JP2021066528A - Fluid supply device - Google Patents

Abstract

To increase a degree of freedom of a design of a fluid supply device, while improving durability and reliability.SOLUTION: A fluid supply device 1 comprises: a valve stem 213 connected to a main valve 212; a piston part 215 that receives an operating force of an operating lever 221; a cylinder part 211 in which a portion of a fuel F is filled in a fluid chamber 211A; a regulating valve 233 that blocks a first ejection hole 211D of the cylinder part 211; and an atmospheric pressure variable chamber 232 that opens the first ejection hole 211D by sucking the regulating valve 233 by a negative pressure when the fuel F discharged from a discharge pipe 4 reaches a specified quantity. The fluid supply device 1 transmits the operating force of the operating lever 221 to the valve stem 213 by the piston part 215 and the fuel F inside the fluid chamber 211A to move the main valve 212 to an open position (valve opening operation), and opens the first ejection hole 211D when a liquid level detector 42 detects a discharge amount of the fuel F discharged from the discharge pipe 4 and ejects the fuel F inside the fluid chamber 211A to return the valve stem 213 and the main valve 212 to a closed position (valve closing operation).SELECTED DRAWING: Figure 1

Description

The present invention relates to, for example, a fluid supply device such as a refueling nozzle used when supplying fuel to a fuel tank of a vehicle at a gas station.

Conventionally, a pistol-type refueling nozzle is known as a refueling nozzle used in a gas station (see Patent Document 1, FIGS. 1 and 2).

When the user inserts the discharge pipe protruding from the nozzle body of the refueling nozzle into the refueling port of the vehicle and then grasps or pulls the operation lever, the main valve provided in the nozzle body opens. It is configured to discharge fuel from the discharge pipe to the fuel tank of the vehicle. Then, when the amount of fuel supplied to the fuel tank reaches the amount that fills the fuel tank, the liquid level detection unit that detects the liquid level of the fuel provided at the tip of the discharge pipe detects it, and the user operates the lever. The main valve is automatically closed to stop the fuel from being discharged from the discharge pipe without canceling the operation of.

That is, in the refueling nozzle, the main valve, which is normally held at a position where the fuel flow path in the nozzle body is cut off (hereinafter referred to as "closed position"), is opened by operating the operation lever of the user. After switching the manual valve opening mechanism to the open position (hereinafter referred to as the "open position") and the main valve to the open position, the amount of fuel discharged from the discharge pipe by the liquid level detection unit has reached a predetermined amount. When this is detected, an automatic valve closing mechanism is provided that automatically returns the main valve to the closed position even when the user maintains the operation of the operating lever.

FIG. 2 of Patent Document 1 describes the configuration of the valve opening / closing mechanism shown in FIG. 14 (cross-sectional view) as a valve opening / closing mechanism having a manual valve opening mechanism and an automatic valve closing function of the refueling nozzle.

In the refueling nozzle 500 shown in FIG. 14, the operating force of the first valve shaft 506 to which the main valve body 505 is connected and the operating force of the nozzle lever 513 are transmitted to the valve shaft that transmits the operating force of the nozzle lever 513 to the main valve body 505. The second valve shaft 509 is separated into two valve shafts so that the valve shafts 506 and 509 can be moved independently, and the user is not operating the nozzle lever 513 (the state of FIG. 14; , "Initial state"), the first valve shaft 506 and the second valve shaft 509 are locked by the locking member 511.

In the initial state, the first valve shaft 506 is urged by the first spring 507 so that the main valve body 505 is pressed against the valve seat 504, and the second valve shaft 509 is also urged by the second spring 510. It is urged in the same direction as the first valve shaft 506. Then, in the initial state, the first valve shaft 506 and the second valve shaft 509 are held at positions where the portion (locking portion) 512 into which the locking member 511 is fitted coincide with each other, and both locking members 511 are locked. Both valve shafts 506 and 509 are locked by fitting into the portion 512.

A diaphragm 508 is connected to the locking member 511, and the locking member 511 can release the lock between the first valve shaft 506 and the second valve shaft 509 by the displacement of the diaphragm 508. The diaphragm 508 is provided with a negative pressure chamber 508A, and the negative pressure chamber 508A is communicated to the outside by an air suction pipe line 502 provided in the discharge pipe 501. The air suction pipeline 502 communicates with the negative pressure chamber 508A and is branched in the middle to provide a check valve 503 for the flow path on the downstream side of the main valve body 505 (a portion where negative pressure is generated. Hereinafter, It also communicates with the "negative pressure generating part").

When the liquid level of the fuel supplied to the fuel tank of the vehicle reaches the air introduction port (not shown) of the air suction pipe line 502 provided at the tip of the discharge pipe 501, the diaphragm 508 reaches the negative pressure generating unit 503. Due to the generated negative pressure, the air pressure in the negative pressure chamber 508A is lowered to displace the diaphragm 508.

Therefore, after the main valve body 505 is switched from the position where the main valve body 505 is pressed against the valve seat 504 (closed position) to a position away from the valve seat 504 (open position) (after fuel discharge is started from the discharge pipe 501). When the liquid level of the fuel supplied to the fuel tank of the vehicle reaches the air inlet, the air pressure in the negative pressure chamber 508A drops and the diaphragm 508 is displaced, so that the locking member 511 becomes the first and second valves. Only the main valve body 505 and the first valve shaft 506 are disengaged from the locking portion 512 of the shafts 506 and 509 and returned to the closed position by the urging force of the first spring 507.

After that, when the user stops the operation of the nozzle lever 513, the second valve shaft 509 moves in the direction of the first valve shaft 506 by the urging force of the second spring 510, and the second valve shaft 509 is locked. When the portion 512 coincides with the locking portion 512 of the first valve shaft 506, the locking member 511 is fitted into the locking portion 512 and returns to the initial state.

As described above, the valve opening / closing mechanism of the conventional refueling nozzle 500 urges the main valve body 505, the first valve shaft 506, the second valve shaft 509, and the first and second valve shafts 506 and 509, respectively. A manual valve opening mechanism is configured by the first and second springs 507 and 510 and the nozzle lever 513, and the valve is automatically closed by the air suction pipe line 502 of the discharge pipe 501, the diaphragm 508, the negative pressure chamber 508A and the locking member 511. The mechanism is configured.

Japanese Unexamined Patent Publication No. 2008-247407 (Figs. 1 and 2)

The conventional refueling nozzle 500 having an automatic valve closing function transmits the operating force of the nozzle lever 513 from the second valve shaft 509 to the first valve shaft 506 to move the main valve body 505 to the open position. , Only the main valve body 505 and the first valve shaft 506 can be returned to the closed position while holding the operating position of the nozzle lever 513 (the state where the second valve shaft 509 is held in the open position). Therefore, the first valve shaft 506 and the second valve shaft 509 are separated, and the locking member 511 can be inserted / detached from the locking portion 512 of the first valve shaft 506 and the second valve shaft 509. It is provided so that the operating force of the nozzle lever 513 transmitted to the second valve shaft 509 is transmitted to the first valve shaft 506 via the locking member 511.

Since the first valve shaft 506, the second valve shaft 509, and the locking member 511 are solid objects, the first valve shaft 506 and the locking member 506 are locked on the line in the direction in which the second valve shaft 509 transmits the operating force. There is a drawback that the member 511 must be arranged and the degree of freedom in designing the valve opening / closing mechanism is small.

Since the locking member 511 of the automatic valve closing mechanism is a movable member, there is a problem that the number of parts is increased and the mechanical structure is complicated. Further, when the automatic valve closing mechanism operates, the locking member 511 is in pressure contact with the first valve shaft 506 and the second valve shaft 509 (a state in which a large frictional force is applied to the locking member 511). Since the locking member 511 is moved laterally, the locking member 511 is deteriorated over time such as wear and rattling. Such deterioration over time is the same for the locking portion 512 of the first valve shaft 506 and the second valve shaft 509. Therefore, there is a problem that the durability and reliability of the valve opening / closing mechanism are not sufficient.

The present invention has been made in view of the above problems, and an object of the present invention is to provide a fluid supply device having a valve opening / closing mechanism having a degree of freedom in design, durability and reliability as compared with the conventional one. ..

The fluid supply device provided in the first aspect of the present invention is connected to a nozzle body having a flow path for guiding the supplied fluid to the discharge pipe and the flow path, and a part of the fluid is filled. The connection portion between the cylinder portion having the fluid chamber to be formed and the cylinder portion of the flow path is provided so as to be movable between an open position for opening the flow path and a closed position for closing the flow path, and is usually in a closed position. The main valve urged to, an operating means for switching the main valve to the open position, one end is movably housed in the fluid chamber, and the other end is exposed from the fluid chamber. The valve shaft, which is connected to the main valve and is normally urged toward the fluid chamber side of the cylinder portion, has one end protruding from the cylinder portion and brought into contact with the operating means, and the other end is the cylinder portion. It is characterized in that it is provided with a piston portion that is provided so as to be movable in and out of the fluid chamber in a state of facing the inflow port into which the fluid flows, and is normally urged toward the operating means. (Claim 1).

According to a preferred embodiment of the fluid supply device, the flow path of the nozzle body is regulated to regulate the movement of the main valve at a predetermined position when the main valve moves from the closed position to the open position. It is preferable that the means is provided (claim 2).

Further, according to a preferred embodiment of the fluid supply device, a first discharge hole provided at an appropriate position on the inner surface of the cylinder portion for discharging the fluid in the fluid chamber to the outside, and the first discharge hole. It is preferable to further provide a safety mechanism including a safety valve that is openably and closably attached to the discharge hole and is usually urged on the first discharge hole side (claim 3).

Further, according to a preferred embodiment of the above-mentioned fluid supply device, a second is provided at a position different from the first discharge valve on the inner surface of the cylinder portion to discharge the fluid in the fluid chamber to the outside. A control valve that is displaceably provided at an open position that opens the second discharge hole and a closed position that closes the second discharge hole, and is normally urged to the closed position, and the main An automatic valve closing mechanism including a valve closing means for returning the main valve to the closed position when a predetermined condition is satisfied after the valve is switched to the open position may be further provided (claim 4). ..

Further, according to a preferred embodiment of the fluid supply device according to claim 4, the valve closing means is communicated to the outside via the discharge pipe, and the negative pressure of the flow path in the nozzle body is applied. It is preferable that the side surface of the diaphragm communicating with the generated portion and facing the discharge hole is composed of a pressure fluctuation chamber sealed with a diaphragm, and the adjusting valve is attached to the surface of the diaphragm facing the discharge hole (claim). Item 5).

Further, according to a preferred embodiment of the fluid supply device according to claim 4 or 5, the second discharge hole may be arranged closer to the valve shaft piston portion than the first discharge hole. (Claim 6).

Further, according to a preferred embodiment of the fluid supply device according to any one of claims 4 to 6, the valve closing means means that the amount of fluid discharged from the discharge pipe has reached a predetermined amount of fluid. It is preferable that the fluid amount detecting means for detecting is provided and the predetermined condition is satisfied when the fluid amount detecting means detects that the discharge amount from the discharge pipe has reached the predetermined fluid amount (claimed). Item 7).

Further, according to a preferred embodiment of the fluid supply device according to any one of claims 4 to 7, the piston portion is provided at a position above the upper end of the piston portion, and the front operating means is not operated at the initial stage. In the state, the first and second discharge holes are shielded, and when the operating means is operated, the upper end of the piston portion reaches a position of closing the inflow port of the cylinder portion. It is preferable to further include a shielding member for releasing the shielding of the discharge hole of the above, and a connecting member for connecting the shielding member to the piston portion (claim 8).

Further, according to a preferred embodiment of the fluid supply device according to claim 8, the shielding member and the connecting member have the length of the piston portion, and the upper end portion of the piston portion discharges the first portion in the initial state. When a hollow portion with an open tip is formed in the extended portion while extending to a position where the hole is shielded, and the piston portion is moved to a position where the upper end of the piston portion closes the inflow port of the cylinder portion. It is preferable that the first and second discharge holes are provided at a position above the upper end of the piston portion by forming a communication hole that communicates with the cavity portion (claim 9).

Further, according to a preferred embodiment of the fluid supply device, the piston portion has a rotation prevention portion that prevents rotation of the piston portion around an axis when the piston portion moves in and out of the fluid chamber. (Claim 10).

According to the fluid supply device according to the present invention, when the piston portion is pushed into the fluid chamber of the cylinder portion by the operating means, the fluid pressure in the fluid chamber rises. The valve shaft is pushed out of the cylinder due to the rise in the fluid pressure in the fluid chamber, and the main valve urged in the closed position moves to the open position against the urging force in the flow path in the nozzle body. The blocked fluid is discharged to the discharge pipe (main valve opening operation).

As described above, according to the present invention, the valve opening of the main valve is caused by a change in the fluid pressure of the fluid interposed between the valve shaft to which the main valve is connected and the piston portion on which the operating force of the operating means acts. Since the operation is performed, there is no mechanical damage to the conventional configuration in which the piston portion and the valve shaft are mechanically connected / detached, and deterioration over time can be reduced.

Further, there is no restriction that the moving direction of the piston portion and the moving direction of the valve shaft are set linearly, and the degree of freedom in designing the valve opening / closing mechanism is improved.

Further, since a locking member for locking the conventional piston portion and the valve shaft is not required, the structure of the valve opening / closing mechanism is simplified.

It is a vertical cross-sectional view which shows the internal structure of the fluid supply device (refueling nozzle) which concerns on 1st Embodiment. It is a figure for demonstrating the refueling operation of a refueling nozzle. It is a figure for demonstrating the refueling operation of a refueling nozzle. It is a figure for demonstrating the function of a regulation part and a safety valve. It is a figure for demonstrating the function of a regulation part and a safety valve. It is a vertical sectional view which shows the internal structure of the refueling nozzle which concerns on 2nd Embodiment. It is a vertical sectional view which shows the internal structure of the refueling nozzle which concerns on 3rd Embodiment. It is a vertical sectional view which shows the internal structure of the refueling nozzle which concerns on 4th Embodiment. It is a vertical sectional view which shows the internal structure of the refueling nozzle which concerns on 5th Embodiment. It is a vertical sectional view of a main part which shows the modification of the structure of a main valve. It is a vertical sectional view which shows the internal structure of the refueling nozzle which concerns on 6th Embodiment. It is a perspective view which shows the structure of the piston part used for the refueling nozzle which concerns on 6th Embodiment. FIG. 9 is a cross-sectional view of a main part of line XX of FIG. It is a figure which shows the structure of the piston part used for the refueling nozzle which concerns on 6th Embodiment, (a) is a front view, (b) is a sectional view taken along line YY of FIG. 12 (a) is a sectional view taken along line ZZ. In the refueling nozzle according to the sixth embodiment, (a) is a diagram showing a state in which the operation lever is operated until the bottom surface of the hollow portion of the piston portion rises to the position of the inflow port of the cylinder portion, and (b) is a main diagram. It is a figure which shows the state which the operation lever was operated until the valve was raised to the open position. It is a figure which shows an example of the valve opening and closing mechanism of the conventional refueling nozzle.

Hereinafter, embodiments of the fluid supply device according to the present invention will be described with reference to the drawings. In the embodiment, the components with the same reference numerals perform the same operation, and thus the description may be omitted again.

FIG. 1 is a vertical cross-sectional view showing the internal structure of the fluid supply device according to the first embodiment. In the fluid supply device 1 shown in FIG. 1, a user supplies (subdivides) a fluid (mainly a liquid) having fluidity from a storage chamber or a storage tank to a small or portable tank (container). It is used as an operating device for starting and stopping supply. In the cross-sectional views of FIGS. 1 to 13, in order to make it easier to see the structure of the members, the cross sections of the members are displayed in gray colors having different densities instead of diagonal lines.

As a typical example to which such an operating device is applied, for example, a refueling nozzle used when supplying fuel from a weighing device to a fuel tank of a vehicle at a gas station is known.

When a user or a salesperson operates a refueling nozzle at a gas station to supply fuel until the fuel tank of the vehicle is full, it is difficult for the user or the like to know when the fuel tank is full. Even if the timing can be known, the fuel is discharged at high speed, so it is difficult to stop the fuel supply at the optimum timing.Therefore, in general, the refueling nozzle is provided with an automatic valve closing mechanism. Has been done.

The automatic valve closing mechanism is provided at the tip of the discharge pipe with a detection unit that detects that the liquid level of the fuel supplied to the fuel tank has reached the tip (the fuel tank is full), and the detection unit is the fuel. When it detects that the tank is full, it is a mechanism that automatically closes the main valve provided in the main body of the fluid supply device to stop the fuel supply.

A fluid supply device equipped with an automatic valve closing mechanism not only supplies fuel at a gas station, but also supplies fluids such as water, fuel, solvent, and chemicals from a storage tank or water truck to a small or portable tank. It is widely applied as an operating device of. Further, in a production line for manufacturing a product in which a fluid is stored in a container of a bottle or a can body, a fluid supply device provided with an automatic valve closing mechanism can be applied as a filling nozzle for filling a container with a predetermined amount of fluid.

In the following description, the fluid supply device 1 will be referred to as a “refueling nozzle 1”, and a case where the fluid supply device 1 is applied to a refueling nozzle used in a gas station will be described as an example.

The refueling nozzle 1 is roughly divided into a nozzle body 2, a grip portion 3, and a discharge portion 4. The nozzle body 2 is a portion provided with a valve opening / closing mechanism 21, an operating mechanism 22, an automatic valve closing mechanism 23, and a safety mechanism 24. The valve opening / closing mechanism 21 discharges the fluid (fuel) supplied by the liquid supply hose 6 from the measuring device (not shown) from the discharge unit 4 to the outside (fuel tank of the vehicle) (hereinafter, referred to as “discharge state”). It is a mechanism that switches the state of shutting off the discharge of fuel to the fuel tank (hereinafter, referred to as "discharge shutoff state") by the main valve 212.

The operation mechanism 22 is a mechanism for switching the fuel discharge cutoff state to the discharge state by operating the operation lever 221 by the user. The operating lever 221 corresponds to the "operating means" of the present invention. The automatic valve closing mechanism 23 is a mechanism that detects that the fuel tank of the vehicle is full by the liquid level detection unit 42 provided in the discharge unit 4 and automatically switches the fuel discharge state to the discharge cutoff state. .. The liquid level detecting unit 42 corresponds to the "fluid amount detecting means" of the present invention. Detecting that the fuel tank of a vehicle is full corresponds to "detecting that a predetermined condition is satisfied" of the present invention.

When the hydraulic pressure of the fluid chamber 211A of the cylinder portion 211, which will be described later, becomes equal to or higher than a predetermined hydraulic pressure threshold value, the safety mechanism 24 discharges the fluid from the fluid chamber 211A to lower the hydraulic pressure, and the cylinder portion 211 has an excessive liquid. It is a mechanism that prevents damage due to pressure. The hydraulic pressure threshold value is a hydraulic pressure value at which the cylinder portion 211 may be damaged by the hydraulic pressure of the fluid chamber 211A. When the user normally operates the operation lever 221, the hydraulic pressure of the fluid chamber 211A of the cylinder portion 211 is set so as not to exceed the hydraulic pressure threshold value.

The normal operation of the operation lever 221 is a predetermined position (main) that does not exceed the position where the operation amount is regulated by the user at a normal speed (the position where the movement of the main valve 212 is regulated by the regulation unit 219A described later). The operation of gripping the operation lever 221 to the position where the valve 212 opens the flow path blocking portion 5A), and the operation of gripping at a high speed higher than the normal speed (steep operation) or the operation lever beyond the position where the amount of operation is regulated. The operation of squeezing the 221 is an abnormal operation of the operation lever 221. Therefore, the safety mechanism 24 is a mechanism that operates when the hydraulic pressure of the fluid chamber 211A becomes equal to or higher than the hydraulic pressure threshold value due to an abnormal operation of the operation lever 221 by the user.

The grip portion 3 is a portion for the user to grip the nozzle body 2. The grip portion 3 is provided on one end side (right end side in FIG. 1) of the upper portion of the nozzle body 2, and a liquid supply hose 6 is connected to the tip of the grip portion 3.

The discharge unit 4 is a portion that discharges the fuel F supplied to the nozzle body 2 at a predetermined pressure by the liquid supply hose 6 to the fuel tank of the vehicle. The discharge portion 4 is composed of a thin pipe and is provided on the other end side (left end side in FIG. 1) of the upper portion of the nozzle body 2. A liquid level detection unit 42 is provided in the vicinity of the discharge port 41 from which the fuel F of the discharge unit 4 (hereinafter referred to as “discharge pipe 4”) is discharged. The liquid level detection unit 42 is an opening 235A of a thin tube 235 that communicates with the atmospheric pressure fluctuation chamber 232, which is a component of the automatic valve closing mechanism 23, provided in the discharge pipe 4. The liquid level detection operation in the fuel tank by the liquid level detection unit 42 will be described later.

An L-shaped curved flow path 5 from the grip portion 3 to the discharge pipe 4 is formed in the nozzle body 2. The flow path 5 is composed of a first flow path 51 formed in the grip portion 3 and a second flow path 52 formed at the base end portion of the discharge pipe 4. A valve opening / closing mechanism 21 is provided below the bent portion 5A of the flow path 5, and an automatic valve closing mechanism 23 is provided below the second flow path 52. The bent portion 5A is a portion that functions as a gate that shuts off the fuel F flowing in the flow path 5, and a main valve 212 is provided in the bent portion 5A (hereinafter, referred to as “flow path blocking portion 5A”). Further, a check valve 43 for preventing the backflow of the fuel F is provided at the tip end portion (base end portion of the discharge pipe 4) of the second flow path 52.

The check valve 43 has the shape of a truncated cone, and is attached so that the tip end side of the tip constriction faces the upstream side (flow path blocking portion 5A side) of the second flow path 52. The base end side of the check valve 43 is urged to the upstream side of the second flow path 52 by the fifth spring 44. A conical bowl-shaped valve seat 45 is provided at the arrangement position of the check valve 43 of the second flow path 52, and when the main valve 212 closes the flow path blocking portion 5A, the check valve 43 is checked by the fifth spring 44. The valve 43 is pressed against the valve seat 45 to block the second flow path 52.

When the main valve 212 opens the flow path blocking portion 5A, the fuel F cut off by the main valve 212 flows out from the first flow path 51 to the second flow path 52 at a predetermined pressure, and the fifth spring 44 is attached. The check valve 43 is pushed toward the discharge pipe 4 against the force. As a result, a gap is created between the check valve 43 and the valve seat 45, and the fuel F flows out to the discharge pipe 4 side from the gap. When the fuel F flows out to the discharge pipe 4, a negative pressure is generated in the gap portion 52A between the check valve 43 and the valve seat 45 due to the Venturi effect.

The atmospheric pressure fluctuation chamber 232 is communicated with a gap portion 52A (hereinafter, referred to as “negative pressure generating portion 52A”) between the check valve 43 and the valve seat 45, and the fuel F is discharged to the discharge pipe 4. In the state, the air in the atmospheric pressure fluctuation chamber 232 is sucked by the negative pressure generated in the negative pressure generating unit 52A.

When the opening 235A of the discharge pipe 4 is exposed to the outside air, air is supplied from the thin tube 235 to the air pressure fluctuation chamber 232. Therefore, even if a negative pressure is generated in the negative pressure generating portion 52A, the air pressure in the pressure fluctuation chamber 232 Is the same as the outside air pressure. On the other hand, when the opening 235A is closed by the fuel F supplied to the fuel tank, the air pressure in the pressure fluctuation chamber 232 is lower than the outside air pressure because the air supply from the opening 235A to the pressure fluctuation chamber 232 is stopped. The liquid level detecting unit 42 detects that the liquid level of the fuel F supplied to the fuel tank of the vehicle reaches a position of closing the opening 235A of the thin pipe 235 in the discharge pipe 4 by utilizing this phenomenon.

The valve opening / closing mechanism 21 includes a cylinder portion 211 in which a part of the fuel F supplied from the liquid supply hose 6 is filled in the internal space 211A, a cylindrical valve shaft 213 in which the main valve 212 is connected to the upper end, and a main body. A first spring 214 that urges the valve 212 downward (the direction in which the main valve 212 closes the flow path blocking portion 5A), and a piston portion 215 that transmits the vertical movement of the operating lever 221 operated by the user to the valve shaft 213. , It is composed of a second spring 216 that urges the piston portion 215 in the downward direction (operation lever 221 side).

The cylinder portion 211 has a tubular shape. The cylinder portion 211 is arranged so that the opening on the upper end side faces the flow path blocking portion 5A of the flow path 5. A diversion that branches from the first flow path 51 to a part of the outer surface of the cylinder portion 211 (on the right side in FIG. 1) and guides a part of the fuel F in the first flow path 51 to the internal space 211A of the cylinder portion 211. A road 53 is formed. The branch flow path 53 extends from the first flow path 51 to the lower end of the cylinder portion 211 and communicates with the inflow port 211B provided at the lower end of the cylinder portion 211. Since the fuel F is supplied to the first flow path 51 at a predetermined pressure, a part of the fuel F is constantly supplied from the branch flow path 53 to the internal space 211A of the cylinder portion 211 through the inflow port 211B. In the following description, the internal space 211A of the cylinder portion 211 will be referred to as a "fluid chamber 211A".

Two discharge holes 211C and 211D are formed at appropriate positions on the side surface of the cylinder portion 211 to discharge the fuel F in the fluid chamber 211A and reduce the hydraulic pressure in the fluid chamber 211A. In the first embodiment, the areas of the first discharge hole 211D and the second discharge hole 211C are set to substantially the same size, but they may be set to different sizes. The second discharge hole 211C is formed on the side surface of the cylinder portion 211 facing the automatic valve closing mechanism 23 (the side surface substantially in the center on the left side in FIG. 1), and the first discharge hole 211D is the second discharge hole 211C of the cylinder portion 211. It is a side surface facing the second discharge hole 211C and is formed on the valve shaft 213 side (upper side than the second discharge hole 211C in FIG. 1). In FIG. 1, the first discharge hole 211D is formed at a position different from the position facing the second discharge hole 211C in the vertical direction, but the first discharge hole 211D is arranged at a position facing the second discharge hole 211C. You may. The first discharge hole 211D corresponds to the "first discharge hole" of the present invention, and the second discharge hole 211C corresponds to the "second discharge hole" of the present invention.

The second discharge hole 211C communicates with the fuel discharge chamber 231 of the automatic valve closing mechanism 23, and is closed so as to be openable and closable by a control valve 233 movably provided in the fuel discharge chamber 231. As will be described later, the second discharge hole 211C mainly moves to a position where the main valve 212 opens the bent portion 5A (hereinafter, referred to as an “open position”; see FIG. 2B), and the fuel F is moved from the discharge pipe 4. When the liquid level detection unit 42 of the automatic valve closing mechanism 23 detects that the fuel tank is full, the fuel F in the fluid chamber 211A is discharged to the fuel discharge chamber 231 (the liquid pressure in the fluid chamber 211A). The main valve 212 is automatically returned to the position where the road blocking portion 5A is closed (the position shown in FIG. 1, hereinafter referred to as “closed position”). As will be described later, the second discharge hole 211C also has a function of discharging the fuel F of the fluid chamber 211A to lower the liquid pressure when the hydraulic pressure of the fluid chamber 211A rises abnormally, but normally, the valve is automatically closed. The mechanism 23 is closed by the adjusting valve 233 except when the valve is closed.

For example, when the hydraulic pressure in the fluid chamber 211A rises abnormally, the first discharge hole 211D discharges the fuel F in the fluid chamber 211A to the branch flow path 53 side (decreases the hydraulic pressure in the fluid chamber 211A). ). As will be described later, when the main valve 212 rises (moves) beyond a predetermined open position when the main valve 212 opens (when an overshoot occurs when the main valve 212 opens). In addition, a regulation unit 219A for restricting the movement is provided. The case where the hydraulic pressure in the fluid chamber 211A rises abnormally is, for example, when the piston portion 215 is pushed into the fluid chamber 211A even if the rise (movement) of the main valve 212 is regulated by the regulation portion 219A. is there.

A safety valve 217 is provided in the branch flow path 53 so as to face the first discharge hole 211D so as to open and close the first discharge hole 211D. The safety valve 217 is normally urged toward the first discharge hole 211D by the third spring 218, and closes the first discharge hole 211D so as to be openable and closable. The first discharge hole 211D, the safety valve 217, and the third spring 218 constitute the safety mechanism 24. The safety operation (operation of the safety mechanism 24) when the hydraulic pressure abnormality of the first discharge hole 211D and the safety valve 217 and the second discharge hole 211C and the adjustment valve 233 occurs will be described later.

The valve shaft 213 is attached to the upper part of the cylinder portion 211. One end (lower end in FIG. 1) of the valve shaft 213 is movably housed in the fluid chamber 211A, and the other end (upper end in FIG. 1) is exposed from the fluid chamber 211A and connected to the main valve 212. .. A ceiling for sealing the fluid chamber 211A is provided on the inner wall on which the valve shaft 213 of the cylinder portion 211 moves.

An opening for mounting the valve shaft 213 inside the nozzle body 2 is provided above the valve shaft 213 of the nozzle body 2, and a main valve 212 is provided on the lower surface of the sealing plug 219 that seals the opening. A regulation unit 219A is formed to regulate the rise (movement) at a predetermined position when the nozzle rises (moves) beyond a predetermined open position when the nozzle is opened. Further, a first spring 214 is arranged between the lower surface of the sealing plug 219 and the main valve 212. The regulatory unit 219A corresponds to the "regulatory means" of the present invention.

The piston portion 215 projects the lower end portion of the piston portion 215 to the outside from the cylinder portion 211 at a position facing the inflow port 211B at the lower portion of the cylinder portion 211, and the upper end portion of the piston portion 215 is projected from the inflow port 211B. It is movably mounted in the cylinder portion 211. A second spring 216 is attached between the lower surface of the cylinder portion 211 and the lower end portion of the piston portion 215. The piston portion 215 is normally urged downward by the second spring 216 (the direction in which the lower end of the piston portion 215 is brought into contact with the operating lever 221). The inner wall on which the piston portion 215 of the cylinder portion 211 moves is provided with a sealing for preventing liquid leakage of the fuel F from the cylinder portion 211.

The operating mechanism 22 includes an operating lever 221 and a support portion 222 and a shaft 223. The support portion 222 is projected from the lower end of the portion of the cylinder portion 211 provided with the automatic valve closing mechanism 23. The operation lever 221 forms a cassotte shape in which one end of the "K" shape is extended in a straight line, and the other end of the "K" shape portion is rotatably supported by the tip of the support portion 222 by the shaft 223. Has been done.

The linear portion 221A of the operation lever 221 is a grip operation portion in which the user grips the grip portion 3 by hand together with the grip portion 3 and pulls the operation lever 221 toward the grip portion 3. Although not shown, the tip of the grip operation unit 221A becomes a contact member when the grip operation unit 221A rotates clockwise to the state shown in FIG. 1 (hereinafter, this state is referred to as "initial state"). It comes into contact and its rotation is regulated. Then, in the initial state, the lower end of the piston portion 215 urged downward by the second spring 216 is in contact with the "dogleg" -shaped portion of the operating lever 221.

Therefore, when the user grasps the grip operation portion 221A of the operation lever 221 together with the grip portion 3 in the initial state and performs the "grip operation", the operation lever 221 rotates counterclockwise around the shaft 223, and the rotational power thereof is increased. It is transmitted to the piston portion 215 so that the upper end portion of the piston portion 215 is immersed in the fluid chamber 211A of the cylinder portion 211. After that, when the user releases the grip operation portion 221A, the piston portion 215 moves in the direction of protruding from the cylinder portion 211 by the urging force of the second spring 216, and this moving force is transmitted to the operation lever 221 to be transmitted to the operation lever 221. Rotates clockwise and returns to the initial state.

The automatic valve closing mechanism 23 mainly includes a fuel discharge chamber 231 communicating with the second discharge hole 211C of the cylinder portion 211, a pressure fluctuation chamber 232 provided adjacent to the fuel discharge chamber 231, and a fuel discharge chamber 231 and a pressure fluctuation. It includes an adjusting valve 233 movably provided between the chamber 232, a fourth spring 234 that urges the adjusting valve 233 toward the cylinder portion 211, and a thin tube 235 described above.

The regulating valve 233 includes a plate-shaped base portion 233A having the same cross-sectional shape as the pressure fluctuation chamber 232 and a valve portion 233B projecting from the center of the surface of the base portion 233A facing the second discharge hole 211C. The side surface of the base 233A is sealed to seal the pressure fluctuation chamber 232. The base portion 233A functions as a partition member for partitioning the atmospheric pressure fluctuation chamber 232 and the fuel discharge chamber 231 and also functions as a support member for the valve portion 233B. The fourth spring 234 is provided in the pressure fluctuation chamber 232 and urges the base 233A toward the second discharge hole 211C.

The upper end of the pressure fluctuation chamber 232 on the base end side (left side in FIG. 1) is communicated with the negative pressure generating portion 52A of the second flow path 52 by the communication passage 236. The communication passage 236 is branched and connected to the thin tube 235, and is also connected to the outside via the thin tube 235. As described above, in the state where the opening 235A of the discharge pipe 4 is exposed to the outside air, the atmospheric pressure fluctuation chamber 232 is communicated to the outside through the thin tube 235, so that the atmospheric pressure fluctuations even if a negative pressure is generated in the negative pressure generating portion 52A. The air pressure inside the chamber 232 is the same as the outside air pressure.

Therefore, when the opening 235A of the discharge pipe 4 is exposed to the outside air, the adjusting valve 233 is pressed against the second discharge hole 211C of the cylinder portion 211 by the urging force of the fourth spring 234, and the second discharge hole 211C is pressed. Block. On the other hand, when the opening 235A of the discharge pipe 4 is closed by the fuel F in the fuel tank, the air pressure fluctuation chamber 232 is closed, and the pressure fluctuation chamber is caused by the negative pressure generated in the negative pressure generating portion 52A of the second flow path 52. The air in the 232 is taken out to the side of the second flow path 52, and the volume in the pressure fluctuation chamber 232 is reduced. As a result, the adjusting valve 233 moves to the pressure fluctuation chamber 232 side against the urging force of the fourth spring 234, the second discharge hole 211C is opened, and the fuel F in the fluid chamber 211A is discharged to the fuel discharge chamber 231. To. The fuel discharge chamber 231 is connected to the tip of the discharge pipe 4 by a communication passage 237, and the fuel F discharged to the fuel discharge chamber 231 is led out to the tip of the discharge pipe 4 and is led out from the discharge pipe 4. It is discharged to the fuel tank.

When the fuel F in the fluid chamber 211A of the cylinder portion 211 is discharged to the fuel discharge chamber 231, the hydraulic pressure of the fluid chamber 211A decreases, so that the valve shaft 213 is urged by the first spring 214 to cause the cylinder portion 211. Immerse yourself in the fluid chamber 211A and the main valve 212 returns from the open position to the closed position.

Next, the refueling operation of the refueling nozzle 1 when the user normally operates the operation lever 221 will be described with reference to FIGS. 2A and 2B.

2A and 2B are diagrams showing an operating state of each process in the refueling operation of the refueling nozzle 1 (opening / closing operation of the main valve 212). 2A (a) is a diagram showing an initial state, FIG. 2A (b) is a diagram showing a state in which the main valve 212 is opened when the operating lever 221 is pulled, and FIG. 2B (c) is a diagram showing a valve opening operation. FIG. 2B (d), which shows a state in which the adjusting valve 233 opens a hole when the liquid level detection unit 42 detects that the fuel tank of the vehicle is full, shows that the operation lever 221 is released. It is a figure which shows the state which returns to the initial state when it is done. Since the safety valve 217 and the regulation unit 219A are not involved in the normal opening / closing operation of the main valve 212, the safety valve 217, the third spring 218, and the sealing plug 219 are omitted in FIGS. 2A and 2B.

When fuel F is not supplied to the refueling nozzle 1 from the weighing device, the first spring 214, the second spring 216, and the second spring 216 and the check valve 43 of the main valve 212, the valve shaft 213, the piston portion 215, the adjusting valve 233, and the check valve 43, respectively. Since only the urging force of the 4 spring 234 and the 5th spring 44 acts, the main valve 212 and the valve shaft 213 are held in the closed position, the piston portion 215 is held in the state of being in contact with the operating lever 221, and the adjusting valve 233 is held. Is held at a position that closes the second discharge hole 211C (hereinafter, referred to as a "closed position"), and the check valve 43 is held in a state of being pressed against the valve seat 45.

In this state, when the fuel F is supplied to the refueling nozzle 1 from the measuring device, the fuel F is filled in the first flow path 51, the branch flow path 53, and the fluid chamber 211A. When the fuel F is filled in the fluid chamber 211A, the hydraulic pressure acts on the adjusting valve 233 from the fuel F. Assuming that the liquid pressure per unit area in the fluid chamber 211A is P (N / m ² ) and the area of the surface of the adjusting valve 233 in contact with the fuel F is S1 (m ² ), the adjusting valve 233 has a cylinder portion 211. A force of FA = P × S1 (N) (hereinafter, the force in this direction is referred to as “pushing output”) acts from the liquid in the fluid chamber 211A in the direction of pushing out from, but is adjusted by the urging force of the fourth spring 234. Since the force for pushing the valve 233 toward the second discharge hole 211C (hereinafter, the force in this direction is referred to as "pushing force") is larger than the pushing output FA, the pushing force acts on the adjusting valve 233 and the adjusting valve 233 is the first. 2 It is held in the closed position of the discharge hole 211C.

A push-out force acts on the valve shaft 213 from the fuel F in the fluid chamber 211A, but the push-out force is the same as the push-in force acting on the main valve 212 from the fuel F in the first flow path 51, and both forces are mutually exclusive. Since the directions are opposite, they are offset. Therefore, only the pushing force that pushes the cylinder portion 211 toward the fluid chamber 211A by the first spring 214 acts on the main valve 212 and the valve shaft 213, and the main valve 212 and the adjusting valve 233 are held in the closed positions.

When the operation lever 221 is operated by the refueling nozzle 1 to perform the refueling operation even once, the fuel F staying in the first flow path 51 is supplied to the second flow path 52, and the check valve 43 is used. The hydraulic pressure is received from the fuel F, but when the main valve 212 is held in the closed position, the fuel F in the second flow path 52 stays and the check valve 43 is immersed in the fuel F. , The hydraulic pressure acting on the entire check valve 43 is offset, and only the urging force of the fifth spring 44 acts on the check valve 43. Therefore, the check valve 43 is pressed against the valve seat 45 by the fifth spring 44, and shuts off the second flow path 52 and the discharge pipe 4.

(1) Initial state (Fig. 2A (a))
As described above, the main valve 212 and the valve shaft 213 are in a state of being immersed in the fuel F filled in the first flow path 51 and the fluid chamber 211A in the nozzle body 2, and are pushed by the first spring 214 in the initial state. Since the force (see the white arrow in FIG. 2A) acts on the main valve 212 and the valve shaft 213, the main valve 212 is held in the closed position, and the first flow path 51 and the second flow path 52 are shut off. ing. Further, when the first flow path 51 and the second flow path 52 are cut off, the fuel F on the second flow path 52 side stays, so that only the urging force of the fifth spring 44 acts on the check valve 43. , The check valve 43 is pressed against the valve seat 45, and the second flow path 52 and the discharge pipe 4 are also shut off.

Further, the push output FA acts on the adjusting valve 233 by the fuel F in the fluid chamber 211A, but the push force by the fourth spring 234 (see the white arrow in FIG. 2A (a)) is larger than the push output FA. The adjusting valve 233 is held in the closed position of the second discharge hole 211C. Further, the push output by the fuel F in the fluid chamber 211A and the push output due to the extension force of the second spring 216 act on the piston portion 215, and the piston portion 215 has these push outputs (white arrows in FIG. 2A (a)). The lower end of the piston portion 215 is held in contact with the operating lever 221.

(2) A state in which the operation lever 221 is pulled (FIG. 2A (b)).
After the user holds the grip portion 3 of the refueling nozzle 1 and inserts the discharge pipe 4 into the fuel tank of the vehicle, the user grips the operation lever 221 together with the grip portion 3 (operation of pulling the operation lever 221). As shown by the arrow R in b), the operating lever 221 rotates counterclockwise around the shaft 223. By this rotational operation, the piston portion 215 in contact with the operating lever 221 is pushed into the fluid chamber 211A side (upper side in FIG. 2A (b)) of the cylinder portion 211 (see the black arrow in FIG. 2A (b)), and the piston. The upper end of the portion 215 enters the fluid chamber 211A from the inflow port 211B. When the upper end portion of the piston portion 215 enters the fluid chamber 211A, the fuel F filled in the fluid chamber 211A is compressed, so that the hydraulic pressure P of the fluid chamber 211A rises.

The push output acting on the adjusting valve 233 and the valve shaft 213 increases as the hydraulic pressure P rises, but the area S2 of the surface where the fuel F in the fluid chamber 211A is in contact with the valve shaft 213 is the fuel in the fluid chamber 211A. Since F is larger than the area S1 in contact with the control valve 233, the push output FB acting on the valve shaft 213 (see the black mark in FIG. 2A (b)) is larger than the push output FA of the control valve 233. Therefore, the valve shaft 213 is pushed out from the fluid chamber 211A against the pushing force of the first spring 214 before the adjusting valve 233, and the main valve 212 moves from the closed position to the open position. Since the increase in the hydraulic pressure P in the fluid chamber 211A is absorbed by the movement of the valve shaft 213, the pushing force FA acting on the adjusting valve 233 is the pushing force by the fourth spring 234 (see the white arrow in FIG. 2A (a)). ) Will not be exceeded.

Further, as described above, when the main valve 212 moves to the open position and the fuel F flows out from the first flow path 51 to the second flow path 52, the fuel F resists the urging force of the fifth spring 44. The check valve 43 is pushed toward the discharge pipe 4 (see the black arrow in FIG. 2A (b)), and flows out from the negative pressure generating portion 52A generated between the check valve 43 and the valve seat 45 to the discharge pipe 4. It is discharged from 4 to the fuel tank of the vehicle. When the fuel F flows through the negative pressure generating portion 52A, a negative pressure is generated in the negative pressure generating portion 52A due to the Venturi effect, but the atmospheric pressure fluctuation chamber 232 communicates with the outside air through the opening 235A of the discharge pipe 4, so that the atmospheric pressure fluctuates. The air pressure in the chamber 232 is the same as the outside air pressure. Therefore, since the adjusting valve 233 does not generate a suction force due to the fluctuation of the atmospheric pressure in the atmospheric pressure fluctuation chamber 232, the adjusting valve 233 holds the second discharge hole 211C in a closed state by the pushing force of the fourth spring 234.

Therefore, when the user grips the operation lever 221 together with the grip portion 3, the valve opening / closing mechanism switches to the state shown in FIG. 2A (b), and the main valve 212 moves to the open position and enters the first flow path 51. As long as the retained fuel F flows out to the second flow path 52 and the user maintains the gripping operation of the operation lever 221 thereafter, the fuel F passes through the first flow path 51 and the second flow path 52 and is a discharge pipe. It flows out to 4.

(3) State when it is detected that the fuel tank of the vehicle is full (Fig. 2B (c))
When the liquid level of the fuel F supplied to the fuel tank of the vehicle rises to a position that closes the opening 235A of the discharge pipe 4, the outside air is not supplied from the opening 235A to the atmospheric pressure fluctuation chamber 232, so that it is generated in the negative pressure generating portion 52A. The air in the air pressure fluctuation chamber 232 is sucked by the negative pressure, and the air pressure in the pressure fluctuation chamber 232 decreases. Since the volume of the pressure fluctuation chamber 232 contracts due to this decrease in air pressure, the suction force (black in FIG. 2B (c)) of the adjusting valve 233 in the direction away from the second discharge hole 211C against the urging force of the fourth spring 234. (Refer to the arrow) acts, and the adjusting valve 233 moves from the closed position to the open position of the second discharge hole 211C.

As a result, the second discharge hole 211C opens, the fuel F in the fluid chamber 211A flows out from the second discharge hole 211C to the fuel discharge chamber 231, and the hydraulic pressure P in the fluid chamber 211A decreases. When the hydraulic pressure P of the fluid chamber 211A decreases, a pushing force by the first spring 214 (see the white arrow in FIG. 2B (c)) acts on the main valve 212, so that the main valve 212 and the valve shaft 213 are in the fluid chamber. It is pushed toward the 211A side (downward in FIG. 2B (c)), the main valve 212 returns to the closed position, and the first flow path 51 and the second flow path 52 are shut off.

Note that FIG. 2B (c) shows a state in which the main valve 212 is moved to the closed position by the pushing force acting on the main valve 212. During the period when the main valve 212 is moving to the closed position, the fuel F flowing out from the flow path blocking portion 5A to the second flow path 52 decreases, so that the pushing force of the fuel F pushing the check valve 43 decreases. As shown in FIG. 2B (c), the check valve 43 moves to the valve seat 45 side by the urging force of the fifth spring 44. During this period, since the main valve 212 does not completely shut off the flow path blocking portion 5A, the check valve 43 is not completely pressed against the valve seat 45, and the fuel F flows through the negative pressure generating portion 52A. ing.

When the first flow path 51 and the second flow path 52 are completely shut off by the main valve 212, the check valve 43 is also completely pressed against the valve seat 45 to shut off the second flow path 52 and the discharge pipe 4. Since the fuel F does not flow to the negative pressure generating portion 52A due to this cutoff, the negative pressure does not occur, but if the closed state of the opening 235A of the discharge pipe 4 is maintained, the air pressure in the pressure fluctuation chamber 232 is maintained at a low pressure. Therefore, the adjusting valve 233 is stopped at an open position for opening the second discharge hole 211C as shown in FIG. 2B (c).

After that, when the user pulls out the discharge pipe 4 from the fuel tank of the vehicle, the blocked state of the opening 235A of the discharge pipe 4 is cleared, and the outside air flows into the pressure fluctuation chamber 232 from the opening 235A. Rise to the outside air pressure. The suction force of the adjusting valve 233 disappears due to the rise in the air pressure in the pressure fluctuation chamber 232, and the adjusting valve 233 is urged toward the second discharge hole 211C by the urging force of the fourth spring 234 to close the second discharge hole 211C. It becomes a state (see the state in FIG. 2B (d)).

(4) State when the operation of the operation lever 221 is released (FIG. 2B (d))
When the main valve 212 returns to the closed position, the check valve 43 returns to the state of being pressed against the valve seat 45, and the adjusting valve 233 returns to the closed position of the second discharge hole 211C, the user grips the operating lever 221. When the operation is stopped, the urging force of the second spring 216 (pushing output, see the white arrow in FIG. 2B (d)) is transmitted to the operating lever 221 via the piston portion 215. As shown by the arrow S in FIG. 2B (d), the operating lever 221 rotates clockwise around the shaft 223 to a predetermined position and returns to the initial state position.

As the operating lever 221 returns to the initial state position, the piston portion 215 moves outward of the cylinder portion 211 (downward in FIG. 2B (d)), so that the upper end portion of the piston portion 215 moves from the fluid chamber 211A. At the same time as being drawn out, the fuel F flows into the fluid chamber 211A from the branch flow path 53 through the inflow port 211B, and the hydraulic pressure P in the fluid chamber 211A becomes the pressure of the fuel F (the pressure in the initial state) supplied by the liquid supply hose 6. Return. That is, the nozzle body 2 returns to the initial state shown in FIG. 2A (a).

Next, the safety function by the regulation unit 219A and the safety valve 217 will be described with reference to FIGS. 3A and 3B.

FIG. 3A (a) is a diagram showing a state in which the operating lever 221 is pulled (a state in which the fuel F is normally supplied to the fuel tank of the vehicle). In FIG. 3A (b), the movement of the main valve 212 is restricted by the regulation unit 219A when the user feels an abnormality in the fuel F discharge state and momentarily grasps the operation lever 221 (when an abnormal operation is performed). It is a figure which shows the state which was done. FIG. 3B (c) is a diagram showing a state in which the adjustment valve 233 operates due to the movement of the main valve 212 being restricted by the regulation unit 219A to absorb an increase in the hydraulic pressure P of the fluid chamber 211A. FIG. 3B (d) is a diagram showing a state in which the safety valve 217 is operated after the adjusting valve 233 is operated to further absorb the increase in the hydraulic pressure P of the fluid chamber 211A. The black arrows in the fluid chamber 211A in FIGS. 3A (a) and 3B and 3B (c) and 3B (d) indicate the valve shaft due to the hydraulic pressure P increased by the piston portion 215 entering the fluid chamber 211A. The push output acting on 213, the safety valve 217 and the adjusting valve 233 is shown.

When the operating lever 221 is pulled and the fuel F is normally supplied to the fuel tank of the vehicle, as shown in FIG. 3A (a), the tip of the piston portion 215 is inside the fluid chamber 211A of the cylinder portion 211. As the volume of the fluid chamber 211A decreases due to the entry, the hydraulic pressure P in the fluid chamber 211A rises. As the hydraulic pressure P in the fluid chamber 211A rises, the push output FB (see the black arrow in FIG. 3A (a)) acting on the surface of the valve shaft 213 in contact with the fuel F in the fluid chamber 211A rises, and the valve The shaft 213 rises to a position (open position) where the pushing output FB and the pushing force of the first spring 214 are balanced. The main valve 212 also rises as the valve shaft 213 rises, but the raised position (open position) of the main valve 212 does not reach the regulation unit 219A.

In the state shown in FIG. 3A (a), when the user notices some abnormality and momentarily tightens the grip operation unit 221A, the operation lever 221 pushes the shaft 223 as shown by the arrow R in FIG. 3A (b). It rotates counterclockwise to the center. By this rotation, the piston portion 215 is further pushed into the fluid chamber 211A of the cylinder portion 211, and the volume of the fluid chamber 211A is sharply reduced. When the hydraulic pressure P rises sharply due to the reduction in the volume of the fluid chamber 211A, the valve shaft 213 and the main valve 212 rise due to the rise in the hydraulic pressure P (the valve shaft 213 moves outward of the cylinder portion 211), and the flow path The opening amount of the blocking portion 5A increases.

As the hydraulic pressure P in the fluid chamber 211A rises, the push output acting on the regulating valve 233 and the safety valve 217 also increases, but the area S2 on which the hydraulic pressure P acts on the valve shaft 213 increases the liquid in the regulating valve 233 and the safety valve 217. Since the area S1 on which the pressure P acts is larger, the push output FB larger than the adjusting valve 233 and the safety valve 217 acts on the valve shaft 213. Therefore, as shown in FIG. 3A (b), the valve shaft 213 first moves in the direction of protruding from the cylinder portion 211 to absorb the increase in the hydraulic pressure P of the fluid chamber 211A, so that the adjusting valve 233 and the safety valve 217 does not move to the open position.

When the opening amount of the flow path blocking portion 5A momentarily increases, the amount of fuel F flowing from the flow path blocking portion 5A into the second flow path 52 rapidly increases, and the liquids in the flow path blocking portion 5A and the second flow path 52 The pressure may increase and the nozzle body 2 may be damaged. In the refueling nozzle 1 according to the first embodiment, as shown in FIG. 3A (b), when the main valve 212 rises above the open position, the upper surface of the main valve 212 is brought into contact with the regulating portion 219A to bring the main valve into contact with the main valve. Limits the ascending movement of 212.

As a result, even when the user tightens the operation lever 221 more than the normal gripping operation, the opening amount of the flow path blocking portion 5A is limited so as not to increase more than a predetermined amount. It is possible to prevent damage to the nozzle body 2 due to the generation of excessive hydraulic pressure of the fuel F inside.

On the other hand, when the movement amount of the valve shaft 213 pushed out from the cylinder portion 211 is limited by the regulation portion 219A, the hydraulic pressure P in the fluid chamber 211A increases due to the entry of the piston portion 215 into the fluid chamber 211A, and the cylinder portion 211 May cause damage.

In the refueling nozzle 1 of the first embodiment, when the sudden increase in the hydraulic pressure P of the fluid chamber 211A cannot be sufficiently suppressed by the movement of the valve shaft 213, the adjusting valve is shown by the black arrow in FIG. 3B (c). Since a push-out FA larger than the urging force of the fourth spring 234 acts on the 233, the push-out FA pushes the adjusting valve 233 toward the pressure fluctuation chamber 232 and opens the second discharge hole 211C. As a result, the fuel F in the fluid chamber 211A flows out from the second discharge hole 211C to the fuel discharge chamber 231 and lowers the hydraulic pressure in the fluid chamber 211A. The fuel F that has flowed out to the fuel discharge chamber 231 is led out to the tip of the discharge pipe 4 by pushing the communication passage 237, and is discharged from the discharge pipe 4 to the fuel tank.

Similarly, since the push output FC larger than the urging force of the third spring 218 acts on the safety valve 217, the safety valve 217 is pushed toward the shunt flow path 53 by the push output FC, and as shown in FIG. 3B (c). , The first discharge hole 211D is opened. As a result, the fuel F in the fluid chamber 211A flows out from the first discharge hole 211D to the branch flow path 53, further lowering the hydraulic pressure P in the fluid chamber 211A.

That is, in the refueling nozzle 1 according to the first embodiment, when a sudden pushing operation of the piston portion 215 into the fluid chamber 211A occurs, the opening amount of the main valve 212 in the flow path blocking portion 5A is adjusted by the regulating portion 219A. While limiting, the adjusting valve 233 and the safety valve 217 are used to absorb the excessive hydraulic pressure P of the fluid chamber 211A. The opening operation of the safety valve 217 and the adjusting valve 233 may be earlier than the other, or may be substantially the same timing.

In the first embodiment, the position of the first discharge hole 211D is arranged above the position of the second discharge hole 211C (the side farther than the piston portion 215), and therefore, as shown in FIG. 3B (d). Even when the upper end of the piston portion 215 that has entered the fluid chamber 211A reaches the second discharge hole 211C and the second discharge hole 211C is blocked by the piston portion 215, the safety valve 217 is open, so that the fluid chamber is open. The sudden rise in the hydraulic pressure P in 211A is surely absorbed, and the occurrence of an abnormality based on the user's operation can be surely prevented.

In the first embodiment, the area S1 of the surface in which the fuel F in the fluid chamber 211A is in contact with the control valve 233 is substantially the same as the area S3 of the surface in contact with the safety valve 217, but both areas S1 and S3 May be different. The area S1 of the adjusting valve 233 is made larger than the area S3 of the safety valve 217, and the spring force of the fourth spring 234 of the adjusting valve 233 and the spring force of the third spring 218 of the safety valve 217 are adjusted so that the adjusting valve 233 discharges the second. When the timing for opening the hole 211C is earlier than the timing for the safety valve 217 to open the first discharge hole 211D, the adjusting valve 233 is quickly moved to the open position even when the piston portion 215 excessively enters the fluid chamber 211A. Next, the safety valve 217 can be moved to the open position to ensure safe operation.

In the above description, a case where an abnormality occurs in the hydraulic pressure P of the fluid chamber 211A of the cylinder portion 211 based on an abnormal operation of the operation lever 221 by the user has been described. Due to other factors such as the pressure of the fuel F supplied to the refueling nozzle 1 suddenly drops or the supply of the fuel F from the measuring device suddenly stops, the hydraulic pressure P of the fluid chamber 211A of the cylinder portion 211 is increased. Even when an abnormality occurs, the abnormality occurring in the refueling nozzle 1 can be prevented by the operation of the regulation unit 219A, the safety valve 217 and the adjusting valve 233 described above.

For example, when the hydraulic pressures of the first flow path 51 and the branch flow path 53 suddenly decrease, the hydraulic pressure P in the fluid chamber 211A of the cylinder portion 21 is relative to the hydraulic pressures of the first flow path 51 and the branch flow path 53. As it rises, the main valve 212 and the valve shaft 213 are pushed out toward the first flow path 51, and the piston portion 215 is pulled into the fluid chamber 211A. However, also in this case, since the second discharge hole 211C and the first discharge hole 211D are opened to absorb the relative rapid rise of the hydraulic pressure P in the fluid chamber 211A, the hydraulic pressure generated in the nozzle body 2 is absorbed. Abnormality will be surely prevented.

As described above, according to the refueling nozzle 1 according to the first embodiment, the opening of the piston portion 215 to the valve shaft 213 when the valve opening / closing mechanism 21 moves the main valve 212 from the closed position to the open position. The transmission of the valve operating force and the release of the valve opening operating force acting on the valve shaft 213 when moving the main valve 212 from the open position to the closed position are the hydraulic pressure in the fluid chamber 211A of the cylinder portion 211. Since it is performed by changing P, there is no mechanical damage to the configuration in which the valve shaft 213 and the piston portion 215 are mechanically connected / detached as in the prior art, and deterioration over time is reduced. be able to.

Further, when a situation occurs in which the hydraulic pressure P of the fluid chamber 211A of the cylinder portion 211 increases abnormally with respect to the hydraulic pressure P of the first flow path 51 and the branch flow path 53, the main flow blocking portion 5A is used. The adjustment valve 233 and the first discharge that block the second discharge hole 211C of the fluid chamber 211A while restricting the movement amount of the main valve 212 and the valve shaft 213 so that the opening amount of the valve 212 does not increase more than a predetermined amount. Since the safety valve 217 that closes the hole 211D is opened and the fuel F is discharged from the fluid chamber 211A to lower the hydraulic pressure P in the fluid chamber 211A, the refueling nozzle 1 is damaged due to the hydraulic pressure abnormality in the nozzle body 2. Etc. can be prevented.

In this case, since the first discharge hole 211D is arranged so as to be farther from the piston portion 215 than the second discharge hole 211C, the second discharge hole 211C is blocked by the piston portion 215. Even in this case, the fuel F can be discharged from the fluid chamber 211A through the first discharge hole 211D to reliably prevent damage to the refueling nozzle 1 due to an abnormality in the hydraulic pressure in the nozzle body 2.

In the first embodiment, the fluid chamber 211A of the cylinder portion 211 is a linear cylinder, and the valve shaft 213 and the piston portion 215 are arranged linearly, but the valve shaft 213 and the piston portion 215 are arranged linearly. It does not have to be. For example, as shown in FIG. 4, the fluid chamber 211A may be bent in an L shape, and the valve shaft 213 may be arranged in a direction orthogonal to the piston portion 215.

In the second embodiment shown in FIG. 4, the upper end portion of the cylinder portion 211 is bent toward the second flow path 52, and the main valve 212 and the valve shaft 213 are used as the axes of the first flow path 51 and the second flow path 52. It is arranged so that it can be moved along the direction. A flow path blocking portion 5A is provided between the first flow path 51 and the second flow path 52, the main valve 212 is arranged on the second flow path 52 side, and the first spring 214 is provided between the main valve 212 and the second flow. It is arranged between the road and the tip surface of the road 52. Although the regulation unit 219A is omitted in FIG. 4, it is preferable to provide the regulation unit 219A even in the configuration shown in FIG.

In the configuration of FIG. 4, when the valve shaft 213 is pushed out from the cylinder portion 211, the main valve 212 moves to the check valve 43 side (moves to the open position), the flow path blocking portion 5A opens, and the fuel F is released. It flows out from the first flow path 51 to the second flow path 52 side. When the fuel F flows out of the flow path cutoff portion 5A to the second flow path 52 side, if the main valve 212 projects from the valve shaft 213 in a brim shape, the fuel F collides with the main valve 212 and the outflow resistance becomes large. Therefore, in the second embodiment, the inclined surface 212A is provided at the connection portion between the main valve 212 and the valve shaft 213. The main valve 212 and the valve shaft 213 shown by the dotted line in FIG. 4 show the state when the main valve 212 is moved to the open position, and the fuel F flowing out from the flow path blocking portion 5A is the first due to the inclined surface 212A. Since it is guided to the two flow paths 52 side, the outflow resistance can be reduced as much as possible.

In the configuration shown in FIG. 4, the main valve 212 is arranged on the second flow path 52 side with respect to the flow path cutoff portion 5A, but the main valve 212 is on the first flow path 51 side with respect to the flow path cutoff portion 5A. May be placed in. FIG. 5 is a diagram showing an example of the configuration of the cylinder portion 211, the main valve 212, and the valve shaft 213 when the main valve 212 is arranged on the first flow path 51 side with respect to the flow path blocking portion 5A. In FIG. 5, the second discharge hole 211C, the first discharge hole 211D, the safety valve 217, and the fourth spring 234, which are not related to the explanation of the opening / closing operation of the main valve 212, are omitted. Further, the operation lever 221 is also omitted.

In the third embodiment shown in FIG. 5, a valve seat 54 having a tapered recess formed in the opening of the flow path blocking portion 5A is provided, and the main valve 212 attached to the tip of the valve shaft 213 is a valve. It is molded into a truncated cone shape that fits into the recess of the seat 54. A cylindrical support 220 having one end opened is provided in a portion of the cylinder portion 211 in the fluid chamber 211A to which the valve shaft 213 is attached, and the base end portion of the valve shaft 213 can be moved in the support 220. It is supported. A piston 213A having substantially the same inner diameter as the inner diameter of the support 220 is formed at the base end of the valve shaft 213. The space sandwiched between the bottom surface of the support 220 and the piston 213A is communicated with the first flow path 51 by a thin tube (not shown). A first spring 214 is inserted into this space, and a push output acts on the main valve 212 and the valve shaft 213 by the first spring 214.

A pushing force based on the hydraulic pressure P in the fluid chamber 211A (see the black arrow in FIG. 5B) acts on the surface of the piston 213A opposite to the first spring 214, but in the initial state, it is in the initial state. Since the pushing force by the first spring 214 is larger than the pushing force based on the hydraulic pressure P, the main valve 212 is pressed against the valve seat 54 by the pushing force, and the flow path blocking portion is cut off. It is blocking 5A. That is, the main valve 212 is held in the closed position.

When the piston portion 215 enters the fluid chamber 211A of the cylinder portion 211 by operating the operating lever 221, the hydraulic pressure P in the fluid chamber 211A rises, and the pushing force acting on the piston 213A is pushed by the first spring 214. When it becomes larger than the output, the valve shaft 213 moves to the bottom surface side of the support 220 due to the pushing force (see the black arrow in FIG. 5B), and the main valve 212 pressed against the valve seat 54 moves to the valve seat. The flow path blocking portion 5A is opened apart from 54. That is, the main valve 212 moves from the closed position to the open position. Although the regulation unit 219A is omitted in FIG. 5, it is preferable to provide the regulation unit 219A also in the configuration shown in FIG.

In the second embodiment and the third embodiment, the moving direction of the main valve 212 is the same as the axial direction of the first flow path 51 and the second flow path 52, so that the first flow path 51 and the second flow path are the same. There is an advantage that the 52s can be arranged on substantially the same axis, and the flow path 5 in the nozzle body 2 can be made substantially linear.

In the first embodiment, the area S2 of the surface of the valve shaft 213 and the piston portion 215 in the fluid chamber 211A where the fuel F contacts is the same, but the area S2 of the valve shaft 213 is made different from the area of the piston portion 215. You may do so. For example, as shown in FIG. 6, if the shape of the fluid chamber 211A is cylindrical, the diameter d2 of the valve shaft 213 may be larger than the diameter d1 of the piston portion 215. The main valve 212 and the valve shaft 213 shown by the alternate long and short dash line in FIG. 6 show a state in which the main valve 212 has been moved to the open position.

When the diameter d2 of the valve shaft 213 is made larger than the diameter d1 of the piston portion 215, the push force acting on the valve shaft 213 when the piston portion 215 is made to enter the fluid chamber 211A and the hydraulic pressure P is increased is a valve. It is larger than the case where the diameter d2 of the shaft 213 and the diameter d1 of the piston portion 215 are substantially the same. The pushing force FC acts on the piston portion 215, the piston portion 215 enters the fluid chamber 211A by a distance LC, the pushing output FB based on the rise in hydraulic pressure P acts on the valve shaft 213, and the valve shaft 213 acts on the valve shaft 213 to move the valve shaft 213 into the fluid chamber. Assuming that the distance LB is extruded from the 211A, the distance LB satisfies the relational expression of FC × LC = FB × LB. According to this relational expression, the distance LB from which the valve shaft 213 is pushed out is inversely proportional to the push output FB acting on the valve shaft 213. Therefore, in the fourth embodiment shown in FIG. 6, the diameter d2 of the valve shaft 213 is set. The larger the diameter d1 of the piston portion 215 is, the shorter the distance LB for pushing out the valve shaft 213 can be shortened, and there is an advantage that the nozzle body 2 can be made compact in the height direction in FIG.

In the automatic valve closing mechanism 23 of the first to fourth embodiments, the piston structure is used as the adjusting valve 233, but a diaphragm or bellows may be used. FIG. 7 is a diagram showing a fifth embodiment using a regulating valve 233 in which a valve portion 233B is formed in the center of a disk-shaped diaphragm 238.

The diaphragm 238 is usually displaced so that the valve portion 233B is brought into contact with the second discharge hole 211C by the pushing force of the fourth spring 234. That is, the diaphragm 238 is displaced to the closed position. Then, when the volume of the pressure fluctuation chamber 232 contracts due to negative pressure, a suction force acts on the diaphragm 238, and when the suction force exceeds the pushing force of the fourth spring 234, the diaphragm 238 is displaced toward the fourth spring 234. The valve portion 233B opens the second discharge hole 211C. That is, the diaphragm 238 is displaced to the open position. After that, when the negative pressure in the pressure fluctuation chamber 232 disappears, the diaphragm 238 is displaced to the closed position again by the pushing force of the fourth spring 234, and the valve body 233B closes the second discharge hole 211C.

In the fifth embodiment, since the second discharge hole 211C is opened and closed only by the displacement of the diaphragm, the base 233A can be made more compact than the piston structure that moves the base 233A in the atmospheric pressure fluctuation chamber 232, and the automatic valve closing mechanism 23 Miniaturization becomes possible. In the configuration using the bellows, the portion of the diaphragm 238 may be replaced with the bellows in FIG. 7.

In the first embodiment described above, for example, in FIG. 1, the valve shaft 213 is supported so as to be vertically movable only by the upper end portion of the cylinder portion 211 (at only one point), but the structure of the main valve 212 and the valve shaft 213. As shown in FIG. 8A, a tubular guide portion 212B may be provided on the upper surface of the main valve 212, and the regulation portion 219A may be fitted into the guide portion 212B.

The space 212C sealed by the guide portion 212B and the regulation portion 219A is separated from the first flow path 51, and the air pressure in the space 212C fluctuates due to the vertical movement of the main valve 212. In order to suppress the fluctuation of the atmospheric pressure, the space 212C is communicated with the outside by a thin tube 219D provided in a portion passing through the regulation portion 219A of the sealing plug 219.

In the modified example shown in FIG. 8A, the regulating portion 219A functions as a guide rod for guiding the vertical movement of the main valve 212 and the valve shaft 213, and the upper surface of the guide portion 213B of the sealing plug 219 is in contact with the regulating portion 219A. The contact surface 219B functions as a regulating unit that regulates the upward movement of the main valve 212. In the first embodiment shown in FIG. 1, since the valve shaft 213 is supported only by the upper end portion of the cylinder portion 211, the main valve 212 opens the flow path blocking portion 5A to allow the fuel F to flow from the first flow path 51. When the fuel F flows out to the second flow path 52, the flow output of the fuel F acts on the main valve 212 and the valve shaft 213, which adversely affects the smooth vertical movement of the main valve 212 and the valve shaft 213, and abnormal noise may be generated. There is sex.

On the other hand, in the modified example shown in FIG. 8A, since the main valve 212 and the valve shaft 213 are supported at two points, the upper end portion of the main valve 212 and the valve shaft 213, the flow output of the fuel F described above The adverse effect on the vertical movement of the main valve 212 and the valve shaft 213 can be suppressed, the main valve 212 and the valve shaft 213 can be smoothly moved up and down, and the generation of abnormal noise can be prevented.

In FIG. 8A, the first spring 214 is arranged outside the guide portion 212B, but as shown in FIG. 8B, the first spring 214 is arranged inside the recess of the guide portion 212B. You may. In the modified example shown in FIG. 8 (b), the shape of the main valve 212 is changed to a cylindrical shape by removing the flange portion for fixing the first spring 214 of the main valve 212 shown in FIG. 8 (a), and the regulating portion. The 219A has a cylindrical shape having an inner diameter substantially the same as the outer diameter of the guide portion 213B, and the guide portion 213B is fitted into the recess of the cylindrical regulation portion 219C. The regulatory unit 219C corresponds to the "regulatory means" of the present invention.

Similar to the modification shown in FIG. 8A, the modification shown in FIG. 8B can suppress the adverse effect of the flow output of the fuel F on the vertical movement of the main valve 212 and the valve shaft 213. There is an effect that the valve 212 and the valve shaft 213 can be smoothly moved up and down and the generation of abnormal noise can be prevented.

By the way, in the first to fifth embodiments shown in FIGS. 1 and 4 to 7 and the modified example shown in FIG. 8, the upper end portion of the piston portion 215 is moved from the lower portion of the inflow port 211B of the cylinder portion 211 to the fluid chamber 211A. Since the structure is such that the fluid pressure P in the 211A is increased by entering the piston portion 215, the piston portion 215 operates at a high speed when the user performs an abnormal operation such as grasping the operation lever 221 at a high speed higher than the normal speed. By being pushed into the fluid chamber 211A of the fluid chamber 211, the hydraulic pressure P in the fluid chamber 211A rises sharply.

When the hydraulic pressure P in the fluid chamber 211A suddenly rises at a predetermined rate of change or more from the initial state, the safety valve 217 and the regulating valve 233 operate immediately after the valve shaft 213 and the main valve 212 start to rise, and the liquid in the fluid chamber 211A operates. There is a risk that the pressure P will drop sharply. That is, when the hydraulic pressure P in the fluid chamber 211A rises at a rate of change Vp (= dP / dt) equal to or higher than a predetermined threshold value, immediately after the valve shaft 213 and the main valve 212 start rising in response to the rise in the hydraulic pressure P. The safety valve 217 and the adjusting valve 233 operate to lower the hydraulic pressure P, and even if the piston portion 215 is pushed into the fluid chamber 211A to the open position, there may be a problem that the main valve 212 does not rise to the open position.

To solve this problem, the hydraulic pressure P of the fluid chamber 211A acts only on the valve shaft 213 from the timing when the hydraulic pressure P of the fluid chamber 211A starts to rise until the main valve 212 rises to the open position. If the hydraulic pressure P of the fluid chamber 211A can act on the safety valve 217 and the adjusting valve 233 after the main valve 212 rises to the open position (the automatic valve closing mechanism 23 and the safety mechanism 24 can be operated). Good.

In order to realize the above configuration, the sixth embodiment shown in FIG. 9 is obtained by changing the piston portion 215 to the piston portion 315 shown in FIGS. 10 and 12. The piston portion 315 is provided with a shielding portion 215A that shields the first discharge hole 211D and the second discharge hole 211C and a connecting portion 215B that connects the shielding portion 215A to the upper end of the piston portion 215 above the piston portion 215. Is. 10 is a perspective view of the piston portion 315 according to the sixth embodiment, FIG. 12 (a) is a front view of the piston portion 315, and FIG. 12 (b) is YY of FIG. 12 (a). FIG. 12 (c) is a sectional view taken along line ZZ of FIG. 12 (a).

The shielding portion 215A shields the first discharge hole 211D and the second discharge hole 211C in the initial state (see FIG. 9), and when the operation lever 221 is operated, the upper end of the piston portion 215 becomes the inflow port 211B of the cylinder portion 211. It is a member for releasing the shielding of the first discharge hole 211D and the second discharge hole 211C at the timing of reaching the position of closing (see FIG. 13B). The connecting portion 215B is a member for connecting the shielding portion 215A to the upper end of the piston portion 215.

The piston portion 315 shown in FIGS. 10 and 12 is manufactured by integrally forming the piston portion 215, the shielding portion 215A, and the connecting portion 215B using a columnar rod member. Specifically, the piston portion 315 forms a cavity portion 316 (recessed portion 316) having a predetermined length along the axial direction at the upper end portion of the columnar main body 315A (see FIG. 12), and the outer circumference of the upper end portion of the main body 315A. It is manufactured by drilling two elongated holes 317 and 318 having predetermined lengths extending in the axial direction at predetermined positions on the surface. The elongated holes 317 and 318 communicate with the cavity 316.

As shown in FIG. 9, the cavity portion 316 has a length L1 in which the bottom surface 316B of the cavity portion 316 is located below the inflow port 211B of the cylinder portion 211 in the initial state (see FIGS. 10 and 12 (b)). have. That is, the length L1 from the front end surface 316A to the bottom surface 316B of the cavity portion 316 has a length that allows the cavity portion 316 to communicate with the branch flow path 53 in the initial state.

As shown in FIGS. 9 and 11, the elongated hole 317 is provided at a position where the elongated hole 317 faces the first discharge hole 211D of the main body 315A when the piston portion 315 moves up and down. Although FIG. 11 is a sectional view taken along line XX of FIG. 9, the first discharge hole 211D, the second discharge hole 211C, the elongated hole 317, and the elongated hole 318 can be seen in the positional relationship of the first discharge hole 211D. The 211D, the second discharge hole 211C, the slotted hole 317, and the slotted hole 318 are also drawn by a alternate long and short dash line.

The elongated hole 317 is formed when the lower end 317B (see FIG. 12B) of the elongated hole 217 is located near the bottom surface 316A of the cavity portion 316 and the piston portion 315 is in the initial state (state of FIG. 9). , The length L2 (see FIGS. 10 and 12 (a)) at which the upper end 317A (see FIG. 12 (b)) of the elongated hole 317 is located below the first discharge hole 211D (see FIG. 9). Have. That is, the length L2 from the upper end 317A to the lower end 317B of the elongated hole 317 shields the first discharge hole 211D in the initial state, and enters the fluid chamber 211A until the piston portion 315 pushes the main valve 212 to the open position. Then, it has a length that opens the first discharge hole 211D.

As shown in FIGS. 9 and 11, the elongated hole 318 is provided at a position where the elongated hole 318 faces the second discharge hole 211C of the main body 315A when the piston portion 315 moves up and down. The elongated hole 318 is when the lower end 318B (see FIG. 12B) of the elongated hole 218 is located near the bottom surface 316A of the cavity portion 316 and the piston portion 315 is in the initial state (state of FIG. 9). A length L3 (see FIGS. 10 and 12 (a)) at which the upper end 318A (see FIG. 12 (b)) of the elongated hole 318 is located below the second discharge hole 211C (see FIG. 9). Have. That is, the length L2 from the upper end 318A to the lower end 318B of the elongated hole 318 shields the second discharge hole 211C in the initial state, and enters the fluid chamber 211A until the piston portion 315 pushes the main valve 212 to the open position. Then, it has a length that opens the second discharge hole 211C.

At the lower end of the piston portion 315, rotation to prevent rotation of the piston portion 315 so that the elongated holes 317 and the elongated holes 318 do not deviate from each other with respect to the first discharge hole 211D and the second discharge hole 211C. A prevention unit 319 is provided. The rotation prevention portion 319 is a fitting hole 211E that movably supports the portion 319A (see FIG. 11) in which the cross-sectional shape of the lower end portion of the piston portion 315 is a semi-cylindrical shape and the piston portion 315 at the lower end portion of the cylinder portion 211. It is composed of a portion 319B (see FIG. 11) having a semi-cylindrical cross-sectional shape.

As shown in FIG. 10, the rotation prevention portion 319A on the piston portion 315 side is formed by providing a notch at the lower end portion of the piston portion 315 having a circular cross section and making the cross-sectional shape of the lower end portion into a semi-cylindrical shape. On the other hand, as shown in FIG. 9, the rotation prevention portion 319B on the cylinder portion 211 side extends a conical body having a narrowed tip at the lower end of the cylinder portion 211, and the piston portion 315 can be moved to the conical portion. When the fitting hole 211E to be supported is bored, the cross-sectional shape of the fitting hole 211E on the tip side (the side facing the operation lever 221) of the conical portion of the cylinder portion 211 is formed by forming a hook shape as shown in FIG. Has been done. The cross-sectional shape of the rotation prevention portion 319A on the piston portion 315 side and the cross-sectional shape of the rotation prevention portion 319B on the cylinder portion 211 side are substantially the same.

In the piston portion 315, the piston portion 315 is inserted into the fluid chamber 211A from the fitting hole (hole on which the valve shaft 213 is mounted) on the upper end side of the cylinder portion 211, and the lower end of the piston portion 315 is inserted into the inflow port 211 of the cylinder portion 211. Is mounted on the cylinder portion 211 so as to be exposed to the operation lever 221 side through the fitting hole formed in and the fitting hole 211E on the lower side thereof. At this time, the piston portion 315 is attached to the cylinder portion 211 so that the rotation prevention portion 319A on the piston portion 315 side is fitted to the rotation prevention portion 319B on the cylinder portion 211 side.

When the piston portion 315 moves forward and backward with respect to the fluid chamber 211A of the cylinder portion 211, the rotation prevention portion 319A (the portion cut out of the outer peripheral surface) of the piston portion 315 becomes the rotation prevention portion 319B (cross-section sword shape) of the cylinder portion 211. Since it engages with the string portion of the piston portion 315, the piston portion 315 moves straight ahead with respect to the cylinder portion 211 without rotating about the axis. As a result, when the upper end of the piston portion 315 enters the fluid chamber 211A of the cylinder portion 211 until the main valve 212 rises to the open position, the elongated holes 317 and the elongated holes 318 become the first discharge holes 211D and the second discharge holes, respectively. It can be moved to a position facing the 211C, and the first discharge hole 211D and the second discharge hole 211C can be reliably communicated with the cavity portion 316, respectively.

In the examples of FIGS. 10 and 11, the cross-sectional shape of the rotation prevention portion 319 of the piston portion 315 is a semi-cylindrical shape, but if the cross-sectional shape is not circular, an arbitrary shape such as an ellipse or a polygon may be adopted. Good. Further, in the examples of FIGS. 10 and 11, the components of the rotation prevention unit 319 are provided in the piston unit 315 and the cylinder unit 211, but the components of the rotation prevention unit 319 are provided in the piston unit 315 and the operation lever 221. For example, a projecting piece (engagement portion) may be provided at a portion of the lower end of the piston portion 315 that contacts the operation lever 221 while the projecting piece is provided at a portion of the operating lever 221 that abuts at the lower end of the piston portion 315. A recess (engaged portion) to be fitted may be provided, and the projecting piece of the piston portion 315 may be non-rotatably fitted into the recess of the operating lever 221. Of course, also in this case, the projecting piece may be provided on the operation lever 221 side, and the recess may be provided on the piston portion 315 side.

Further, in the examples of FIGS. 10 and 11, the rotation prevention portion 319 is configured by the cross-sectional shape of the piston portion 315 and the cylinder portion 211, but any other configuration can prevent the piston portion 315 from rotating around the axis. Any structure can be adopted. For example, the lower end of the piston portion 315 and the lower end of the cylinder portion 211 may be provided with a convex portion and a concave portion so that the two portions are engaged with each other. The rotation prevention portion 319 is provided in the piston portion 315 according to the sixth embodiment, but may be preferably provided in the piston portion 215 according to the first to fifth embodiments.

In the sixth embodiment shown in FIG. 9, the length L2 of the elongated hole 317 and the length L2 of the elongated hole 318 are set according to the difference in the distances from the inflow port 211B of the cylinder portion 211 of the first discharge hole 211D and the second discharge hole 211C. Although the lengths L3 are different, the length L2 of the elongated hole 317 may be substantially the same as the length L3 of the elongated hole 318, and conversely, the length L3 of the elongated hole 318 is changed to the length L2 of the elongated hole 317. May be substantially the same as. When the length L2 of the elongated hole 317 and the length L3 of the elongated hole 318 are made substantially the same, after a cavity portion 316 having a predetermined length is bored in the upper end portion of the columnar main body 315A, a predetermined upper end portion of the main body 315A is formed. If a through hole having a length L2 or L3 is formed at the position, there is an advantage that the elongated holes 317 and 318 can be easily formed.

In the sixth embodiment shown in FIG. 9, in the cross-sectional view of FIG. 12 (c), the first discharge hole 211D and the second discharge hole 211C are located 180 ° apart from each other with respect to the piston portion 315 (FIG. 9). Since they are arranged at positions separated from each other in 12 (c)), the piston portion 215 and the shielding portion 215A are provided by providing the elongated holes 317 and the elongated holes 318 in the form of forming a through hole at the upper end of the main body 315A. The connecting portion 215B to be connected is formed by two outer peripheral surfaces sandwiched between the elongated hole 317 and the elongated hole 318.

For example, in the cross-sectional view of FIG. 11, when the first discharge hole 211D and the second discharge hole 211C are arranged at positions 90 ° apart from each other with respect to the piston portion 315, that is, the first discharge hole 211D and the second discharge hole 211D 2 When the discharge holes 211C are arranged in the directions orthogonal to the piston portion 315, the first discharge hole 211D and the second discharge hole 211C may be provided with the elongated holes 317 and the elongated holes 318, respectively. However, only one rectangular hole including the elongated hole 317 and the elongated hole 318 may be provided. By forming the rectangular hole, it becomes easy to form the connecting portion 215B (the portion excluding the rectangular hole at the upper end of the main body 315A) with respect to the columnar main body 315A.

Next, the valve opening operation of the refueling nozzle 1 according to the sixth embodiment will be described with reference to FIGS. 9 and 13. FIG. 9 is a diagram showing an initial state, and FIG. 13A shows a state in which the operating lever 221 is pulled until the bottom surface 316B of the cavity portion 316 of the piston portion 315 rises to the position of the inflow port 211B of the cylinder portion 211. FIG. 13 (b) is a diagram showing a state in which the operating lever 221 is pulled until the main valve 212 rises to the open position.

In the initial state, as shown in FIG. 9, the shielding portion 215A of the piston portion 315 shields the first discharge hole 211D and the second discharge hole 211C, while the lower end portion of the cavity portion 316 of the piston portion 315 is a long hole. Since the fluid chamber 211A of the cylinder portion 211 and the cavity portion 316 of the piston portion 315 communicate with the inflow port 211B of the cylinder portion 211 through the 317 and the elongated hole 318, the fluid chamber that applies the hydraulic pressure P to the valve shaft 213 is provided. It is configured. Hereinafter, for convenience of explanation, the fluid chamber composed of the fluid chamber 211A and the cavity portion 316 of the piston portion 315 will be referred to as "fluid chamber 211A'" in order to distinguish it from the fluid chamber 211A.

When the user grips the operation lever 221 together with the grip portion 3 of the refueling nozzle 1 from the initial state (the operation of pulling the operation lever 221), the operation lever 221 holds the shaft 223 as shown by the arrow R in FIG. 13 (a). It rotates counterclockwise to the center. By this rotational operation, the piston portion 215 in contact with the operating lever 221 is pushed into the fluid chamber 211A side (upper side in FIG. 13A) of the cylinder portion 211, and the shielding portion 215A and the connecting portion 215B of the piston portion 315 are brought into contact with each other. It enters the fluid chamber 211A from the inflow port 211B. Then, when the lower end 317B of the elongated hole 317 of the piston portion 315 and the lower end 318B of the elongated hole 318 reach the position of the inflow port 211B of the cylinder portion 211, as shown in FIG. The inflow of fuel F into the fluid chamber 211A'is blocked through the holes 317 and the elongated holes 318. At this time, since the shielding portion 215A of the piston portion 315 continues to shut off the first discharge hole 211D and the first discharge hole 211D, it exists in the fluid chamber 211A of the cylinder portion 211 and the cavity portion 316 of the piston portion 315. The fuel F will be confined in the fluid chamber 211A'.

When the piston portion 315 is further pushed into the fluid chamber 211A of the cylinder portion 211 from the state of FIG. 13A, the volume of the fluid chamber 211A'decreases and the hydraulic pressure P of the fluid chamber 211A' increases. When the user grips the operation lever 221 at a speed higher than the normal speed, the hydraulic pressure P of the fluid chamber 211A'increases sharply, but the elongated holes 317 and the elongated holes 318 of the piston portion 315 are the first discharge holes, respectively. The first discharge hole 211D and the second discharge hole 211C are shielded by the shielding portion 215A until the state of the 211D and the second discharge hole 211C is opposed to each other (the state shown in FIG. 13B). All of the hydraulic pressure P of 211A'is applied to the lower surface of the valve shaft 213, whereby the valve shaft 213 and the main valve 212 rise sharply.

Even if the valve shaft 213 and the main valve 212 suddenly rise, the first discharge hole 211D and the second discharge hole 211C are shielded by the shielding portion 215A until the main valve 212 rises to the open position. The hydraulic pressure P does not decrease, and the main valve 212 surely rises to the open position (see the state of FIG. 13B).

When the main valve 212 rises to the open position, as shown in FIG. 13B, the elongated holes 317 and the elongated holes 318 face each other in the first discharge hole 211D and the second discharge hole 211C, respectively. The fluid chamber 211A'is in a state where it can communicate with the first discharge hole 211D and the second discharge hole 211C, respectively, via the long hole 317 and the long hole 318. Therefore, if the hydraulic pressure P of the fluid chamber 211A'is abnormally high at this point, the safety valve 217 and the adjusting valve 233 are moved by the hydraulic pressure P at the opening positions of the first discharge hole 211D and the second discharge hole 211C, respectively. Even if the hydraulic pressure P in the fluid chamber 211A'is momentarily lowered by momentarily moving to the open position and discharging the fuel F in the fluid chamber 211A'to the outside of the cylinder portion 211, the main valve 212 is in the open position. Never returns to the closed position.

After that, when the liquid level of the fuel F supplied to the fuel tank of the vehicle rises to a position that closes the opening 235A of the discharge pipe 4, as described with reference to FIG. Since the outside air is no longer supplied, the negative pressure generated in the negative pressure generating portion 52A causes a suction force to act on the adjusting valve 233 in a direction away from the second discharge hole 211C against the urging force of the fourth spring 234, and the adjusting valve. 233 moves from the closed position to the open position of the second discharge hole 211C. When the main valve 212 is in the open position, the second discharge hole 211C communicates with the fluid chamber 211A'by the elongated hole 318. Therefore, when the adjusting valve 233 moves to the open position of the second discharge hole 211C, the second discharge hole 211C is second. The discharge hole 211C opens. Due to the opening of the second discharge hole 211C, the fuel F in the fluid chamber 211A'flows out to the fuel discharge chamber 231 and the hydraulic pressure P in the fluid chamber 211A' drops, and the main valve 212 automatically moves from the open position to the closed position. Return.

As a method for manufacturing the piston portion 315 according to the sixth embodiment, a hollow portion (or a recess) having a predetermined length along the axial direction is formed at the upper end portion of the columnar rod member, and a predetermined outer peripheral surface of the rod member is specified. An example of manufacturing by drilling an elongated hole or a rectangular hole extending in the axial direction at the position of the piston portion 215 has been described. However, if the method is to provide the shielding portion 215A and the connecting portion 215B at the upper end of the piston portion 215, this manufacturing method is used. Not limited to. For example, the shielding portion 215A and the connecting portion 215B may be separate members, and the shielding portion 215A may be connected to the upper end of the piston portion 215 by using the connecting portion 215B.

In this case, the shielding portion 215A need only be a member capable of partially shielding the first discharge hole 211D and the second discharge hole 211C, and does not need to be an annular member. For example, a shielding portion 215A is formed by a first shielding member that shields the first discharge hole 211D and a second shielding member that shields the second discharge hole 211C, and the first shielding member is placed on the upper end of the piston portion 215. The connecting portion 215B may be formed by the first connecting member to be connected and the second connecting member connecting the second shielding member to the upper end of the piston portion 215.

In the first to sixth embodiments described above, the lower ends of the piston portions 215 and 315 are brought into contact with the operating lever 221 and the rotational operation of the operating lever 221 is directly transmitted to the piston portions 215 and 315 to directly transmit the piston portions 215 and 315. Although the 315 was moved, an actuator for moving the pistons 215 and 315 was provided at the lower ends of the pistons 215 and 315, and a sensor for detecting the operation of the operation lever 221 was provided, and the detection signal of the sensor was provided. (Trigger signal) may be used to operate the actuator to move the piston portions 215 and 315 into the fluid chamber 211A of the cylinder portion 211.

When this configuration is adopted, it is possible to control the piston portions 215 and 315 to be moved into the fluid chamber 211A of the cylinder portion 211 by a predetermined amount at a constant speed regardless of how the user operates the operating lever 221. Therefore, a safety mechanism is adopted. 24 can be omitted, and the mechanical structure of the refueling nozzle 1 can be simplified. Further, by unitizing the circuit block including the actuator and the sensor that controls the movement of the piston portions 215 and 315 into the fluid chamber 211A based on the operation of the operating lever 221, the component unit can be attached to the refueling nozzle 1. It also has the advantage of being easy to replace in the event of a failure.

The refueling nozzle 1 used in the gas station has been described above for the fluid supply device according to the present invention. However, the fluid supply device according to the present invention is used when supplying or replenishing fluid from a large-capacity container to a small-capacity container. It can be widely applied to the liquid supply nozzle. Further, in the above embodiment, the device is described as a device when the user manually supplies the fluid. However, as described above, the fluid supply device according to the present invention is used in the manufacturing line for manufacturing the liquid storage product. It can also be applied as a filling nozzle that fills a container with a predetermined amount of fluid. In this case, instead of the operation lever 221, the above-mentioned actuator is provided at the lower end of the piston portion 215 or the piston portion 315, and the drive of the actuator is controlled by a control measure device (for example, a computer) that controls the manufacturing process of the liquid storage product. It is better to control by. In this case, the actuator and the control device function as the "operating means" of the present invention.

Further, in the above embodiment, the discharge amount of the fuel F discharged from the discharge pipe 4 reaches the amount that fills the fuel tank as a predetermined condition for executing the automatic valve closing, but the discharge amount of the fuel F May reach any preset amount. Alternatively, as a predetermined condition, the time during which the fuel F is discharged from the discharge pipe 4 may reach the predetermined discharge time.

Further, in the above embodiment, the fluid supply device having the automatic valve closing function has been described, but the fluid supply device according to the present invention does not necessarily have to have the automatic valve closing function. That is, the automatic valve closing function of the adjusting valve 233 due to the negative pressure of the atmospheric pressure fluctuation chamber 232 is omitted, the main valve 212 is moved from the closed position to the open position by the pulling operation of the operating lever 221, and the pulling open operation of the operating lever 221 is performed. The main valve 212 may be configured to return from the open position to the closed position.

1 Refueling nozzle (fluid supply device)
2 Nozzle body 21 Valve opening / closing mechanism 211 Cylinder part 211A, 211A'Internal space (fluid chamber)
211B Inflow port 211C 2nd discharge hole 211D 1st discharge hole 211E Fitting hole 212 Main valve 213 Valve shaft 213A Piston 213B Guide part 214 1st spring 215,315 Piston part 215A Shielding part (shielding member)
215B connecting part (connecting member)
316 Recess (hollow part)
317,318 Long holes 319, 319A, 319B Rotation prevention part 216 Second spring 217 Safety valve 218 Third spring 219 Sealing plug 219A, 219B, 219C Regulation part (regulatory means)
219D thin tube 220 support 22 operation mechanism 221 operation lever (operation means)
221A Grip operation part 222 Support part 223 Shaft 23 Automatic valve closing mechanism (valve closing means)
231 Fuel discharge chamber 232 Pressure fluctuation chamber 233 Control valve 234 4th spring 235 Thin pipe 235A Opening 236 Communication passage 237 Communication pipe 238 Diaphragm 24 Safety mechanism 3 Grip part 4 Discharge part (discharge pipe)
41 Discharge port 42 Liquid level detection unit (fluid amount detection means)
43 Check valve 44 Fifth spring 45 Valve seat 5 Flow path 5A Bending part (flow path blocking part)
51 1st flow path 52 2nd flow path 52A Gap (negative pressure generating part)
53 Minute flow path 54 Valve seat 6 Liquid supply hose F Fuel (fluid)

Claims (10)

A nozzle body with a flow path that guides the supplied fluid to the discharge pipe,
A cylinder portion connected to the flow path and having a fluid chamber filled with a part of the fluid, and a cylinder portion.
A main valve that is movably provided at a connection portion of the flow path with the cylinder portion to an open position that opens the flow path and a closed position that closes the flow path, and is normally urged to the closed position.
An operating means for switching the main valve to the open position,
A valve shaft whose one end is movably housed in the fluid chamber and whose other end is exposed from the fluid chamber and connected to the main valve, which is usually urged toward the fluid chamber side of the cylinder portion. When,
One end protrudes from the cylinder portion and comes into contact with the operating means, and the other end is provided so as to be movable in and out of the fluid chamber in a state of facing the inflow port into which the fluid flows into the cylinder portion. Normally, the piston part urged on the operating means side and
A fluid supply device characterized by being equipped with. The flow path of the nozzle body is provided with a regulating means for restricting the movement of the main valve at a predetermined position when the main valve moves from the closed position to the open position.
The fluid supply device according to claim 1. It is provided at an appropriate position on the inner surface of the cylinder portion, and is attached to a first discharge hole for discharging the fluid in the fluid chamber to the outside and the first discharge hole so as to be openable and closable, and is usually attached to the first discharge hole. Further equipped with a safety mechanism including a safety valve urged on the discharge hole side,
The fluid supply device according to claim 1 or 2. A second discharge hole for discharging the fluid in the fluid chamber to the outside and an opening position for opening the second discharge hole, which are provided at a position different from the first discharge valve on the inner surface of the cylinder portion. After the adjustment valve, which is displaceably provided at the closed position where the second discharge hole is closed and is normally urged to the closed position, and the main valve are switched to the open position, predetermined conditions are met. An automatic valve closing mechanism including a valve closing means for returning the main valve to the closed position when the main valve is established is further provided.
The fluid supply device according to claim 3. The valve closing means communicates with the outside via the discharge pipe, communicates with a portion of the nozzle body where negative pressure is generated in the flow path, and seals a side surface facing the discharge hole with a diaphragm. Consists of a pressure fluctuation chamber
The regulating valve is attached to a surface of the diaphragm facing the discharge hole.
The fluid supply device according to claim 4. The second discharge hole is arranged closer to the valve shaft piston portion than the first discharge hole.
The fluid supply device according to claim 4 or 5. The valve closing means includes a fluid amount detecting means for detecting that the amount of the fluid discharged from the discharge pipe has reached a predetermined fluid amount.
The establishment of the predetermined condition is that the fluid amount detecting means detects that the discharge amount from the discharge pipe has reached the predetermined fluid amount.
The fluid supply device according to any one of claims 4 to 6. The piston part
It is provided above the upper end of the piston portion, shields the first and second discharge holes in the initial state in which the front operating means is not operated, and is operated by the operating means to operate the upper end of the piston portion. A shielding member that releases the shielding of the first and second discharge holes at the timing when the piston reaches a position that closes the inflow port of the cylinder portion.
A connecting member that connects the shielding member to the piston portion,
Further prepare,
The fluid supply device according to any one of claims 4 to 7. The shielding member and the connecting member
In the initial state, the length of the piston portion is extended to a position where the upper end portion of the piston portion shields the first discharge hole, and a hollow portion having an open tip is formed in the extended portion, and the piston portion is formed. The piston portion is formed by forming a communication hole for communicating the first and second discharge holes with the cavity portion when the portion is moved to a position where the upper end of the piston portion closes the inflow port of the cylinder portion. It is provided above the upper edge of the
The fluid supply device according to claim 8. The piston portion is provided with a rotation prevention portion that prevents rotation of the piston portion around an axis when the piston portion moves in and out of the fluid chamber.
The fluid supply device according to any one of claims 1 to 9.

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