Air Tools

Abstract

To provide a driving tool which enables reduction of its entire length.SOLUTION: A pneumatic tool comprises a driving mechanism, which is driven by compressed air supplied from an air intake port. The pneumatic tool has: an air chamber in which the supplied compressed air is stored; and a pressure regulation mechanism which regulates a pressure of the compressed air in the air chamber. The pressure regulation mechanism includes: a valve body which opens or closes a passage allowing communication between the air intake port and the air chamber; an elastic body which applies a biasing force to the valve body in a direction such that the passage is opened; and a pressure receiving member which receives an air pressure in the air chamber and applies a biasing force to the elastic body in a direction such that the passage is closed. The elastic body is disposed closer to the air intake port than the valve body.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to a pneumatic tool. [Background technology]

[0002] Known pneumatic tools that use compressed air as their driving source include driving machines that drive fasteners such as nails, screws, and nails into workpieces such as boards, wood, gypsum boards, steel plates, etc. The compressed air that serves as the driving source is generated, for example, by an air compressor and supplied to the driving machine via an air hose.

[0003] Such a driving tool includes, for example, a piston driven by compressed air, a driver attached to the piston, and a cylinder that houses the piston. When the piston is near its top dead center, compressed air is introduced into the upper chamber of the cylinder to move the piston and the driver attached to it toward its bottom dead center, allowing the driver to drive the fastener.

[0004] Here, 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 a 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 a 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.

[0005] Patent Document 1 describes a driving tool equipped with a valve mechanism that adjusts the pressure of compressed air. Specifically, the driving tool has a pressure adjustment mechanism provided between a pressure accumulator chamber and a driving compressed air chamber provided in the handle.

[0006] Patent Document 2 also describes a driving tool equipped with a valve mechanism that adjusts the pressure of compressed air. Specifically, the driving tool described includes a valve body that is movable in a first direction that closes a main flow path and in a second direction that opens the main flow path, a piston that is connected to the valve body and has a first pressure-receiving surface that receives pressure in the first direction from the compressed air and a second pressure-receiving surface and a third pressure-receiving surface that receive pressure in the second direction, and a spring that constantly urges the piston in the second direction. [Prior art documents] [Patent documents]

[0007] [Patent Document 1] Japanese Patent Application Laid-Open No. 2015-226952 [Patent Document 2] Japanese Patent Application Laid-Open No. 2016-215353 Summary of the Invention [Problem to be solved by the invention]

[0008] However, in such driving tools, a valve mechanism for reducing or regulating pressure (hereinafter collectively referred to as a "valve mechanism" or "pressure regulation mechanism") causes the driving tool to become larger. If a valve mechanism is to be disposed 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 disposed 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 have a shorter overall length.

[0009] 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 operating load of the pressure regulating mechanism is large, making it difficult for users to operate the pressure regulating mechanism. Therefore, an object of the present invention is 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.

[0010] Furthermore, the pressure of compressed air supplied to a pneumatic tool can fluctuate due to various factors. It is known that in a direct-acting pressure regulating mechanism, when the primary pressure, which is the pressure of the compressed air upstream of the pressure regulating mechanism, decreases, the secondary pressure, which is the pressure of the compressed air downstream of the pressure regulating mechanism, increases. Therefore, even if a desired pressure is set with the pressure regulating mechanism, the secondary pressure may be adjusted to a pressure different from the set pressure, resulting in variations in the fastener driving depth. Therefore, an object of the present invention is to provide a pneumatic tool in which the secondary pressure is less affected by fluctuations in the primary pressure. [Means for solving the problem]

[0011] The present disclosure relates to a pneumatic tool including a drive mechanism driven by compressed air supplied from an air intake. The pneumatic tool includes an air chamber that stores the supplied compressed air, and a pressure regulating mechanism that adjusts the pressure of the compressed air in the air chamber. The pressure regulating mechanism includes a valve 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 so as 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 being located closer to the air intake than the valve body.

[0012] In the above aspect, the valve body and the elastic body may be disposed 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.

[0013] In the above aspect, the flow path from the air intake to the pressure adjustment mechanism may have a portion that extends in the first direction, and at least a portion of the flow path may overlap with the region in which the elastic body is provided in the first direction.

[0014] In the above aspect, the pressure-receiving member may be a piston component that is disposed between the valve body and the elastic body and presses the valve body with the elastic body.

[0015] In the above aspect, an adjustment unit that adjusts the biasing force exerted by the elastic body may be further provided.

[0016] In the above aspect, the pneumatic tool may be applied to a driving tool that drives fasteners. Furthermore, the elastic body may be configured to apply a biasing force to the valve body in a first direction, 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 propels compressed air in the first direction. Note that the present invention may also be applied to compressed fluids other than compressed air.

[0017] 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. A plug, an elastic body, a piston component pressed by the elastic body, and a valve body pressed by the piston component are arranged in this order along a first direction from the outside to the inside of the pneumatic tool. A flow path is also formed that connects a valve chamber in which the valve body is arranged to a flow path in the plug.

[0018] The present disclosure also provides a pneumatic tool having a drive mechanism driven by compressed air supplied from an air intake port, the drive mechanism 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 including 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.

[0019] In the above aspect, the support portion may move when switching from the normal state to the load reducing state.

[0020] In the above aspect, an operation input unit may be further provided that allows a user to operate the biasing force of the elastic body, and the normal state may be switched to the load reduction state in conjunction with an operation input to the steering input unit.

[0021] 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 outer surface of 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.

[0022] In the above aspect, the valve body and the 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 approximately parallel to the first axis, and the elastic body may be arranged in a position closer to the air intake than the valve body.

[0023] In the above aspect, the pressure regulator may have a load release region which is a closed space facing the support portion and partitioned on the opposite side of the valve body across the support portion, a pressurized flow path which can introduce compressed air upstream of the valve body into the load release region, a reduced pressure flow path which can discharge the compressed air introduced into the load release region to the outside of the pressure adjustment mechanism, and a load release valve which opens and closes the reduced pressure flow path.

[0024] 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 to the side where the valve body is located as the load release region is depressurized.

[0025] 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 inlet to which compressed air is supplied and an air outlet from which pressure-adjusted compressed air is taken out; 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 inlet 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 the 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 the direction of opening the flow path by air pressure upstream of the valve body.

[0026] In the above aspect, the valve body and the elastic body may be disposed 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.

[0027] In the above aspect, a bypass flow path that causes air pressure upstream of the valve body to act on the third pressure-receiving surface may be formed across the second shaft and the first shaft.

[0028] In the above aspect, the pressure-receiving member may be a piston component that is disposed between the valve body and the elastic body and presses the valve body with the elastic body.

[0029] In the above aspect, the pressure receiving member may further include an inner cylindrical portion that can abut against 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. [Effects of the Invention]

[0030] According to the present invention, it is possible to provide a driving tool that can have a shorter overall length. Alternatively, it is 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. Alternatively, it is possible to provide a pneumatic tool in which the secondary pressure is less affected by fluctuations in the primary pressure. [Brief explanation of the drawings]

[0031] [Figure 1] 1 is a cross-sectional view of a nail driving tool according to an embodiment. [Figure 2] 1 is a view of a front end of a regulator before being assembled to a nail driving tool according to an embodiment. [Figure 3A] 3 is a cross-sectional view taken along the line AA in FIG. 2. [Figure 3B] 3 is a cross-sectional view of FIG. 2 taken along line B-B. [Figure 3C] 3 is a cross-sectional view taken along CC in FIG. 2. [Figure 3D] 3 is a cross-sectional view taken along the line DD in FIG. 2. [Figure 4] FIG. 2 is a partially enlarged view of the cross section taken along line AA when the valve opens in the intake direction. [Figure 5] FIG. 2 is a partially enlarged view of the AA cross section when the valve opens in the exhaust direction. [Figure 6A] 3D is an enlarged view of the dial shown in FIG. 3C viewed from a first direction. FIG. [Figure 6B] 6B is an enlarged view showing a state in which an operation is input to the dial shown in FIG. 6A. FIG. [Figure 7] FIG. 6C is a perspective view of the dial shown in FIG. 6B seen obliquely. [Figure 8] FIG. 2 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. [Figure 9] 9 is a cross-sectional view showing a modified example of the load reducing mechanism shown in FIG. 8. FIG. [Figure 10] FIG. 2 is a partially enlarged view of the cross section taken along line AA when the valve is closed. [Figure 11] 11 is a cross-sectional view showing a first modified example of the primary pressure balance mechanism shown in FIG. 10. FIG. [Figure 12] 11 is a cross-sectional view showing a second modified example of the primary pressure balance mechanism shown in FIG. [Figure 13A] 1 is a cross-sectional view of a nail driving tool according to an embodiment. [Figure 13B] 1 is a cross-sectional view of a nail driving tool according to an embodiment. [Figure 14A] 1 is a cross-sectional view of a nail driving tool according to an embodiment. [Figure 14B] 1 is a cross-sectional view of a nail driving tool according to an embodiment. [Figure 15] FIG. 2 is a view of the nail driving tool 110 as seen from a first direction. [Figure 16] FIG. 2 is a perspective view showing a component configuration of a pressure regulating mechanism including a cam according to an embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0032] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The following embodiments of the present invention will be described 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.

[0033] Hereinafter, a pneumatic tool according to a first embodiment will be described. Fig. 1 is a cross-sectional view of a nailing tool (an example of a "pneumatic tool") according to the first embodiment. For convenience, the upward and downward directions on the paper surface in Fig. 1 may be simply referred to as the upward and downward directions, and the leftward and rightward directions on the paper surface 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 Fig. 1, the second direction D2 side is the grip end side of the grip 32, and the first direction D1 side is the main body side.

[0034] [An example of the overall configuration of a pneumatic tool]

[0035] A nail driving tool (an example of a "driving tool") is a pneumatic tool that uses compressed air as a drive source to drive nails (an example of a "fastener"). The nail driving tool 10 includes a drive mechanism 20 driven by compressed air and a regulator 50 (an example of a "pressure adjustment mechanism") for supplying compressed air to the drive mechanism.

[0036] The drive mechanism 20 includes 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 enter and strike the nail, and a magazine 30 that houses nails that are supplied to the nose 28.

[0037] The nail driving tool 10 further includes a grip 32 that is held by a 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 the air to the air chamber 34.

[0038] In this nail driving tool 10, when a user presses the trigger 38, the main valve 36 opens and the compressed air in the air chamber 34 flows 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 the nail downward.

[0039] [Basic configuration of pressure regulation mechanism]

[0040] The configuration of the regulator 50 (an example of a "pressure regulating mechanism") will be described below with reference to the drawings. FIG. 2 is a front view of the regulator 50 alone as viewed from the second direction D2 before it is assembled to the nail driving tool 10. After assembly, the regulator 50 corresponds to the view of the regulator 50 as viewed from inside the nail driving tool 10 in the second direction D2 in FIG. 1. FIGS. 3A to 3D are cross-sectional views taken along lines AA, BB, CC, and DD in FIG. 2, respectively. FIG. 4 is a partial enlarged view of the cross-sectional view taken along line AA when the compressed fluid in the valve chamber 64 flows into the secondary pressure region AR2, and FIG. 5 is a partial enlarged view of the cross-sectional view taken along line AA when the compressed fluid in the secondary pressure region AR2 is exhausted.

[0041] 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 body 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 body 52 in the second direction D2, and a main spring 54 (an example of an "elastic body") that is arranged on the second direction D2 side of the valve body 52 and applies a force to the valve body 52 in the first direction D1.

[0042] 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.

[0043] The regulator 50 includes, in addition to the adjusting screw 66, a dial 80, a spacer 72, a cam plate 82, a load release valve 84 (shown in FIG. 3C ), and a load release piston 86, which serve 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.

[0044] The plug 62 is a component for receiving a supply of compressed air from the outside. One end of the plug 62 is configured to be connectable to an air hose (not shown). Therefore, compressed air generated by an air compressor can be supplied to the plug 62 via the air hose. The other end of the plug 62 is connected to the first end cap 58. At this time, the flow path formed in the plug 62 communicates with the first flow path CH1 formed in the first end cap 58.

[0045] The plug 62 is attached on the second axis AX2 (so as to be coaxial with the second axis AX2). A first axis AX1 and a second axis AX2 (described later) are two spaced apart, substantially parallel axes. The first axis AX1 and the second axis AX2 are parallel to the first direction D1 and the second direction D2.

[0046] 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 disc 52 is disposed. This first flow path CH1 supplies compressed air supplied from the plug 62 to the valve chamber 64. As shown in Fig. 3A, the valve chamber 64 is disposed at a position further in the first direction D1 than the end of the first end cap 58 in the second direction D2 and on the first axis AX1 spaced apart in the direction 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.

[0047] In this embodiment, the portion of the first flow path CH1 that travels in the first direction D1 includes a flow path that is 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, and may be formed, for example, to form an acute angle with respect to the first direction D1.

[0048] The valve element 52, together with the piston 56, is a component for adjusting the secondary pressure downstream of the valve element 52. Specifically, when the secondary pressure on the downstream side drops, the valve element 52 moves in the first direction D1 to allow the upstream compressed fluid having a primary pressure to flow downstream, thereby increasing the secondary pressure until it reaches 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.

[0049] 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.

[0050] The outer edge of the top surface of the circular truncated cone portion 52A is supported by the valve seat, and 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 other parts 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.

[0051] The valve element 52 is disposed on the first axis AX1 (so as to be coaxial with the first axis AX1) within the valve chamber 64. Because the first flow path CH1 is connected to the valve chamber 64, a 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 the primary pressure.

[0052] 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 a 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.

[0053] 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, it can be said that the main spring 54 presses 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 area 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 that is 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 regulating action including the valve disc 52 will be described in detail later.

[0054] When the secondary pressure is in an equilibrium state where it reaches a predetermined pressure, a portion of the top surface of the valve disc 52 is in close contact with the valve seat, and therefore the valve chamber 64 (an example of a "primary pressure region") does not communicate with 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 as described below (see FIG. 4), thereby connecting the valve chamber 64 with the downstream secondary pressure region AR2 and allowing the compressed fluid having the primary pressure to flow downstream, thereby increasing the secondary pressure.

[0055] The piston 56 transmits the biasing force of the main spring 54 to the valve element 52 to press the valve element 52 in the first direction D1. When the secondary pressure exceeds a predetermined pressure, the piston 56 exhausts the compressed fluid in the secondary pressure region AR2 to reduce the secondary pressure.

[0056] 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 communicates with a second flow path CH2 (an example of a "secondary pressure flow path") for supplying compressed fluid to the drive mechanism 20, and 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 that 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 receives air pressure from the air chamber 34 and is pressed in a direction that closes the flow paths CH1 and CH2.

[0057] 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. The cylindrical space is maintained at atmospheric pressure.

[0058] Furthermore, the end of the piston 56 in the first direction D1 extends cylindrically about the first axis AX1 and abuts against the top surface of the valve body 52. ​​A through-hole H that communicates with a cylindrical space maintained at atmospheric pressure is formed within this cylindrically extending portion.

[0059] When the secondary pressure is in an equilibrium state where it reaches a predetermined pressure, the biasing force from the main spring 54, which applies a force to the piston 56 in the first direction D1, is balanced with the force from the compressed air of the secondary pressure and the valve body 52, which applies a force to the piston 56 in the second direction D2, so that the piston 56 does not move.

[0060] However, when the secondary pressure drops below a predetermined pressure, the force with which the compressed air having the 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 FIG. 4). This allows the valve chamber 64, which is the primary pressure region, to communicate with the secondary pressure region AR2, allowing compressed air having the primary pressure to flow downstream, thereby 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 an equilibrium state.

[0061] On the other hand, when the secondary pressure rises above the 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 does not move in the second direction D2 (see FIG. 5).

[0062] A through-hole H is formed in 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 to a space maintained at atmospheric pressure, as shown by the arrow in FIG. 5 . This allows the secondary pressure to be reduced. When the secondary pressure is reduced to a predetermined pressure, the piston 56 returns to the first direction D1, thereby achieving an equilibrium state. Through the above-described 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 having other configurations.

[0063] The main spring 54 presses the valve element 52 in the first direction D1 via the piston 56. The main spring 54 is disposed 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, and therefore is configured to be able to press the valve element 52 with a force stronger than that of the valve spring 68.

[0064] The end of the main spring 54 facing in the first direction D1 abuts against the piston 56, and the end of the main spring 54 facing in the second direction D2 is supported by the adjustment screw 66. Therefore, 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, it is possible to adjust the initial load of the main spring 54.

[0065] The adjusting screw 66 presses the main spring 54 in the first direction D1. The adjusting screw 66 is disposed on the first axis AX1 (so as to be coaxial with the first axis AX1). That is, the valve body 52, the piston 56, the main spring 54, and the adjusting screw 66 are disposed in this order on the first axis AX1 in a 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 disposed on the second axis AX2.

[0066] 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 or by inserting a washer or the like. If the initial load of the main spring 54 fluctuates toward a lower pressure, the pneumatic tool will malfunction, and if it fluctuates toward a higher pressure, the amount of compressed air consumed by the drive mechanism will increase, thereby reducing the benefit of incorporating a regulator. However, in the nail driving tool 10 according to this embodiment, the adjustment screw 66 is disposed 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 nail driving tool 10.

[0067] In other words, because springs have large variations in load characteristics, simply assembling regulators in the same way results in regulators with different load characteristics being installed on each pneumatic tool. Therefore, after assembling the regulator, the variations in the regulator's load characteristics are eliminated by inserting washers or adjusting the initial load adjustment screw.

[0068] When adjusting the load characteristics, one end of the spring must maintain contact with the piston, so a pressure regulating mechanism must be provided on the other end of the spring. However, in conventional pneumatic tools, the spring is provided further inward than the piston, so the pressure regulating mechanism is also provided further inward than the piston. In order to operate the pressure regulating mechanism in this state, it may be possible to expose the operating portion of the pressure regulating mechanism from the pneumatic tool, but this would require drilling a hole in the grip used as an air chamber, which is not practical.

[0069] 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 port, so that it is possible to easily adjust the variation in the load characteristics of the main spring 54.

[0070] Furthermore, the valve body 52, the piston 56, and the main spring 54 are disposed on a first axis AX1, while the plug 62, which is located upstream of the valve body 52, is disposed on a second axis AX2 different from the first axis AX1. As a result of this configuration, the plug 62 can be moved further toward the first direction than in the past, 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 FIG. 1).

[0071] In this case, in the first direction D1, the region 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 where the first flow path CH1 is provided at least partially overlap. In particular, in the regulator 50 shown in this embodiment, in the first direction D1, the region where the main spring 54 is provided and the region where the piston 56 is provided are encompassed by the region where 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, and the overall length of the nail driving tool 10 can be shortened.

[0072] Furthermore, because there is more space on the second axis AX2, it is possible to provide a large air filter 60 on the second axis AX2 (so as to be coaxial with the second axis AX2), as shown in Fig. 3A. As a result, it is possible to reduce the possibility that dust will get inside regulator 50 and become caught in valve element 52, etc., causing regulator 50 to malfunction. However, air filter 60 may not be provided or may be made smaller, and plug 62 may be disposed further toward the first direction D1.

[0073] [Load reduction mechanism]

[0074] The pressure adjustment mechanism and load reduction mechanism of the regulator 50 will be described below with reference to Figures 6A to 9. The pressure adjustment mechanism enables 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 according to this embodiment makes it possible to temporarily reduce the load on the user when adjusting the pressure.

[0075] First, an overview of each mechanism will be described, followed by a description of the specific configuration of each mechanism. In addition to the valve element 52, main spring 54, and pressure-receiving member described above, the pressure adjustment mechanism further includes a dial 80, a spacer 72, and an adjusting screw 66. The load reduction mechanism also includes a cam plate 82, a load release valve 84, and a load release piston 86.

[0076] The load release piston 86 is an example of a support portion that supports the end portion of the main spring 54 in the second direction D2, and is located closer to the second direction D2 than the piston 56. The load release piston 86 can move relative to the piston 56. When an operation is input to an operation input portion such as the dial 80, the load release piston 86 moves toward the second direction D2, which is opposite to the first direction D1 on which the valve body 52 is located.

[0077] The pressure adjustment mechanism changes the position of a "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 portion between the spacer 72, which rotates together 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 can be displaced in the axial direction depending on the rotational position of the dial 80 (spacer 72).

[0078] The component that determines the position of the second direction D2 end of the main spring 54 is configured integrally 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 integrally 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 component that determines the position of the second direction D2 end of the main spring 54 in the direction that compresses the spring (D1 direction).

[0079] The load reduction mechanism extends the main spring 54 when the dial 80 is turned. When the main spring 54 extends, it is possible to weaken the biasing force acting from the main spring 54 on the adjustment screw 66, 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 the load release piston 86 is normally 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).

[0080] 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 to the adjusting screw 66. Because the adjusting 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 will be outlined below.

[0081] FIG. 6A is an enlarged view of the dial 80 shown in FIG. 3C as viewed from the first direction D1. FIG. 6B is an enlarged view showing a state in which the dial 80 shown in FIG. 6A is rotated to input an operation. As shown in FIGS. 6A and 6B, the dial 80 is configured to be rotatable about a first axis AX1. The dial 80 includes an inner dial 801 formed in a substantially disk shape, an outer dial 802 surrounding the inner dial 801 from the outside in the radial direction, and an elastic member 803 connecting the inner dial 801 and the outer dial 802. The elastic member 803 is formed in a cylindrical shape from, for example, rubber. Recesses for accommodating 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.

[0082] The inner dial 801 is fixed to the aforementioned adjusting screw 66, and is fixed to the load release piston 86 via the adjusting screw 66. When the load release valve 84, which will be described later, is not opened, the biasing force from the main spring 54 acting on the inner dial 801 is large. Therefore, when an attempt is made to rotate the dial 80 by pinching the outer dial 802, the inner dial 801, which has a large 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.

[0083] Figure 7 is a perspective view of the dial 80 shown in Figure 6B, viewed from an angle. As shown in Figure 7, the dial 80 abuts against a cam plate 82, and is configured so that when an outer dial 802 of the dial 80 rotates, the cam plate 82 is displaced in a first direction D1. Specifically, a plurality of protrusions 81A are periodically provided rotationally symmetrically about the first axis AX1 on the surface of the outer dial 802 that abuts against the cam plate 82.

[0084] Meanwhile, a plurality of recesses 81B are provided at the same interval and rotationally symmetrical about the first axis AX1 on the surface of cam plate 82 that abuts against outer dial 802. With this configuration, as outer dial 802 rotates, the position of cam plate 82 in first direction D1 can be displaced depending on whether or not convex portions 81A and concave portions 81B face each other.

[0085] 7, the cam plate 82 abuts against the second direction D2 end of the load release valve 84. Therefore, as the cam plate 82 is displaced in the first direction D1, the load release valve 84 is displaced in the first direction D1. When the load release valve 84 is displaced in the first direction D1, it switches from a closed state to an open state.

[0086] 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 passage AR32 communicating therewith from the open area AR4, which is open to atmospheric pressure. The load release area AR3 communicates with the first passage CH1 via the pressure reduction passage AR31 (see FIG. 3A), so the load release area AR3 and the pressure reduction passage 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 the pressure is reduced.

[0087] Figure 8 is a partially enlarged view of the AA cross section when the main spring 54 is extended to its natural length in the open 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 the load release area AR3 and the pressure reduction flow path AR32 communicating with it are in an open state.

[0088] 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 on the adjusting screw 66 from the main spring 54.

[0089] 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 portion and the concave portion face each other again, the cam plate 82 is displaced in the second direction D2. As a result, the load release valve 84 is also displaced in the second direction D2 and returns to 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.

[0090] 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-reducing passage AR32 communicating with it are again sealed against the open area AR4, which is open to atmospheric pressure. The load-release area AR3 is connected to the first passage CH1 through the pressure-reducing passage AR31 shown in FIG. 3A, so the pressure in the load-release area AR3 rises to the primary pressure. As a result, the load-release piston 86 is displaced in the first direction D1.

[0091] 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 integral structure. However, the spacer 72 and the load release piston 86 may 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.

[0092] The position of the end of the main spring 54 in the second direction D2 also displaces in the first direction D1. At this time, a slope provided on the spacer 72, which rotates together 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 weakens the compressive force of the main spring 54, enabling pressure adjustment. Furthermore, the structure is not limited to one in which the slope allows for stepless adjustment of the amount of displacement; the engagement portion may be formed in a stepped shape to allow for stepwise adjustment. Increasing the inclination angle of the slope increases the amount of displacement when the dial 80 is rotated a predetermined angle.

[0093] Fig. 9 is a cross-sectional view showing a modified example of the load reduction mechanism shown in Fig. 8. This modified example 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 an outer cylindrical portion 862 configured as a support portion. The inner cylindrical portion 861 is formed in a tubular shape into which the main spring 54 is inserted. The shape of the inner cylindrical portion 861 may be cylindrical or rectangular.

[0094] 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. Even with the configuration of the modified example shown in FIG. 9, the operating load of the pressure adjustment mechanism can be reduced, similar to the configuration shown in FIG. 8.

[0095] [Primary pressure balance mechanism]

[0096] The primary pressure balance mechanism provided in regulator 50 will be described below with reference to Figures 10 to 12. It is known that when the primary pressure drops, valve element 52 is pushed toward the primary side, opening the valve and increasing the secondary pressure. The primary pressure balance mechanism is configured to apply the primary pressure to piston 56, constantly applying a load in the direction D1 to piston 56, thereby reducing the effect of fluctuations in the primary pressure on the secondary pressure by offsetting at least a portion of the fluctuations in the primary pressure.

[0097] Fig. 10 is a partially enlarged view of the AA cross section when the valve is closed. As shown in Fig. 10, the primary pressure balance mechanism includes flow paths CH3 and AR51 that introduce compressed fluid on the primary side (upstream side of the valve body 52) to the secondary side (downstream side of the valve body 52), and a third pressure-receiving surface F that receives pressure from the compressed fluid introduced from the primary side.

[0098] In the illustrated example, the piston 56 includes a cylindrical expanded diameter portion 561 and a cylindrical reduced diameter portion 562 having a smaller diameter than the expanded diameter portion 561. In the piston 56, the expanded diameter portion 561 is provided on the first direction D1 side, and the 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 the expanded diameter portion 561 and the reduced diameter portion 562. The shape of the third pressure-receiving surface F is not limited to the illustrated example. For example, when the cylinders 561 and 562 have the same diameter, the outer peripheral surface of the cylinder 562 on the second direction D2 side may be scraped away to form a notched third pressure-receiving surface F.

[0099] 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 a primary pressure balance area AR5. A flow path CH3 that penetrates the first inner circumferential surface 86A is formed in the load release piston 86. The flow path CH3 is connected to a bypass flow path (not shown) that branches off from the primary-side 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 the flow path CH3. The third pressure-receiving surface F receives air pressure upstream of the valve body 52 and is pressed in a direction to open the flow paths CH1 and CH2.

[0100] 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 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 larger 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 formed smaller than the second pressure-receiving surface (the surface of the piston 56 facing the first direction D1).

[0101] [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.

[0102] 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 urges the end of the piston 56 on the second direction D2 side in the first direction D1. Even in this modified primary pressure balance mechanism, as in the primary pressure balance mechanism of the present embodiment, the primary pressure is applied to the piston 56, and a load in the D1 direction is always applied to the piston 56, thereby reducing the effect of fluctuations in the primary pressure on the secondary pressure.

[0103] [Second Modification]

[0104] Fig. 12 is a cross-sectional view showing a second modified example of the primary pressure balance mechanism shown in Fig. 10. The second modified example differs from the present 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.

[0105] The inner cylindrical portion 861 is configured to be able to come into contact with the piston 56, which is a pressure-receiving member. A primary pressure balance area AR5 is defined in 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 in this modified primary pressure balance mechanism, as in the primary pressure balance mechanism of the present embodiment, the primary pressure is applied to the piston 56, and a load in the D1 direction is always applied to the piston 56, thereby reducing the effect of fluctuations in the primary pressure on the secondary pressure.

[0106] With the above-described 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 load release piston 86 may be further displaced in the first direction D1 by the slope provided on the spacer 72. With this configuration, it is possible to adjust the secondary pressure in multiple stages. As described above, according to the present invention, it is possible to provide a pneumatic tool that allows for a reduced operating load of the pressure adjustment mechanism.

[0107] 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 in which the load characteristics vary greatly from one another, it is customary to eliminate the variation in the load characteristics of the regulator after assembling the regulator 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, it is possible to easily adjust the position of the end of the main spring 54 in the second direction D2 by, for example, removing the dial 80 and changing the position of the adjustment screw 66. As a result, it is possible to easily adjust the variation in the load characteristics of the main spring 54.

[0108] 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 (FIG. 3A) of the regulator 50 in the first direction D1 compared to the prior art, 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 above the second axis AX2, it is possible to provide a large air filter 60 on the second axis AX2 (so as to be coaxial with the second axis AX2), as shown in FIG. 3A. This makes it possible to reduce the possibility that the regulator 50 will not operate normally.

[0109] The present invention can be applied to pneumatic tools in general, such as air nailers, air drivers, and pneumatic screw drivers. The present invention may also be applied to compressed fluids other than compressed air. Furthermore, various modifications of the present invention are possible without departing from the spirit of the present invention. For example, some components in the embodiments may be replaced with other known configurations that perform similar functions within the scope of the ordinary creativity of a person skilled in the art.

[0110] [Second embodiment] A pneumatic tool according to the second embodiment will be described below. However, components that a person skilled in the art would understand to have the same or similar configuration or function 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, and the 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 the second embodiment when set to low pressure and high pressure, respectively. Figure 15 is a view of the nail driving tool 110 as seen from a first direction D1.

[0111] The components of the nail driving tool 110 other than the regulator 150 are the same as those of the nail driving tool 10, and therefore a description thereof will be omitted.

[0112] [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.

[0113] 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 arranged to surround 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, and further 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.

[0114] 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 disposed at a position 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 apart perpendicularly from the second axis AX2.Therefore, the first flow path CH1 is similar to the regulator 50 in that it has a portion that causes compressed air to advance in the first direction D1 and a portion that causes compressed air to advance from the second axis AX2 to the first axis AX1 (including the case where it has a flow path that is inclined so as to advance in the second direction D2 while advancing in the first direction D1).

[0115] Furthermore, the valve element 152 is a component that, together with the piston 156, adjusts the secondary pressure downstream of the valve element 152; when the downstream secondary pressure drops, the valve element 152 moves in a first direction D1, thereby opening the flow path connecting the air intake and the air chamber, and allowing the compressed fluid upstream of the valve element 152, which has a primary pressure, to flow downstream, thereby increasing the secondary pressure; and when the downstream secondary pressure rises, the valve element 152 moves in a second direction D2, thereby closing the flow path and decreasing the secondary pressure. More specifically, the valve body 152 is arranged in 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 the 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 body 152 facing the second direction D2 is similar to the regulator 50 in that the surface of the valve body 152 facing the second direction D2 is exposed to a compressed fluid having a secondary pressure, thereby pressing the valve body 152 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 spring force corresponding to the compression amount of the main spring 154 arranged on the first direction D1 side of the valve body 152.

[0116] In addition, the present embodiment is similar to the regulator 50 in that a valve seat is arranged in the second direction D2 relative to the valve element 152, thereby restricting movement of the valve element 152 in the second direction D2 by the valve seat; a surface of the piston 156 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, thereby pressing the piston 156 in the second direction D2 (in a direction to close the flow path) by the compressed fluid having the secondary pressure; and the valve element 152, piston 156, and main spring 154 are arranged in this order coaxially with the first axis AX in the first direction D1. The 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 the second flow path CH2. The mechanism by which the regulator 150 regulates the secondary pressure is the same as that in the first embodiment, and therefore a description thereof will be omitted.

[0117] [Regulator detailed configuration] The regulator 50 according to the first embodiment is configured such that the user can 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 such 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 such that the length of the main spring 154 can be changed in four levels using the 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 stepwise changeable secondary pressure may be configured to vary depending on the magnitude of the primary pressure.

[0118] 13(B) and other figures, regulator 150 includes: operating lever 180 rotatable by user operation; cam 182 rotatable by operating lever 180; pin 184 for moving cam 182 in the direction of the rotational axis by sliding against the surface of cam 182; spring adjuster 186 (an example of a "pressure adjustment member" and a "second biasing force adjustment member"; hereinafter, this may be referred to as the "pressure adjustment member 186" or the "pressure adjustment shaft 186") configured to be movable in conjunction with cam 182 in the direction of the rotational axis; and pressure adjustment spacer 188 supporting the second direction D2 end of main spring 154, and configured to be movable in the direction of the rotational axis as spring adjuster 186 moves in the direction of the rotational axis.

[0119] With this configuration, when the user rotates operating lever 180, cam 182, which is rotated by operating lever 180, converts the rotational motion into translational motion, thereby translating pressure adjustment spacer 188 that supports main spring 154. This makes it possible to set the length of main spring 154 supported by pressure adjustment spacer 188 in stages, and therefore to set the secondary pressure.

[0120] 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 as to have a rotation axis on the first axis AX. As shown in FIG. 15, the operating lever 180 is provided with a protrusion 180A that protrudes radially outward from 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. Moreover, because the set pressure of the secondary pressure is determined according to the position of the protrusion 180A, as will be described later, the user can visually grasp whether the set pressure is high or low based on the position of the protrusion 180A.

[0121] Operating lever 180 has metal portion 180B that engages with cam engagement portion 182C (FIG. 16) formed in a polygonal shape at the tip of metal cam 182. By providing plate-shaped metal portion 180B so that it engages (contacts) with metal cam engagement portion 182C, it becomes possible to rotate cam 182 in conjunction with the rotation of operating lever 180.

[0122] Furthermore, operating lever 180 is provided with nut 180C ( FIG. 13 ) that screws onto the male thread provided on pressure adjustment member 186. As will be described later, cam 182 screws onto the male thread provided on pressure adjustment member 186. Thus, a double-nut structure in which cam 182 that screws onto a region on the base end side of the male thread formed on pressure adjustment member 186 functions as a first nut, and nut 180C that screws onto a region on the tip end side of the male thread formed on pressure adjustment member 186 functions as a second nut makes it possible to prevent pressure adjustment member 186, cam 182, and operating lever 180 from loosening from one another.

[0123] Cam 182 (an example of a "biasing force adjusting 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 so that its central axis is on first axis AX when biased in second direction D2.

[0124] 16 is a perspective view of a component including cam 182. As shown in the drawing, cam 182 in this embodiment includes an annular tubular portion 182A having an internal thread formed on its inner circumferential surface, a bottom portion 182B that expands in the outer diameter direction at the end of tubular portion 182A in the first direction D1, and a cam engagement portion 182C for engaging with operating lever 180 at the end of tubular portion 182A in the 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 cam 182 and are arranged 180 degrees rotationally symmetrically about the central axis on the surface of bottom portion 182B facing the axial direction (second direction D2).

[0125] By biasing cam 182 in the second direction D2 so that the first direction D1 end (tip) of pin 184 attached to the body of regulator 150 abuts against the surface of any one of these step surfaces 182B1 to 182B4, it becomes possible to move cam 182 in the first direction D1 or the second direction D2 depending on which of step surfaces 182B1 to 182B4 the pin 184 abuts against. In this embodiment, the steps between step surface 182B1, step surface 182B2, and step surface 182B3 are relatively small, and the step between step surface 182B3 and step surface 182B4 is relatively large.

[0126] For example, when the primary pressure is 2.3 MPa and pin 184 abuts against step surface 182B1, the secondary pressure is adjusted to 1.4 MPa. Similarly, when pin 184 abuts against step surfaces 182B2 to 182B4, the secondary pressures are 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.

[0127] 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 against the step surfaces.

[0128] The number of steps provided on the cam 182 may be two or more. If the number of steps is two or more, it becomes possible to set the secondary pressure in two or more stages.

[0129] In addition, in this embodiment, two pins 184, pin 184A and pin 184B, are prepared, and four step surfaces 182B1 to 182B4 are provided at 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 cam 182, or the number of pins may be three and multiple step surfaces may be provided at 120-degree rotational symmetry.

[0130] The pin 184 (an example of a "member configured to be slidable on the surface of the cam") moves the cam 182 in the first direction D1 or the second direction D2 by sliding against the stepped surfaces 182B1 to 182B4 of the cam 182. 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 any 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. Note that instead of the pin 184, a member such as a steel ball may be provided slidably on the surface of the cam.

[0131] 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 stepped surface 182B1, the other pin 184B is arranged rotationally symmetrically with the stepped surface 182B1 by 180 degrees and abuts against a stepped surface having the same height as the stepped surface 182B1. By abutting the two pins 184A and 184B against stepped surfaces having the same height in this way, it is possible to move the cam 182 in the first direction D1 or the second direction D2 in a stable posture.

[0132] Preferably, both pin 184 and cam 182 are made of metal, and more preferably, cam 182 is made of metal having a hardness greater than that of the metal making up pin 184. By providing this difference in hardness, it becomes possible for pin 184 to be the main part that wears out due to sliding contact. Therefore, regulator 150 can be maintained by replacing only pin 184 out of cam 182 and pin 184.

[0133] Pressure adjustment member 186, which is a spring adjuster, is a component that moves together with cam 182 in the first direction D1 or the second direction D2 to change the length of main spring 154. Pressure adjustment member 186 according to this embodiment is formed in a cylindrical shape extending in the second direction D2 so that its central axis is aligned with first axis AX when biased in the second direction D2 by main spring 154. An expanded-diameter portion 186A extending outward is provided at the end of pressure adjustment member 186 in the first direction D1. The end of main spring 154B engages with the bottom surface of expanded-diameter portion 186A facing the first direction D1, thereby biasing pressure adjustment member 186 and cam 182, which is fixed by being threadedly engaged with pressure adjustment member 186, in the second direction D2. An external thread is formed in the middle of pressure adjustment member 186 to threadably engage with an internal thread formed on the inner circumferential surface of cylindrical portion 182A of cam 182. A second male thread is formed on the end of pressure adjustment member 186 facing in the second direction D2, and is threadedly engaged with nut 180C provided inside operating lever 180. Note that the first male thread and the second male thread do not necessarily have to be formed separately from each other, and may be formed continuously or integrally, for example.

[0134] Furthermore, regulator 150 according to this embodiment allows fine adjustment of the length of main spring 154 by changing the relative positional relationship between pressure regulating member 186 and cam 182. When pressure regulating member 186 is biased in second direction D2, the bias prevents the male thread of pressure regulating member 186 from loosening easily from the female thread of cam 182. Furthermore, the double-nut structure formed by the engagement with the female thread of nut 180C further reduces loosening resistance. However, because pressure regulating member 186 and cam 182 are threadedly engaged, the relative position of pressure regulating member 186 with respect to cam 182 can be changed by rotating pressure regulating member 186 relative to cam 182. Furthermore, when pressure regulating member 186 is not biased, such as during the manufacture of regulator 150, the relative position of pressure regulating member 186 with respect to cam 182 can be easily changed by rotating pressure regulating member 186 relative to cam 182. This configuration also makes it possible to easily adjust for variations in load characteristics due to individual differences in the main springs 154 or changes over time.

[0135] Main spring 154 presses valve element 152 in first direction D1 via piston 156. Main spring 154 is disposed on first axis AX1 and is similar to main spring 54 of regulator 50 according to the first embodiment in that it moves valve element 152 in first direction D1 when secondary pressure drops. Main spring 154 of regulator 150 according to the present embodiment is composed of three elastic bodies, main springs 154A to 154C, which differs from regulator 50 according to the first embodiment, which is composed of a single main spring 54. All of main springs 154A to 154C are components for pressing valve element 152 in first direction D1 via piston 156, and are disposed so as to have their central axes on first axis AX1.

[0136] 14(A) and other figures, main spring 154A is an elastic body that is disposed at a position advanced in the second direction D2 from the first direction D1 end (tip) of piston 156, and at a position advanced in the first direction D1 from pressure adjustment spacer 188, with the first direction D1 end of main spring 154A engaging with piston 156 and the second direction D2 end supported by pressure adjustment spacer 188. Therefore, when cam 182 moves in the first direction D1 and pressure adjustment member 186 moves in the first direction D1 accordingly, pressure adjustment spacer 188 moves in the first direction D1 so as to compress main spring 154A, making it possible to shorten the length of 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 accordingly, the pressure adjustment spacer 188 moves in the second direction D2 so as to extend or restore the main spring 154A (so as to reduce the amount of compression), thereby making it possible to increase the length of the main spring 154A.

[0137] Note that 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 therebetween. This allows a force equivalent to the resultant force of the elastic forces 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.

[0138] As shown in the same figure, main spring 154C is an elastic body arranged 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 spring 154A and main spring 154B, which have approximately the same outer diameter.

[0139] Regulator 150 according to this embodiment is configured such that the spring load (elastic force) of main spring 154A and the spring load (elastic force) of main spring 154C act on piston 156, while only the spring load (elastic force) of main spring 154A acts on pressure adjustment member 186. With this configuration, it is possible to reduce the operating load of operating lever 180. For example, when the primary pressure is at the lowest setting value (e.g., 1.4 MPa), main spring 154A may be extended to its natural length, so that only the (constant) spring load of main spring 154C acts on piston 156. When the primary pressure is at the second lowest setting value (e.g., 1.6 MPa), main spring 154A may be compressed, so that a (relatively small) spring load of main spring 154A and a (constant) spring load of main spring 154C act on piston 156. When the primary pressure is at the third lowest setting value (e.g., 1.8 MPa), main spring 154A may be further compressed, so that a (relatively large) spring load of main spring 154A and a (constant) spring load of main spring 154C act on piston 156. This configuration reduces the operating load and suppresses wear on cam 182 and pin 184 compared to when the cam 182 and pin 184 are configured from a single elastic body.

[0140] However, main spring 154 does not necessarily have to be made up of multiple elastic bodies. For example, pressure adjustment spacer 188 and main spring 154B may be omitted, and main spring 154A may be configured to engage with pressure adjustment member 186. Furthermore, main spring 154C may be omitted. Conversely, multiple elastic bodies whose lengths change according to cam 182 may be provided.

[0141] 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 as an elastic body, and the valve element 152 may be disposed in this order. In this case, for example, the pin 184 is disposed on the pressure adjusting member 186 side (i.e., at a position advanced in the first direction D1) relative to the abutment surface of the cam 182 with the pin 184. Here, pin 184 and pressure adjustment member 186 may be provided so as to be movable integrally. With this configuration, pressure adjustment member 186 can be configured to be movable in first direction D1 or second direction D2 in conjunction with movement of pin 184 in first direction D1 or second direction D2. [Pressure adjustment method]

[0142] A method for gradually changing the secondary pressure using the regulator 150 according to this embodiment will be described below.

[0143] FIG. 13(A) is a cross-sectional view of regulator 150 taken along a plane passing through first axis AX1 and second axis AX2 when the secondary pressure is set to a low pressure, and FIG. 13(B) is a cross-sectional view taken along line B-B of FIG. 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). Therefore, 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 to press piston 156 in first direction D1.

[0144] Figure 14(A) is a cross-sectional view of regulator 150 taken along a plane passing through first axis AX1 and second axis AX2 when the secondary pressure is set to a high pressure, 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 a high pressure, pin 184 abuts against step surface 182B4 (2.3 MPa). As a result, cam 182 is positioned further in first direction D1 than when the secondary pressure is set to a low pressure, and accordingly, pressure adjustment spacer 188 is also positioned further in first direction D1 than when the secondary pressure is set to a low pressure. As a result, main spring 154A is shorter than when the secondary pressure is set to a low pressure, and therefore exerts a strong elastic force to press piston 156 in first direction D1.

[0145] Here, the user can easily change the set pressure to a low or high pressure by operating the protruding portion 180A. As shown in Fig. 15, the protruding portion 180A protrudes radially outward from the first end cap 158, so the user can 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 about the first axis AX with a relatively small operating load.

[0146] In addition, the step surfaces 182B1 to 182B4 are provided in an area within 180 degrees from the central axis of the cam 182. This allows the user to visually grasp the level of the set pressure based on the position (angle) of the protrusion 180A.

[0147] Furthermore, since the pressure adjusting member 186 is provided so that its relative position with respect 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 and changes over time.

[0148] Furthermore, the cam 182 is made of a metal having a higher hardness than the metal pin 184. Therefore, it is possible to make the pin 184 the main part that wears due to sliding contact, which reduces the frequency of replacing the cam 182, which has a complex shape, and by configuring the pin 184 to be easily replaceable, it is possible to improve the maintainability of the pneumatic tool 110.

[0149] Similarly to the regulator 50 according to the first embodiment, the regulator 150 also includes a valve spring 168, a valve element 152, a piston 156, and a main spring 154, which are arranged coaxially on the first axis AX1 in this order in the second direction D2, which corresponds to the direction toward the plug 162 that functions as an air intake. Furthermore, the regulator 150 also includes a cam 182 and an operating lever 180, which are arranged coaxially on the first axis AX1 in this order, at positions advancing in the second direction D2 relative to the main spring 154. As a result, the main spring 154 is positioned closer to the plug 162, which functions as an air intake, than the valve element 152 in the first direction D1 (or the second direction D2). As a result of this configuration, the high-pressure air entering through the air intake travels in the second direction D2, then makes a U-turn and travels back in the first direction D1 to enter the secondary pressure region AR2. Similar to the regulator 50 according to the first embodiment, this configuration allows the overall length of the driving tool 110 to be shortened by incorporating the regulator 150.

[0150] Similarly to the regulator 50, the regulator 150 according to this embodiment also has the valve element 152 and the main spring 154 disposed on the first axis AX1, while at least a portion of the first flow path CH1 extending from the air intake to the pressure adjustment mechanism of the regulator 150 extends in the first direction D1 along the second axis AX2 that is substantially parallel to the first axis AX1. The portion of the first flow path CH1 extending 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 allows the overall length of the regulator 150 to be shortened in the first direction D1 (or the second direction D2).

[0151] The present application further discloses a pneumatic tool as described below.

[0152] (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 between a normal state and a load reduction state in which the biasing force of the elastic body acting on the valve body is smaller than that of the normal state. Pneumatic tools.

[0153] According to the pneumatic tool described in Appendix A1, it is possible to provide a pressure regulator capable of reducing the operating load of the pressure regulating mechanism, and a pneumatic tool including the pressure regulator.

[0154] (Appendix A2) When the normal state is switched to the load-reducing state, the support portion moves. Pneumatic tools as described in Appendix A1.

[0155] (Appendix A3) The device further includes an operation input unit that allows a user to operate the biasing force of the elastic body, and switches from the normal state to the load-reducing state in response to an operation input to the operation input unit. A pneumatic tool as described in Appendix A1 or Appendix A2.

[0156] (Appendix A4) The pressure-receiving member is a piston component disposed between the valve body and the elastic body, and presses the valve body with the elastic body. A pneumatic tool according to any one of Appendix A1 to Appendix A3.

[0157] (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 elastic body penetrates the inner cylindrical portion and faces the piston part. Pneumatic tools as described in Appendix A4.

[0158] (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 elastic body is disposed closer to the air intake port than the valve body. A pneumatic tool according to any one of Appendix A1 to Appendix A5.

[0159] (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 load relief valve that opens and closes the pressure reduction flow path. A pneumatic tool according to any one of Appendix A1 to Appendix A6.

[0160] (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, When the pressure in the load release area is reduced, the support portion moves to the side opposite to the side where the valve body is located. Pneumatic tools as described in Appendix A7.

[0161] (Appendix A9) The pneumatic tool is a driving tool for driving out fasteners. A pneumatic tool according to any one of Appendix A1 to Appendix A6.

[0162] (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, The valve body further includes a load reduction mechanism that can switch between a normal state and a load reduction state in which the elastic body exerts a biasing force smaller than that in the normal state with respect to the biasing force of the elastic body acting on the valve body. Pressure regulator.

[0163] (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 in contact with 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. Pneumatic tools.

[0164] According to the pneumatic tool described in Appendix B1, it is possible to provide a pneumatic tool in which the secondary pressure is less susceptible to the influence of fluctuations in the primary pressure.

[0165] (Appendix B2) the valve body and the elastic body are disposed on a first shaft, At least a portion of the flow path from the air intake to the pressure regulating mechanism extends along a second axis that is substantially parallel to the first axis. Pneumatic tools as described in Appendix B1.

[0166] (Appendix B3) a bypass flow path that causes air pressure upstream of the valve body to act on the third pressure-receiving surface, the bypass flow path being formed across the second shaft and the first shaft; Pneumatic tools as described in Appendix B2.

[0167] (Appendix B4) 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. A pneumatic tool according to any one of Appendix B1 to Appendix B3.

[0168] (Appendix B5) The pressure-receiving member further includes an inner cylindrical portion that can come into contact with the pressure-receiving member, and an outer cylindrical portion that can slide along the inner cylindrical portion, and the third pressure-receiving surface is provided between the outer cylindrical portion and the inner cylindrical portion. A pneumatic tool according to any one of Appendix B1 to Appendix B4.

[0169] (Appendix B6) 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 in the first direction overlaps with a region in which the elastic body is provided. A pneumatic tool according to any one of Appendix B1 to Appendix B5.

[0170] (Appendix B7) The pneumatic tool is a driving tool for driving out fasteners. A pneumatic tool according to any one of Appendix B1 to Appendix B6.

[0171] (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; The valve element has a biasing force adjusting member configured to be able to change the biasing force of the elastic body acting on the valve element in stages. Pneumatic tools.

[0172] (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; and a biasing force adjusting member configured to change the length of the elastic body in stages. Pneumatic tools.

[0173] In the pneumatic tool described in Appendix C1 or Appendix C2, the biasing force adjusting member may be a cam.

[0174] (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.

[0175] (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).

[0176] (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.

[0177] 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 adjustment member (or cam) may have a female thread, and the force adjustment 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 adjustment member (or cam).

[0178] (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, characterized in that 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).

[0179] (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.

[0180] (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.

[0181] (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 adjustment mechanism extends along a second axis that is substantially parallel to the first axis.

[0182] (Appendix C10) The pneumatic tool according to Appendix C8 or Appendix C9, wherein a flow path from the air intake to the pressure adjustment 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.

[0183] (Appendix C11) The pneumatic tool according to any one of Appendix C8 to Appendix C10, characterized in that 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.

[0184] (Appendix C12) The pneumatic tool according to any one of Appendix C8 to Appendix C11, further comprising an adjustment unit that adjusts the biasing force exerted by the elastic body.

[0185] (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 adjustment mechanism includes a flow path that causes compressed air to travel in the first direction.

[0186] (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.

[0187] (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 according to 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.

[0188] (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 according to 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.

[0189] (Appendix C17) the pin is constructed from a first metal; The pneumatic tool according to appendix C4, wherein the cam is made of a second metal having a hardness greater than the hardness of the first metal.

[0190] (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. [Explanation of symbols]

[0191] 10 Nailer 20 Drive mechanism 22 Driving Piston 24 Driving cylinder 26 Drivers 28 Nose 30 Magazines 32 Grip 34 Air chamber 36 Main valve 38 Trigger 50 Regulator 52 Valve body 54 Main spring 56 Piston 561 Expanded diameter part 562 Reduced diameter part 58 First end cap 60 Air Filter 62 Plug 64 Valve chamber 66 Adjustment screw 68 Valve spring 70 Second end cap 72 Spacer 80 Dial 81A Convex part 81B Recess 82 Cam plate 84 Load relief valve 84A Ring 86 Load-releasing piston (an example of a "support part") 86A 1st inner surface 86B 2nd inner surface 801 Inner Dial 802 Outer Dial 803 Elastic member 861 Inner cylinder 862 Outer tube part (another example of "support part") AR2 Secondary pressure area AR3 load release area AR31 pressurized flow path AR32 pressure reducing channel AR4 Open area open to atmospheric pressure AR5 Primary pressure balance area AR51 flow path AX1 1st axis AX2 2nd axis CH1 First flow path CH2 Second flow path CH3 bypass flow path D1 1st direction D2 2nd direction F Third pressure surface H through hole

Claims

1. 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 external source, 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. 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. 3. The pneumatic tool according to claim 1, further comprising an adjustment unit for adjusting the biasing force exerted by the elastic body.

4. 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. 5. The pneumatic tool according to claim 1, wherein the pneumatic tool is a driving tool for driving out fasteners.

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