation chamber 33 on the outer peripheral side of the convex portion 26d is in communication with the inside of the insertion hole 61a. As will be described later, the ventilation chamber 33 communicates with the ventilation chamber 30 b on the inner peripheral side of the head valve via the ventilation chamber 32. For this reason, when the head valve 30 is opened, compressed air is supplied to the ventilation chamber 33 at an initial stage when the head valve 30 is opened. Therefore, when the damper 26 is moved upward from the initial position, the pressure accumulation chamber 7 is moved to the air motor 50. Compressed air is supplied, whereby the air motor 50 begins to rotate.
On the other hand, as shown in FIG. 9, when the damper 26 is displaced to the lower initial position, the convex portion 26 d is pressed against the upper surface 61 b of the first frame body 61. In this state, the vent chamber 33 and the cylinder lower chamber 25 are in communication with each other as described above, while the vent chamber 33 is hermetically sealed with respect to the insertion hole 61a, the vent chamber 34, and the motor vent 52. It becomes. As will be described later, in this sealed state, the supply of compressed air from the pressure accumulation chamber 7 to the air motor 50 is cut off, and the air motor 50 is stopped.

Next, when the head valve 30 is opened by the pulling operation of the trigger 5, the air motor 50 starts to rotate at the initial stage of the opening. The ventilation chamber 30 b on the lower inner peripheral side of the head valve 30 is communicated with the intake port 52 of the air motor 50 through the ventilation chambers 32, 33, and 34. Therefore, in the state where the head valve 30 is closed with respect to the valve pedestal 35 as shown in FIG. 3, the compressed air is supplied to the motor intake 52 because the ventilation chamber 30 b is blocked from the pressure accumulation chamber 7. Therefore, the air motor 50 is stopped.
When the head valve upper chamber 30a is opened to the atmosphere by the pulling operation of the trigger 5, and the head valve 30 begins to open, the head valve lower chamber 30d on the outer peripheral side of the head valve 30 is communicated with the vent chamber 30b on the inner peripheral side. Compressed air is supplied to the ventilation chamber 30b. The supply of compressed air to the ventilation chamber 30b causes the head valve 30 to move upward to create a gap between the seal ring 27a and the inner peripheral surface of the head valve 30, whereby the ventilation chamber 30b is connected to the inner periphery of the head valve. It starts from the stage before communicating with the side ventilation chamber 30c, that is, before the piston 22 starts to move downward (the initial stage of opening) when compressed air is supplied to the ventilation chamber 30c. As described above, the ventilation chamber 30b communicates with the ventilation chamber 33 via the ventilation chamber 32. Therefore, when compressed air flows into the ventilation chamber 30b, the ventilation chamber 30b flows into the ventilation chamber 33. The compressed air that has flowed into the ventilation chamber 33 acts to move the damper 26 displaced downward. In other words, in the initial state, the compressed air in the ventilation chamber 33 acts on the lower surface of the main body portion 26b of the damper 26 positioned on the lower side and on the outer peripheral side of the convex portion 26d in the direction in which the compressed air is displaced upward. The damper 26 moves up from its initial position. When the damper 26 moves upward, the cylinder lower chamber 25 and the ventilation chamber 33 are hermetically blocked, and the ventilation chamber 33 communicates with the ventilation chamber 34. For this reason, the compressed air that has flowed into the ventilation chamber 30b is supplied to the air motor 50 through the ventilation chamber 34 and the motor intake port 52, whereby the air motor 50 starts to rotate. That is, the air motor 50 starts to rotate immediately after the head valve 30 starts to open.
The rotary shaft 51 of the air motor 50 is provided with a bit insertion hole 51a having a circular cross section through the entire length thereof. The driver bit 23 is inserted into the bit insertion hole 51a so as to be relatively rotatable about the axis and relatively movable in the axial direction.
Since the air motor 50 itself is a conventionally known so-called vane motor, detailed description of its configuration and the like is omitted.
The rotation shaft 53 on the lower side of the air motor 50 is rotatably supported by a third frame 63 attached to the tip of the main body housing 2a via a bearing 54. An air motor 50 is configured between the third frame 63 and the second frame 60.

The lower rotary shaft portion 55 of the air motor 50 is coupled to the speed reduction mechanism portion 70. In this embodiment, a planetary gear mechanism is used for the reduction mechanism unit 70. A sun gear 71 is attached to the rotating shaft portion 55. Two planetary gears 72 and 72 are meshed with the sun gear 71. The two planetary gears 72 and 72 are meshed with an internal gear 75 fixed to the main body housing 2a. The two planetary gears 72 and 72 are supported by a carrier 73. The carrier 73 is rotatably supported at the tip of the main body housing 2a via a bearing 74.
In the center of the carrier 73, an insertion hole 73a for inserting the driver bit 23 is formed so as to penetrate along the central axis. The driver bit 23 can be relatively moved in the axial direction through the insertion hole 73a, and is inserted in a state of being integrated around the shaft so as not to be relatively rotatable.
The insertion hole 73a of the carrier 73 has an oval cross section. On the other hand, in the lower half of the axial direction of the driver bit 23, two flat width portions 23a, 23a that are parallel to each other and corresponding to the oval cross section of the insertion hole 73a are provided along the axial direction. It is provided in a long range. The two-surface width portions 23a, 23a are provided in a long range in the axial direction so that the two-surface width portions 23a, 23a are always located in the insertion hole 73a in the entire range in which the driver bit 23 moves in the axial direction. Yes. Since the two-sided width portions 23a and 23a are always positioned in the insertion hole 73a of the carrier 73 as described above, the driver bit 23 is integrated with the carrier 73 with respect to the rotation about the axis thereof. Rotational torque of the air motor 50 output via the above is transmitted to the driver bit 23.
Thus, the rotational output of the air motor 50 is decelerated by the speed reduction mechanism portion 70 and transmitted to the driver bit 23, and the air motor 50 and the speed reduction mechanism portion 70 are the distal end portion of the main body portion 2 and the screw S is driven in. Since the rotational torque is transmitted to the driver bit 23 at the portion closest to the rotational speed, the rotational torque (screw tightening torque) can be efficiently applied to the screw S without generating twisting of the driver bit 23 as much as possible.
A cylindrical driving tube portion 13 is provided at the lower end of the main body portion 2. The driver bit 23 reciprocates while rotating on the inner peripheral side of the driving cylinder portion 13. The screw connection band feeding mechanism 12 is connected to a halfway position in the longitudinal direction of the driving cylinder portion 13. The screw connection band feed mechanism 12 feeds the screw connection bands one pitch at a time, and the screws S are supplied into the driving cylinder portion 13 one by one in conjunction with the driving operation on the main body portion 2 side.
A bracket 14 to which an elastic sheet 14a is attached is attached to the tip of the driving cylinder portion 13 in order to prevent the screw driving material W from being damaged. The driving cylinder portion 13 is abutted against the screw driving material W through the bracket 14, and the screw S is driven (tightened) into the screw driving material W in this state.

According to the screw driving machine 1 of the present embodiment configured as described above, when the trigger 5 is pulled while the compressed air is supplied to the pressure accumulating chamber 7, the head valve upper chamber 30a is opened to the atmosphere, and the head valve 30 is moved. Move up. When the head valve 30 moves up, compressed air is first supplied to the ventilation chamber 30b at the initial stage of opening thereof, and flows into the ventilation chamber 33 through the ventilation chamber 32. When compressed air is supplied to the ventilation chamber 33, the damper 26 moves upward from the initial position due to the pressure, thereby closing the cylinder lower chamber 25, and bringing the ventilation chamber 33 into communication with the ventilation chamber 34. . Thus, the pressure accumulating chamber 7 is communicated with the venting chambers 30b, 32, 33, and 34, whereby compressed air is supplied to the air motor 50, whereby the air motor 50 starts to rotate. As the air motor 50 rotates, the driver bit 23 rotates in the screw tightening direction.
When the head valve 30 is fully opened, compressed air is supplied to the ventilation chamber 30c via the ventilation chamber 30b, and is supplied to the cylinder upper chamber 24 via the flow rate switching valve 40, whereby the piston 22 moves downward. To do. When the piston 22 moves downward, the driver bit 23 moves downward. Therefore, the driver bit 23 is moved downward in the screw driving direction by the piston 22 while being rotated in the screw tightening direction by the air motor 50, whereby one screw S supplied into the driving cylinder portion 13 is screwed by the driver bit 23. It is tightened while being driven into the driving material W.
In the process in which the piston 22 moves downward, a part of the compressed air in the cylinder lower chamber 25 is released around the driver bit 23 through the insertion hole 26a of the damper 26, and the remaining part is returned to the return holes 21b to 21b. As a result, the piston 22 smoothly moves downward by flowing into the return air chamber 29 and accumulating pressure. As the piston 22 smoothly moves down, the screw S is driven into the screw driving material W by the driver bit 23.
As shown in FIG. 9, when the piston 22 comes into contact with the damper 26 and reaches the lower moving end (bottom dead center), the driving (tightening) of the screw S is completed. As shown in the drawing, the impact is absorbed by the piston 22 reaching the lower moving end and elastically contacting the damper 26. Further, the damper 26 is displaced downward by the contact of the piston 22 (the thrust of the piston 22).
When the damper 26 is displaced downward, the main body portion 26b is disengaged from the lower opening of the cylinder 21, and as a result, a gap 26e is generated over the entire circumference between the damper 26 and the inclined surface 21c. The cylinder lower chamber 25 is in communication with the ventilation chamber 33. In the state where the trigger 5 is kept pulled, the compressed air is maintained in the ventilation chamber 33, so that the return air chamber 29 is passed through the gap 26e, the cylinder lower chamber 25, and the return hole 21b. Sufficient compressed air for returning the piston is supplied from the ventilation chamber 33.
Further, when the damper 26 is displaced to the lower initial position by the thrust of the piston 22, the convex portion 26 d of the main body portion 26 b is pressed against the upper surface of the first frame body 61, and between the ventilation chamber 33 and the ventilation chamber 34. Since the communication state is cut off, the supply of compressed air to the motor intake port 52 is cut off, so that the rotation of the air motor 50 is automatically stopped. For this reason, even when the trigger 5 is kept pulled, the arrival timing of the piston 22 to the lower end of the piston 22 and the stop timing of the air motor 50 are synchronized (performed almost simultaneously), so that the screw S is driven in. Overtightening on the material W is prevented.

Thereafter, when the user stops the pulling operation of the trigger 5, the compressed air is supplied to the head valve upper chamber 30a via the trigger valve 4, and the head valve 30 is moved downward. When the head valve 30 is moved downward and its lower end is in an airtight contact with the valve pedestal 35, the ventilation chamber 30c is blocked from the ventilation chamber 30b by the seal ring 27a, and the ventilation chamber 30b is located under the head valve. It will be in the state interrupted | blocked from the chamber 30d. For this reason, the supply of compressed air to the cylinder upper chamber 24 is shut off. When the supply of the compressed air to the cylinder upper chamber 24 is shut off, the compressed air in the cylinder upper chamber 24 flows into the flow rate switching valve 40, the exhaust holes 21a to 21a, the exhaust holes 30g to 30g of the head valve 30, and the exhaust chamber. 30 h and the state through which the air can be released through the exhaust pipe 8 (a state in which no downward thrust is generated with respect to the piston 22).
Thus, when the head valve 30 is closed and the supply of compressed air to the cylinder upper chamber 24 is shut off, when the cylinder upper chamber 24 becomes open to the atmosphere, the compressed air accumulated in the return air chamber 29 The piston 22 is returned to the top dead center.
Further, when the head valve 30 is closed, the supply of compressed air to the ventilation chamber 33 is interrupted, so that the damper 26 is maintained in a state of being displaced downward (an initial position of the damper 26).

As described above, according to the screw driving machine 1 of the present embodiment, the flow rate switching valve 40 for changing the intake amount to the cylinder upper chamber 24 is provided. According to the flow rate switching valve 40, the switching lever 43 is turned from the outside by about 60 ° to switch between two steps, a large flow rate for steel plate driving (steel plate mode) and a small flow rate for wood driving (wood plate mode). be able to. By switching to the steel plate mode, the piston 22 can be moved with a large thrust, so that the screw S can be reliably driven into the base W2 (steel plate), and therefore the upper member W1 is firmly screwed to the base W2. Can do. On the other hand, by switching to the wood board mode, the piston 22 can be moved with a weaker thrust than the steel plate mode, and the screw S can be driven to an appropriate depth with respect to the base W2 (wood board). Further, the upper member W1 can be firmly screwed to the base W2 by tightening the screw S with high pulling strength.
As described above, the intake flow rate to the cylinder upper chamber 24 can be switched in two stages. On the other hand, according to the flow rate switching valve 40 of this embodiment, the exhaust efficiency is impaired even when the intake flow rate is reduced to the wood board mode. It is supposed not to be. That is, when the intake flow rate is reduced by switching to the wood board mode, the pressure receiving surface 42d of the valve body 42 is exposed to the cylinder upper chamber 24 in the reference vent hole 41a. The compressed air pressure in the cylinder upper chamber 24 acts on the surface 42d, and as a result, the valve body 42 moves up against the compression spring 44 as shown in FIG. When the valve main body 42 moves up, the valve main body 42 is separated from the valve pedestal 41, so that a gap 42e is generated between them. By generating the gap 42e, the cylinder upper chamber 24 is communicated with the three large vent holes 42a to 42a in addition to the three small vent holes 42b to 42b of the valve body 42. As a result, the compression in the cylinder upper chamber 24 is performed. Since air is exhausted to the exhaust chamber 30h through the flow path having the total area of the three small vents 42b to 42b and the three large vents 42a to 42a, high exhaust efficiency can be realized.
According to the flow rate switching valve 40 exemplified in this way, it is possible to achieve both a driving force switching function and high exhaust efficiency.
Further, according to the illustrated flow rate switching valve 40, the valve pedestal portion 41 fixed to the upper end portion of the cylinder 21 has appropriate elasticity, and the piston 22 abuts on the valve pedestal portion 41 and its top dead center. Is regulated. Therefore, the valve pedestal portion 41 has a function as a damper on the top dead center side of the piston 22, which makes it possible to reduce the number of parts as compared with a configuration in which a damper is separately provided. Further, the assembly cost can be reduced and the screw driving machine 1 can be made compact.

Various modifications can be made to the embodiment described above. For example, the valve pedestal 41 has three reference vents 41a to 41a and the valve main body 42 has three large vents 42a to 42a and three small vents 42b to 42b. The number of pores can be set arbitrarily. That is, one or two reference holes are provided in the valve pedestal, one or two large vents and one or two small vents are provided in the valve body, or four or more reference holes are provided in the valve pedestal. It is good also as a structure which provides a pore and provides a valve main body with four or more large ventilation holes and four or more small ventilation holes.
Further, the number of reference vent holes in the valve pedestal portion and the number of large vent holes or small vent holes in the valve body do not necessarily have to be the same. By changing the switching lever 43 to a switching dial and rotating it, it can be configured to alternately switch between a large flow rate and a small flow rate.
In addition, the configuration that switches the intake air flow rate in two stages, steel plate mode and wood board mode, is illustrated, but the reference vent on the valve seat is set to two or more stages, or the vent on the valve body is set to three or more stages. By doing so, the intake flow rate can be switched more finely.
Further, the configuration in which the valve main body 42 is urged toward the closing side by using the compression spring 44 is illustrated. However, instead of the compression spring 44, a similar operation is performed on the valve main body by using a tension spring, elastic rubber, or compressed air. Can be made.
Furthermore, although the configuration in which the valve pedestal portion 41 has the function of the damper on the piston top dead center side is exemplified, the damper function may be realized by another member. Therefore, the flow rate switching valve according to the present invention may be arranged in the intake passage further upstream than the cylinder 21.
In short, the valve body can move when the cylinder upper chamber 24 is exhausted (when the piston moves up) in the state where the intake flow rate to the cylinder upper chamber 24 can be switched in at least two stages and is switched to the small intake flow rate side. Thus, the object of the present invention can be achieved if the exhaust flow rate is switched larger than the small intake flow rate and smooth exhaust is performed.

It is a longitudinal section of the whole screw driving machine concerning this embodiment. This figure shows the initial state. It is a longitudinal cross-sectional view of the main-body part of the driving machine which concerns on this embodiment. This figure shows the initial state of the main body. FIG. 3 is a partially enlarged view of FIG. 2, and is a longitudinal sectional view of the vicinity of a head valve and a cylinder upper part. This figure shows the fully closed state of the head valve in the initial state of the main body as in FIG. It is a longitudinal cross-sectional view of a cylinder lower part and a damper periphery. This figure shows the stage where the damper has moved up from the lower initial position and the air motor has started to rotate. It is a longitudinal cross-sectional view of the main-body part of the screw driving machine which concerns on this embodiment. This figure shows a stage where the air motor starts to rotate with the head valve half open. At this stage, the piston is still at top dead center. It is a longitudinal cross-sectional view of the main-body part of the screw driving machine which concerns on this embodiment. This figure shows a state in which the head valve is fully opened, the air motor rotates, and the piston starts to move downward. FIG. 7 is a partially enlarged view of FIG. 6, which is a longitudinal sectional view of a fully opened head valve and a cylinder upper portion periphery. In this figure, the piston is shown in which the head valve is fully opened and begins to move downward. It is a longitudinal cross-sectional view of the main-body part of the screw driving machine which concerns on this embodiment. This figure shows a stage where the piston reaches bottom dead center, and as a result, the air motor stops and the screw driving is completed. FIG. 9 is a partially enlarged view of FIG. 8, and is an enlarged view of the periphery of a piston and a damper that have reached bottom dead center. This figure shows a state in which the air passage for the air motor is closed as a result of the damper being pushed down by the piston and moving downward. It is the rear view which looked at the main-body part from the arrow (10) direction in FIG. This figure shows a state in which the lever is switched to the steel plate mode position for steel plate driving. It is the (11)-(11) sectional view taken on the line in FIG. This figure shows the internal structure around the head valve in a longitudinal section. FIG. 12 is a sectional view taken along line (12)-(12) in FIG. 11. In this figure, the valve pedestal and the head valve of the switching valve are shown in cross section. It is a rear view of a main-body part. This figure shows a state in which the lever is switched to the wood board mode position for wood board driving. FIG. 14 is a sectional view taken along the line (14)-(14) in FIG. 13. In this figure, the valve pedestal and the head valve of the switching valve are shown in cross section. It is the (15)-(15) sectional view taken on the line in FIG. In this figure, the valve pedestal and the head valve of the switching valve are shown in cross section. FIG. 4 is a longitudinal sectional view around the flow rate switching valve at the top of the main body. This figure shows the flow rate switching valve when the piston moves up. The valve body moves up against the valve seat against the compression spring, and as a result, it is generated between the valve seat and the valve body. A state in which exhaust is performed through a gap is shown.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Screw driving machine 2 ... Main-body part 2a ... Main body housing, 2b ... Head housing, 2c ... Concave part 2d ... Position holding convex part (for steel plate mode) 2e ... Position holding convex part (for wood board mode)
3 ... handle part 4 ... trigger valve 5 ... trigger S ... screw W ... screw driving material W1 ... upper material (gypsum board)
W2: Base (steel or wood)
6 ... Air hose 7 ... Accumulation chamber 8 ... Exhaust pipe, 8a ... Exhaust port, 8b ... Exhaust chamber 11 ... Magazine 12 ... Screw connection band feed mechanism 13 ... Driving cylinder part 14 ... Bracket, 14a ... Elastic sheet 20 ... Blow mechanism part 21 ... Cylinder 21a ... Exhaust hole, 21b ... Return hole, 21c ... Inclined surface 22 ... Piston 23 ... Driver bit, 23a ... Two-sided width portion 24 ... Cylinder upper chamber 25 ... Cylinder lower chamber 26 ... Damper (bottom dead center side)
26a ... insert hole, 26b ... main body part, 26c ... support shaft part, 26d ... convex part, 26e ... gap 27 ... holding sleeve, 27a ... seal ring 28 ... seal ring 29 ... return air chamber 30 ... head valve 30a ... head valve Upper chamber, 30b ... venting chamber, 30c ... venting chamber 30d ... head valve lower chamber, 30e ... pressure receiving surface (outer peripheral side), 30f ... pressure receiving surface (inner peripheral side)
30g ... exhaust hole, 30h ... exhaust chamber 31 ... compression spring 32 ... vent chamber 33 ... vent chamber 34 ... vent chamber 35 ... valve seat portion 40 ... flow rate switching valve 41 ... valve seat portion, 41a ... reference vent hole 42 ... valve body 42a ... large vent hole, 42b ... small vent hole, 42c ... support shaft portion, 42d ... pressure receiving surface, 42e ... gap 43 ... switching lever 44 ... compression spring 50 ... air motor 51 ... rotating shaft portion, 51a ... bit insertion hole 52 ... motor Vent 53 ... Bearing 54 ... Bearing 55 ... Rotating shaft 60 ... Second frame 60a ... Support hole 61 ... First frame 61a ... Insertion hole 61b ... Upper surface 63 ... Third frame 70 ... Deceleration mechanism 71 ... Sun gear 72 ... Planetary gear 73 ... Carrier, 73a ... Insertion hole 74 ... Bearing 75 ... Internal gear

Claims (6)

A screw driving machine equipped with a flow rate switching valve for switching an intake flow rate to a cylinder upper chamber of a cylinder containing a piston for screw driving,
The flow rate switching valve is switched by the pressure in the cylinder upper chamber generated by the upward movement of the piston, and the exhaust flow rate when the piston is moved through the flow rate switching valve is the piston that is made through the flow rate switching valve. A screw driving machine that is larger than the intake flow rate during downward movement. The screw driving machine according to claim 1, comprising: a valve pedestal portion fixed to a cylinder; and a valve main body that is relatively displaced with respect to the valve pedestal portion, the valve main body in a direction around a cylinder axis with respect to the valve pedestal portion. A screw driving machine in which the intake flow rate is switched by rotation and the exhaust flow rate is switched by movement in the cylinder axis direction. The screw driving machine according to claim 2, wherein a reference vent hole is provided in one of the valve pedestal portion or the valve main body, and a large vent hole and a small vent hole having different opening areas are provided in the other, and the valve main body is A screw driving machine that rotates around a cylinder axis and switches a vent hole aligned with the reference vent hole to the large vent hole or the small vent hole to switch the intake air flow rate to the cylinder upper chamber. 4. The screw driving machine according to claim 3, wherein the valve body is pressed against the valve seat portion by a spring biasing force, and the valve body is resisted by the spring biasing force by an exhaust pressure of the cylinder upper chamber. And a screw tightening machine that exhausts the upper chamber of the cylinder by separating it from the valve pedestal portion and communicating the reference vent hole with both the large vent hole and the small vent hole through a gap generated thereby. 5. The screw driving machine according to claim 4, wherein the valve body is provided with a lever for switching operation, and the position of the lever is held using a biasing force of the compression spring. 3. The screw driving machine according to claim 2, wherein the valve pedestal portion is provided with an elastic body as a material, and the valve pedestal portion functions as a cushion body when the piston moves up.

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