Flow control valve

Abstract

This invention provides a flow control valve capable of displaying the opening degree of a flow path and achieving miniaturization. The flow control valve includes: a scale body that adjusts the opening degree of a second flow path within the first body by moving a needle valve along a first axis direction according to a rotational operation of a handle provided at one end of a first body, and is provided with a scale indicating the rotational operation of the handle; a scale indicator that indicates a scale corresponding to the rotational operation of the handle; a shaft that moves relative to the handle along the first axis direction and rotates integrally about the first axis; and a clutch mechanism that switches the scale when the handle rotates at a predetermined angle. The clutch mechanism includes an engaging part, a engaged part, and a clutch drive mechanism. When the engaging part and the engaged part are engaged, the scale indicator and the scale body rotate integrally. When the handle rotates at a predetermined angle, the clutch drive mechanism disengages the engaging part from the engaged part, rotates the scale indicator, and re-engages the engaging part with the engaged part after switching the scale.

Description

Technical Field

[0001] The present invention relates to a flow control valve that controls the flow rate of fluid flowing in a flow path by adjusting the opening of a flow path formed in a valve body using a needle valve that is linked to the rotational operation of the handle, and particularly to a flow control valve that can display the amount of rotational operation of the handle, i.e., the opening of the flow path adjusted by the needle valve. Background Technology

[0002] A flow control valve is a small device that restricts the flow of fluid and controls the speed of an actuator, and is used, for example, in automated production lines for assembling mechanical devices, electronic equipment, etc. As shown in Patent Document 1, a flow control valve includes a needle valve that adjusts the opening of a flow path, a rotary handle linked to the needle valve, and a display that shows the opening of the flow path adjusted by the needle valve, i.e., the amount of rotation of the handle.

[0003] The flow control valve described in Patent Document 1 comprises: a housing extending axially and formed into a cylindrical shape; a cylindrical frame mounted on one (upper) end of the housing along its axial direction; and a topped cylindrical handle disposed on the upper side of the frame in a manner rotatable about an axis. A needle valve is disposed inside the housing in a manner rotatable both axially and about an axis. The upper part of the needle valve is inserted into a shaft portion disposed within the frame and extending axially, the needle valve and the shaft portion being fixed to each other about the axis and fitting together in a manner movable relative to each other axially. Furthermore, a hole extending axially downward is provided in the central portion of the handle, and the shaft portion extending from the upper part of the frame is inserted into the hole in a state of being fixed to each other about the axis. That is, when the handle is rotated, the shaft portion and the needle valve can rotate together.

[0004] Furthermore, a cylindrical needle guide is disposed below the shaft portion within the housing, and an internal thread on the inner surface of the needle guide engages with an external thread on the outer periphery of the needle valve. Therefore, when the handle is rotated, the needle valve rotates relative to the needle guide while moving axially. By adjusting the opening of the flow path within the housing through this axial movement of the needle valve, the flow rate of the fluid flowing in that flow path can be controlled.

[0005] Furthermore, in the flow control valve described in Patent Document 1, an annular display ring is provided at a position radially outward from the upper side of the frame, offset from the shaft portion. The central axis of the display ring extends parallel to the rotation center axis of the shaft portion. An axially penetrating hole is provided on the inner side of the display ring, and internal teeth are equally spaced along the circumference on the inner surface of the display ring forming the hole. The shaft portion is inserted into the hole of the display ring, and a meshing portion capable of engaging with the internal teeth is provided on the side of the shaft portion. The inner diameter of the hole of the display ring is larger than the outer diameter of the shaft portion, and the shaft portion is positioned close to the radial side of the hole of the display ring. When the shaft portion rotates one revolution, the meshing portion extends one internal tooth portion circumferentially, causing the display ring to rotate at a predetermined rotation angle. Furthermore, a scale is provided on the outer peripheral surface of the display ring, which indicates the opening degree of the fluid flow path regulated by the needle valve (rotation operation amount of the handle), and a display window is provided on the frame facing the outer peripheral surface of the display ring so that the scale can be visually confirmed.

[0006] Existing technical documents

[0007] Patent documents

[0008] Patent Document 1: Japanese Patent No. 6179510

[0009] Thus, in the flow control valve described in Patent Document 1, the central axis of the display ring is positioned radially outward from the shaft portion, which is coaxially arranged with the handle and needle valve. Therefore, the frame housing the display ring must also be formed in a manner that bulges radially outward from the shaft portion, making it impossible to avoid a large frame size, and consequently, a large overall flow control valve size. On the other hand, users, with the pursuit of space saving, also desire further miniaturization of such flow control valves. Summary of the Invention

[0010] The problem that the invention aims to solve

[0011] Therefore, the technical challenge of the present invention is to provide a flow control valve that can be further miniaturized in a flow control valve capable of displaying the amount of rotational operation of the handle, i.e., the opening of the flow path regulated by the needle valve.

[0012] Technical solutions for solving the problem

[0013] To address the aforementioned issues, the flow control valve of the present invention comprises: a body extending axially; a flow path formed within the body; a handle disposed on one axial side of the body and supported on the body in a manner rotatable about the axis; and a needle valve, wherein the needle valve is disposed coaxially within the body and on the handle, and moves axially according to the rotational amount of the handle, thereby adjusting the opening of the flow path. The flow control valve is capable of controlling the flow rate of fluid flowing in the flow path according to the rotational amount of the handle. The flow control valve is further characterized by: a scale body supported on the handle in a manner rotatable about the axis, and having a scale indicating the rotational amount of the handle; a scale indicator portion that rotates integrally with the handle about the axis and indicates the scale corresponding to the rotational amount of the handle; and a shaft portion disposed on the opposite axial side of the scale body and supported on the handle in a manner rotatable about the axis. The mechanism includes a rotating portion that rotates integrally with the shaft; and a clutch mechanism that transmits rotation of the handle portion to the scale body or cuts off the transmission, thereby switching the scale indicated by the scale indicator whenever the handle portion is rotated by a predetermined angle. The clutch mechanism has an engaging portion and a engaged portion, one of which is disposed on the shaft portion and the other on the scale body. By engaging with each other, the rotation of the handle portion is transmitted to the scale body, causing the scale indicator and the shaft portion to rotate together. The scale body rotates integrally about the shaft; and the clutch drive mechanism releases the engagement of the engaging part from the engaged part by moving the shaft to the other side axially whenever the handle is rotated by a predetermined angle, allowing the scale indicator to rotate relative to the scale body about the shaft by rotation of the handle, and after switching the scale indicated by the scale indicator relative to the scale body by this rotation of the scale indicator relative to the scale body, the engaging part and the engaged part are engaged again.

[0014] In this case, preferably, the clutch drive mechanism has: a cam surface fixedly disposed on the main body and extending annularly around the shaft; and a cam-shaped protrusion disposed on the shaft and facing the cam surface, rotating around the shaft and sliding on the cam surface as the handle rotates. The cam surface has: a cam hole extending through the axial direction; and a cam plane extending planarly from one axial end of the cam hole toward the axial direction. The clutch drive mechanism releases the engagement between the engaged portion and the engaged portion by moving the cam-shaped protrusion into the cam hole and engaging whenever the handle rotates by a predetermined angle, allowing the scale indicator to rotate relative to the scale body around the shaft by rotation of the handle. Additionally, preferably, the clutch drive mechanism has a spring portion that always applies force to the shaft portion toward the other side of the axial direction. Through the force applied by the spring portion, the shaft portion moves toward the other side of the axial direction along with the cam-shaped protrusion moving into the cam hole portion. After switching the scale indicated by the scale indicator portion, the cam-shaped protrusion overcomes the force applied by the spring portion and moves toward the axial direction to abut against the cam plane portion, thereby causing the engaged portion to engage with the engaged portion again.

[0015] Furthermore, preferably, the scale body has a plurality of resistance-generating protrusions spaced apart around the axis, and the flow control valve has a locking protrusion that slidably abuts against the plurality of resistance-generating protrusions. The locking protrusion is positioned on one side axially closer than the plurality of resistance-generating protrusions and is fixedly disposed in the body. When the engagement between the locked portion and the locking portion is released, the resistance generated by the locking protrusion abutting against any one of the resistance-generating protrusions prevents the scale body from rotating along with the rotation of the handle. More preferably, the locking protrusion has a first abutting portion protruding towards the other side axially and slidably abutting against the resistance-generating protrusions, and the plurality of resistance-generating protrusions extend radially outward at equal intervals around the axis.

[0016] Additionally, preferably, the flow control valve has an abutment surface fixedly disposed on the main body and facing the other side of the axial direction, and the shaft has a second abutment portion disposed opposite to the abutment surface and capable of abutting. The second abutment portion abuts against the abutment surface when the cam-shaped protrusion is pulled out of the cam hole by rotating the handle from the state where the cam-shaped protrusion is engaged with the cam hole, thereby preventing the shaft from moving to one side of the axial direction.

[0017] Invention Effects

[0018] As described above, according to the present invention, it is possible to provide a flow control valve that can be further miniaturized in a flow control valve capable of displaying the amount of rotational operation of the handle, i.e., the opening of the flow path adjusted by the needle valve. Attached Figure Description

[0019] Figure 1 This is a side view illustrating one embodiment of the flow control valve of the present invention.

[0020] Figure 2 yes Figure 1 The diagram shows a top view of the flow control valve.

[0021] Figure 3 This is the front view of the flow control valve.

[0022] Figure 4 yes Figure 1 The flow control valve shown is viewed in a sectional view along line IV-IV.

[0023] Figure 5 yes Figure 1 An exploded perspective view of the display switching mechanism in the flow control valve shown.

[0024] Figure 6 yes Figure 4 The side view of the needle valve shown.

[0025] Figure 7 yes Figure 4 A three-dimensional view of the needle guide shown.

[0026] Figure 8 Viewed from one side Figure 5 A three-dimensional view of the shaft shown.

[0027] Figure 9 This is a three-dimensional view of the shaft from the other side.

[0028] Figure 10 This is the front view of the shaft.

[0029] Figure 11 yes Figure 10 XX-direction sectional view.

[0030] Figure 12 yes Figure 5 The side view of the scale shown.

[0031] Figure 13 This is the front view of the scale body.

[0032] Figure 14 This is the rear view of the scale body.

[0033] Figure 15 yes Figure 5 The side view of the spacer shown.

[0034] Figure 16 This is the front view of the spacer.

[0035] Figure 17 yes Figure 16 Sectional view along line XVII-XVII.

[0036] Figure 18 yes Figure 4 The diagram shows a perspective view of the needle valve retainer.

[0037] Figure 19 yes Figure 5 The front view of the handle shown.

[0038] Figure 20 yes Figure 19 Sectional view along the XX-XX direction.

[0039] Figure 21 It is used for explanation Figure 5 The diagram illustrates the operation of the clutch mechanism; the rotation of the lever and scale indicates the locked state.

[0040] Figure 22 It is used for explanation Figure 5 The diagram illustrates the operation of the clutch mechanism. Rotation of the lever indicates the unlocked state, while rotation of the scale indicates the locked state.

[0041] Figure 23 It is used for explanation Figure 5 The diagram illustrates the operation of the clutch mechanism. The rotation of the lever and scale indicates the unlocked state.

[0042] Figure 24 This is an explanatory diagram used to prevent the shaft from jumping during scale switching, showing the situation where the contact surface and the second contact part are in a non-contact state.

[0043] Figure 25 This is an explanatory diagram used to prevent the shaft from jumping during scale switching, showing the contact surface and the second contact part in a contact state.

[0044] Figure 26 This is an explanatory diagram used to prevent the shaft from jumping during scale switching, showing the situation where the contact surface and the second contact part are in a non-contact state.

[0045] Figure 27 This is a partial sectional view showing a modified example of the spacer.

[0046] Explanation of reference numerals in the attached figures

[0047] 10 Flow control valves

[0048] 12. First Subject (Subject)

[0049] 12a Valve housing

[0050] 12b Port Forming Section

[0051] 13 Second Subject

[0052] 14 First Port

[0053] 15 Second Port

[0054] 16 Fluid flow path

[0055] 16a First flow path

[0056] 16b Second Flow Path (Flow Path)

[0057] 16c Internal flow path

[0058] 17 Pipe fittings

[0059] 17a Cadence tablets

[0060] 17b Release bushing

[0061] 18, 30 external threads

[0062] 19 Connecting Flow Paths

[0063] 19a Connecting Flow Path

[0064] 19b port flow path

[0065] 20 Check valve retainer

[0066] 20a recess

[0067] 21 Needle valve retainer

[0068] 21a Valve Port

[0069] 21b Fixing hole

[0070] 21b1 First fixed face

[0071] 21b2 Second fixed face

[0072] 21c perimeter

[0073] 21d, 21d' step section

[0074] 22 Center Hole

[0075] 23 Sealing components

[0076] 25 Check valve

[0077] 26 seats

[0078] 27 Needle valve

[0079] 27a Throttling section

[0080] 27b Needle body

[0081] 27c cut surface

[0082] 28 Valve seals

[0083] 29 throttling orifice

[0084] 31-pin guide

[0085] 31a Internal thread

[0086] 31b, 43 Through Holes

[0087] 32. Handle

[0088] 32a Engaging protrusion

[0089] 32b Top plate section

[0090] 32c Side panel

[0091] 32d engaging protrusion

[0092] 32e Engaging claw section

[0093] 33, 51a Carding protrusion

[0094] 34. Scale indicator section (scale indicator opening)

[0095] 40 Shaft

[0096] 41 First Axis Section

[0097] 41a Force-applying flange

[0098] 41b Cam contouring protrusion

[0099] 41b1 side

[0100] 42 Second Axis Section

[0101] 42a Side wall portion

[0102] 42a1 Planar Part

[0103] 42a2, 44b, 45b Bends

[0104] 42b space

[0105] 42c Step section

[0106] 44. Handle insertion hole

[0107] 44a Second planar portion on the base side

[0108] 45 Needle valve insertion hole

[0109] 45a First planar portion on the base side

[0110] 46 Cam surface

[0111] 46a Cam hole section

[0112] 46a1 inclined surface

[0113] 46b Cam Plane

[0114] 47. Clutch Mechanism

[0115] 47a Engaging part (locking part)

[0116] 47a' meshing plate

[0117] 47b Gear section (engaged part)

[0118] 47b' gear plate

[0119] 48. Clutch drive mechanism

[0120] 49 Second contact section

[0121] 50 spacers

[0122] 51 Locking Claw Section

[0123] 51c inner surface

[0124] 51b, 72a Planar Section

[0125] 51d First contact section

[0126] 52 Through hole section

[0127] 52a Small diameter section

[0128] 53. Annular protrusions

[0129] 54, 54' step section

[0130] 55 Locking recess

[0131] 56. Edge section

[0132] 57 Fixing plate

[0133] 57a First face

[0134] 57b Second face

[0135] 58 opening

[0136] 59. Legs

[0137] 59a Locking convex part

[0138] 60 Jump prevention mechanism

[0139] 61 Jump Prevention Wall

[0140] 61a Abutment surface

[0141] 62 Helical Spring (Spring Section)

[0142] 70 scale

[0143] 71 Ring Body

[0144] 71a recess

[0145] 71b Spring seat

[0146] 72 dials

[0147] 72b scale

[0148] 73. Resistance-generating protrusion

[0149] 74. Circular Hole Section

[0150] A arrow

[0151] J central axis

[0152] L1 First Axis

[0153] L2 Second Axis

[0154] Pr locks the position Detailed Implementation

[0155] The following describes a flow control valve according to one embodiment of the present invention. In this embodiment, the fluid is compressed air, and the flow control valve is described as an example of a speed controller using an outlet throttling control method that is directly installed in a fluid pressure cylinder and controls the operating speed of the fluid pressure cylinder by limiting the exhaust flow rate from the fluid pressure cylinder. However, the present invention can also be applied to, for example, an inlet throttling control method speed controller that controls the operating speed of the fluid pressure cylinder by limiting the supply flow rate of compressed air supplied to the fluid pressure cylinder. Furthermore, this flow control valve is not specifically designed for fluid pressure cylinders and can be used in various other fluid pressure devices.

[0156] like Figures 1-4As shown, the flow control valve 10 of this embodiment has: a substantially cylindrical first body 12 (body) extending along a first axis L1, and a substantially cylindrical second body 13 connected to the side of the first body 12 in a manner extending along a second axis L2 orthogonal to the first axis L1. That is, the first axis L1 and the second axis L2 are in a torsional position relative to each other.

[0157] The interior of the first body 12 is hollow. A first port 14 for connecting a pipe from a pressure source such as a compressor (not shown) is provided at one end of the first body 12 in the first axis L1 direction (hereinafter referred to as "axis L1 direction"). In addition, a second port 15 for connecting, for example, to the supply and exhaust port of a reciprocating fluid pressure cylinder is provided at one end of the second axis L2 direction (hereinafter referred to as "axis L2 direction"). A fluid flow path 16 connecting the first port 14 and the second port 15 is formed inside the first body 12 and the second body 13.

[0158] The first body 12 has a valve receiving portion 12a formed at the other end (hereinafter referred to as "base end in the L1 direction") of the first body 12 and a port forming portion 12b formed at the top end in the L1 direction. Furthermore, a first port 14 is provided at the top end in the L1 direction of the port forming portion 12b, and a simple connection type pipe connector 17 is installed at the first port 14.

[0159] The pipe fitting 17 is configured such that when one end of the pipe is inserted into the interior of the pipe fitting 17, a plurality of locking tabs 17a bite into the outer periphery of the pipe and lock it in place, thereby making the pipe in an anti-dislodgement state. In addition, when the release bushing 17b is pressed into the interior of the pipe fitting 17, the top end of the release bushing 17b expands the locking tabs 17a outward and separates them from the pipe, thereby enabling the pipe to be pulled out.

[0160] Within the hollow portion inside the valve housing 12a, a cylindrical check valve retainer 20 and a cylindrical needle valve retainer 21 with different inner and outer diameter portions at multiple steps are coaxially arranged from the top end side in the direction of axis L1 toward the base end side in the direction of axis L1. The check valve retainer 20 branches a portion of the fluid flow path 16 into a first flow path 16a and a second flow path 16b (flow path) that run parallel to each other. A sealing member 23 is installed on the outer periphery of the needle valve retainer 21 near the top end in the direction of axis L1 to provide an airtight seal with the inner circumferential surface of the valve housing 12a. Both the check valve retainer 20 and the needle valve retainer 21 are integrally molded from synthetic resin.

[0161] The first flow path 16a is an annular flow path formed between the outer periphery of the check valve retainer 20 and the inner periphery of the first body 12. The second flow path 16b is a flow path through the central hole 22 of the check valve retainer 20. The first flow path 16a and the second flow path 16b are connected to the communicating flow path 19 in the second body 13 through the internal flow path 16c between the check valve retainer 20 and the needle valve retainer 21.

[0162] An annular check valve 25 is provided within the first flow path 16a to restrict the flow direction of the compressed fluid flowing in the first flow path 16a to only one direction. The check valve 25 is hermetically mounted within an annular recess 20a formed on the outer periphery of the check valve holder 20, and deforms radially outward under the action of compressed air. Furthermore, the check valve 25 opens and closes the first flow path 16a by separating its surface from the base end side in the direction of axis L1 relative to the annular seat 26 protruding radially inward from the inner periphery of the first body 12.

[0163] That is, in this embodiment, since the check valve 25 extends radially outward, it separates from the seat 26 to open the first flow path 16a relative to the forward flow of compressed air from the first port 14 to the second port 15, thereby allowing the forward flow. On the other hand, relative to the reverse flow of compressed air from the second port 15 to the first port 14, the check valve 25 abuts against the seat 26 to hermetically close the first flow path 16a, thereby preventing the reverse flow.

[0164] Furthermore, a valve hole 21a extending along the axis L1 is formed inside the needle valve holder 21. The needle valve 27 is airtightly fitted into the valve hole 21a via the valve seal 28 and can move freely forward and backward along the axis L1. Moreover, by moving the needle valve 27 forward and backward, the throttling portion 27a formed at the top of the needle valve 27 can be inserted and removed relative to the throttling orifice 29 of the center hole 22 of the check valve holder 20. That is, when the throttling portion 27a moves forward and backward relative to the throttling orifice 29 along the axis L1, the distance (i.e., the flow path cross-sectional area) between the throttling portion 27a and the throttling orifice 29 changes, thereby controlling the flow rate of compressed air flowing in the second flow path 16b.

[0165] Here, the needle valve 27 and the needle guide 31 that moves it axially are described in detail. For example... Figure 6As shown, the needle valve 27 is formed as a cylinder extending along the axis L1, and has a throttling portion 27a at the top end and a needle body portion 27b formed at a position closer to the base end of the throttling portion 27a along the axis L1. The needle valve 27 is formed, for example, from a synthetic resin such as PBT resin. Furthermore, the diameter of the needle body portion 27b is larger than that of the throttling portion 27a, and a pair of flat cut surfaces 27c, 27c are formed on its radially opposite sides across the central axis J (i.e., the first axis L1). The needle body portion 27b, having these cut surfaces 27c, 27c, is inserted into the shaft portion 40, and as described above, the needle valve 27 is fixed relative to the shaft portion 40 about the axis L1. Moreover, external threads 30 are formed on the outer peripheral surface of the needle body portion 27b, excluding the cut surfaces 27c, 27c.

[0166] like Figure 4 and Figure 7 As shown, the needle guide 31 is cylindrical and positioned at the top end of the shaft portion 40 along the axis L1. A through hole 31b extending along the axis L1 is provided on the inner side of the needle guide 31, and an internal thread 31a is formed on its inner circumferential surface to engage with the external thread 30 of the needle valve 27. The needle guide 31 is made of metal, for example, preferably of an alloy (e.g., brass).

[0167] A plurality of locking protrusions 33 protruding radially outward are formed at equal intervals along the circumferential direction on the outer peripheral surface of the needle guide 31. These locking protrusions 33 are used to prevent the needle guide 31 from rotating relative to the needle valve retainer 21 or being pulled out of the valve hole 21a by pressing against the inner wall of the valve hole 21a of the needle valve retainer 21 when the needle guide 31 is fitted into a predetermined position within the valve hole 21a of the needle valve retainer 21.

[0168] At the base end of the needle valve 27 in the L1 direction, a cap-shaped rotating handle 32 is connected via a cylindrical shaft portion 40. Specifically, the needle valve 27 is inserted into the shaft portion 40 in a state where it is fixed to itself in the rotational direction (around the L1 axis) and is movable in the L1 direction. Furthermore, the handle 32 is inserted into the end of the shaft portion 40 at its base end in the L1 direction, also fixed to itself in the L1 axis and movable in the L1 direction. Therefore, when the handle 32 is rotated in the forward and reverse directions, the needle valve 27 rotates in the forward and reverse directions and is guided by the needle guide 31 to move forward and backward in the L1 direction. Thus, the needle valve 27 can adjust the opening of the second flow path 16b by moving forward and backward in tandem with the rotation of the handle 32.

[0169] Furthermore, in the flow control valve 10 of this embodiment, the opening degree of the second flow path 16b adjusted by the needle valve 27 can be visually confirmed by displaying the rotation operation amount of the handle 32 with numbers or symbols. Therefore, the flow control valve 10 has: a scale body 70 supported to rotate about an axis L1 and having a scale 72b indicating the rotation operation amount of the handle 32; a scale indicator 34 that rotates integrally with the handle 32 about the axis L1 and indicates the scale 72b corresponding to the rotation operation amount of the handle 32; and a clutch mechanism 47 (see reference). Figure 21 The clutch mechanism 47 transmits the rotation of the handle 32 to the scale body 70 or cuts off the transmission, thereby switching the scale 72b indicated by the scale indicator 34 whenever the handle 32 is rotated by a predetermined angle.

[0170] The following is for reference Figures 4 to 23 The display mechanism for the rotational operation of such a display handle 32 (i.e., the opening degree of the second flow path 16b adjusted by the needle valve 27) will be described in detail. For example... Figure 4 and Figure 5 As shown, in the flow control valve 10 of this embodiment, the main structures related to the display mechanism, namely the spacer 50, the shaft 40, the helical spring 62, the scale body 70, and the handle 32, are coaxially arranged on the first shaft L1 within the valve housing 12a and at a position on the base end side of the valve housing 12a in the direction of the shaft L1.

[0171] like Figure 4 , Figures 8-11 As shown, the shaft portion 40 is formed as a cylinder extending along the axis L1, and has a first shaft portion 41 at its top end in the axis L1 direction and a second shaft portion 42 at its base end in the axis L1 direction, which is closer to the first shaft portion 41 than the first shaft portion 41. The shaft portion 40 is formed, for example, of a synthetic resin, preferably of polyphenylene sulfide resin (PPS resin). The diameter of the second shaft portion 42 is smaller than that of the first shaft portion 41, and a pair of sidewall portions 42a, 42a extending towards the axial base end are formed at the axial base end of the second shaft portion 42. When viewed from the front, the sidewall portions 42a, 42a are arranged facing each other across the central axis J, and a space 42b is formed between the pair of sidewall portions 42a, 42a for insertion of the shaft portion 40. This space 42b is open at its base end in the axis L1 direction and on both radial sides, communicating with a through hole 43 extending through the shaft portion 40.

[0172] A planar portion 42a1 extending axially is formed on the inner side of the sidewall portions 42a, 42a, and a curved portion 42a2 formed by an arc centered on the central axis J is formed on the outer side of the sidewall portions 42a, 42a. A helical spring 62 (spring portion) is mounted on the radially outer side of the pair of sidewall portions 42a, 42a. The axial L1-direction tip of the helical spring 62 abuts against the axial L1-direction base end of the second shaft portion 42, which protrudes radially outward and extends in an annular shape. This stepped portion 42c functions as a spring seat on the axial tip side of the helical spring 62.

[0173] A through hole 43 is provided in the shaft portion 40, extending along the central axis J. The through hole 43 is formed as a shank insertion hole 44 on the base end side in the axis L1 direction for inserting the engaging protrusion 32a of the shank portion 32, and a needle valve insertion hole 45 on the top end side in the axis L1 direction for inserting the needle valve 27. The cross-sectional shapes of these shank insertion holes 44 and needle valve insertion holes 45 are different in size.

[0174] The shank insertion hole 44 extends from the base end of the first shaft portion 41 in the L1 direction to the base end of the second shaft portion 42 in the L1 direction, and is formed by a pair of base end side second planar portions 44a facing each other across the central axis J and a curved portion 44b formed by an arc centered on the central axis J. The base end side second planar portions 44a and the planar portions 42a1 of the sidewall portions 42a, 42a are integrally formed and extend on the same plane. In this embodiment, the integrally formed planar portions 42a1 and base end side second planar portions 44a are formed as rectangles extending along the L1 direction.

[0175] On the other hand, the needle valve insertion hole 45 extends from the top end of the first shaft portion 41 in the direction of axis L1 to the base end side in the direction of axis L1, and is formed by a pair of base end side first flat portions 45a facing each other across the central axis J and a curved portion 45b formed by an arc centered on the central axis J. The base end side first flat portion 45a is located radially outward than the base end side second flat portion 44a, and is formed such that its width in the direction orthogonal to the axial direction is narrower than that of the base end side second flat portion 44a. Furthermore, the curved portion 44b of the shank insertion hole 44 on the second shaft portion 42 side and the curved portion 45b of the needle valve insertion hole 45 on the first shaft portion 41 side both have the same radius of curvature and are formed on the same curved surface.

[0176] When the engaging protrusion 32a of the shank 32 is inserted into the shank insertion hole 44 in the through hole 43, the shaft 40 can move axially relative to the shank 32 and can rotate integrally with the shank 32 about the axis. Furthermore, the needle valve insertion hole 45 in the through hole 43 has a cross-sectional shape similar to that of the needle body 27b of the needle valve 27, and is formed to have a slightly larger cross-sectional area than the needle body 27b. Thus, the shaft 40 is fixed to the needle valve 27 and rotates integrally about the axis L1, while the needle valve 27 is supported by the needle guide 31 in a manner that allows it to move along the axis L1.

[0177] An annular force-applying flange 41a protruding radially outward is formed at the end of the first shaft portion 41 on the base end side in the L1 direction. Furthermore, on the end face of the force-applying flange 41a on the base end side in the L1 direction, a plurality of engaging plates 47a' protruding towards the base end side in the L1 direction are formed at equal intervals along the circumferential direction, constituting an engaging portion 47a (engaging portion). This engaging portion 47a engages with the gear portion 47b (see reference) provided on the scale body 70 described later. Figure 12 The engaging parts 47a and 47b engage with each other. Furthermore, these engaging parts 47a and 47b constitute part of the clutch mechanism 47 described later.

[0178] The force-applying flange 41a has a cam-shaped protrusion 41b at its radially outer end face, protruding towards the apex in the direction of axis L1. This cam-shaped protrusion 41b is triangular in side view, and its apex aligns with the cam surface 46 of the spacer 50 described later (see reference). Figure 17 The cam profiled protrusions 41b and 41b1 are arranged facing each other and can slide against the cam surface 46. The cam profiled protrusions 41b have side surfaces 41b1 and 41b1 on both circumferential sides. The side surfaces 41b1 tilt towards the base end in the direction of the axis L1 as they move outward in the circumferential direction. Furthermore, the cam profiled protrusions 41b and the cam surface 46 together constitute the clutch drive mechanism 48 (see reference). Figure 21 That is, the clutch drive mechanism 48 has the following function: as the shaft portion 40 rotates due to the rotational operation of the handle portion 32, the cam profile protrusion 41b slides while rotating on the annular cam surface 46, thereby causing the shaft portion 40 to reciprocate in the direction of shaft L1.

[0179] Furthermore, the force-applying flange 41a has a second abutment portion 49 protruding towards the base end in the direction of axis L1 at its radially outer end face. This second abutment portion 49, when viewed from the side, is formed as a triangle protruding towards the axial base end, and a circumferentially extending planar portion 49a is formed at the apex of the second abutment portion 49. This planar portion 49a interacts with the jump prevention wall 61 (see reference 61) of the spacer 50 described later. Figure 17 , Figure 25They are arranged facing each other and can abut against each other. In this embodiment, the second abutting part 49 is arranged 90° apart circumferentially from the cam-shaped protrusion 41b.

[0180] When the engaging protrusion 32a of the handle 32 (refer to) Figure 4 When fitted into the through hole 43 within the second shaft portion 42, as described above, the shaft portion 40 can be fixed to the handle portion 32 and rotate integrally around the shaft L1; on the other hand, it can move relative to the handle portion 32 in the direction of the shaft L1. Furthermore, as... Figure 4 As shown, a helical spring 62 (spring portion) composed of a compression spring is installed radially outside a pair of sidewall portions 42a, 42a of the second shaft portion 42. The end of the helical spring 62 at its top end in the L1 direction abuts against the stepped portion 42c at the base end end in the L1 direction of the second shaft portion 42 of the shaft portion 40. On the other hand, the end at the base end in the L1 direction abuts against a spring seat 71b formed on the scale body 70 (see reference). Figure 14 The coil spring 62 abuts against the scale body 70 and applies force to the shaft portion 40 towards the top end in the direction of shaft L1. Additionally, the coil spring 62 applies force to the scale body 70 towards the base end in the direction of shaft L1 via the spring seat 71b and the stepped portion 42c, causing a resistance protrusion 73 (see reference) on the scale body 70 described later. Figure 14 ) and the first abutting portion 51d provided on the spacer 50 (refer to Figure 15 (arrival)

[0181] In this embodiment, the clutch drive mechanism 48 is composed of the aforementioned shaft portion 40, cam surface 46, cam contouring protrusion 41b, and coil spring 62. Furthermore, the clutch mechanism 47 is composed of the clutch drive mechanism 48, the engagement portion (engaging portion) 47a, and the gear portion (engaged portion) 47b.

[0182] like Figure 4 , Figures 12-14As shown, the scale body 70 is formed as a cylinder extending along the axis L1, arranged to surround the portion of the shaft 40 at its base end in the axis L1 direction, and configured to be rotatable relative to the shaft 40 about the axis L1. The scale body 70 is formed, for example, of a synthetic resin, preferably of polyacetal (POM). Furthermore, the scale body 70 has a cylindrical annular body portion 71, and a flange-shaped scale 72 protruding radially outward and extending annularly in the circumferential direction is formed at the end of the annular body portion 71 at its base end in the axis L1 direction. An annular planar portion 72a extending circumferentially is formed on the end face of the scale 72 at its base end in the axis L1 direction, and graduations 72b indicating the amount of rotation of the handle 32 (e.g., the number of rotations) are attached to this planar portion 72a. An annular hole 74 is provided on the inner side of the ring body 71, which extends along the axis L1. The engaging protrusion 32a of the handle 32 is rotatably inserted into the annular hole 74.

[0183] In this embodiment, the scale 72b displays numbers such as 1, 2, 3... indicating the number of rotations of the handle 32 (i.e., the number of times the handle 32 is rotated 180 degrees). Furthermore, the scale 72b that corresponds to the actual rotation amount of the handle 32 in this series of scales 72b is indicated by the scale indicator 34 provided on the handle 32.

[0184] A plurality of resistance-generating protrusions 73 are formed on the outer surface of the middle portion in the axial L1 direction of the ring body portion 71, protruding radially outward and spaced apart around the axis. The outer diameter of these resistance-generating protrusions 73 is smaller than the outer diameter of the dial 72 and smaller than the outer diameter of the locking protrusion 51a of the spacer 50 described later. In addition, the resistance-generating protrusions 73 are located at a position closer to the top end of the locking protrusion 51a in the axial L1 direction than the locking protrusion 51a of the spacer 50. The resistance-generating protrusions 73 pass through a first abutting portion 51d (see reference) that protrudes from the inner surface of the locking protrusion 51a of the spacer 50 described later. Figure 15 The abutment prevents the dial 72 from rotating relative to the handle 32 during rotational operation. In this embodiment, multiple resistance-generating protrusions 73 extend radially outward relative to the central axis J.

[0185] Furthermore, by inserting a locking protrusion 51a of a spacer 50 into the space between the dial 72 and the resistance-generating protrusion 73, the movement of the dial body 70 in the direction of axis L1 is restricted. In this embodiment, a gap is formed between the flat portion 72a of the dial 72 and the top plate portion 32b of the handle portion 32.

[0186] like Figure 4 and Figure 14As shown, a circular recess 71a is formed on the inner side of the ring body portion 71, recessed towards the base end in the L1 direction. An opening communicating with the annular hole portion 74 is formed at the base end of the recess 71a in the L1 direction. A locking protrusion 32a, which is inserted into the handle portion 32 of the annular hole portion 74, and a coil spring 62 are housed in the recess 71a. An annular spring seat 71b recessed towards the base end in the L1 direction is formed around the periphery of the opening. The end of the coil spring 62 at the base end in the L1 direction abuts against the spring seat 71b.

[0187] A plurality of gear plates 47b' protruding toward the top end of the ring body portion 71 in the L1 direction are provided. In this embodiment, the plurality of gear plates 47b' are arranged at predetermined intervals in the circumferential direction to form a gear portion 47b (engaged portion). The gear portion 47b is arranged facing the engagement portion 47a of the shaft portion 40 at a position closer to the base end in the L1 direction. By reciprocating the shaft portion 40 in the L1 direction, it switches between an engaged state of engaging with the engagement portion 47a and a disengaged state of being pulled out of the engaged engagement portion 47a. Furthermore, as described above, the gear portion 47b together with the engagement portion 47a provided on the shaft portion 40 constitutes part of the clutch mechanism 47. By disengaging from the engagement portion 47a during the rotation of the handle portion 32, the rotation of the shaft portion 40 can be transmitted to the scale body 70 or the transmission of the rotation of the shaft portion 40 relative to the scale body 70 can be cut off.

[0188] That is, such as Figure 4 and Figure 23 As shown, in the clutch mechanism 47, when the engagement portion 47a and the gear portion 47b are engaged, the scale body 70 rotates integrally with the handle 32 by transmitting the rotation of the handle 32. On the other hand, when the engagement between these engagement portions 47a and the gear portion 47b is disengaged, the transmission of rotation of the handle 32 relative to the scale body 70 is cut off, and the scale 72b indicated by the scale indicator 34 of the handle 32 is switched by rotating the handle 32 relative to the scale body 70.

[0189] However, when the rotation of the handle 32 is cut off relative to the transmission of the scale body 70, if the scale body 70 is in contact with the handle 32 and a component that rotates integrally with the handle 32, the scale body 70 may rotate with the handle 32 and thus fail to switch the scale 72b accurately. Therefore, in this embodiment, the scale body 70 is provided with a plurality of resistance-generating protrusions 73 that protrude radially outward from the outer surface of the ring body 71 and are arranged at equal intervals around the axis. Furthermore, a first abutment portion 51d (see reference) is provided on the inner surface 51c of the locking protrusion 51a of the spacer 50, protruding toward the top end in the direction of axis L1. Figure 15 ).

[0190] like Figure 15 As shown, the first abutment portion 51d is provided on both radial sides of the central axis J separated by the spacer 50. On the other hand, the resistance-generating protrusion 73 is integrally formed with the ring body portion 71, and its top end can elastically deform in the direction of axis L1 with the base end integrally formed with the ring body portion 71 as the fulcrum. The resistance-generating protrusion 73 is formed into a rectangle extending in the direction of axis L1 when viewed from the side, and the first abutment portion 51d and the surface (resistance-generating surface) of the base end side of the resistance-generating protrusion 73 in the direction of axis L1 can slide against each other. Therefore, when the scale 72b indicated by the scale indicator 34 is switched, the resistance generated between the resistance-generating protrusion 73 and the first abutment portion 51d can prevent the scale body 70, which rotates with the rotation of the handle portion 32, from rotating together.

[0191] Furthermore, the number of first abutment portions 51d provided on the spacer is not limited to two as in this embodiment; multiple portions are acceptable. Additionally, the shape of the resistance-generating protrusion 73 is not limited to a rectangle; any shape suitable for sliding while rubbing can be used.

[0192] like Figure 4 , Figures 15-17 As shown, the spacer 50 is formed as a cylinder extending along the axis L1 direction (central axis J direction), and is disposed radially outside the shaft portion 40 to surround it. A through hole 52 extending along the axis L1 is formed inside the spacer 50, and the inner diameter of the through hole 52 is slightly larger than the outer diameter of the force-applying flange portion 41a of the shaft portion 40. Therefore, the shaft portion 40 can move relative to the spacer 50 along the axis L1 direction. The spacer 50 is formed, for example, of a synthetic resin, preferably of polybutylene terephthalate resin (PBT resin).

[0193] like Figure 17 As shown, a fixing piece 57 protruding radially inward is provided at the top end of the inner surface of the through hole portion 52 of the spacer 50 in the L1 direction. In this embodiment, fixing pieces 57, 57 are provided on both radially opposite sides separated by the central axis J. The fixing piece 57 has: a first facet 57a, which extends along the L1 direction and has an acute angle relative to the inner surface of the through hole portion 52 when viewed from above and extends radially inward; and a second facet 57b, which has a smaller acute angle relative to the inner surface and extends radially inward.

[0194] These fixing pieces 57 are inserted into the formed in Figure 18The spacer 50 is prevented from rotating about the axis L1 within the fixing hole 21b on the base end side of the needle valve holder 21 in the axis L1 direction. This fixing hole 21b is formed in the peripheral wall 21c on the base end side of the needle valve holder 21 in the axis L1 direction, opening at the end of the peripheral wall 21c on the base end side in the axis L1 direction and extending towards the top end side in the axis L1 direction. Furthermore, when viewed from above, the fixing hole 21b extends in a direction inclined relative to the radial direction, and has a first fixing surface 21b1 that abuts against the first surface 57a of the fixing piece 57 and a second fixing surface 21b2 that abuts against the second surface 57b of the fixing piece 57.

[0195] like Figure 17 As shown, an opening 58 extending from the base end side to the top end side in the axial direction is formed on the spacer 50 at a position adjacent to the fixing piece 57 in the circumferential direction. A plate-shaped leg 59 is formed within the opening 58, connected to the end portion on the base end side in the axial direction and extending towards the top end side in the axial direction. A locking protrusion 59a protruding radially inward is provided on the inner surface of the leg 59 on the base end side in the axial direction. The radially inward end of the locking protrusion 59a protrudes slightly inward from the inner surface of the through hole 52 and is locked to a plate-shaped leg 59 formed at intervals in the axial direction. Figure 18 The spacer 50 is fixed between a pair of annular stepped portions 21d and 21d' on the base end side in the L1 direction of the needle valve retainer 21. Therefore, the spacer 50 is restricted from moving relative to the L1 direction of the needle valve retainer 21 and is thus fixed.

[0196] like Figure 16 and Figure 17 As shown, on the base end side of the inner surface of the spacer 50 forming the through hole 52 in the axial L1 direction, a circumferentially annular flange 56 protruding radially inward is formed. This flange 56 has a predetermined thickness in the axial L1 direction. Inside the flange 56, a small-diameter portion 52a of the through hole 52, whose inner diameter is narrowed by the flange 56, passes through in the axial L1 direction. The inner diameter of the small-diameter portion 52a is slightly larger than the outer diameter of the shaft portion 40; therefore, the shaft portion 40 can move freely within the small-diameter portion 52a in the axial L1 direction.

[0197] A cam surface 46 extending circumferentially is formed at the base end of the edge portion 56 in the L1 direction. This cam surface 46 has a cam hole portion 46a extending in the L1 direction and a planar cam plane portion 46b extending circumferentially from the base end of the cam hole portion 46a in the L1 direction. The aforementioned cam-shaped protrusion 41b (see reference) Figure 8The cam can slide on the cam plane portion 46b. The cam hole portion 46a is formed on both radially opposite sides of the spacer 50, separated by the central axis J, in the edge portion 56. The cam hole portion 46a has inclined surfaces 46a1 on both circumferential sides that extend towards the base end in the axis L1 direction as it moves outward in the circumferential direction. In this embodiment, the inclined surfaces 46a1 are formed from the middle portion of the cam hole portion 46a in the axis L1 direction to the base end in the axis L1 direction. The cam hole portion 46a engages with or disengages from the cam-shaped protrusion 41b formed in the aforementioned shaft portion 40, thereby enabling the rotation of the handle portion 32 to be transmitted to the scale body 70 or interrupting the transmission.

[0198] like Figure 16 and Figure 17 As shown, a jump prevention wall 61 is formed at the base end of the inner surface of the spacer 50 forming the through hole portion 52 in the axial L1 direction, protruding radially inward and extending towards the top end in the axial L1 direction. In this embodiment, the jump prevention wall 61 is formed on both radially sides across the central axis J of the spacer 50. The jump prevention wall 61 has an abutment surface 61a extending in a planar shape in the circumferential direction at its top end in the axial L1 direction. This abutment surface 61a, by abutting against the second abutment portion 49 provided in the shaft portion 40 described later, can prevent the shaft portion 40 from moving towards the base end in the axial L1 direction.

[0199] like Figure 15 and Figure 17 As shown, in the middle portion of the spacer 50 in the radially outer direction along the axis L1, an annular protrusion 53 is formed in a ring shape in the circumferential direction, protruding radially outward. When configured to engage the pawl 32e of the handle 32 (see reference...) Figure 20 When the annular protrusion 53 is locked in place, the handle 32 is locked relative to the spacer 50 in the rotational direction, as will be described in detail later. At positions relative to the base end and top end of the annular protrusion 53 in the direction of axis L1, stepped portions 54 and 54' are formed in an annular shape extending radially outward.

[0200] A pair of locking claw portions 51 are provided on the base end side of the spacer 50 in the L1 direction, disposed on both radially opposite sides separated from the central shaft J and protruding towards the base end side in the L1 direction. A locking protrusion 51a is provided at the end of the base end of the locking claw portion 51 in the L1 direction, protruding radially inward. Furthermore, the surface of the locking protrusion 51a facing the base end side in the L1 direction is formed as a planar portion 51b extending in a direction orthogonal to the L1 direction (radial).

[0201] Furthermore, a first abutment portion 51d protruding towards the top end in the L1 direction is provided on the inner surface 51c of the locking protrusion 51a. The first abutment portion 51d is formed as a convex shape protruding towards the top end in the L1 direction. By abutting against the resistance-generating protrusion 73 of the scale body 70 through the first abutment portion 51d, as described above, the co-rotation of the scale 72 relative to the handle 32 can be prevented during the rotation operation of the handle 32. In addition, a plurality of locking recesses 55 recessed radially inward are provided circumferentially at intervals on the outer peripheral surface of the spacer 50 on the base end side in the L1 direction. These locking recesses 55 are used when the rotation of the handle 32 is locked.

[0202] like Figure 4 , Figure 19 and Figure 20 As shown, the handle 32 has a radially extending top plate portion 32b and a cylindrical side plate portion 32c extending from the periphery of the top plate portion 32b toward the top end in the direction of axis L1. The handle 32 is formed into a top cylindrical shape. The handle 32 is formed, for example, from a synthetic resin, preferably from polyacetal resin (POM resin). The handle 32, having this shape, is mounted radially outward of the spacer 50 in a manner surrounding the base end side in the direction of axis L1. Furthermore, a locking protrusion 32a is provided on the inner surface of the top plate portion 32b of the handle 32, extending along the central axis J (i.e., axis L1) and protruding toward the top end in the direction of axis L1. This locking protrusion 32a has a shape similar to the cross-sectional shape of the through hole 43 of the shaft portion 40, relative to the handle insertion hole 44 of the shaft portion 40 (see reference). Figure 11 Insertion. Therefore, as described above, the handle 32 can be fixed to the shaft 40 and rotate integrally around the shaft L1, and on the other hand, it can move relative to the shaft 40 in the direction of the shaft L1.

[0203] Furthermore, a scale indicator 34 is provided on the top plate portion 32b of the handle portion 32, which indicates a scale 72b corresponding to the rotation amount of the handle portion 32. In this embodiment, the scale indicator 34 is a "scale indicator opening" that extends through the top plate portion 32b in the axial L1 direction, and is trapezoidal in shape extending radially inward from the periphery of the top plate portion 32b. The flat portion 72a of the scale dial 72 of the scale body 70 is exposed through the scale indicator opening 34. Therefore, the scale 72b displayed on the flat portion 72a (see reference) can be viewed through the scale indicator 34. Figure 13 ).

[0204] like Figure 20As shown, on the inner circumferential surface of the middle portion in the L1 direction of the side plate portion 32c, a plurality of engaging protrusions 32d are provided at equal intervals in the circumferential direction, protruding radially inward and extending in the L1 direction. When the handle portion 32 moves relative to the shaft portion 40 towards the top end in the L1 direction, the engaging protrusions 32d engage with the locking recess 55 (see reference 50) of the spacer 50. Figure 15 The engagement locks the rotation of the handle 32. On the other hand, when the handle 32 moves toward the base end in the direction of axis L1 from the state of engagement between the engaging protrusion 32d and the locking recess 55, the engaging protrusion 32d is pulled out from the locking recess 55, and the locking state of the rotation direction of the handle 32 is released.

[0205] Here, when the engaging protrusion 32d engages with the locking recess 55 to lock the rotation of the handle 32, as Figure 4 As shown, the engaging claw portion 32e, located on the inner surface of the top end portion in the L1 direction of the side plate portion 32c, engages with the annular protrusion portion 53 located on the outer peripheral surface of the spacer 50, thereby holding the handle portion 32 in the locked position Pr. On the other hand, when the handle portion 32 is moved from the locked position Pr toward the base end side in the L1 direction, the engaging claw portion 32e passes over the annular protrusion portion 53 and engages with the step portion 54 located at a position closer to the base end side in the L1 direction than the annular protrusion portion 53. The engaging claw portion 32e engaged with the step portion 54 becomes clamped between the step portion 54 and the annular protrusion portion 53, and the handle portion 32 is held in an unlocked state.

[0206] Thus, in the flow control valve 10 of this embodiment, the shaft portion 40, the scale body 70, and the spacer 50 are coaxially arranged on the shaft L1 inside the handle portion 32. Therefore, compared with the conventional structure in which the central axis J of the scale body 70 is arranged at a position offset radially relative to the first shaft L1, the flow control valve 10 can be further miniaturized.

[0207] In addition, such as Figure 1 , Figure 2 , Figure 3 and Figure 4 As shown, a second body 13 is connected to the side of the valve receiving portion 12a of the first body 12, extending radially outward from the first body 12. The second body 13 is generally cylindrical in shape, with its base end side extending along its second axis L2 direction (…). Figure 1 The end of the upper part (in the middle) is airtightly sealed, and the top end side in the second axis L2 direction ( Figure 1 The lower end of the shaft L2 has a second port 15. An external thread 18 is formed on the outer periphery of the second port 15 around the shaft L2, which can be connected to the flow path formed in the body of a pneumatic device such as a pneumatic cylinder by screwing.

[0208] Furthermore, a connecting flow path 19 is formed inside the second body 13. This connecting flow path 19 constitutes part of the fluid flow path 16 and connects the internal flow path 16c formed in the first body 12 with the second port 15. The connecting flow path 19 is composed of a connecting flow path 19a and a port flow path 19b. The connecting flow path 19a extends radially within the second body 13, orthogonal to the second axis L2, and connects to the internal flow path 16c of the first body 12. The port flow path 19b extends along the second axis L2 within the second body 13, with one end connected to the connecting flow path 19a and the other end connected to the second port 15. That is, the port flow path 19b is formed at a distance X (referring to...) radially outward from the axis L1 away from the second axis L2. Figure 2 The position of ).

[0209] Next, refer to Figures 21-23 The switching action of the scale 72b corresponding to the rotation operation amount of the handle 32 will be explained. Figure 21 This shows the state where the handle 32 moves to the locked position Pr, thus restricting the rotation of the handle 32. In this state, the handle 32 is pressed against the top side in the direction of axis L1, and the engaging protrusion 32d of the handle 32 (see reference) Figure 20 The locking recess 55 of the spacer 50 (see reference) Figure 15 The rotation of the handle 32 is restricted by the engagement of the spring 62. Additionally, the shaft 40 is protected by the coil spring 62 (see reference). Figure 4 The force of the clutch drive mechanism 48 is applied to the top side in the direction of shaft L1, and the cam profile protrusion 41b of the clutch drive mechanism 48 abuts against the cam plane portion 46b of the cam surface 46, and is in the state of engagement between the meshing portion 47a and the gear portion 47b of the clutch mechanism 47.

[0210] When the handle 32 is moved towards the base end in the direction of shaft L1 from this state to release the locking state of the handle 32, and the handle 32 is rotated in the counterclockwise direction, the handle 32 and the shaft 40 rotate, and the cam-shaped protrusion 41b slides on the cam plane 46b. When the handle 32 is rotated in the counterclockwise direction (the + direction of the arrow) with the scale body 70 and the shaft 40 fixed to each other around shaft L1, the scale body 70 and the shaft 40 rotate in the same direction as the handle 32, and the cam-shaped protrusion 41b of the clutch drive mechanism 48 moves toward the cam hole 46a while sliding on the cam plane 46b.

[0211] And, as Figure 22As shown, when the cam-contouring protrusion 41b approaches the cam hole 46a of the cam surface 46, the shaft 40 moves towards the top end in the direction of shaft L1 due to the force of the coil spring 62. Simultaneously, the cam-contouring protrusion 41b moves into the cam hole 46a, thereby disengaging the engagement between the meshing part 47a and the gear part 47b. Therefore, the rotation of the shaft 40 is no longer transmitted to the scale body 70, and the rotation of the scale body 70 stops. In this state, when the handle 32 is further rotated, the side surface 41b1 of the cam-contouring protrusion 41b overcomes the force of the coil spring 62 and moves along the inclined surface 46a1 of the cam hole 46a towards the base end in the direction of shaft L1. Simultaneously, the scale indicator 34 (scale indicator opening) formed on the handle 32 rotates on the scale 72 of the stopped scale body 70, and the scale 72b indicated by the scale indicator 34 is switched to the adjacent scale 72b. For example, in Figure 21 In the middle, the scale 72b displayed by the scale indicator opening 34 switches from "0" to "1".

[0212] Furthermore, when the cam-shaped protrusion 41b is pulled out from the cam hole portion 46a and moves to the position abutting on the cam plane portion 46b, as... Figure 23 As shown, the gear portion 47b of the clutch mechanism 47 re-engages with the meshing portion 47a, and the scale body 70 and the handle portion 32 are fixed to each other around the axis L. Therefore, the scale body 70 and the handle portion 32 rotate as a single unit again.

[0213] Here, when the handle 32 is violently rotated counterclockwise while the cam-following protrusion 41b is engaged with the cam hole 46a, the shaft 40 violently moves towards the base end in the direction of shaft L1 due to the reaction force from the inclined surface 46a1 of the cam hole 46a, which abuts against the side 41b1 of the cam-following protrusion 41b. Sometimes, the meshing part 47a abuts against the gear part 47b, producing a sound. Therefore, in the flow control valve 10 of this embodiment, a jump prevention mechanism 60 is provided, which is used to prevent the shaft 40 from violently moving towards the base end in the direction of shaft L1 even when the handle 32 is violently rotated counterclockwise while the cam-following protrusion 41b is engaged with the cam hole 46a.

[0214] Next, refer to Figures 21-26 The jump prevention mechanism 60 is described. Furthermore, Figure 24 Showing views from other angles Figure 21 A partial cross-sectional view of the flow control valve 10 shown. Figure 25 Showing views from other angles Figure 22 A partial cross-sectional view of the flow control valve 10 shown. Figure 26 Showing views from other angles Figure 23 A partial cross-sectional view of the flow control valve 10 shown.

[0215] like Figure 24 As shown, the jump prevention mechanism 60 is configured to have a second abutment portion 49 provided on the aforementioned shaft portion 40 and a jump prevention wall 61 provided on the spacer 50. Figure 21 and Figure 24 As shown, with the cam contouring protrusion 41b abutting against the cam plane portion 46b and the meshing portion 47a meshing with the gear portion 47b, the second abutting portion 49 is located circumferentially closer to the front side than the jump prevention wall 61, and is in a non-contact state relative to the jump prevention wall 61.

[0216] Furthermore, rotate the handle 32 counterclockwise, as follows: Figure 22 and Figure 25 As shown, when the cam-shaped protrusion 41b moves into the cam hole 46a of the cam surface 46, the second abutment portion 49 moves directly below the top end side of the jump prevention wall 61 in the axial L1 direction. In this state, the flat portion 49a of the second abutment portion 49 approaches and faces the abutment surface 61a of the jump prevention wall 61, and the meshing portion 47a and the gear portion 47b are in a non-engaged state, separated from each other.

[0217] Therefore, when the shank 32 is violently rotated counterclockwise while the cam profile protrusion 41b is engaged with the cam bore 46a, causing the shaft 40 to move towards the base end in the direction of shaft L1, the flat surface 49a of the second abutment 49 abuts against the abutment surface 61a of the jump prevention wall 61, preventing further movement of the shaft 40 towards the base end in the direction of shaft L1, thereby preventing the meshing part 47a from abutting against the gear part 47b. Thus, noise generated by the meshing part 47a abutting against the gear part 47b can be prevented.

[0218] Furthermore, when the handle 32 is rotated further counterclockwise while the second abutment portion 49 is close to and facing the jump prevention wall 61, as... Figure 26 As shown, the second abutment part 49 moves circumferentially inward toward the jump prevention wall 61, and the meshing part 47a engages with the gear part 47b again.

[0219] Thus, in the flow control valve 10 of this embodiment, the top cylindrical handle 32, the scale body 70, the clutch mechanism 47 for switching the scale body 70, and the spacer 50 are coaxially arranged on the shaft L1. Therefore, compared with the conventional structure in which the central axis J of the scale body 70 is arranged at a position offset radially relative to the shaft L1, for example, the radial dimension of the first body 12 can be made smaller, and thus the flow control valve 10 can be further miniaturized.

[0220] Figure 27 A modified example of the spacer 50 of the aforementioned flow control valve 10 is shown. In the above embodiment, as... Figure 17 As shown, a case is described in which cam holes 46a, 46a are provided on both radially opposite sides of the guard portion 56 of the spacer 50, separated by the central shaft J. In this case, the scale 72b switches every time the handle 32 is rotated 180 degrees, therefore the scale does not correspond to the number of rotations of the handle. Therefore, as... Figure 27 As shown, when only one cam hole 46a is provided in the cutter 56, the scale 72b can be switched every time the handle 32 rotates 360 degrees, that is, every time the handle 32 rotates one revolution. Therefore, the number of rotations of the handle 32 can be made consistent with the scale 72b.

[0221] Furthermore, in the above embodiment, the scale indicator 34 indicating the scale 72b is shown as a scale indicator opening provided in the top plate portion 32b of the handle portion 32, but it is not limited to this; the scale indicator 34 may also be, for example, an arrow. Moreover, the numbers on the scale 72b do not need to represent the number of times the handle portion 32 is rotated 180 degrees as in this embodiment. For example, it may be set to represent the number of rotation operations of the handle portion 32 corresponding to each opening degree of the needle valve 27 by equally dividing the integer opening degree of the needle valve 27.

[0222] In addition, in the above embodiment, a clutch drive mechanism 48 is shown as an axial drive unit that moves the shaft 40 in the direction of shaft L1, but it is not limited to this and various drive units can be used.

Claims

1. A flow control valve, the flow control valve comprising: The main body extends axially; Flow path, the flow path being formed within the body; A handle is disposed on one axial side of the body and is supported on the body in a manner that allows it to rotate about the axial direction; as well as A needle valve, wherein the needle valve is arranged coaxially with the handle within the body and moves axially according to the rotational operation of the handle, thereby adjusting the opening of the flow path. The flow control valve is capable of controlling the flow rate of the fluid flowing in the flow path based on the amount of rotation of the handle, and the flow control valve is characterized in that... The flow control valve also has: A scale body, which is supported on the handle in a manner that allows it to rotate about the axis, and is provided with scales indicating the amount of rotation of the handle; A scale indicator, wherein the scale indicator and the handle rotate integrally around the axis and indicate the scale corresponding to the rotation operation amount of the handle; A shaft portion is disposed on the opposite side of the axial direction from the scale body, and is supported on the handle portion in a manner that allows it to move along the axial direction and rotate integrally with the handle portion about the axial direction. as well as A clutch mechanism that transmits rotation of the lever to the scale body or cuts off the transmission, thereby switching the scale indicated by the scale indicator whenever the lever is rotated by a predetermined angle. The clutch mechanism is configured to have an engaging portion and a engaged portion. The engaging portion is disposed on the shaft portion, and the engaged portion is disposed on the scale body and positioned axially closer to the engaging portion. By engaging the engaging portion and the engaged portion with each other, the rotation of the handle portion is transmitted to the scale body, causing the scale indicator portion and the scale body to rotate integrally around the axial direction. The clutch mechanism also includes a clutch drive mechanism, which releases the engagement of the engaging part from the engaged part by moving the shaft to the other side of the axis whenever the handle is rotated by a predetermined angle. This allows the scale indicator to rotate about the axis relative to the scale body by rotating the handle. After switching the scale indicated by the scale indicator relative to the scale body by this rotation of the scale indicator relative to the scale body, the engaging part and the engaged part are engaged again.

2. The flow control valve according to claim 1, characterized in that, The clutch drive mechanism includes: a cam surface fixedly disposed on the main body and extending annularly around the axial direction; and a cam-shaped protrusion disposed on the shaft and facing the cam surface, rotating around the axial direction and sliding on the cam surface as the handle rotates. The cam surface has: A cam hole portion, the cam hole portion extending axially; and The cam planar portion extends in a planar shape from one axial end of the cam bore portion toward the axial side. The clutch drive mechanism releases the engagement between the engaged portion and the engaged portion by moving the cam-shaped protrusion into the cam hole and engaging whenever the handle is rotated by a predetermined angle, thereby allowing the scale indicator to rotate about the axis relative to the scale body by rotating the handle.

3. The flow control valve according to claim 2, characterized in that, The clutch drive mechanism has a spring portion that always applies force to the shaft portion toward the other side of the axial direction. Through the force applied by the spring portion, the shaft portion moves toward the other side of the axial direction along with the cam-shaped protrusion moving into the cam hole portion. After switching the scale indicated by the scale indicator portion, the cam-shaped protrusion overcomes the force applied by the spring portion and moves toward the axial side to abut against the cam plane portion, thereby causing the engaged portion to engage with the engaged portion again.

4. The flow control valve according to claim 2 or 3, characterized in that, The scale body has a plurality of resistance-generating protrusions spaced apart around the axial direction. The flow control valve has a locking protrusion that can slidably abut against the plurality of resistance-generating protrusions. The locking protrusion is positioned on any side axially relative to the plurality of resistance-generating protrusions and is fixedly attached to the main body. When the engagement between the locked part and the locking part is released, the resistance generated by the locking protrusion abutting against any one of the plurality of resistance generating protrusions prevents the scale body from rotating together with the rotation of the handle.

5. The flow control valve according to claim 4, characterized in that, The locking protrusion has a first abutting portion that protrudes towards the other side of the axial direction and can slidably abut against the resistance-generating protrusion. The plurality of resistance-generating protrusions extend radially outward at equal intervals around the axial direction.

6. The flow control valve according to claim 2 or 3, characterized in that, The flow control valve has an abutment surface that is fixedly disposed on the main body and faces the other side of the axial direction. The shaft portion has a second abutting portion that is arranged facing the abutting surface and is capable of abutting against it. The second abutting part abuts against the abutting surface when the cam-shaped protrusion is pulled out of the cam hole by rotating the handle from the state where the cam-shaped protrusion is engaged with the cam hole, thereby preventing the shaft from moving to one side in the axial direction.

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