JP7769864B2 - Air Tools - Google Patents

Description

The present invention relates to pneumatic tools.

A known example of a pneumatic tool powered by compressed air is a driving tool used to drive fasteners such as nails, screws, and nails into workpieces such as boards, wood, gypsum boards, and steel plates. The compressed air that serves as the driving source is generated, for example, by an air compressor and supplied to the driving tool via an air hose.

Such a driving tool, for example, comprises a piston driven by compressed air, a driver attached to the piston, and a cylinder that houses the piston. By introducing compressed air into the upper chamber of the cylinder when the piston is near top dead center, the piston and the driver attached to it can be moved toward bottom dead center, allowing the driver to drive the fastener.

However, the pressure of the compressed air supplied through the air hose is not necessarily constant. Meanwhile, the impact force during driving depends on the pressure of the compressed air. For this reason, pneumatic tools equipped with an internal pressure-reducing valve mechanism to maintain a constant pressure are known. Furthermore, 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 workpiece. For this reason, pneumatic tools equipped with an internal pressure-regulating valve mechanism to adjust the pressure of the supplied compressed air are known. By adjusting the pressure, it becomes possible to adjust the driving depth of the fastener.

Patent Document 1 describes a driving tool equipped with a valve mechanism that adjusts the pressure of compressed air. Specifically, the tool has a pressure adjustment mechanism provided between a pressure accumulator chamber provided in the handle and a driving compressed air chamber.

Patent Document 2 also describes a driving tool equipped with a valve mechanism that adjusts the pressure of compressed air. Specifically, the document describes a driving tool that includes a valve body that can move in a first direction to close the main flow path and a second direction to open the main flow path, a piston connected to the valve body and provided with a first pressure-receiving surface that receives pressure in the first direction from the compressed air and second and third pressure-receiving surfaces that receive pressure in the second direction, and a spring that constantly biases the piston in the second direction.

Japanese Patent Application Laid-Open No. 2015-226952 Japanese Patent Application Laid-Open No. 2016-215353

However, in such driving tools, the valve mechanism for reducing or regulating pressure (hereinafter collectively referred to as the "valve mechanism" or "pressure regulation mechanism") causes the driving tool to become larger. If the valve mechanism is located inside the grip of the driving tool to prevent the tool from becoming larger, the radial direction is restricted by the wall surface of the grip, limiting the available layout space. On the other hand, if the valve mechanism is located at the end of the grip, as in the driving tools described in Patent Documents 1 and 2, the air plug protrudes significantly from the driving tool, increasing the overall length of the driving tool. Therefore, an object of the present invention is to provide a driving tool that can be made shorter in overall length.

In addition, the spring load of the pressure regulating mechanism increases according to the set pressure. In pneumatic tools such as nail guns that operate at relatively high pressures, the pressure regulating mechanism requires a large operating load, making it difficult for users to operate the mechanism. Therefore, the present invention aims to provide a pressure regulator that can reduce the operating load of the pressure regulating mechanism, and a pneumatic tool equipped with such a pressure regulator.

Furthermore, the pressure of compressed air supplied to pneumatic tools can fluctuate due to various factors. It is known that with a direct-acting pressure regulating mechanism, when the primary pressure, which is the pressure of the compressed air upstream of the pressure regulating mechanism, drops, the secondary pressure, which is the pressure of the compressed air downstream of the pressure regulating mechanism, rises. Therefore, even if the desired pressure is set with the pressure regulating mechanism, the secondary pressure may be adjusted to a pressure different from the setting, which could result in variations in the amount of fastener driving. Therefore, the present invention aims to provide a pneumatic tool in which the secondary pressure is less affected by fluctuations in the primary pressure.

The present disclosure relates to a pneumatic tool equipped with a drive mechanism that is driven by compressed air supplied from an air intake. This pneumatic tool has an air chamber that stores the supplied compressed air, and a pressure adjustment mechanism that adjusts the pressure of the compressed air in the air chamber. The pressure adjustment mechanism includes a valve body that opens and closes a flow path connecting the air intake and the air chamber, an elastic body that applies a biasing force to the valve body to open the flow path, and a pressure-receiving member that receives air pressure in the air chamber and applies a biasing force to the elastic body in a direction to close the flow path. The elastic body is located closer to the air intake than the valve body.

In the above aspect, the valve body and elastic body may be arranged on a first axis, and at least a portion of the flow path from the air intake to the pressure adjustment mechanism may extend along a second axis that is substantially parallel to the first axis.

In the above aspect, the flow path from the air intake to the pressure adjustment mechanism may have a portion extending in the first direction, and may at least partially overlap with the region in which the elastic body is provided in the first direction.

In the above aspect, the pressure-receiving member may be a piston component disposed between the valve body and the elastic body, and pressing the valve body with the elastic body.

The above aspect may further include an adjustment unit that adjusts the biasing force exerted by the elastic body.

In the above aspect, the pneumatic tool may be applied to a driving tool that drives out fasteners. Furthermore, the elastic body may be configured to apply a biasing force to the valve body in a first direction, and the pressure-receiving member may be configured to apply a biasing force to the valve body in a second direction opposite to the first direction, and the flow path from the air intake to the pressure regulating mechanism may include a flow path that allows compressed air to travel in the first direction. Note that the present invention can also be applied to compressed fluids other than compressed air.

The present disclosure also provides a pneumatic tool including a drive mechanism driven by compressed fluid and a valve mechanism that supplies compressed fluid to the drive mechanism. Arranged in this order along a first direction, from the outside to the inside of the pneumatic tool, are a plug, an elastic body, a piston component pressed by the elastic body, and a valve element pressed by the piston component. A flow path is also formed that connects the valve chamber in which the valve element is located with a flow path within the plug.

The present disclosure also provides a pneumatic tool equipped with a drive mechanism powered by compressed air supplied from an air intake port, including an air chamber that stores the supplied compressed air, and a pressure adjustment mechanism that adjusts the pressure of the compressed air in the air chamber. The pressure adjustment mechanism includes a valve body that opens and closes a flow path connecting the air intake port and the air chamber, an elastic body that applies a biasing force to the valve body in a direction that opens the flow path, a pressure-receiving member that receives air pressure in the air chamber and presses the elastic body in a direction that closes the flow path, and a load reduction mechanism that can switch the biasing force of the elastic body acting on the valve body between a normal state and a load-reduced state in which a biasing force smaller than that in the normal state is exerted.

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

In the above aspect, an operation input unit may be further provided that allows the user to operate the biasing force of the elastic body, and the state may be switched from the normal state to the load reduction state in conjunction with an operation input to the steering input unit.

In the above aspect, the piston may further include an inner cylindrical portion formed in a cylindrical shape, the support portion being an outer cylindrical portion fitted onto the inner cylindrical portion and slidable along the inner cylindrical portion, and the elastic body may pass through the inner cylindrical portion and face the piston component.

In the above aspect, the valve body and elastic body may be arranged on a first axis, and at least a portion of the flow path from the air intake to the pressure adjustment mechanism may extend along a second axis that is substantially parallel to the first axis, with the elastic body being positioned closer to the air intake than the valve body.

In the above aspect, the pressure regulator may have a load release region, which is a closed space that faces the support portion and is partitioned on the opposite side of the support portion from the valve body; a pressurized flow path that can introduce compressed air upstream of the valve body into the load release region; a reduced pressure flow path that can discharge the compressed air introduced into the load release region to the outside of the pressure adjustment mechanism; and a load release valve that opens and closes the reduced pressure flow path.

In the above aspect, the load release valve may open in response to operation of the operation input unit, and the support portion may move to the side opposite the side where the valve body is located as the load release region is depressurized.

The present disclosure also provides a pressure regulator that adjusts the pressure of compressed air, comprising: a valve element that opens and closes a flow path connecting an air intake port to which compressed air is supplied and an air outlet port from which pressure-regulated compressed air is extracted; an elastic body that applies a biasing force to the valve element in a direction that opens the flow path; and a pressure-receiving member that receives air pressure downstream of the valve element and presses the elastic body in a direction that closes the flow path, and includes a pressure regulating mechanism that adjusts the pressure of compressed air acting on the valve element; the pressure regulating mechanism comprises: a valve element that opens and closes the flow path connecting the air intake port and an air chamber; an elastic body that applies a biasing force to the valve element in a direction that opens the flow path; and a pressure-receiving member that receives air pressure in the air chamber and presses the elastic body in a direction that closes the flow path, and the pressure-receiving member is provided with a second pressure-receiving surface that is pressed in a direction that closes the flow path by air pressure in the air chamber. The pressure-receiving member or a member that abuts against the pressure-receiving member is provided with a third pressure-receiving surface that is smaller than the second pressure-receiving surface and is pressed in a direction to open the flow path when it receives air pressure upstream of the valve body.

In the above aspect, the valve body and elastic body may be arranged on a first axis, and at least a portion of the flow path from the air intake to the pressure adjustment mechanism may extend along a second axis that is substantially parallel to the first axis.

In the above aspect, a bypass flow path may be formed across the second shaft and the first shaft, allowing air pressure upstream of the valve body to act on the third pressure-receiving surface.

In the above aspect, the pressure-receiving member may be a piston component disposed between the valve body and the elastic body, and pressing the valve body with the elastic body.

The above aspect may further include an inner cylindrical portion that can contact the pressure-receiving member and an outer cylindrical portion that can slide along the inner cylindrical portion, and the third pressure-receiving surface may be provided between the outer cylindrical portion and the inner cylindrical portion.

The present invention can provide a driving tool that can be shortened in overall length. Alternatively, the present invention can provide a pressure regulator that can reduce the operating load of the pressure regulating mechanism, and a pneumatic tool equipped with the pressure regulator. Alternatively, the present invention can provide a pneumatic tool in which the secondary pressure is less affected by fluctuations in the primary pressure.

1 is a cross-sectional view of a nail driving tool according to an embodiment. 1 is a view of a front end of a regulator before being assembled to a nail driving tool according to an embodiment. 3 is a cross-sectional view taken along line AA in FIG. 2. 3 is a cross-sectional view taken along the line BB in FIG. 2. 3 is a cross-sectional view taken along the line CC in FIG. 2. 3 is a cross-sectional view taken along the line DD in FIG. 2. FIG. 10 is a partially enlarged view of the AA cross section when the valve opens in the intake direction. FIG. 10 is a partially enlarged view of the AA cross section when the valve opens in the exhaust direction. FIG. 3D is an enlarged view of the dial shown in FIG. 3C viewed from a first direction. 6B is an enlarged view showing a state in which an operation is input to the dial shown in FIG. 6A. FIG. FIG. 6C is a perspective view of the dial shown in FIG. 6B seen from an angle. FIG. 10 is a partially enlarged view of the AA cross section when the main spring is extended to its natural length in the valve open state. FIG. 9 is a cross-sectional view showing a modified example of the load reduction mechanism shown in FIG. 8 . FIG. 2 is a partially enlarged view of the AA cross section when the valve is closed. FIG. 11 is a cross-sectional view showing a first modified example of the primary pressure balance mechanism shown in FIG. 10 . FIG. 11 is a cross-sectional view showing a second modified example of the primary pressure balance mechanism shown in FIG. 10 . 1 is a cross-sectional view of a nail driving tool according to an embodiment. 1 is a cross-sectional view of a nail driving tool according to an embodiment. 1 is a cross-sectional view of a nail driving tool according to an embodiment. 1 is a cross-sectional view of a nail driving tool according to an embodiment. FIG. 2 is a view of the nail driving tool 110 as seen from a first direction. FIG. 2 is a perspective view showing a component configuration of a pressure regulating mechanism including a cam according to an embodiment.

Embodiments of the present invention will be described below with reference to the accompanying drawings. The following embodiments are merely examples for explaining the present invention, and are not intended to limit the present invention to these embodiments alone.

The pneumatic tool according to the first embodiment will be described below. Figure 1 is a cross-sectional view of the nailing tool (an example of a "pneumatic tool") according to the first embodiment. For convenience, the upward and downward directions on the paper in Figure 1 may be simply referred to as the upward and downward directions, and the leftward and rightward directions on the paper in the same figure may be referred to as the first direction D1 and the second direction D2 (the opposite direction to the first direction D1), respectively. In the case of the nailing tool 10 shown in Figure 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.

[An example of the overall configuration of a pneumatic tool]

A nail driving tool (an example of a "driving tool") is a pneumatic tool that uses compressed air as a power source to drive nails (an example of a "fastener"). The nail driving tool 10 includes a drive mechanism 20 that is driven by compressed air, and a regulator 50 (an example of a "pressure adjustment mechanism") that supplies compressed air to the drive mechanism.

The drive mechanism 20 comprises a driving piston 22 that reciprocates up and down using compressed air, a cylindrical driving cylinder 24 that houses the driving piston 22, a driver 26 that is attached to the driving piston 22 and moves integrally with the driving piston 22 to strike the nail, a nose 28 that extends downward so that the driver 26 can penetrate and strike the nail, and a magazine 30 that stores nails that are supplied to the nose 28.

The nailing tool 10 also includes a grip 32 that is held by the user, an air chamber 34 provided within the grip 32, and a main valve (head valve) 36 for controlling the flow of compressed air stored in the air chamber 34 into the driving cylinder 24. The regulator 50 reduces the pressure of compressed air supplied from an external air compressor via an air hose (not shown) and supplies it to the air chamber 34.

When the user presses the trigger 38 in this nail driving tool 10, the main valve 36 opens, allowing compressed air from the air chamber 34 to flow into the upper chamber of the driving cylinder 24. As a result, the driving piston 22 moves downward, and the driver 26 attached to the driving piston 22 strikes the nail, driving it downward.

[Basic configuration of pressure regulation mechanism]

The configuration of the regulator 50 (an example of a "pressure regulating mechanism") will be described below with reference to the drawings. Figure 2 shows the front end of the regulator 50 alone, as viewed from the second direction D2, before it is assembled to the nail driving tool 10. Note that after assembly, the view corresponds to the regulator 50 as viewed from inside the nail driving tool 10 in the second direction D2 in Figure 1. Figures 3A to 3D are cross-sectional views A-A, B-B, C-C, and D-D in Figure 2, respectively. Figure 4 is a partial enlarged view of the A-A cross-sectional view when compressed fluid in the valve chamber 64 flows into the secondary pressure region AR2, and Figure 5 is a partial enlarged view of the A-A cross-sectional view when compressed fluid in the secondary pressure region AR2 is exhausted.

The regulator 50 includes 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, an air filter 60 provided within the first end cap 58, a valve element 52 that is pressed in the second direction D2 by compressed air that passes through the first flow path CH1 from the first end cap 58 and enters the valve chamber 64, a valve spring 68 that presses the valve element 52 in the second direction D2, and a main spring 54 (an example of an "elastic body") that is disposed on the second direction D2 side of the valve element 52 and applies a force to the valve element 52 in the first direction D1.

The regulator 50 further includes a piston 56 (an example of a "piston component") disposed between the valve body 52 and the main spring 54, and an adjustment screw 66 (an example of a "screw component") disposed on the second direction D2 side of the main spring 54 and supporting the main spring 54 by pressing the end of the main spring 54 in the first direction D1.

In addition to the adjustment screw 66, the regulator 50 also includes a dial 80, a spacer 72, a cam plate 82, a load release valve 84 (shown in Figure 3C), and a load release piston 86 as a pressure adjustment mechanism that changes and adjusts the pressure of the compressed air supplied to the drive mechanism 20, and a load reduction mechanism that reduces the operating load during pressure adjustment. These components will be described in detail later.

The plug 62 is a component for receiving a supply of compressed air from an external source. One end of the plug 62 is configured to allow connection to an air hose (not shown). This allows compressed air generated by an air compressor to 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. In this case, 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 attached on the second axis AX2 (so as to be 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 spaced apart. The first axis AX1 and the second axis AX2 are also parallel to the first direction D1 and the second direction D2.

A first flow path CH1 is formed within the first end cap 58, to which the plug 62 is attached, and within the components extending from the first end cap 58 to the valve chamber 64 in which the valve body 52 is disposed. This allows compressed air from the plug 62 to flow into the valve chamber 64. As shown in FIG. 3A , the valve chamber 64 is located further in the first direction D1 than the second direction D2 end of the first end cap 58 and on the first axis AX1, which is spaced perpendicular to the second axis AX2. Therefore, the first flow path CH1 has a portion that allows compressed air to flow in the first direction D1 and a portion that allows compressed air to flow from the second axis AX2 to the first axis AX1.

In this embodiment, the portion of the first flow path CH1 that travels 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 travels in the first direction D1 does not necessarily have to be formed on the second axis AX2 that is parallel to the first direction D1; for example, it may be formed so as to form an acute angle with respect to the first direction D1.

The valve element 52, together with the piston 56, is a component that adjusts the secondary pressure downstream of the valve element 52. Specifically, when the downstream secondary pressure drops, the valve element 52 moves in the first direction D1, allowing upstream compressed fluid with a primary pressure to flow downstream, thereby increasing the secondary pressure to a predetermined pressure. Here, the primary pressure is the pressure upstream of the valve element 52. The secondary pressure is the pressure downstream of the valve element 52.

As shown in Figure 3A and other figures, the valve body 52 according to this embodiment has a cylindrical portion 52B located on the first direction D1 side and formed in a cylindrical shape, and a truncated cone portion 52A located on the second direction D2 side and formed integrally therewith and formed in a truncated cone shape with a bottom surface having a larger diameter than the cylindrical portion 52B. Furthermore, a hole is formed in the truncated cone portion 52A, extending from the top surface of the truncated cone portion 52A toward the cylindrical portion 52B.

The outer edge of the circular top surface of the truncated cone portion 52A is supported by the valve seat, while the area toward the center of the outer edge and the surface of the hole are exposed to the compressed fluid of the secondary pressure. The remaining portions of the valve body 52, i.e., at least the bottom and side surfaces of the cylindrical portion 52B and the truncated cone portion 52A, are exposed to the compressed fluid of the primary pressure.

The valve element 52 is disposed on the first axis AX1 (coaxially with the first axis AX1) within the valve chamber 64. Because the first flow path CH1 is connected to the valve chamber 64, compressed fluid having a primary pressure is present within the valve chamber 64. The bottom surface of the valve element 52 facing the first direction D1 (an example of a "first pressure-receiving surface exposed to the primary pressure region") is exposed to the space within the valve chamber 64, and therefore the valve element 52 is pressed in the second direction D2 by the compressed fluid having a primary pressure.

Furthermore, as shown in the figure, the valve element 52 is supported by a valve spring 68, which is a compression spring disposed on the first direction D1 side of the valve element 52. Therefore, the valve element 52 is pressed in the second direction D2 by a biasing force corresponding to the compression amount of the valve spring 68 and the pressure of the compressed fluid having a primary pressure exposed on the surface of the valve element 52 facing the first direction D1. The valve spring 68 is disposed so as to surround the cylindrical portion 52B within a cylindrical space provided in a component attached to the second end cap 70 provided at the first direction D1 end of the regulator 50, and its end engages with the bottom surface of the truncated cone portion 52A.

Meanwhile, the top surface of the valve disc 52 facing the second direction D2 is pressed in the first direction D1 by the piston 56 and the valve seat that supports the valve disc 52. Because the piston 56 is pressed in the first direction D1 by the main spring 54, the main spring 54 can be said to press the valve disc 52 in the first direction D1 via the piston 56. Furthermore, a portion of the top surface of the valve disc 52 is exposed to the secondary pressure region AR2. Therefore, the valve disc 52 is pressed in the first direction D1 by the biasing force corresponding to the compression amount of the main spring 54 and the pressure of the compressed fluid having a secondary pressure exposed on the surface of the valve disc 52 facing the second direction D2, and movement in the second direction D2 is restricted by the valve seat. The pressure regulation function including the valve disc 52 will be described in detail later.

When the secondary pressure is in equilibrium at a predetermined pressure, a portion of the top surface of the valve disc 52 is in close contact with the valve seat, preventing communication between the valve chamber 64 (an example of a "primary pressure region") and the secondary pressure region AR2, which is the region on the second direction D2 side of the valve disc 52. However, when the secondary pressure decreases, the valve disc 52 moves in the first direction D1 away from the valve seat (see Figure 4), as described below. This connects the valve chamber 64 to the downstream secondary pressure region AR2, allowing compressed fluid at primary pressure to flow downstream, thereby increasing the secondary pressure.

The piston 56 transmits the biasing force of the main spring 54 to the valve element 52, pressing the valve element 52 in the first direction D1. Furthermore, if the secondary pressure rises above a predetermined pressure, the piston 56 exhausts the compressed fluid in the secondary pressure region AR2, lowering the secondary pressure.

The piston 56 is disposed on the first axis AX1 (so as to be coaxial with the first axis AX1). The secondary pressure region AR2 is connected to a second flow path CH2 (an example of a "secondary pressure flow path") that supplies compressed fluid to the drive mechanism 20. The surface of the piston 56 facing the first direction D1 (an example of a "second pressure-receiving surface exposed to the secondary pressure region") is exposed to the secondary pressure region AR2, so the piston 56 is pressed in the second direction D2 by the compressed fluid having a secondary pressure. In other words, the second pressure-receiving surface is pressed in a direction that closes the flow paths CH1 and CH2 due to the air pressure in the air chamber 34.

A cylindrical space (spring seat) with the first axis AX1 as its central axis is provided at the end of the piston 56 in the second direction D2, and the main spring 54 is disposed within this cylindrical space. The piston 56 is pressed in the first direction D1 by the main spring 54, which is a compression spring. This cylindrical space is maintained at atmospheric pressure.

Furthermore, the end of the piston 56 in the first direction D1 extends cylindrically with the first axis AX1 as its central axis and abuts against the top surface of the valve body 52. Within this cylindrically extending portion, a through-hole H is formed that communicates with a cylindrical space maintained at atmospheric pressure.

When the secondary pressure reaches a predetermined equilibrium pressure, the biasing force from the main spring 54, which applies a force in the first direction D1 to the piston 56, is balanced with the force from the compressed air of the secondary pressure and the valve body 52, which applies a force in the second direction D2, so the piston 56 does not move.

However, when the secondary pressure drops below a predetermined pressure, the force with which the compressed air having secondary pressure presses the piston 56 in the second direction D2 at the second pressure-receiving surface decreases, causing the piston 56 and the valve element 52 pressed thereby to move in the first direction D1. As a result, the valve formed by the valve element 52 opens in the intake direction (see Figure 4). This connects the valve chamber 64, which is the primary pressure region, with the secondary pressure region AR2, allowing compressed air having primary pressure to flow downstream, increasing the secondary pressure. When the secondary pressure rises to a predetermined pressure, the valve element 52 returns to the second direction D2, closing the valve and achieving equilibrium.

On the other hand, when the secondary pressure rises above a predetermined pressure, the force with which the compressed air having the secondary pressure presses the second pressure-receiving surface of the piston 56 in the second direction D2 increases, causing the piston 56 to move in the second direction D2. As a result, a small gap is formed between the piston 56 and the valve element 52, which is restrained by the valve seat and cannot move in the second direction D2 (see Figure 5).

A through-hole H is formed within the cylindrically extending portion of the piston 56. At this time, the valve formed by the valve element 52 opens in the exhaust direction, and the compressed air in the secondary pressure region AR2 is exhausted through the through-hole H into a space maintained at atmospheric pressure, as shown by the arrow in Figure 5. This makes it 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, achieving an equilibrium state. Through the above operation, the regulator 50 is configured 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 pressure regulating mechanisms with other configurations.

The main spring 54 presses the valve element 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). When the secondary pressure drops, the main spring 54 is required to move the valve element 52, which is pressed in the second direction D2 by the valve spring 68, in the first direction D1. Therefore, the main spring 54 is configured to be able to press the valve element 52 with a force stronger than that of the valve spring 68.

The first direction D1 end of the main spring 54 abuts the piston 56, and the second direction D2 end is supported by the adjustment screw 66. Therefore, the initial load of the main spring 54 can be adjusted by changing the position of the adjustment screw 66 or by inserting a washer or the like between the adjustment screw 66 and the main spring 54.

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

As a result, the position of the end of the main spring 54 in the second direction D2 can be easily adjusted by removing the dial 80 and changing the position of the adjustment screw 66 or by inserting a washer or similar. If the initial load of the main spring 54 fluctuates toward the low pressure side, the pneumatic tool will malfunction, while if it fluctuates toward the high pressure side, the amount of compressed air consumed by the drive mechanism will increase, thereby negating the benefits of incorporating a regulator. However, with the nailing tool 10 according to this embodiment, the adjustment screw 66 is positioned outward of the valve body 52, piston 56, and main spring 54, making it easy to adjust the initial load of the main spring 54. This makes it possible to improve the ease of assembly of the nailing tool 10.

In other words, because springs have large variations in load characteristics, simply assembling regulators in the same way means that each pneumatic tool will be equipped with a regulator with different load characteristics. Therefore, after assembling the regulator, washers are inserted or the initial load adjustment screw is adjusted to eliminate variations in the regulator's load characteristics.

When adjusting the load characteristics, one end of the spring must maintain contact with the piston, so a pressure adjustment mechanism must be installed on the other end of the spring. However, in conventional pneumatic tools, the spring is installed further inside the pneumatic tool than the piston, so the pressure adjustment mechanism is also installed further inside the pneumatic tool than the piston. In order to operate the pressure adjustment mechanism in this situation, it is possible to consider exposing the operating part of the pressure adjustment mechanism from the pneumatic tool, but this would require drilling a hole in the grip used as the air chamber, which is not practical.

In the nailing tool 10 according to this embodiment, the main spring 54, which is an elastic body, is positioned outside the valve body 52, i.e., closer to the air intake, making it possible to easily adjust for variations in the load characteristics of the main spring 54.

Furthermore, the valve body 52, piston 56, and main spring 54 are disposed on a first axis AX1, while the plug 62, which is upstream of the valve body 52, is disposed on a second axis AX2 that is different from the first axis AX1. As a result of this configuration, the plug 62 can be moved further in the first direction than before, and only the end of the plug 62 in the second direction D2 can be disposed so that it protrudes from the rest of the nail driving tool 10, rather than the entire plug 62 (see Figure 1).

In this case, the region in the first direction D1 where the main spring 54 is provided (the region from the first direction D1 end of the main spring 54 to the second direction D2 end) and the region in which the first flow path CH1 is provided at least partially overlap. In particular, in the case of the regulator 50 shown in this embodiment, the region in the first direction D1 where the main spring 54 is provided and the region in which the piston 56 is provided are encompassed within the region in which the first flow path CH1 is provided (the first direction D1 end of the flow path from the second direction D2 end of the first end cap 58 to the valve chamber 64). As a result of this configuration, the overall length W (shown in FIG. 3A) of the regulator 50 in the first direction D1 can be made shorter than in the prior art. In other words, the amount of protrusion of the plug 62 can be reduced, thereby shortening the overall length of the nail driving tool 10.

Furthermore, because there is more space on the second axis AX2, it is possible to install a large air filter 60 on the second axis AX2 (so that it is coaxial with the second axis AX2), as shown in Figure 3A. As a result, it is possible to reduce the possibility that dust will get inside the regulator 50 and become caught in the valve body 52, etc., causing the regulator 50 to malfunction. However, the air filter 60 may not be installed or may be made smaller, and the plug 62 may be positioned further toward the first direction D1.

[Load Reduction Mechanism]

The pressure adjustment mechanism and load reduction mechanism provided in the regulator 50 will be described below with reference to Figures 6A to 9. The pressure adjustment mechanism allows the regulator 50 to adjust the secondary pressure. This makes it possible to change the impact force of the nailing tool 10 depending on the type of fastener or workpiece. Furthermore, the load reduction mechanism of this embodiment makes it possible to temporarily reduce the load on the user when adjusting the pressure.

First, an overview of each mechanism will be provided, followed by a description of the specific configuration of each mechanism. In addition to the valve body 52, main spring 54, and pressure-receiving member described above, the pressure adjustment mechanism further comprises a dial 80, a spacer 72, and an adjustment screw 66. The load reduction mechanism also comprises 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 part that supports the end of the main spring 54 in the second direction D2, and is located closer to the piston 56 in the second direction D2. The load release piston 86 can move relative to the piston 56. When an operation is input to an operation input part such as the dial 80, the load release piston 86 moves in the second direction D2, which is opposite the first direction D1 on which the valve body 52 is located.

The pressure adjustment mechanism changes the position of the "support portion," which is a component that determines the position of the end of the main spring 54 in the second direction D2, when the user turns the dial 80 (an example of an "operation input portion"). The amount of compression of the main spring 54 varies depending on the position of the end 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 this embodiment, a slope is provided at the contact point between the spacer 72, which rotates with the dial 80, and the first end cap 58, so that the position of the spacer 72 relative to the first end cap 58 changes axially depending on the rotational position of the dial 80 (spacer 72).

The part that determines the position of the second direction D2 end of the main spring 54 is configured as one piece with the spacer 72, so by operating the dial 80, the position of the second direction D2 end of the main spring 54 can be displaced and the spring force of the main spring 54 can be adjusted. Furthermore, because the spacer 72 is configured as one piece with the load release piston 86, the axial force of the load release piston 86 in the D1 direction generates a force that presses the part that determines the position of the second direction D2 end of the main spring 54 in the direction that compresses the spring (D1 direction).

The load reduction mechanism extends the main spring 54 when the dial 80 is turned. When the main spring 54 extends, the biasing force acting from the main spring 54 on the adjustment screw 66 can be weakened, thereby reducing the operating load during pressure adjustment. In this embodiment, the surface of the load release piston 86 facing the second direction D2 is exposed to the load release area AR3, which is the primary pressure area, so that under normal conditions, the load release piston 86 is pressed in the first direction. The load release area AR3 is a closed space that faces the load release piston 86 and is partitioned on the opposite side of the load release piston 86 from the valve body 52 (the second direction D2 side).

When the dial 80 is turned, the load release valve 84, which operates in response to the operation of the dial 80, opens the load release area AR3 to atmospheric pressure or reduces the pressure. As a result, the load release piston 86 is able to move in the second direction D2, allowing the main spring 54 to extend to its natural length or close to its natural length. This makes it possible to weaken the biasing force acting from the main spring 54 on the adjustment screw 66. Because the adjustment screw 66 is engaged with the dial 80, it is possible to reduce the load on the user when turning the dial 80. The specific configuration is outlined below.

Figure 6A is an enlarged view of the dial 80 shown in Figure 3C as viewed from the first direction D1. Figure 6B is an enlarged view showing the state in which the dial 80 shown in Figure 6A has been rotated to input an operation. As shown in Figures 6A and 6B, the dial 80 is configured to be rotatable about a 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. The elastic member 803 is formed in a cylindrical shape from, for example, rubber. Recesses that accommodate the elastic member 803 are formed in 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 aforementioned adjustment screw 66 and is fixed to the load release piston 86 via the adjustment screw 66. When the load release valve 84 (described later) is not open, the biasing force from the main spring 54 acting on the inner dial 801 is strong. Therefore, when an attempt is made to rotate the dial 80 by pinching the outer dial 802, the inner dial 801, which has a high rotational resistance, does not rotate, while only the outer dial 802 rotates relative to the inner dial 801 while elastically deforming the elastic member 803.

Figure 7 is an oblique view of the dial 80 shown in Figure 6B. As shown in Figure 7, the dial 80 abuts against the cam plate 82, and is configured so that when the outer dial 802 of the dial 80 rotates, the cam plate 82 is displaced in the first direction D1. Specifically, on the surface of the outer dial 802 that abuts against the cam plate 82, multiple protrusions 81A are periodically arranged in rotational symmetry around the first axis AX1.

On the other hand, the surface of the cam plate 82 that abuts against the outer dial 802 has multiple recesses 81B arranged at the same interval and rotationally symmetrical about the first axis AX1. This configuration makes it possible to displace the position of the cam plate 82 in the first direction D1 as the outer dial 802 rotates, depending on whether the protrusions 81A and recesses 81B face each other or not.

As shown in FIG. 7, the cam plate 82 abuts against the second direction D2 end of the load release valve 84. Therefore, as the cam plate 82 displaces in the first direction D1, the load release valve 84 displaces in the first direction D1. When the load release valve 84 displaces in the first direction D1, it switches from a closed state to an open state.

In the closed state before movement, the O-ring 84A of the load release valve 84 is pressed against the opposing cylindrical inner wall surface, sealing the load release area AR3 and the pressure reduction flow path AR32 connected to it from the open area AR4, which is open to atmospheric pressure. Because the load release area AR3 is connected to the first flow path CH1 via the pressurized flow path AR31 (see Figure 3A), the load release area AR3 and the pressure reduction 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, it switches from the closed state to the open state, and the load release area AR3 is opened to atmospheric pressure or depressurized.

Figure 8 is a partially enlarged view of the A-A cross section when the main spring 54 is extended to its natural length in the open valve state. As shown in Figure 8, the cylindrical inner wall surface facing the load release valve 84 is formed with a slightly larger diameter so that it does not fully abut against the O-ring 84A when the load release valve 84 moves in the first direction D1. Therefore, when the load release valve 84 moves in the first direction D1, the load release area AR3 and the pressure reduction flow path AR32 communicating with it are not completely sealed from the open area AR4, which is open to atmospheric pressure, and enters an open valve state in which they are connected.

As a result, the compressed air in the load release area AR3 that had been pressing 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. This makes it possible to weaken the biasing force acting from the main spring 54 on the adjustment screw 66.

When the biasing force of the main spring 54 acting on the inner dial 801 weakens, the rotational resistance of the inner dial 801 drops significantly. 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, returning to the state shown in FIG. 6A. As a result, when the convex and concave portions 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 its initial position. A compression spring for biasing the load release valve 84 in the second direction D2 may be provided at the end of the load release valve 84 facing the first direction D1.

When the load release valve 84 is displaced in the second direction D2 and returns to its original position, the load release area AR3 and the pressure reduction flow path AR32 connected to it are again sealed against the open area AR4, which is open to atmospheric pressure. Because the load release area AR3 is connected to the first flow path CH1 via the pressure reduction flow path AR31 shown in Figure 3A, the pressure 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, which is supported by the load release piston 86 at the end in 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 integrated structure. The spacer 72 and the load release piston 86 may also be formed separately and fixed to each other. When the load release area 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 second direction D2 end of the main spring 54 also displaces in the first direction D1. At this time, the slope on the spacer 72, which rotates with the dial 80, abuts against the first end cap 58, determining the amount of displacement of the load release piston 86 in the first direction D1. In other words, the distance between the spacer 72 and the first end cap 58 can be adjusted by rotating the dial 80. This reduces the compressive force of the main spring 54, making it possible to adjust the pressure. Furthermore, rather than relying on a structure that allows for continuous adjustment of the displacement using a slope, the engagement portion may be formed in a stepped pattern to allow for stepwise adjustment. Increasing the inclination angle of the slope increases the amount of displacement when the dial 80 is rotated a specified angle.

Figure 9 is a cross-sectional view showing a modified example of the load reduction mechanism shown in Figure 8. This modification differs from the present embodiment in that the load release piston 86 further includes an inner cylindrical portion 861 fitted into the outer cylindrical portion 862, in addition to the outer cylindrical portion 862 that serves as a support portion. The inner cylindrical portion 861 is formed in a tubular shape through which the main spring 54 is inserted. The shape of the inner cylindrical portion 861 may be cylindrical or rectangular.

The outer cylinder portion 862 is configured to be slidable along the inner cylinder portion 861 that surrounds the main spring 54. The end of the main spring 54 on the second direction D2 side is supported by the outer cylinder portion 862. The end of the main spring 54 on the first direction D1 side passes through the inner cylinder portion 861 and faces the piston 56. The modified configuration shown in Figure 9 can also reduce the operating load of the pressure adjustment mechanism, similar to the configuration shown in Figure 8.

[Primary pressure balance mechanism]

The primary pressure balance mechanism provided in the regulator 50 will now be described with reference to Figures 10 to 12. It is known that when the primary pressure drops, the valve element 52 is pushed toward the primary side, opening the valve and increasing the secondary pressure. The primary pressure balance mechanism is designed to apply the primary pressure to the piston 56, constantly applying a load in the direction D1 to the piston 56. By offsetting at least a portion of the fluctuations in the primary pressure, the effect of fluctuations in the primary pressure on the secondary pressure is reduced.

Figure 10 is a partially enlarged view of the A-A cross section when the valve is closed. As shown in Figure 10, the primary pressure balance mechanism includes flow paths CH3 and AR51 that introduce compressed fluid from the primary side (upstream of the valve body 52) to the secondary side (downstream of the valve body 52), and a third pressure-receiving surface F that receives pressure from the compressed fluid introduced from the primary side.

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

The load release piston 86 includes a generally cylindrical portion and has a first inner circumferential surface 86A that is in sliding contact with at least a portion of the outer circumferential surface of the enlarged diameter portion 561, and a second inner circumferential surface 86B that is in sliding contact with at least a portion of the outer circumferential surface of the reduced diameter portion 562. As shown in FIG. 7 , a space AR5 is defined by the first inner circumferential surface 86A, the outer circumferential surface of the reduced diameter portion 562, and the third pressure-receiving surface F of the enlarged diameter portion 561. In the following description, this space may be referred to as the primary pressure balance area AR5. A flow path CH3 is formed in the load release piston 86, penetrating the first inner circumferential surface 86A. Flow path CH3 is connected to a bypass flow path (not shown) that branches off from the primary flow path CH1. The bypass flow path is formed across the second axis AX2 and the first axis AX1. Primary-side compressed air is introduced into the primary pressure balance area AR5 through flow path CH3. The third pressure-receiving surface F receives air pressure upstream of the valve body 52 and is pressed in a direction that opens 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 in opposite directions. At least a portion of the force of the fluctuations in the primary pressure is canceled out between the valve body 52 and the third pressure-receiving surface F, which are pressed in opposite directions. The area of the third pressure-receiving surface F, as viewed from the first direction D1, is smaller than the area of the bottom surface of the cylindrical portion 52B of the valve body 52, as viewed from the second direction D2. Because the valve body 52 receives a greater force from the primary pressure than the pressure-receiving surface F, it can push back the piston 56 until it is balanced with the main spring 54 and the secondary pressure. In the illustrated example, the third pressure-receiving surface F is smaller than the second pressure-receiving surface (the surface of the piston 56 facing the first direction D1).

[First Modification]
Fig. 11 is a cross-sectional view showing a first modified example of the primary pressure balance mechanism shown in Fig. 10. The first modified example differs from the present embodiment in that the piston 56 slides along a housing constituting the regulator 50 instead of along a load release piston 86, and the housing is formed with a bypass flow path CH3 that branches off from the primary-side flow path CH1 and communicates with the primary pressure balance region AR5. As shown in Fig. 8, the bypass flow path CH3 is formed across the second axis AX2 and the first axis AX1.

In the illustrated example, the load release piston 86 is positioned closer to the second direction D2 than the piston 56. The main spring 54 is fitted inside the cylindrical load release piston 86. The main spring 54 biases the end of the piston 56 on the second direction D2 side in the first direction D1. Even with this modified primary pressure balance mechanism, like the primary pressure balance mechanism of this embodiment, the primary pressure acts on the piston 56, constantly applying a load in the D1 direction to the piston 56, thereby reducing the impact of fluctuations in the primary pressure on the secondary pressure.

[Second Variant]

Figure 12 is a cross-sectional view showing a second modified example of the primary pressure balance mechanism shown in Figure 10. The second modified example differs from this embodiment in that the pressure-receiving surface F, which receives the same primary pressure as the valve body 52 and is pressed in the opposite direction to the valve body 52, is formed not on the piston 56 but on the inner cylindrical portion 861 of the load-release piston 86, which is divided into an inner cylindrical portion 861 and an outer cylindrical portion 862.

The inner cylindrical portion 861 is configured to be able to abut against the piston 56, which is a pressure-receiving member. The primary pressure balance area AR5 is defined by the gap between the inner cylindrical portion 861 and the outer cylindrical portion 862, which have a spigot-joint structure. Primary-side compressed fluid is introduced into the primary pressure balance area AR5 through a bypass flow path (not shown). Even with this modified primary pressure balance mechanism, as with the primary pressure balance mechanism of this embodiment, primary pressure is applied to the piston 56, constantly applying a load in the D1 direction to the piston 56, thereby reducing the impact of fluctuations in the primary pressure on the secondary pressure.

With the above configuration, it is possible to change and adjust the secondary pressure of the compressed air supplied to the drive mechanism 20. It is also possible to reduce the operating load when adjusting the pressure. Note that when the dial 80 is further rotated so that the next convex portion and concave portion face each other, the slope provided on the spacer 72 can be used to further displace the load release piston 86 in the first direction D1. With this configuration, it is possible to adjust the secondary pressure in multiple stages. As described above, the present invention provides a pneumatic tool that reduces the operating load of the pressure adjustment mechanism.

Furthermore, according to this embodiment, it is possible to easily adjust the variation in the load characteristics of the main spring 54. Because springs have characteristics that result in large variations in their load characteristics, after assembling the regulator, variations in the regulator's load characteristics are eliminated by inserting a washer or adjusting the initial load adjustment screw. In this embodiment, the main spring 54, which is an elastic body, is positioned outside the valve body 52, i.e., closer to the air intake. Therefore, the position of the end of the main spring 54 in the second direction D2 can be easily adjusted by removing the dial 80 and changing the position of the adjustment screw 66, for example. As a result, it is possible to easily adjust variations in the load characteristics of the main spring 54.

In addition, in this embodiment, the region in the first direction D1 where the main spring 54 is provided (the region from the first direction D1 end of the main spring 54 to the second direction D2 end) and the region in which the first flow path CH1 is provided at least partially overlap. This makes it possible to reduce the overall length W (Figure 3A) of the regulator 50 in the first direction D1 compared to conventional technology, thereby reducing the amount of protrusion of the plug 62 and shortening the overall length of the nail driving tool 10. Furthermore, in this embodiment, because there is more space in the region on the second axis AX2, it is possible to provide a large air filter 60 on the second axis AX2 (coaxially with the second axis AX2), as shown in Figure 3A. This makes it possible to reduce the possibility that the regulator 50 will not operate normally.

The present invention can be applied to pneumatic tools in general, such as air nailers, air drivers, and pneumatic screw drivers. It may also be applied to compressed fluids other than compressed air. The present invention can also be modified in various ways without departing from its spirit. For example, within the scope of the ordinary creative ability of a person skilled in the art, some of the components in the embodiments can be replaced with other known configurations that perform similar functions.

Second Embodiment
A pneumatic tool according to a second embodiment will be described below. However, components that are understood by those skilled in the art to have the same or similar configurations or functions as those described in the first embodiment and its modified examples will be given the same or similar names and detailed descriptions will be omitted. The following description will focus on differences from the pneumatic tool according to the first embodiment. Figures 13 and 14 show cross-sectional views of a regulator 150 (an example of a "pressure adjusting mechanism") mounted on a nail driving tool 110 (an example of a "pneumatic tool"; Figure 15) according to a second embodiment when set to low pressure and high pressure, respectively. Figure 15 is a view of the nail driving tool 110 as viewed from a first direction D1.

Other than the regulator 150, the components of the nailing tool 110 are the same as those of the nailing tool 10, so explanations will be omitted.

[Basic configuration of pressure regulation mechanism]
Similar to regulator 50, regulator 150 regulates the pressure of compressed air supplied through the air intake and stored by the air chamber.

The regulator 150 is similar to the regulator 50 in that it includes a plug 162 (an example of an "air intake") for receiving a supply of compressed air from the outside, a first end cap 158 that is arranged surrounding at least the outer periphery of the regulator 150 to connect the plug 162, an air filter 160 provided within the first end cap 158, a valve element 152 that is pressed in the second direction D2 by compressed air that passes through the first flow path CH1 from the first end cap 158 and enters the valve chamber 164, a valve spring 168 (an example of a "coil spring") that presses the valve element 152 in the second direction D2, and a main spring 154 (an example of an "elastic body") that is arranged on the second direction D2 side of the valve element 152 and applies a force to the valve element 152 in the first direction D1. The regulator 150 is also similar to the regulator 50 in that it includes a piston 156 (an example of a "piston component" or "pressure-receiving member") that is arranged between the valve element 152 and the main spring 154.

Furthermore, a first flow path CH1 for supplying compressed air supplied from the plug 162 into the valve chamber 164 is formed within the first end cap 158, to which the plug 162 is attached, and within the components from the first end cap 158 to the valve chamber 164 in which the valve body 152 is disposed. The valve chamber 164 is located further in the first direction D1 than the second direction D2 end of the first end cap 158 and on the first axis AX1, spaced perpendicular to the second axis AX2. Therefore, the first flow path CH1 is similar to the regulator 50 in that it has a portion that allows compressed air to travel in the first direction D1 and a portion that allows compressed air to travel from the second axis AX2 to the first axis AX1 (including the case where it has a flow path that travels in the first direction D1 while tilting to travel in the second direction D2).

Furthermore, the valve body 152, together with the piston 156, is a component for adjusting the secondary pressure downstream of the valve body 152, and when the downstream secondary pressure drops, the valve body 152 moves in the first direction D1 to open the flow path connecting the air intake and the air chamber, allowing compressed fluid upstream of the valve body 152, which has a primary pressure, to flow downstream, thereby increasing the secondary pressure, and when the downstream secondary pressure rises, the valve body 152 moves in the second direction D2 to close the flow path and reduce the secondary pressure. More specifically, the valve body 152 is arranged within the valve chamber 164 on the first axis AX1 (so as to be coaxial with the first axis AX1), and the surface of the valve body 152 facing the first direction D1 (an example of a "first pressure-receiving surface exposed to the primary pressure region") is exposed to a compressed fluid having a primary pressure, thereby pressing the valve body 152 in the second direction D2, and is also similar to the regulator 50 in that it is configured to be pressed in the second direction D2 by a spring force corresponding to the compression amount of a valve spring 168, which is a compression spring arranged on the first direction D1 side of the valve body 152 and engages with the valve body 152. On the other hand, the top surface of the valve element 152 facing the second direction D2 is exposed to the compressed fluid having a secondary pressure, so that the valve element 152 is pressed in the first direction D1, and is configured to be able to be pressed in the first direction D1 (the direction to open the flow path) via the piston 156 by a biasing force corresponding to the compression amount of the main spring 154 disposed on the first direction D1 side of the valve element 152, similar to the regulator 50.

In addition, the present embodiment shares with regulator 50 the following points: a valve seat is arranged in the second direction D2 relative to valve element 152, thereby restricting movement of valve element 152 in the second direction D2; the surface of piston 156 facing first direction D1 (an example of a "second pressure-receiving surface exposed to the secondary pressure region") is exposed to secondary pressure region AR2, thereby pressing piston 156 in the second direction D2 (in the direction to close the flow path) by compressed fluid having secondary pressure; and the valve element 152, piston 156, and main spring 154 are arranged in this order and coaxially with first axis AX in the first direction D1. This regulator 150 is used to regulate the secondary pressure, and the pressure of the compressed fluid in the air chamber can be adjusted by supplying the regulated compressed fluid to the air chamber via second flow path CH2. The mechanism by which this regulator 150 regulates the secondary pressure is the same as in the first embodiment, so a description thereof will be omitted.

[Detailed configuration of the regulator]
The regulator 50 according to the first embodiment was configured so that the user could set the secondary pressure by operating the dial 80. The regulator 150 according to the present embodiment differs in that the user can set the secondary pressure by rotating the control lever 180. Specifically, the regulator 150 is configured so that when the primary pressure is 2.3 MPa or higher, the user can set the secondary pressure to four levels—1.4 MPa, 1.6 MPa, 1.8 MPa, and 2.3 MPa—depending on the rotation angle of the control lever 180. The regulator 150 according to the present embodiment is configured so that the length of the main spring 154 can be changed in four levels using a cam 182, thereby allowing the secondary pressure to be set in four levels. The detailed configuration of the regulator 150 will be described below. The magnitude of the secondary pressure, which is configured to be changeable in stages, may be configured to vary depending on the magnitude of the primary pressure.

As shown in Figure 13(B) and other figures, the regulator 150 comprises an operating lever 180 rotatable by user operation, a cam 182 rotatable by the operating lever 180, a pin 184 for moving the cam 182 in the direction of the rotational axis by sliding against the surface of the cam 182, a spring adjuster 186 (an example of a "pressure adjustment member" and "second biasing force adjustment member"; hereinafter, sometimes referred to as the "pressure adjustment member 186" or "pressure adjustment shaft 186") configured to be movable in conjunction with the cam 182 in the direction of the rotational axis, and a pressure adjustment spacer 188 supporting the second direction D2 end of the main spring 154 and configured to be movable in the direction of the rotational axis as the spring adjuster 186 moves in the direction of the rotational axis.

With this configuration, when the user rotates the operating lever 180, the cam 182, which is rotated by the operating lever 180, converts the rotational motion into translational motion, causing the pressure adjustment spacer 188 that supports the main spring 154 to move translationally. This makes it possible to set the length of the main spring 154 supported by the pressure adjustment spacer 188 in stages, thereby setting the secondary pressure.

As shown in FIG. 13 and other figures, the operating lever 180 is disposed at the end of the first axis AX in the second direction D2 so that its rotation axis is on the first axis AX. As shown in FIG. 15, the operating lever 180 is provided with a protrusion 180A that protrudes radially outward beyond the first end cap 158 that surrounds the outer periphery of the regulator 150 when viewed in the second direction D2 parallel to the first axis AX, which is the rotation axis. This configuration makes it possible to rotate the operating lever 180 and the cam 182 connected to the operating lever 180 around the first axis AX with a small operating load. Furthermore, because the set pressure of the secondary pressure is determined according to the position of the protrusion 180A, as described below, the user can visually grasp the level of the set pressure based on the position of the protrusion 180A.

The operating lever 180 has a metal portion 180B that engages with a polygonal cam engagement portion 182C (Figure 16) formed at the tip of a metal cam 182. By arranging the plate-shaped metal portion 180B to engage (contact) with the metal cam engagement portion 182C, it is possible to rotate the cam 182 in conjunction with the rotation of the operating lever 180.

The operating lever 180 also includes a nut 180C (Figure 13) that threads onto the male threads on the pressure regulating member 186. As described below, a cam 182 threads onto the male threads on the pressure regulating member 186. This double-nut structure, in which the cam 182 that threads onto the base end of the male threads on the pressure regulating member 186 functions as a first nut and the nut 180C that threads onto the tip end of the male threads on the pressure regulating member 186 functions as a second nut, makes it possible to prevent the pressure regulating member 186, cam 182, and operating lever 180 from loosening from one another.

Cam 182 (an example of a "biasing force adjustment member") is a member that converts rotational motion into translational motion by rotating with the rotation of operating lever 180. Cam 182 is disposed at a position advanced in first direction D1 relative to operating lever 180, with its central axis located on first axis AX when biased in second direction D2.

Figure 16 shows a perspective view of components including the cam 182. As shown in the figure, the cam 182 in this embodiment comprises an annular cylindrical portion 182A with a female thread formed on its inner peripheral surface, a bottom portion 182B that expands radially outward at the end of the cylindrical portion 182A in the first direction D1, and a cam engagement portion 182C at the end of the cylindrical portion 182A in the second direction D2 for engaging with the operating lever 180. On the surface of the bottom portion 182B facing the axial direction (second direction D2), four stepped surfaces 182B1 to 182B4 (examples of "the surface of the cam on which the pin slides") are provided at different heights in the central axial direction of the cam 182, with 180-degree rotational symmetry about the central axis.

By biasing the cam 182 in the second direction D2 so that the first direction D1 end (tip) of the pin 184 attached to the main body of the regulator 150 abuts against the surface of one of these step surfaces 182B1 to 182B4, it is possible to move the cam 182 in the first direction D1 or the second direction D2 depending on which step surface 182B1 to 182B4 the pin 184 abuts against. In this embodiment, the steps between step surfaces 182B1, 182B2, and 182B3 are relatively small, and the steps between step surfaces 182B3 and 182B4 are relatively large.

For example, when the primary pressure is 2.3 MPa and the pin 184 abuts against step surface 182B1, the secondary pressure is adjusted to 1.4 MPa. Similarly, when the pin 184 abuts against step surfaces 182B2 to 182B4, the secondary pressure is adjusted to 1.6 MPa, 1.8 MPa, and 2.3 MPa, respectively. This configuration makes it possible to set the secondary pressure with fine resolution in a relatively small pressure range. This makes it possible to precisely set the pressure for driving the fastener when performing work that requires relatively low pressure, such as finishing.

Note that a protrusion that protrudes in the second direction D2 beyond the adjacent step surfaces may be provided at the boundary between step surface 182B1 and step surface 182B2, and similarly, a protrusion that protrudes in the second direction D2 beyond the adjacent step surfaces may be provided at the boundary between step surface 182B2 and step surface 182B3 and the boundary between step surface 182B3 and step surface 182B4. Providing such protrusions allows pin 184 to stably abut the step surfaces.

The number of steps provided on the cam 182 may be two or more. If the number of steps is two or more, it will be possible to set the secondary pressure in two or more stages.

In addition, in this embodiment, two pins 184, pin 184A and pin 184B, are provided, and four step surfaces 182B1 to 182B4 are provided with 180-degree rotational symmetry, i.e., a total of eight step surfaces are provided, but this is not limited to this. For example, the number of pins may be one and two step surfaces may be provided on the cam 182, or the number of pins may be three and multiple step surfaces may be provided with 120-degree rotational symmetry.

The pin 184 (an example of a "member configured to slide on the surface of the cam") slides against the stepped surfaces 182B1 to 182B4 of the cam 182, thereby moving the cam 182 in the first direction D1 or the second direction D2. In this embodiment, the pin 184 is attached such that its movement in the second direction D2 and a direction perpendicular thereto is restricted by being inserted into a hole that opens in the first direction D1 and extends in the second direction D2 of an annular ring part 190 that is fixed to the main body of the regulator 150 at its first direction D1 end. In this state, the first direction D1 end of the pin 184 abuts against one of the stepped surfaces 182B1 to 182B4 of the cam 182, allowing the pin 184 to move the cam 182 in the first direction D1 or the second direction D2. Instead of the pin 184, a member such as a steel ball may be provided to slide on the surface of the cam.

In this embodiment, the pin 184 is composed of two pins, 184A and 184B, which are arranged rotationally symmetrically with respect to the first axis AX. Therefore, when one pin, 184A, abuts against the step surface 182B1, the other pin, 184B, is arranged 180 degrees rotationally symmetrically with the step surface 182B1 and abuts against a step surface having the same height as the step surface 182B1. In this way, by abutting the two pins, 184A and 184B, against step surfaces having the same height, it is possible to move the cam 182 in the first direction D1 or the second direction D2 in a stable position.

It is preferable that both the pin 184 and the cam 182 are made of metal, and it is even more preferable that the cam 182 be made of a metal with a greater hardness than the metal that makes up the pin 184. By creating this hardness difference, it becomes possible for the pin 184 to be the main part that wears due to sliding contact. Therefore, it is possible to maintain the regulator 150 by replacing only the pin 184 of the cam 182 and pin 184.

The pressure adjusting member 186, which serves as a spring adjuster, moves in the first direction D1 or the second direction D2 together with the cam 182 to change the length of the main spring 154. In this embodiment, the pressure adjusting member 186 is cylindrical and extends in the second direction D2, with its central axis aligned with the first axis AX when biased in the second direction D2 by the main spring 154. The end of the pressure adjusting member 186 in the first direction D1 is provided with an enlarged diameter portion 186A extending outward. The end of the main spring 154B engages with the bottom surface of the enlarged diameter portion 186A facing the first direction D1, thereby biasing the pressure adjusting member 186 and the cam 182, which is fixed by threading onto the pressure adjusting member 186, in the second direction D2. The middle portion of the pressure adjusting member 186 is formed with a male thread that threads into a female thread formed on the inner surface of the cylindrical portion 182A of the cam 182. A second male thread is formed on the end of the pressure adjustment member 186 facing in the second direction D2, and threads into a nut 180C provided inside the operating lever 180. Note that the first male thread and the second male thread do not necessarily have to be formed separately; for example, they may be formed continuously or integrally.

Furthermore, the regulator 150 according to this embodiment allows for fine adjustment of the length of the main spring 154 by changing the relative positional relationship between the pressure regulating member 186 and the cam 182. When the pressure regulating member 186 is biased in the second direction D2, the bias prevents the male thread of the pressure regulating member 186 from loosening easily with the female thread of the cam 182. Furthermore, the double-nut structure formed by the engagement with the female thread of the nut 180C further reduces loosening resistance. However, because the pressure regulating member 186 and the cam 182 are threadedly engaged, the relative position of the pressure regulating member 186 with respect to the cam 182 can be changed by rotating the pressure regulating member 186 relative to the cam 182. Furthermore, when the pressure regulating member 186 is not biased, such as during the manufacture of the regulator 150, the pressure regulating member 186 can be easily rotated relative to the cam 182 to change the relative position of the pressure regulating member 186 with respect to the cam 182. This configuration also makes it easy to adjust for variations in load characteristics due to individual differences or changes over time in the main spring 154.

The main spring 154 presses the valve disc 152 in the first direction D1 via the piston 156. The main spring 154 is arranged on the first axis AX1 and is similar to the main spring 54 of the regulator 50 according to the first embodiment in that it moves the valve disc 152 in the first direction D1 when the secondary pressure drops. The main spring 154 of the regulator 150 according to this embodiment is composed of three elastic bodies, main springs 154A to 154C, which differs from the regulator 50 according to the first embodiment, which is composed of a single main spring 54. All of the main springs 154A to 154C are components that press the valve disc 152 in the first direction D1 via the piston 156, and are arranged so that their central axes are on the first axis AX1.

As shown in Figure 14(A) and other figures, the main spring 154A is an elastic body disposed at a position advanced in the second direction D2 from the first direction D1 end (tip) of the piston 156, and at a position advanced in the first direction D1 from the pressure adjustment spacer 188. The first direction D1 end of the main spring 154A engages with the piston 156, and the second direction D2 end is supported by the pressure adjustment spacer 188. Therefore, when the cam 182 moves in the first direction D1 and the pressure adjustment member 186 moves in the first direction D1 accordingly, the pressure adjustment spacer 188 moves in the first direction D1 so as to compress the main spring 154A, thereby making it possible to shorten the length of the main spring 154A. On the other hand, when the cam 182 moves in the second direction D2 and the pressure adjustment member 186 moves in the second direction D2 as a result, the pressure adjustment spacer 188 moves in the second direction D2 to extend or restore the main spring 154A (to reduce the amount of compression), making it possible to lengthen the length of the main spring 154A.

The main spring 154 may additionally include main spring 154B and main spring 154C. As shown in the figure, main spring 154B is an elastic body disposed in a position advanced in the second direction D2 relative to main spring 154A and pressure adjustment spacer 188, and in a position advanced in the first direction D1 relative to the expanded diameter portion of pressure adjustment member 186. The first direction D1 end of main spring 154B engages with the expanded diameter portion of pressure adjustment spacer 188, and the second direction D2 end is supported by expanded diameter portion 186A of pressure adjustment member 186. In other words, main spring 154A and main spring 154B are connected in series with pressure adjustment spacer 188 sandwiched between them. This allows a force equivalent to the resultant elastic force of main spring 154A and main spring 154B to act in the first direction D1 on piston 156 from main spring 154A and main spring 154B.

As shown in the figure, main spring 154C is an elastic body disposed at a position advanced in the second direction D2 from the end (tip) of piston 156 in the first direction D1, so as to surround main springs 154A and 154B, which have approximately the same outer diameter.

Regulator 150 according to this embodiment is configured such that the spring loads (elastic forces) of main spring 154A and main spring 154C act on piston 156, while only the spring load (elastic force) of main spring 154A acts on pressure adjusting member 186. This configuration makes it possible to reduce the operating load of operating lever 180.
For example, when the primary pressure is at the lowest set value (e.g., 1.4 MPa), the main spring 154A may be extended to its natural length, so that only the (constant) spring load of the main spring 154C acts on the piston 156. When the primary pressure is at the second lowest set value (e.g., 1.6 MPa), the main spring 154A may be compressed, so that the (relatively small) spring load of the main spring 154A and the (constant) spring load of the main spring 154C act on the piston 156. When the primary pressure is at the third lowest set value (e.g., 1.8 MPa), the main spring 154A may be further compressed, so that the (relatively large) spring load of the main spring 154A and the (constant) spring load of the main spring 154C act on the piston 156. This configuration makes it possible to reduce the operating load and suppress wear between the cam 182 and the pin 184 compared to when the cam 182 is configured from a single elastic body.

However, the main spring 154 does not necessarily have to be made up of multiple elastic bodies. For example, the pressure adjustment spacer 188 and main spring 154B may be removed, and the main spring 154A may be configured to engage with the pressure adjustment member 186. Furthermore, the main spring 154C may be removed. Conversely, multiple elastic bodies whose length changes depending on the cam 182 may be provided.

Although the regulator 150 according to this embodiment employs a configuration in which the pin 184 moves the cam 182 in the first direction D1 or the second direction D2, the present invention is not limited to such a configuration. For example, a configuration in which the pin 184, which abuts against the cam 182 that rotates with the rotation of the operating lever 180, is movable in the first direction D1 or the second direction D2, so that the cam 182 moves the pin 184 in the first direction D1 or the second direction D2, may be employed. In this case, the positional relationship between the cam 182 and the pin 184 may be reversed. That is, in the first direction D1 parallel to the first axis AX1, the surface of the cam 182 on which the pin 184 slides, the pin 184, the main spring 154 serving as an elastic body, and the valve element 152 may be arranged in this order. In this case, for example, the pin 184 is arranged closer to the pressure adjusting member 186 (i.e., further in the first direction D1) than the abutting surface of the cam 182 with the pin 184. Here, the pin 184 and the pressure adjusting member 186 may be configured to be movable integrally. With this configuration, the pressure adjusting member 186 can be configured to be movable in the first direction D1 or the second direction D2 in conjunction with the movement of the pin 184 in the first direction D1 or the second direction D2.
[Pressure adjustment method]

The following describes a method for gradually changing the secondary pressure using the regulator 150 according to this embodiment.

Figure 13(A) is a cross-sectional view of regulator 150 cut along a plane passing through first axis AX1 and second axis AX2 when the secondary pressure is set to a low pressure, and Figure 13(B) is a cross-sectional view taken along line B-B of Figure 13(A). When the secondary pressure is set to a low pressure, pin 184 abuts against step surface 182B1 (for 1.4 MPa), step surface 182B2 (for 1.6 MPa), or step surface 182B3 (for 1.8 MPa). As a result, cam 182 is positioned further in second direction D2 than when the secondary pressure is set to a high pressure, and accordingly, pressure adjustment spacer 188 is also positioned further in second direction D2 than when the secondary pressure is set to a high pressure. Therefore, main spring 154A is relatively longer than when the secondary pressure is set to a high pressure, and therefore exerts a weaker elastic force, pressing piston 156 in first direction D1.

Figure 14(A) is a cross-sectional view of the regulator 150 taken along a plane passing through the first axis AX1 and the second axis AX2 when the secondary pressure is set to high, and Figure 14(B) is a cross-sectional view taken along line B-B of Figure 14(A). When the secondary pressure is set to high, the pin 184 abuts against the stepped surface 182B4 (2.3 MPa). As a result, the cam 182 is positioned further in the first direction D1 than when the secondary pressure is set to low, and accordingly, the pressure adjustment spacer 188 is also positioned further in the first direction D1 than when the secondary pressure is set to low. As a result, the main spring 154A is relatively shorter than when the secondary pressure is set to low, and therefore exerts a strong elastic force to press the piston 156 in the first direction D1.

The user can easily change the set pressure to a low or high pressure by operating the protrusion 180A. As shown in FIG. 15, the protrusion 180A protrudes radially outward from the first end cap 158, allowing the user to generate a large moment with a small force. This makes it possible to rotate the operating lever 180 and the cam 182 connected to the operating lever 180 around the first axis AX with a relatively small operating load.

In addition, step surfaces 182B1 to 182B4 are located within an area of 180 degrees from the central axis of cam 182. This allows the user to visually grasp the level of the set pressure based on the position (angle) of protrusion 180A.

Furthermore, the pressure adjustment member 186 is provided so that its relative position to the cam 182 can be changed. By changing the relative position of the two during manufacturing, etc., it is possible to easily adjust for variations in load characteristics due to individual differences in the main spring 154 or changes over time.

Furthermore, the cam 182 is made of a metal with a harder hardness than the metal pin 184. This means that the pin 184 is the main part that wears due to sliding contact, reducing the frequency of replacement of the complexly shaped cam 182. Also, by making the pin 184 easily replaceable, the maintainability of the pneumatic tool 110 can be improved.

Also, in the regulator 150 according to this embodiment, similar to the regulator 50, the valve spring 168, valve body 152, piston 156, and main spring 154 are coaxially arranged in this order on the first axis AX1 in the second direction D2, which corresponds to the direction of approach to the plug 162, which functions as an air intake. Furthermore, in the regulator 150, the cam 182 and operating lever 180 are coaxially arranged in this order on the first axis AX1, positioned to move in the second direction D2 relative to the main spring 154. As a result, in the first direction D1 (or second direction D2), the main spring 154 is positioned closer to the plug 162, which serves as an air intake, than the valve body 152. As a result of this configuration, high-pressure air entering through the air intake travels in the second direction D2, then makes a U-turn and travels in the first direction D1 to enter the secondary pressure region AR2. With this configuration, similar to the regulator 50 according to the first embodiment, by incorporating the regulator 150, the overall length of the driving tool 110 can be shortened.

Also, in the regulator 150 according to this embodiment, similar to the regulator 50, the valve element 152 and main spring 154 are disposed on the first axis AX1, while at least a portion of the first flow path CH1, which runs from the air intake to the pressure adjustment mechanism of the regulator 150, has a portion that extends in the first direction D1 along a second axis AX2 that is substantially parallel to the first axis AX1. The portion of the first flow path CH1 that extends in the first direction D1 and the region where the main spring 154 is provided overlap in part or in whole in the first direction D1 (or the second direction D2). This configuration makes it possible to shorten the overall length of the regulator 150 in the first direction D1 (or the second direction D2).

The present application further discloses the pneumatic tool described below.

(Appendix A1)
A pneumatic tool having a drive mechanism driven by compressed air supplied from an air intake,
an air chamber that stores the supplied compressed air;
a pressure regulating mechanism that adjusts the pressure of the compressed air in the air chamber,
The pressure regulating mechanism is
a valve body that opens and closes a flow path that connects the air intake port and the air chamber;
an elastic body that applies a biasing force to the valve body in a direction that opens the flow path;
a support portion that supports an end portion of the elastic body;
a pressure-receiving member that receives air pressure in the air chamber and presses the elastic body in a direction that closes the flow path;
a load reduction mechanism that can 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 exerted.

The pneumatic tool described in Appendix A1 makes it possible to provide a pressure regulator that can reduce the operating load of the pressure regulating mechanism, and a pneumatic tool equipped with the pressure regulator.

(Appendix A2)
The pneumatic tool according to Appendix A1, wherein the support portion moves when switching from the normal state to the load reduction state.

(Appendix A3)
The pneumatic tool according to Appendix A1 or Appendix A2, further comprising an operation input unit that allows a user to operate the biasing force of the elastic body, and that switches from the normal state to the load reduction state in conjunction with an operation input to the operation input unit.

(Appendix A4)
The pneumatic tool according to any one of Appendix A1 to Appendix A3, wherein the pressure-receiving member is a piston part that is disposed between the valve body and the elastic body and presses the valve body by the elastic body.

(Appendix A5)
Further provided with an inner cylindrical portion formed in a cylindrical shape,
the support portion is an outer cylindrical portion fitted onto the outer cylindrical portion and slidable along the inner cylindrical portion,
The pneumatic tool according to Appendix A4, wherein the elastic body passes through the inner cylindrical portion and faces the piston part.

(Appendix A6)
the valve body and the elastic body are disposed on a first shaft,
At least a portion of a flow path from the air intake to the pressure regulating mechanism extends along a second axis that is substantially parallel to the first axis,
The pneumatic tool according to any one of Appendix A1 to Appendix A5, wherein the elastic body is disposed at a position closer to the air intake port than the valve body.

(Appendix A7)
a load release region that faces the support portion and is a closed space partitioned on the opposite side of the valve body across the support portion;
a pressure passage capable of introducing compressed air upstream of the valve body into the load release region;
a pressure reduction flow path that can discharge the compressed air introduced into the load release area to the outside of the pressure adjustment mechanism;
A pneumatic tool according to any one of appendices A1 to A6, further comprising: a load release valve that opens and closes the pressure reduction flow path.

(Appendix A8)
Further, an operation input unit is provided that allows a user to operate the biasing force of the elastic body,
the load release valve opens in response to operation of the operation input unit,
The pneumatic tool according to Appendix A7, wherein the support portion moves to a side opposite to a side on which the valve body is located when the load release region is depressurized.

(Appendix A9)
The pneumatic tool according to any one of Appendix A1 to Appendix A6, wherein the pneumatic tool is a driving tool for driving out fasteners.

(Appendix A10)
A pressure regulator that adjusts the pressure of compressed air,
a valve element that opens and closes a flow path that connects an air intake port to which compressed air is supplied and an air outlet port from which pressure-regulated compressed air is taken out;
an elastic body that applies a biasing force to the valve body in a direction that opens the flow path;
a pressure-receiving member that receives air pressure downstream 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 comprising a load reduction mechanism that can 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 exerted.

(Appendix B1)
A pneumatic tool having a drive mechanism driven by compressed air supplied from an air intake,
an air chamber that stores the supplied compressed air;
a pressure regulating mechanism that adjusts the pressure of the compressed air in the air chamber,
The pressure regulating mechanism is
a valve body that opens and closes a flow path that connects the air intake port and the air chamber;
an elastic body that applies a biasing force to the valve body in a direction that opens the flow path;
a pressure-receiving member that receives air pressure in the air chamber and presses the elastic body in a direction that closes the flow path,
the pressure-receiving member is provided with a second pressure-receiving surface that is pressed in a direction to close the flow path by receiving air pressure in the air chamber,
The pressure-receiving member or a member abutting against the pressure-receiving member is provided with a third pressure-receiving surface that is smaller than the second pressure-receiving surface and is pressed in a direction to open the flow path by air pressure upstream of the valve body.

The pneumatic tool described in Appendix B1 makes it possible to provide a pneumatic tool in which the secondary pressure is less affected by fluctuations in the primary pressure.

(Appendix B2)
the valve body and the elastic body are disposed on a first shaft,
The pneumatic tool according to appendix B1, wherein at least a portion of a flow path from the air intake to the pressure regulating mechanism extends along a second axis that is substantially parallel to the first axis.

(Appendix B3)
The pneumatic tool according to Appendix B2, wherein a bypass flow path is formed across the second shaft and the first shaft, causing air pressure upstream of the valve body to act on the third pressure-receiving surface.

(Appendix B4)
The pneumatic tool according to any one of Appendix B1 to Appendix B3, wherein the pressure-receiving member is a piston component disposed between the valve body and the elastic body and pressing the valve body by the elastic body.

(Appendix B5)
The pneumatic tool according to any one of Appendix B1 to Appendix B4, further comprising: an inner cylindrical portion capable of contacting the pressure-receiving member; and an outer cylindrical portion capable of sliding along the inner cylindrical portion, wherein the third pressure-receiving surface is provided between the outer cylindrical portion and the inner cylindrical portion.

(Appendix B6)
A pneumatic tool according to any one of Appendix B1 to Appendix B5, wherein a flow path from the air intake to the pressure regulating mechanism has a portion extending in a first direction and at least partially overlaps with a region in which the elastic body is provided in the first direction.

(Appendix B7)
The pneumatic tool according to any one of appendices B1 to B6, wherein the pneumatic tool is a driving tool for driving out fasteners.

(Appendix C1)
A pneumatic tool having a drive mechanism driven by compressed air supplied from an air intake,
an air chamber that stores the supplied compressed air;
a pressure adjusting mechanism that adjusts the pressure of the compressed air in the air chamber,
The pressure regulating mechanism is
a valve body that opens and closes a flow path that connects the air intake port and the air chamber;
an elastic body that applies a biasing force to the valve body so as to open the flow path;
a pressure-receiving member that receives air pressure in the air chamber and applies a biasing force to the elastic body in a direction that closes the flow path;
A pneumatic tool comprising: a biasing force adjusting member configured to be able to change in stages the biasing force of the elastic body acting on the valve body.

(Appendix C2)
A pneumatic tool having a drive mechanism driven by compressed air supplied from an air intake,
an air chamber that stores the supplied compressed air;
a pressure adjusting mechanism that adjusts the pressure of the compressed air in the air chamber,
The pressure regulating mechanism is
a valve body that opens and closes a flow path that connects the air intake port and the air chamber;
an elastic body that applies a biasing force to the valve body so as to open the flow path;
a pressure-receiving member that receives air pressure in the air chamber and applies a biasing force to the elastic body in a direction that closes the flow path;
a biasing force adjusting member configured to change the length of the elastic body in stages.

In the pneumatic tools described in Appendix C1 or Appendix C2, the biasing force adjustment member may be a cam.

(Appendix C3)
The pneumatic tool according to appendix C1 or C2, wherein the biasing force adjusting member (or cam) has a rotation axis parallel to the central axis of the elastic body.

(Appendix C4)
The pneumatic tool according to any one of appendices C1 to C3, further comprising a member configured to be slidable on a surface of the biasing force adjusting member (or cam).

(Appendix C5)
The pneumatic tool according to any one of appendices C1 to C4, further comprising a second biasing force adjusting member configured to be able to change the biasing force of the elastic body acting on the valve body.

The second biasing force adjustment member may be an adjustment member configured to be able to further change the length of the elastic body by changing its position relative to the biasing force adjustment member (or cam).
Furthermore, the force adjusting member (or cam) may have a female thread, and the force adjusting member may have a male thread that screws into the female thread, and the length of the elastic body may be further changed by changing its position relative to the force adjusting member (or cam).

(Appendix C6)
an end cap surrounding at least the pressure regulating mechanism;
an operating unit for rotating the cam,
The pneumatic tool according to any one of appendices C1 to C5, wherein the operating portion has a portion that protrudes radially outward from the end cap when viewed in a direction parallel to the rotation axis of the force adjustment member (or cam).

(Appendix C7)
the elastic body is composed of a plurality of elastic bodies that apply a biasing force to the valve body so as to open the flow path,
The pneumatic tool according to any one of appendices C1 to C6, wherein the biasing force adjusting member is configured to be able to gradually change the biasing force of only some of the elastic bodies among the plurality of elastic bodies.

(Appendix C8)
The pneumatic tool according to any one of appendices C1 to C7, wherein the elastic body is disposed at a position closer to the air intake port than the valve body.

(Appendix C9)
the valve body and the elastic body are disposed on a first shaft,
The pneumatic tool according to appendix C8, wherein at least a portion of a flow path from the air intake to the pressure regulating mechanism extends along a second axis that is substantially parallel to the first axis.

(Appendix C10)
The pneumatic tool according to Appendix C8 or Appendix C9, characterized in that a flow path from the air intake to the pressure regulating mechanism has a portion extending in a first direction, and at least a portion of the flow path overlaps with a region in which the elastic body is provided in the first direction.

(Appendix C11)
The pneumatic tool according to any one of appendices C8 to C10, wherein the pressure-receiving member is a piston component disposed between the valve body and the elastic body and pressing the valve body by the elastic body.

(Appendix C12)
The pneumatic tool according to any one of appendices C8 to C11, further comprising an adjustment unit that adjusts the biasing force exerted by the elastic body.

(Appendix C13)
The elastic body is configured to apply a biasing force in a first direction to the valve body,
the pressure-receiving member is configured to apply a biasing force to the valve body in a second direction opposite to the first direction,
The pneumatic tool according to any one of appendices C8 to C12, wherein a flow path from the air intake to the pressure regulating mechanism includes a flow path that causes compressed air to travel in the first direction.

(Appendix C14)
The pneumatic tool according to any one of appendices C8 to C13, wherein the pneumatic tool is a driving tool for driving out fasteners.

(Appendix C15)
the valve body and the elastic body are disposed on a first shaft,
The pin, the cam, the elastic body, and the valve body are
The pneumatic tool described in Appendix C4, characterized in that the pin, the surface of the cam on which the pin slides, the elastic body, and the valve body are arranged in this order in a first direction parallel to the first axis.

(Appendix C16)
the valve body and the elastic body are disposed on a first shaft,
The pin, the cam, the elastic body, and the valve body are
The pneumatic tool described in Appendix C4, characterized in that the surface of the cam on which the pin slides, the pin, the elastic body, and the valve body are arranged in this order in a first direction parallel to the first axis.

(Appendix C17)
the pin is made of a first metal;
The pneumatic tool of claim C4, wherein the cam is made of a second metal having a hardness greater than the hardness of the first metal.

(Appendix C18)
a coil spring that applies a biasing force to the valve body in a direction that closes the flow path,
The pneumatic tool according to appendix C1 or C2, wherein the biasing force adjusting member (or cam) has a rotation axis that is coaxial with the central axis of the coil spring.

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 Expanded diameter portion 562 Reduced diameter portion 58 First 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 portion 81B Concave portion 82 Cam plate 84 Load release valve 84A Ring 86 Load release piston (an example of a "support portion")
86A First inner circumferential surface 86B Second inner circumferential surface 801 Inner dial 802 Outer dial 803 Elastic member 861 Inner cylinder portion 862 Outer cylinder portion (another example of a "support portion")
AR2 Secondary pressure area AR3 Load release area AR31 Pressurized flow path AR32 Reduced pressure flow path AR4 Open area AR5 open to atmospheric pressure 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 (5)

A pneumatic tool having a drive mechanism driven by compressed air supplied from an air intake provided for receiving a supply of compressed air from an outside ,
an air chamber that stores the supplied compressed air;
a pressure adjusting mechanism that adjusts the pressure of the compressed air in the air chamber,
The pressure regulating mechanism is
a valve body that opens and closes a flow path that connects the air intake port and the air chamber;
an elastic body that applies a biasing force to the valve body so as to open the flow path;
a pressure-receiving member that receives air pressure in the air chamber and applies a biasing force to the elastic body in a direction that closes the flow path;
Equipped with
the elastic body is disposed downstream of the valve body and at a position closer to the air intake than the valve body ,
the valve body and the elastic body are disposed on a first shaft,
At least a portion of a flow path from the air intake to the pressure regulating mechanism extends along a second axis that is substantially parallel to the first axis,
a flow path from the air intake to the pressure regulating mechanism having a portion extending in a first direction parallel to the first axis, and at least a portion of the flow path overlapping in the first direction with a region in which the elastic body is provided . 2. The pneumatic tool according to claim 1 , wherein the pressure-receiving member is a piston part disposed between the valve body and the elastic body, and presses the valve body with the elastic body. 3. The pneumatic tool according to claim 1, further comprising an adjustment unit for adjusting the biasing force exerted by the elastic body. the elastic body is configured to apply a biasing force in the first direction to the valve body,
the pressure-receiving member is configured to apply a biasing force to the valve body in a second direction opposite to the first direction,
The pneumatic tool according to any one of claims 1 to 3 , wherein a flow path from the air intake to the pressure regulating mechanism includes a flow path that causes compressed air to travel in the first direction. 5. The pneumatic tool according to claim 1, wherein the pneumatic tool is a driving tool for driving out fasteners.