JP2022069796A - Pressure regulator and pneumatic tool - Google Patents

Abstract

To provide a pressure regulator which enables reduction of an operation load of a pressure regulation mechanism, and to provide a pneumatic tool including the pressure regulator.SOLUTION: A pneumatic tool comprises a driving mechanism, which is driven by compressed air supplied from an air intake port 62, and includes: an air chamber in which the supplied compressed air is stored; and a pressure regulation mechanism which regulates a pressure of the compressed air in the air chamber. The pressure regulation mechanism includes: a valve body 52 which opens or closes a passage allowing communication between the air intake port and the air chamber; an elastic body 54 which applies a biasing force to the valve body in a direction such that the passage is opened; a support part 86 which supports an end part of the elastic body; a pressure receiving member 56 which receives an air pressure in the air chamber and presses the elastic body in a direction such that the passage is closed; and a load reduction mechanism which may switch the biasing force of the elastic body acting on the valve body between a normal state and a load reduction state in which a biasing force smaller than that in the normal state is applied.SELECTED DRAWING: Figure 3A

Description

The present invention relates to a pressure regulator and a pneumatic tool provided with the pressure regulator.

As a pneumatic tool using compressed air as a drive source, for example, a driving machine for driving a fastener such as a nail, a screw, or a nail that engages with a work material such as a plate material, wood, gypsum board, or a steel plate is known. Compressed air, which is a drive source, is generated by an air compressor, for example, and is supplied to the driving machine via an air hose.

Such a driving machine includes, for example, a piston driven by compressed air, a driver mounted on the piston, and a cylinder accommodating the piston. By introducing compressed air into the upper chamber of the cylinder when the piston is near top dead center, it is possible to move the piston and the driver attached to it toward the bottom dead center and drive the fastener with the driver. Become.

Here, the pressure of the compressed air supplied through the air hose is not always constant. On the other hand, the impact force at the time of driving depends on the pressure of the compressed air. For this reason, a pneumatic tool having a valve mechanism for reducing pressure to keep the pressure constant is known. Further, even if the pressure of the compressed air is constant, it may be preferable to change the impact force depending on the type of fastener or work material. Therefore, a pneumatic tool having a valve mechanism for adjusting the pressure for adjusting the pressure of the supplied compressed air is known. By adjusting the pressure, it is possible to adjust the amount of fasteners to be driven.

Patent Document 1 describes a driving tool provided with a valve mechanism for adjusting the pressure of compressed air. Specifically, a driving tool provided with a pressure adjusting mechanism is described between the accumulator chamber provided in the handle and the compressed air chamber for driving.

Patent Document 2 also describes a driving tool provided with a valve mechanism for adjusting the pressure of compressed air. Specifically, a valve body that can move in the first direction that closes the main flow path and a second direction that opens the main flow path, and a first pressure receiving surface and a first pressure receiving surface that are connected to the valve body and receive pressure in the first direction by compressed air. Described is a driving tool having a piston provided with a second pressure receiving surface and a third pressure receiving surface that receive pressure in two directions, and a spring that constantly urges the piston in the second direction.

JP-A-2015-226952 Japanese Unexamined Patent Publication No. 2016-215353

However, in such a driving tool, the valve mechanism for depressurizing or adjusting the pressure (hereinafter collectively referred to as "valve mechanism" or "pressure adjusting mechanism") causes an increase in the size of the driving tool. When the valve mechanism is to be arranged inside the grip of the driving tool in order to suppress the increase in size, the radial direction is limited by the wall surface of the grip, so that the space that can be laid out is limited. On the other hand, if a valve mechanism is provided at the end of the grip as in the driving tools described in Patent Documents 1 and 2, the air plug protrudes greatly from the driving tool, so that the total length of the driving tool is increased. It gets bigger. Therefore, an object of the present invention is to provide a driving tool capable of shortening the total length.

Further, the spring load of the pressure adjusting mechanism increases according to the set pressure. In a pneumatic tool such as a nail gun that operates at a relatively high pressure, it may be difficult for the user to operate the pressure adjusting mechanism because the operating load of the pressure adjusting mechanism is large. Therefore, an object of the present invention is to provide a pressure regulator capable of reducing the operating load of the pressure regulator and a pneumatic tool provided with the pressure regulator.

Further, the pressure of the compressed air supplied to the pneumatic tool may fluctuate due to various factors. In a direct-acting pressure regulating mechanism, when the primary pressure, which is the pressure of compressed air on the upstream side of the pressure regulating mechanism, decreases, the secondary pressure, which is the pressure of compressed air on the downstream side of the pressure regulating mechanism, may increase. Are known. Therefore, even if a desired pressure is set by the pressure adjusting mechanism, the secondary pressure may be adjusted to a pressure different from the set pressure, and the amount of the fastener charged may vary. Therefore, an object of the present invention is to provide a pneumatic tool in which the secondary pressure is not easily affected even if the primary pressure fluctuates.

The present disclosure is a pneumatic tool provided with a drive mechanism driven by compressed air supplied from an air intake. This pneumatic tool has an air chamber for storing the supplied compressed air and a pressure adjusting mechanism for adjusting the pressure of the compressed air in the air chamber, and the pressure adjusting mechanism includes an air intake and an air chamber. A valve body that opens and closes the flow path that communicates with the valve body, an elastic body that gives an urging force to the valve body to open the flow path, and an urging force that closes the flow path by receiving air pressure in the air chamber. The elastic body is provided with a pressure receiving member that acts on the elastic body, and the elastic body is arranged at a position closer to the air intake port than the valve body.

In the above embodiment, the valve body and the elastic body are arranged on the first axis, and at least a part of the flow path from the air intake to the pressure regulating mechanism is along the second axis substantially parallel to the first axis. It may be stretched.

In the above embodiment, the flow path from the air intake to the pressure regulating mechanism has a portion extending in the first direction, and at least a part thereof overlaps with the region where the elastic body is provided in the first direction. May be good.

In the above embodiment, the pressure receiving member may be a piston component that is disposed between the valve body and the elastic body and presses the valve body by the elastic body.

In the above embodiment, an adjusting unit for adjusting the urging force exerted by the elastic body may be further provided.

In the above aspect, the pneumatic tool may be applied to a driving tool for launching a fastener. Further, the elastic body is configured to give the valve body an urging force in the first direction, and the pressure receiving member is configured to give the valve body an urging force in the second direction opposite to the first direction. The flow path from the air intake to the pressure regulating mechanism may be provided with a flow path for allowing compressed air to travel in the first direction. It is also possible to apply the present invention to compressed fluids other than compressed air.

The present disclosure also provides a pneumatic tool including a drive mechanism driven by a compressed fluid and a valve mechanism for supplying the compressed fluid to the drive mechanism. The plug, the elastic body, the piston part pressed by the elastic body, and the valve body pressed by the piston part are arranged in this order in the direction of traveling in the first direction from the outside to the inside of the pneumatic tool. Will be done. Further, a flow path communicating the valve chamber in which the valve body is arranged and the flow path in the plug is formed.

Further, the present disclosure is a pneumatic tool provided with a drive mechanism driven by compressed air supplied from an air intake, and the air chamber for storing the supplied compressed air and the pressure of the compressed air in the air chamber. The pressure regulating mechanism includes a valve body that opens and closes the flow path that communicates the air intake and the air chamber, and a pressure regulating mechanism that exerts an urging force on the valve body in the direction of opening the flow path. Regarding the urging force of the elastic body to be given, the pressure receiving member that receives the air pressure in the air chamber and presses the elastic body in the direction of closing the flow path, and the elastic body acting on the valve body, the normal state and the normal state It is also equipped with a load reduction mechanism that can switch between a load reduction state that exerts a small urging force.

In the above embodiment, the support portion may move when switching from the normal state to the load reduction state.

In the above embodiment, an operation input unit capable of operating the urging force of the elastic body may be further provided, and the normal state may be switched to the load reduction state in conjunction with the operation input to the steering input unit.

In the above embodiment, the inner cylinder portion formed in a cylindrical shape is further provided, and the support portion is an outer cylinder portion that is fitted onto the inner cylinder portion and is slidable along the inner cylinder portion, and the elastic body is an elastic body. It may penetrate the inner cylinder portion and face the piston component.

In the above embodiment, the valve body and the elastic body are arranged on the first axis, and at least a part of the flow path from the air intake to the pressure regulating mechanism is along the second axis substantially parallel to the first axis. The stretched and elastic body may be located closer to the air intake than the valve body.

In the above embodiment, the compressed air on the upstream side of the valve body is applied to the load release region, which is a closed space facing the support portion and partitioned on the opposite side of the valve body across the support portion, and the load release region. It may have a pressurized flow path that can be introduced, a decompression flow path that can discharge the compressed air introduced in the load release region to the outside of the pressure regulating mechanism, and a load release valve that opens and closes the decompression flow path. ..

In the above embodiment, the load release valve is opened in accordance with the operation of the operation input portion, and the load release region is depressurized so that the support portion moves to the side opposite to the side where the valve body is located. good.

Further, the present disclosure is a pressure regulator for adjusting the pressure of compressed air, and opens and closes a flow path connecting an air inlet to which compressed air is supplied and an air outlet for taking out compressed air whose pressure has been adjusted. The valve body, the elastic body that gives an urging force to the valve body in the direction of opening the flow path, and the air pressure on the downstream side of the valve body, the valve body presses the elastic body in the direction of closing the flow path. A valve body including a pressure receiving member and a pressure adjusting mechanism for adjusting the pressure of compressed air acting on the valve body, wherein the pressure adjusting mechanism opens and closes a flow path communicating an air intake port and an air chamber. An elastic body that gives an urging force to the valve body in the direction of opening the flow path, and a pressure receiving member that receives the air pressure in the air chamber and presses the elastic body in the direction of closing the flow path. The pressure receiving member is provided with a second pressure receiving surface that receives the air pressure in the air chamber and is pressed in a direction of closing the flow path. The pressure receiving member or the member in contact with the pressure receiving member is formed smaller than the second pressure receiving surface, and is pressed in a direction to open the flow path by receiving the air pressure on the upstream side of the valve body. Is provided.

In the above embodiment, the valve body and the elastic body are arranged on the first axis, and at least a part of the flow path from the air intake to the pressure regulating mechanism is along the second axis substantially parallel to the first axis. It may be stretched.

In the above embodiment, a bypass flow path for applying the air pressure on the upstream side of the valve body to the third pressure receiving surface may be formed so as to straddle the second axis and the first axis.

In the above embodiment, the pressure receiving member may be a piston component that is disposed between the valve body and the elastic body and presses the valve body by the elastic body.

In the above embodiment, the inner cylinder portion that can come into contact with the pressure receiving member and the outer cylinder portion that can slide along the inner cylinder portion are further provided, and the third pressure receiving surface includes the outer cylinder portion and the inner cylinder portion. It may be provided between.

According to the present invention, it is possible to provide a driving tool capable of shortening the total length. Alternatively, according to the present invention, it is possible to provide a pressure regulator capable of reducing the operating load of the pressure regulator and a pneumatic tool provided with the pressure regulator. Alternatively, it is possible to provide a pneumatic tool in which the secondary pressure is not easily affected even if the primary pressure fluctuates.

It is sectional drawing of the nail driving tool which concerns on one Embodiment. It is a tip view of the regulator before assembling to the nailing tool according to one embodiment. FIG. 2 is a cross-sectional view taken along the line AA in FIG. FIG. 2 is a cross-sectional view taken along the line BB in FIG. FIG. 2 is a sectional view taken along the line CC in FIG. FIG. 2 is a cross-sectional view taken along the line DD in FIG. It is a partially enlarged view of the AA sectional view when the valve opens in the intake direction. It is a partially enlarged view of the cross-sectional view of AA when the valve opens in the exhaust direction. FIG. 3C is an enlarged view of the dial shown in FIG. 3C as viewed from the first direction. FIG. 6 is an enlarged view showing a state in which an operation is input to the dial shown in FIG. 6A. FIG. 6B is a perspective view of the dial shown in FIG. 6B as viewed from an angle. It is a partially enlarged view of the cross-sectional view of AA when the main spring is extended to the natural length in the valve open state. It is sectional drawing which shows the modification of the load reduction mechanism shown in FIG. It is a partially enlarged view of the cross-sectional view of AA when the valve is closed. It is sectional drawing which shows the 1st modification of the primary pressure balance mechanism shown in FIG. It is sectional drawing which shows the 2nd modification of the primary pressure balance mechanism shown in FIG.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. The following embodiments are examples for explaining the present invention, and the present invention is not intended to be limited only to the embodiments.

Hereinafter, the pneumatic tool according to the first embodiment will be described. FIG. 1 is a cross-sectional view of a nailing tool (an example of a “pneumatic tool”) according to the first embodiment. For convenience, the upward direction and the downward direction on the paper surface in FIG. 1 are simply referred to as the upward direction and the downward direction on the paper surface, and the left direction and the right direction on the paper surface in the figure are the first direction D1 and the second direction D2 (the first direction D1 and the second direction D2, respectively). It may be called one direction (opposite direction of D1). In the case of the nailing tool 10 shown in FIG. 1, the second direction D2 side is the grip end side of the grip 32, and the first direction D1 side is the main body side.

[Example of overall configuration of pneumatic tool]
A nailing tool (an example of a "driving tool") is a pneumatic tool for driving a nail (an example of a "fastener") using compressed air as a drive source. The nailing tool 10 includes a drive mechanism 20 driven by compressed air and a regulator 50 (an example of a “pressure adjusting mechanism”) for supplying compressed air to the drive mechanism.

The drive mechanism 20 is integrated with a driving piston 22 that reciprocates up and down by compressed air, a cylindrical driving cylinder 24 that houses the driving piston 22, and a driving piston 22 that is attached to the driving piston 22. To accommodate a driver 26 for moving to and hitting a nail, a nose 28 for the driver 26 to invade and extend downward to hit the nail, and a nail to supply the nail to the nose 28. It is equipped with a magazine 30.

Further, the nailing tool 10 is for controlling the inflow of the grip 32 gripped by the user, the air chamber 34 provided in the grip 32, and the compressed air stored in the air chamber 34 into the driving cylinder 24. A main valve (head valve) 36 is provided. The regulator 50 decompresses the compressed air supplied from the external air compressor via an air hose (not shown) and supplies the compressed air to the air chamber 34.

In such a nailing tool 10, when the user presses the trigger 38, the main valve 36 opens and the compressed air in the air chamber 34 flows into the upper chamber in the driving cylinder 24. As a result, the driving piston 22 moves downward, and the driver 26 attached to the driving piston 22 hits the nail to launch the nail downward.

[Basic configuration of pressure regulation mechanism]
Hereinafter, the configuration of the regulator 50 (an example of the “pressure regulating mechanism”) will be described with reference to the drawings. FIG. 2 is a front view of the single regulator 50 as viewed from the second direction D2 before being assembled to the nailing tool 10. After assembly, it corresponds to the view of the regulator 50 in the second direction D2 from the inside of the nailing tool 10 in FIG. 3A to 3D are a sectional view taken along the line AA, a sectional view taken along the line BB, a sectional view taken along the line CC, and a sectional view taken along the line DD, respectively. FIG. 4 is a partially enlarged view of a cross-sectional view taken along the line AA when the compressed fluid in the valve chamber 64 flows into the secondary pressure region AR2, and FIG. 5 shows the compressed fluid in the secondary pressure region AR2 being exhausted. It is a partially enlarged view of the cross-sectional view of AA at the time.

The regulator 50 is provided in a plug 62 (an example of an “air intake”) for receiving a supply of compressed air from the outside, a first end cap 58 to which the plug 62 is connected, and a first end cap 58. The air filter 60, the valve body 52 pressed in the second direction D2 by the compressed air that has passed through the first flow path CH1 from the first end cap 58 and entered the valve chamber 64, and the valve body 52 in the second direction. A valve spring 68 that presses against D2, and a main spring 54 (an example of an "elastic body") that is arranged on the valve body 52 on the second direction D2 side and exerts a force on the valve body 52 toward the first direction D1. To prepare for.

Further, the regulator 50 is disposed between the valve body 52 and the main spring 54 with a piston 56 (an example of a "piston component"), and is arranged on the second direction D2 side with respect to the main spring 54, and is an end of the main spring 54. It includes an adjusting screw 66 (an example of a "screw component") that supports the main spring 54 by pressing the portion in the first direction D1.

The regulator 50 includes the adjusting screw 66 and the dial 80 as a pressure adjusting mechanism for changing the pressure of the compressed air supplied to the drive mechanism 20 to adjust the pressure and a load reducing mechanism for reducing the operating load at the time of adjusting the pressure. , Spacer 72, cam plate 82, load release valve 84 (shown in FIG. 3C), load release piston 86. These configurations will be described in detail later.

The plug 62 is a component for receiving the supply of compressed air from the outside. One end of the plug 62 is configured to allow an air hose (not shown) to be connected. Therefore, the compressed air generated by the air compressor can be supplied to the plug 62 via the air hose. The other end of the plug 62 is connected to the first end cap 58. At this time, the flow path formed in the plug 62 communicates with the first flow path CH1 formed in the first end cap 58.

The plug 62 is mounted on the second axis AX2 (so that it is coaxial with the second axis AX2). The first axis AX1 and the second axis AX2, which will be described later, are two substantially parallel axes that are separated from each other. Further, the first axis AX1 and the second axis AX2 are parallel to the first direction D1 and the second direction D2.

The compressed air supplied from the plug 62 is supplied to the valve chamber 64 in the first end cap 58 to which the plug 62 is attached and in the parts from the first end cap 58 to the valve chamber 64 in which the valve body 52 is arranged. A first flow path CH1 for supplying inside is formed. As shown in FIG. 3A, the valve chamber 64 is located at a position advanced in the first direction D1 from the second direction D2 end of the first end cap 58, and is a first axis vertically separated from the second axis AX2. Since it is disposed on the AX1, the first flow path CH1 has a portion for advancing the compressed air in the first direction D1 and a portion for advancing the compressed air from the second axis AX2 to the first axis AX1.

The portion of the first flow path CH1 of the present embodiment that advances in the first direction D1 includes a flow path formed on the second axis AX2. However, the portion of the first flow path CH1 that advances in the first direction D1 does not necessarily have to be formed on the second axis AX2 parallel to the first direction D1, for example, with respect to the first direction D1. It may be formed to form an acute angle.

The valve body 52, together with the piston 56, is a component for adjusting the secondary pressure on the downstream side of the valve body 52. Specifically, the valve body 52 moves to the first direction D1 when the secondary pressure on the downstream side drops, so that the compressed fluid on the upstream side having the primary pressure flows into the downstream side, thereby causing a predetermined pressure. Increase the secondary pressure until. Here, the primary pressure is the pressure on the upstream side of the valve body 52. The secondary pressure is a pressure on the downstream side of the valve body 52.

As shown in FIG. 3A and the like, the valve body 52 according to the present embodiment is located on the first direction D1 side, is formed integrally with the cylindrical portion 52B formed in a cylindrical shape, and is formed in the second direction. It has a truncated cone portion 52A that is located on the D2 side and is formed in a truncated cone shape with a bottom surface having a diameter larger than that of the cylindrical portion 52B. Further, the truncated cone portion 52A is formed with a hole portion extending from the top surface of the truncated cone portion 52A toward the cylindrical portion 52B.

Of the top surface of the truncated cone 52A formed in a circular shape, the outer edge portion is supported by the valve seat, and the region on the center side of the outer edge portion and the surface of the hole portion are exposed to the compressed fluid of the secondary pressure. .. The other parts of the valve body 52, that is, at least the bottom surface and each side surface of the cylindrical portion 52B and the truncated cone portion 52A, are exposed to the compressed fluid of the primary pressure.

The valve body 52 is arranged in the valve chamber 64 on the first axis AX1 (so as to be coaxial with the first axis AX1). Since the first flow path CH1 communicates with the valve chamber 64, a compressed fluid having a primary pressure exists in the valve chamber 64. Since the bottom surface of the valve body 52 facing the first direction D1 (an example of the "first pressure receiving surface exposed to the primary pressure region") is exposed to the space inside the valve chamber 64, the valve body 52 has a primary pressure. Is pressed in the second direction D2 by the compressed fluid having.

Further, as shown in the figure, the valve body 52 is supported by a valve spring 68 which is a compression spring disposed on the first direction D1 side with respect to the valve body 52. Therefore, the valve body 52 has a second direction D2 due to the urging force according to the compression amount of the valve spring 68 and the pressure of the compressed fluid having the primary pressure exposed on the surface of the valve body 52 facing the first direction D1. Is pressed against. The valve spring 68 is arranged so as to surround the cylindrical portion 52B in a cylindrical space provided in a component attached to a second end cap 70 provided at the end of the regulator 50 in the first direction D1. The end engages the bottom surface of the truncated cone 52A.

On the other hand, the top surface of the valve body 52 facing the second direction D2 is pressed in the first direction D1 by the valve seat supporting the piston 56 and the valve body 52. Since the piston 56 is pressed in the first direction D1 by the main spring 54, it can be said that the main spring 54 presses the valve body 52 in the first direction D1 via the piston 56. Further, a part of the top surface of the valve body 52 is exposed to the secondary pressure region AR2. Therefore, the valve body 52 is subjected to the first direction D1 by the urging force according to the compression amount of the main spring 54 and the pressure by the compressed fluid having the secondary pressure exposed on the surface of the valve body 52 facing the second direction D2. It is configured to be pressed against and restricted from moving in the second direction D2 by the valve seat. The action of pressure regulation including such a valve body 52 will be described in detail later.

When the secondary pressure is in equilibrium with a predetermined pressure, a part of the top surface of the valve body 52 is in close contact with the valve seat, so that the valve chamber 64 (an example of the "primary pressure region") and the valve body The secondary pressure region AR2, which is the region on the second direction D2 side with respect to 52, does not communicate with each other. However, when the secondary pressure decreases, the valve body 52 moves away from the valve seat in the first direction D1 as described later (see FIG. 4), so that the valve chamber 64 and the secondary pressure region AR2 on the downstream side Since the compressed fluid having the primary pressure flows into the downstream side, the secondary pressure can be increased.

The piston 56 transmits the urging force of the main spring 54 to the valve body 52 and presses the valve body 52 in the first direction D1. When the secondary pressure rises above the predetermined pressure, the compressed fluid in the secondary pressure region AR2 is exhausted and the secondary pressure is lowered.

The piston 56 is arranged on the first axis AX1 (so as to be coaxial with the first axis AX1). The secondary pressure region AR2 communicates with a second flow path CH2 (an example of a “secondary pressure flow path”) for supplying a compressed fluid to the drive mechanism 20, and is a surface of the piston 56 facing the first direction D1. Since (an example of the "second pressure receiving surface exposed to the secondary pressure region") is exposed to the secondary pressure region AR2, the piston 56 is pressed in the second direction D2 by the compressed fluid having the secondary pressure. .. That is, the second pressure receiving surface receives the air pressure in the air chamber 34 and is pressed in the direction of closing the flow paths CH1 and CH2.

Further, a cylindrical space (spring seat) centered on the first axis AX1 is provided at the end of the piston 56 in the second direction D2, and a main spring 54 is arranged in the cylindrical space. To. The piston 56 is pressed in the first direction D1 by the main spring 54, which is a compression spring. The cylindrical space is maintained at atmospheric pressure.

Further, the end portion of the piston 56 in the first direction D1 extends in a cylindrical shape with the first axis AX1 as the central axis and abuts on the top surface of the valve body 52. A through hole H communicating with a cylindrical space maintained at atmospheric pressure is formed in the portion extending in a cylindrical shape.

When the secondary pressure is in equilibrium with a predetermined pressure, the urging force from the main spring 54 that exerts a force toward the first direction D1 on the piston 56 and the secondary pressure that exerts a force toward the second direction D2. The piston 56 does not move because the compressed air and the force received from the valve body 52 are balanced.

However, when the secondary pressure drops below the predetermined pressure, the force with which the compressed air having the secondary pressure presses the piston 56 in the second direction D2 on the second pressure receiving surface decreases, so that the piston 56 and the valve pressed by the piston 56 have a reduced force. The body 52 moves in the first direction D1. Therefore, the valve composed of the valve body 52 opens in the intake direction (see FIG. 4). Therefore, the valve chamber 64, which is the primary pressure region, and the secondary pressure region AR2 communicate with each other, and the compressed air having the primary pressure flows into the downstream side, so that the secondary pressure can be increased. When the secondary pressure rises to a predetermined pressure, the valve body 52 returns to the second direction D2 and the valve closes, so that an equilibrium state is reached.

On the other hand, when the secondary pressure rises above the predetermined pressure, the force of the compressed air having the secondary pressure to press the second pressure receiving surface of the piston 56 in the second direction D2 increases, so that the piston 56 moves in the second direction. Move to D2. Therefore, a slight gap is formed between the valve body 52, which does not move in the second direction D2 because it is restrained by the valve seat, and the piston 56 (see FIG. 5).

Since the through hole H is formed in the cylindrically extending portion of the piston 56, at this time, the valve composed of the valve body 52 opens in the exhaust direction, as shown by the arrow in FIG. The compressed air in the secondary pressure region AR2 is exhausted to the space maintained at atmospheric pressure through the through hole H. Therefore, it becomes possible to reduce the secondary pressure. When the secondary pressure is reduced to a predetermined pressure, the piston 56 returns to the first direction D1 and is in an equilibrium state. By the above operation, the regulator 50 is configured to be able to maintain the secondary pressure at a predetermined pressure. For example, the predetermined secondary pressure is set to 2.3 MPa. However, the present invention can be applied to a pressure regulating mechanism having other configurations.

The main spring 54 presses the valve body 52 in the first direction D1 via the piston 56. The main spring 54 is arranged on the first axis AX1 (so as to be coaxial with the first axis AX1). Since the main spring 54 needs to move the valve body 52 pressed in the second direction D2 by the valve spring 68 to the first direction D1 when the secondary pressure drops, the main spring 54 has a stronger force than the valve spring 68. The valve body 52 is configured to be pressable.

The first direction D1 end of the main spring 54 abuts on the piston 56, and the second direction D2 end is supported by the adjusting screw 66. Therefore, it is possible to adjust the initial load of the main spring 54 by changing the position of the adjusting screw 66 or by inserting a washer or the like between the adjusting screw 66 and the main spring 54.

The adjusting screw 66 presses the main spring 54 in the first direction D1. Further, the adjusting screw 66 is arranged on the first axis AX1 (so as to be coaxial with the first axis AX1). That is, the valve body 52, the piston 56, the main spring 54, and the adjusting screw 66 are arranged on the first axis AX1 in this order in the second direction D2 toward the outside of the nailing tool 10. Further, at least a part of the plug 62 and the first flow path CH1 is arranged on the second axis AX2.

Therefore, the position of the second direction D2 end of the main spring 54 can be easily adjusted by removing the dial 80 and changing the position of the adjusting screw 66 or inserting a washer or the like. If the initial load of the main spring 54 fluctuates to the low pressure side, a malfunction of the pneumatic tool will occur, and if it fluctuates to the high pressure side, the consumption of compressed air by the drive mechanism will increase and the merit of mounting the regulator will be diminished. According to the nailing tool 10 according to the present embodiment, the adjusting screw 66 is arranged on the outer side of the valve body 52, the piston 56, and the main spring 54, so that the initial load of the main spring 54 can be easily adjusted. .. Therefore, it is possible to improve the assembling property of the nailing tool 10.

That is, since each spring has a characteristic that the load characteristics vary greatly, it is necessary to mount a regulator having different load characteristics for each pneumatic tool just by assembling the regulator in the same manner. It ends up. Therefore, after assembling the regulator, the variation in the load characteristics of the regulator is eliminated by inserting a washer or adjusting the screw for adjusting the initial load.

When adjusting the load characteristics, the contact state between one end of the spring and the piston must be maintained, so it is necessary to provide a pressure regulating mechanism on the other end side of the spring. However, in the case of the conventional pneumatic tool, since the spring is provided inside the pneumatic tool rather than the piston, the pressure adjusting mechanism is also provided inside the pneumatic tool rather than the piston. In order to operate the pressure regulating mechanism in such a state, it is conceivable to expose the operating part of the pressure regulating mechanism from the pneumatic tool, but for that purpose, it is necessary to make a hole in the grip to be used as an air chamber. Not realistic.

In the nailing tool 10 according to the present embodiment, since the main spring 54, which is an elastic body, is arranged outside the valve body 52, that is, at a position close to the air intake port, the variation in the load characteristics of the main spring 54 can be easily adjusted. It becomes possible to do.

Further, the valve body 52, the piston 56 and the main spring 54 are arranged on the first axis AX1, while the plug 62 upstream of the valve body 52 is arranged on the second axis AX2 different from the first axis AX1. Will be set up. As a result of such a configuration, the plug 62 is moved to the first direction side as compared with the conventional case, and is arranged so that only the end portion of the second direction D2, not the entire plug 62, protrudes from the other part of the nailing tool 10. (See Fig. 1).

At this time, in the first direction D1, the region where the main spring 54 is provided (the region from the end of the main spring 54 in the first direction D1 to the end of the second direction D2) and the region where the first flow path CH1 is provided are at least. Some overlap. In particular, in the case of the regulator 50 shown in the present embodiment, in the first direction D1, the region where the main spring 54 is provided and the region where the piston 56 is provided are the regions where the first flow path CH1 is provided (the first end cap 58). It is included in the first direction D1 end of the flow path from the second direction D2 end to the valve chamber 64). As a result of such a configuration, the total length W (shown in FIG. 3A) of the first direction D1 of the regulator 50 can be made smaller than that of the prior art. That is, it is possible to suppress the protrusion amount of the plug 62 and shorten the total length of the nailing tool 10.

Further, since there is a margin in the area on the second axis AX2, a large air filter 60 is provided on the second axis AX2 (so that it is coaxial with the second axis AX2) as shown in FIG. 3A. Will be possible. As a result, it is possible to reduce the possibility that the regulator 50 cannot operate normally due to dust being mixed inside the regulator 50 and engaging with the valve body 52 or the like. However, the plug 62 may be further arranged on the first direction D1 side without providing the air filter 60 or by reducing the size.

[Load reduction mechanism]
Hereinafter, the pressure adjusting mechanism and the load reducing mechanism included in the regulator 50 will be described with reference to FIGS. 6A to 9. The pressure regulating mechanism allows the regulator 50 to adjust the secondary pressure. Therefore, it is possible to change the impact force of the nailing tool 10 according to the type of fastener and the material to be machined. Further, the load reducing mechanism according to the present embodiment makes it possible to temporarily reduce the load applied to the user when adjusting the pressure.

First, the outline of each mechanism will be described, and then the specific configuration of each mechanism will be described. The pressure adjusting mechanism further includes a dial 80, a spacer 72, and an adjusting screw 66 in addition to the valve body 52, the main spring 54, and the pressure receiving member described above. Further, the load reduction mechanism includes a cam plate 82, a load release valve 84, and a load release piston 86.

The load release piston 86 is an example of a support portion that supports the end portion of the main spring 54 in the second direction D2, and is located on the second direction D2 side of the piston 56. The load release piston 86 can move relative to the piston 56. When the operation is input to the operation input unit such as the dial 80, the load release piston 86 moves to the second direction D2 side opposite to the first direction D1 side where the valve body 52 is located.

The pressure adjusting mechanism causes the user to turn the dial 80 (an example of the "operation input unit") to change the position of the "support portion" which is a component that defines the position of the second direction D2 end portion of the main spring 54. The amount of compression of the main spring 54 varies depending on the position of the end portion of the main spring 54 in the second direction D2. Therefore, it is possible to adjust the secondary pressure by changing the position of the load release piston 86. In the present embodiment, by providing a slope at the contact portion between the spacer 72 that rotates with the dial 80 and the first end cap 58, the position of the spacer 72 with respect to the first end cap 58 depends on the rotation position of the dial 80 (spacer 72). Is configured to be displaced in the axial direction.

Since the component that defines the position of the second direction D2 end of the main spring 54 is integrally configured with the spacer 72, the position of the second direction D2 end of the main spring 54 is displaced by the operation of the dial 80, and the main spring 54 is displaced. The spring force of can be adjusted. Further, since the spacer 72 is integrally configured with the load release piston 86, the axial force of the load release piston 86 in the D1 direction compresses the spring from the component that defines the position of the second direction D2 end of the main spring 54. A force to press in the direction (D1 direction) is generated.

The load reduction mechanism extends the main spring 54 when the dial 80 is turned. When the main spring 54 is extended, the urging force acting on the adjusting screw 66 from the main spring 54 can be weakened, so that the operating load at the time of pressure adjustment can be reduced. In the present embodiment, by exposing the surface of the load release piston 86 facing the second direction D2 to the load release region AR3 which is the primary pressure region, the load release piston 86 is normally pressed in the first direction. It is configured as follows. The load release region AR3 faces the load release piston 86, and is a closed space partitioned on the opposite side (second direction D2 side) of the valve body 52 with the load release piston 86 interposed therebetween.

When the dial 80 is turned, the load release valve 84 that follows the operation of the dial 80 opens the load release region AR3 to atmospheric pressure or is configured to reduce the pressure. As a result, the load release piston 86 can move in the second direction D2, so that the main spring 54 can be extended to the natural length or near the natural length. Therefore, it is possible to weaken the urging force acting on the adjusting screw 66 from the main spring 54. Since the adjusting screw 66 is engaged with the dial 80, it is possible to reduce the load applied to the user when the dial 80 is turned. The specific configuration will be outlined below.

FIG. 6A is an enlarged view of the dial 80 shown in FIG. 3C as viewed from the first direction D1. FIG. 6B is an enlarged view showing a state in which the dial 80 shown in FIG. 6A is rotated to input an operation. As shown in FIGS. 6A and 6B, the dial 80 is configured to be rotatable about the first axis AX1. The dial 80 includes an inner dial 801 formed in a substantially disk shape, an outer dial 802 that surrounds the inner dial 801 from the outside in the radial direction, and an elastic member 803 that connects the inner dial 801 and the outer dial 802. There is. The elastic member 803 is formed in a columnar shape from, for example, rubber. A recess for accommodating the elastic member 803 is formed on the outer peripheral surface of the inner dial 801 and the inner peripheral surface of the outer dial 802.

The inner dial 801 is fixed to the adjustment screw 66 described above, and is fixed to the load release piston 86 via the adjustment screw 66. When the load release valve 84, which will be described later, is not opened, the urging force from the main spring 54 acting on the inner dial 801 is large. Therefore, when the outer dial 802 is pinched to rotate the dial 80, the inner dial 801 having a large rotational resistance does not rotate, while only the outer dial 802 elastically deforms the elastic member 803 with respect to the inner dial 801. Rotate.

FIG. 7 is a perspective view of the dial 80 shown in FIG. 6B as viewed from an angle. As shown in FIG. 7, the dial 80 is in contact with the cam plate 82, and the cam plate 82 is configured to be displaced in the first direction D1 when the outer dial 802 of the dial 80 is rotated. Specifically, a plurality of convex portions 81A are periodically provided on the surface of the outer dial 802 that abuts on the cam plate 82 in a rotationally symmetrical manner about the first axis AX1.

On the other hand, a plurality of recesses 81B are provided on the surface of the cam plate 82 in contact with the outer dial 802 in the same period rotationally symmetrically with respect to the first axis AX1. With such a configuration, it is possible to displace the position of the cam plate 82 in the first direction D1 when the convex portion 81A and the concave portion 81B face each other and when the concave portion 81B does not face each other with the rotation of the outer dial 802. ..

As shown in FIG. 7, the cam plate 82 abuts on the second direction D2 end of the load release valve 84. Therefore, the load release valve 84 is displaced in the first direction D1 as the cam plate 82 is displaced in the first direction D1. When the load release valve 84 is displaced in the first direction D1, the valve closed state is switched to the valve open state.

In the closed state before the movement, the O-ring 84A of the load release valve 84 is pressed against the facing cylindrical inner wall surface, so that the load release region AR3 and the decompression flow path AR32 communicating with the load release region AR3 are opened to atmospheric pressure. Seal against the open area AR4. Since the load release region AR3 communicates with the first flow path CH1 by the pressurizing flow path AR31 (see FIG. 3A), the load release region AR3 and the decompression flow path AR32 are maintained at the primary pressure. When the load release valve 84 is displaced in the first direction D1 by the cam plate 82, the valve closed state is switched to the valve open state, and the load release region AR3 is opened to atmospheric pressure or depressurized.

FIG. 8 is a partially enlarged view of a cross-sectional view taken along the line AA when the main spring 54 extends to its natural length in the valve open state. As shown in FIG. 8, the cylindrical inner wall surface facing the load release valve 84 has a slight diameter so as not to sufficiently contact the O-ring 84A when the load release valve 84 moves in the first direction D1. It is formed to a large extent. Therefore, when the load release valve 84 moves in the first direction D1, the load release area AR3 and the decompression flow path AR32 communicating with the load release area AR3 are not completely sealed with respect to the open area AR4 opened to the atmospheric pressure. The valve will be open for communication.

As a result, the compressed air in the load release region AR3 that has pressed the load release piston 86 in the first direction D1 is exhausted, and the load release piston 86 becomes movable in the second direction D2. Therefore, the main spring 54 extends while moving the load release piston 86 in the second direction D2. Therefore, it is possible to weaken the urging force acting on the adjusting screw 66 from the main spring 54.

When the urging force of the main spring 54 acting on the inner dial 801 described above is weakened, the rotational resistance of the inner dial 801 is greatly reduced. As shown in FIG. 6B, the restoring force of the elastically deformed elastic member 803 causes the inner dial 801 to rotate to the same position as the outer dial 802 and return to the state shown in FIG. 6A. As a result, when the convex portion and the concave portion face each other again, the cam plate 82 is displaced in the second direction D2. As a result, the load release valve 84 is also displaced in the second direction D2 and returns to the initial position. A compression spring for urging the load release valve 84 in the second direction D2 may be provided at the end of the load release valve 84 in the first direction D1.

When the load release valve 84 is displaced in the second direction D2 and returns to the original position, the load release area AR3 and the decompression flow path AR32 communicating with the load release area AR3 are sealed with respect to the open area AR4 opened to the atmospheric pressure. .. Since the load release region AR3 communicates with the first flow path CH1 by the pressurizing flow path AR31 shown in FIG. 3A, the load release region AR3 rises to the primary pressure. As a result, the load release piston 86 is displaced in the first direction D1.

As a result, the main spring 54 is compressed, and the piston 56 supported by the load release piston 86 at the end of the second direction D2 is pressed in the first direction D1 by the main spring 54. In the illustrated example, the spacer 72 and the load release piston 86 are configured as an integral structure. The spacer 72 and the load release piston 86 may be formed separately and fixed to each other. When the load release region AR3 rises to the primary pressure, the load release piston 86 moves in the first direction D1 together with the spacer 72.

The position of the end of the main spring 54 in the second direction D2 is also displaced in the first direction D1, but at this time, the slope provided on the spacer 72 that rotates with the dial 80 comes into contact with the first end cap 58, so that the load The amount of displacement of the release piston 86 in the first direction D1 is determined. That is, the distance between the spacer 72 and the first end cap 58 can be adjusted by rotating the dial 80. Therefore, it is possible to adjust the pressure by weakening the compressive force of the main spring 54. Further, the structure is not limited to the structure in which the displacement amount can be adjusted steplessly by the slope, and the engaging portion may be formed in a stepped shape so as to be adjustable stepwise. By increasing the inclination angle of the slope, it is possible to increase the amount of displacement when the dial 80 is rotated by a predetermined angle.

FIG. 9 is a cross-sectional view showing a modified example of the load reduction mechanism shown in FIG. The modified example differs from the present embodiment in that the load release piston 86 further includes an inner cylinder portion 861 fitted in the outer cylinder portion 862 in addition to the outer cylinder portion 862 configured as a support portion. The inner cylinder portion 861 is formed in a tubular shape into which a main spring 54 is inserted. The shape of the inner cylinder portion 861 may be a cylindrical shape or a square tubular shape.

The outer cylinder portion 862 is configured to be slidable along the inner cylinder portion 861 surrounding the main spring 54. The second direction D2 side end of the main spring 54 is supported by the outer cylinder portion 862. The first direction D1 side end portion of the main spring 54 penetrates the inner cylinder portion 861 and faces the piston 56. Even with the configuration of the modified example shown in FIG. 9, the operating load of the pressure regulating mechanism can be reduced as in the configuration shown in FIG.

[Primary pressure balance mechanism]
Hereinafter, the primary pressure balance mechanism included in the regulator 50 will be described with reference to FIGS. 10 to 12. It is known that when the primary pressure becomes low, the valve body 52 is pushed to the primary side to open the valve, and the secondary pressure becomes high. The primary pressure balance mechanism has a structure in which the primary pressure is applied to the piston 56 to constantly apply a load in the D1 direction to the piston 56, and the secondary pressure is primary by canceling at least a part of the fluctuation of the primary pressure. Reduce the effect of pressure fluctuations.

FIG. 10 is a partially enlarged view of a cross-sectional view taken along the line AA when the valve is closed. As shown in FIG. 10, the primary pressure balance mechanism includes flow paths CH3 and AR51 for introducing the compressed fluid on the primary side (upstream side from the valve body 52) to the secondary side (downstream side from the valve body 52). It includes a third pressure receiving surface F that receives pressure from the compressed fluid introduced from the primary side.

In the illustrated example, the piston 56 includes a columnar enlarged diameter portion 561 and a columnar reduced diameter portion 562 having a diameter smaller than that of the enlarged diameter portion 561. In the piston 56, the enlarged diameter portion 561 is provided on the D1 side in the first direction, and the reduced diameter portion 562 is provided on the D2 side in the second direction. An annular third pressure receiving surface F is formed at the boundary between the enlarged diameter portion 561 and the reduced diameter portion 562. The shape of the third pressure receiving surface F is not limited to the illustrated example. For example, when the cylinders 561 and 562 have the same diameter, the outer peripheral surface of the cylinder 562 on the second direction D2 side may be scraped off to form a notch-shaped third pressure receiving surface F.

The load release piston 86 includes a portion formed in a substantially cylindrical shape, and has a first inner peripheral surface 86A that is in sliding contact with at least a part of the outer peripheral surface of the enlarged diameter portion 561 and at least a part of the outer peripheral surface of the reduced diameter portion 562. It has a second inner peripheral surface 86B that is in sliding contact with the surface. As shown in FIG. 7, the space AR5 is partitioned by the first inner peripheral surface 86A, the outer peripheral surface of the reduced diameter portion 562, and the third pressure receiving surface F of the enlarged diameter portion 561. In the following description, the space may be referred to as a primary pressure balance region AR5. The load release piston 86 is formed with a flow path CH3 that penetrates the first inner peripheral surface 86A. The flow path CH3 is connected to a bypass flow path (not shown) branched from the flow path CH1 on the primary side. The bypass flow path is formed so as to straddle the second axis AX2 and the first axis AX1. Compressed air on the primary side is introduced into the primary pressure balance region AR5 through the flow path CH3. The third pressure receiving surface F receives the air pressure on the upstream side of the valve body 52 and is pressed in the direction of opening the flow paths CH1 and CH2.

The valve body 52 and the third pressure receiving surface F receive a common primary pressure and are pressed against each other in opposite directions. At the valve body 52 and the third pressure receiving surface F, which are pressed in opposite directions to each other, at least a part of the force of the fluctuation of the primary pressure is canceled out. The area of the third pressure receiving surface F seen from the first direction D1 is smaller than the bottom surface of the cylindrical portion 52B of the valve body 52 seen from the second direction D2. Since the valve body 52 receives a larger force from the primary pressure than the pressure receiving surface F, the piston 56 can be pushed back until it is balanced with the main spring 54 and the secondary pressure. In the illustrated example, the third pressure receiving surface F is formed smaller than the above-mentioned second pressure receiving surface (the surface of the piston 56 facing the first direction D1).

FIG. 11 is a cross-sectional view showing a first modification of the primary pressure balance mechanism shown in FIG. In the first modification, the piston 56 slides along the housing constituting the regulator 50 instead of the load release piston 86, and the housing branches from the flow path CH1 on the primary side to the primary pressure balance region. It differs from the present embodiment in that the bypass flow path CH3 communicating with AR5 is formed. As shown in FIG. 8, the bypass flow path CH3 is formed so as to straddle the second axis AX2 and the first axis AX1.

In the illustrated example, the load release piston 86 is arranged on the second direction D2 side with respect to the piston 56. A main spring 54 is internally fitted inside the load release piston 86 formed in a cylindrical shape. The main spring 54 urges the end of the piston 56 on the second direction D2 side toward the first direction D1. Even in the primary pressure balance mechanism of such a modification, similarly to the primary pressure balance mechanism of the present embodiment, the primary pressure is applied to the piston 56, and the load in the D1 direction is always applied to the piston 56. The influence of the fluctuation of the primary pressure on the secondary pressure can be reduced.

FIG. 12 is a cross-sectional view showing a second modification of the primary pressure balance mechanism shown in FIG. In the second modification, the pressure receiving surface F, which receives the primary pressure common to the valve body 52 and is pressed in the direction opposite to that of the valve body 52, is divided into an inner cylinder portion 861 and an outer cylinder portion 862 instead of the piston 56. It differs from the present embodiment in that it is formed on the inner cylinder portion 861 of the load release piston 86.

The inner cylinder portion 861 is configured so as to be able to come into contact with the piston 56 which is a pressure receiving member. The primary pressure balance region AR5 is partitioned into a gap between the inner cylinder portion 861 and the outer cylinder portion 862 having an inlay structure. A compressed fluid on the primary side is introduced into the primary pressure balance region AR5 through a bypass flow path (not shown). Even in the primary pressure balance mechanism of such a modification, similarly to the primary pressure balance mechanism of the present embodiment, the primary pressure is applied to the piston 56, and the load in the D1 direction is always applied to the piston 56. The influence of the fluctuation of the primary pressure on the secondary pressure can be reduced.

With the above configuration, it is possible to change the secondary pressure of the compressed air supplied to the drive mechanism 20 to adjust the pressure. It is also possible to reduce the operating load at the time of pressure adjustment. When the dial 80 is further rotated so that the next convex portion and the concave portion face each other, the load release piston 86 is further displaced in the first direction D1 by the slope provided on the spacer 72. It is also good. With such a configuration, the secondary pressure can be adjusted in multiple stages. As described above, according to the present invention, it is possible to provide a pneumatic tool capable of reducing the operating load of the pressure adjusting mechanism.

Further, according to the present embodiment, it is possible to easily adjust the variation in the load characteristics of the main spring 54. Since each spring has the characteristic that the load characteristics vary widely, by inserting a washer or adjusting the initial load adjustment screw after assembling the regulator, the load characteristics of the regulator can be adjusted. Eliminating variability is being done. In the present embodiment, since the main spring 54, which is an elastic body, is arranged outside the valve body 52, that is, at a position close to the air intake port, the main spring is formed by removing the dial 80 and changing the position of the adjusting screw 66. The position of the second direction D2 end of 54 can be easily adjusted. As a result, it becomes possible to easily adjust the variation in the load characteristics of the main spring 54.

Further, in the present embodiment, in the first direction D1, a region where the main spring 54 is provided (a region from the end of the main spring 54 in the first direction D1 to the end of the second direction D2) and the first flow path CH1 are provided. The areas overlap at least in part. As a result, the total length W (FIG. 3A) of the first direction D1 of the regulator 50 can be made smaller than that of the conventional technique, the protrusion amount of the plug 62 can be suppressed, and the total length of the nailing tool 10 can be shortened. It will be possible. Moreover, in the present embodiment, since there is a margin in the region on the second axis AX2, as shown in FIG. 3A, a large-sized air is placed on the second axis AX2 (so that it is coaxial with the second axis AX2). It becomes possible to provide the filter 60. It is possible to reduce the possibility that the regulator 50 cannot operate normally.

The present invention can be applied to pneumatic tools in general, and can be applied to, for example, an air nailer, an air driver, and a pneumatic screwdriver. The present invention may be applied to a compressed fluid other than compressed air. Further, the present invention can be modified in various ways as long as it does not deviate from the gist thereof. For example, within the normal creativity of one of ordinary skill in the art, some components in embodiments may be replaced with other known components that perform similar functions.

10 Nail driving tool 20 Drive mechanism 22 Driving piston 24 Driving cylinder 26 Driver 28 Nose 30 Magazine 32 Grip 34 Air chamber 36 Main valve 38 Trigger 50 Regulator 52 Valve body 54 Main spring 56 Piston 561 Enlarged part 562 Reduced part 58 No. 1 End cap 60 Air filter 62 Plug 64 Valve chamber 66 Adjusting screw 68 Valve spring 70 Second end cap 72 Spacer 80 Dial 81A Convex 81B Concave 82 Cam plate 84 Load release valve 84A Ring 86 Load release piston (“support part” One case)
86A 1st inner peripheral surface 86B 2nd inner peripheral surface 801 Inner dial 802 Outer dial 803 Elastic member 861 Inner cylinder part 862 Outer cylinder part (another example of "support part")
AR2 Secondary pressure area AR3 Load release area AR31 Pressurized flow path AR32 Decompression flow path AR4 Open area open to atmospheric pressure AR5 Primary pressure balance area AR51 Flow path AX1 First axis AX2 Second axis CH1 First flow path CH2 Second Flow path CH3 Bypass flow path D1 First direction D2 Second direction F Third pressure receiving surface H Through hole

Claims (10)

A pneumatic tool equipped with a drive mechanism driven by compressed air supplied from the air intake.
An air chamber that stores the supplied compressed air,
Includes a pressure regulating mechanism that regulates the pressure of compressed air in the air chamber.
The pressure regulating mechanism is
A valve body that opens and closes a flow path that communicates the air intake and the air chamber,
An elastic body that gives an urging force to the valve body in a direction that opens the flow path,
A support portion that supports the end portion of the elastic body, and a support portion that supports the end portion of the elastic body.
A pressure receiving member that receives the air pressure in the air chamber and presses the elastic body in a direction that closes the flow path.
A pneumatic tool provided with a load reduction mechanism capable of switching between a normal state and a load reduction state that exerts a smaller urging force than the normal state with respect to the urging force of the elastic body acting on the valve body. .. The pneumatic tool according to claim 1, wherein the support portion moves when the normal state is switched to the load reduction state. The first or second aspect of claim 1 or 2, further comprising an operation input unit capable of operating the urging force of the elastic body, and switching from the normal state to the load reduction state in conjunction with the operation input to the operation input unit. Pneumatic tool. The pneumatic tool according to any one of claims 1 to 3, wherein the pressure receiving member is a piston component that is disposed between the valve body and the elastic body and presses the valve body by the elastic body. .. Further provided with an inner cylinder formed in a tubular shape,
The support portion is an outer cylinder portion that is externally fitted to the inner cylinder portion and is slidable along the inner cylinder portion.
The pneumatic tool according to claim 4, wherein the elastic body penetrates the inner cylinder portion and faces the piston component. The valve body and the elastic body are arranged on the first axis, and the valve body and the elastic body are arranged on the first axis.
At least a part of the flow path from the air intake to the pressure regulating mechanism extends along a second axis substantially parallel to the first axis.
The pneumatic tool according to any one of claims 1 to 5, wherein the elastic body is arranged at a position closer to the air intake port than the valve body. A load release region which is a closed space facing the support portion and partitioned on the opposite side of the valve body across the support portion.
A pressurized flow path capable of introducing compressed air upstream of the valve body into the load release region,
A decompression flow path capable of discharging the compressed air introduced into the load release region to the outside of the pressure regulating mechanism, and
The pneumatic tool according to any one of claims 1 to 6, further comprising a load release valve that opens and closes the pressure reducing flow path. Further provided with an operation input unit that allows the user to operate the urging force of the elastic body.
The load release valve opens in accordance with the operation of the operation input unit.
The pneumatic tool according to claim 7, wherein when the load release region is depressurized, the support portion moves to the side opposite to the side where the valve body is located. The pneumatic tool according to any one of claims 1 to 6, wherein the pneumatic tool is a driving tool for driving a fastener. A pressure regulator that regulates the pressure of compressed air.
A valve body that opens and closes a flow path that communicates an air intake to which compressed air is supplied and an air outlet to take out compressed air whose pressure has been adjusted.
An elastic body that gives an urging force to the valve body in a direction that opens the flow path,
A pressure receiving member that receives air pressure on the downstream side of the valve body and presses the elastic body in a direction in which the valve body closes the flow path.
A pressure regulator further provided with a load reduction mechanism capable of switching between a normal state and a load reduction state that exerts a smaller urging force than the normal state with respect to the urging force of the elastic body acting on the valve body.

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