JP4939381B2 - Fuel supply device - Google Patents

Description

  The present invention relates to a fuel supply apparatus, and more particularly to a fuel supply apparatus that supplies fuel using a nozzle having a fuel supply stop mechanism that stops fuel supply when a liquid level is detected by a liquid level detection mechanism.

  For example, in a fuel supply device that supplies fuel to a fuel tank (a fuel supply body) mounted on a vehicle, liquid in the fuel tank is detected by a liquid level detection mechanism of a liquid supply nozzle inserted into a liquid supply port of the fuel tank. When a rise in the surface is detected, air suction by the negative pressure generating part in the nozzle is blocked by the liquid level, the locking of the valve mechanism of the liquid supply nozzle is released, and the main valve is closed to operate the fuel in the vehicle Prevents overflow from the liquid supply port.

  In addition, when the liquid level detection mechanism is activated and the liquid supply is to be further performed, the operator operates the nozzle lever of the liquid supply nozzle in the valve opening direction.

Here, when the operator performs additional liquid supply without reducing the flow rate, the oil liquid is ejected vigorously from the liquid supply nozzle, and therefore there is a possibility that the oil liquid may be ejected from the liquid supply port. For this reason, for example, as seen in Patent Document 1, there is an apparatus that controls the flow rate so as to reduce the flow rate by reducing the flow rate step by step every time the liquid supply is restarted (liquid supply stop).
JP-A-56-84296

  However, in the conventional fuel supply device, the flow rate at the time of resuming the supply is reduced every time the supply is stopped. Even if the liquid supply is stopped due to the fluid level detection mechanism being activated by the rebounding of the oil in the liquid port), the flow rate will be reduced, and as a result, the fuel tank will be reduced by the reduced flow rate. There was a problem that it took a long time to fill the inside with fuel.

  In view of the above circumstances, an object of the present invention is to provide a fuel supply device that solves the above-described problems.

  In order to solve the above problems, the present invention has the following means.

  The present invention provides a fuel supply system having a nozzle for supplying fuel to a fuel supply body, a flow meter for measuring a flow rate of fuel supplied from the fuel supply system, and the nozzle. A liquid level detection mechanism that detects a liquid level of fuel supplied to the supply body, and a fuel supply that is provided in the nozzle and stops fuel supply from the nozzle when the liquid level is detected by the liquid level detection mechanism In the fuel supply device having a stop mechanism and a flow rate adjusting valve provided in the fuel supply system for adjusting the flow rate of the fuel discharged from the nozzle, the fuel supply stop mechanism stops the fuel supply from the nozzle. The maximum discharge flow rate that can be discharged from the nozzle when the elapsed time from when the fuel supply by the nozzle is restarted is shorter than a predetermined time specified in advance. By by a control means for adjusting the valve opening of the flow control valve to decrease than the flow rate of the fuel supply stop immediately before, it is to solve the above problems.

  The present invention is the fuel supply device according to claim 1, wherein the control means detects that the discharge of fuel from the nozzle has stopped based on a flow rate measured by the flow meter. Means, a discharge resumption detecting means for detecting that the discharge of fuel from the nozzle is resumed based on a flow rate measured by the flow meter, and the discharge resumption detecting means after the discharge stop is detected by the discharge stop detecting means. Measuring means for measuring the elapsed time until the resumption of discharge is detected, determining means for determining whether the elapsed time measured by the timing means is shorter than a prescribed time defined in advance, and the judging means When the elapsed time is determined to be shorter than a predetermined time, the maximum discharge flow rate that can be discharged from the nozzle is the fuel supply by the fuel supply stop mechanism. A valve opening degree adjustment control means for adjusting the valve opening of the flow regulating valve as decrease than the flow rate of the stop just before, by having solves the above problems.

  The present invention is the fuel supply apparatus according to claim 2, wherein the valve opening degree adjustment control means is configured such that the flow rate measured by the flow meter immediately before the discharge stop detection is detected by the discharge stop detection means. When the flow rate is equal to or higher than a predetermined flow rate, the valve opening degree of the flow rate adjusting valve is adjusted so that the maximum discharge flow rate that can be discharged from the nozzle is smaller than the flow rate immediately before the fuel supply stop mechanism stops the fuel supply. This solves the above-mentioned problem.

  The present invention is the fuel supply apparatus according to claim 2 or 3, wherein the valve opening adjustment control means has a predetermined supply amount of fuel supplied from the nozzle to the fuel supply body. The above-mentioned problem is solved by adjusting the valve opening degree of the flow rate adjusting valve when the amount is less than the supply amount.

  According to the present invention, by comparing the elapsed time from when the liquid supply is stopped to when the fuel supply is restarted, the supply liquid stop immediately before the restart of the supply liquid is not the liquid level detection due to the liquid level rise in the fuel tank. It is possible to determine the factor (for example, whether or not the liquid level detection mechanism has been activated by the rebound of the oil in the liquid supply port), and the elapsed time from the supply stop to the restart of fuel supply If it is short, there is a high possibility that the liquid supply has stopped due to the liquid level detection based on the shape of the liquid supply port instead of the normal liquid level detection. It is possible to eliminate the liquid level detection due to the shape of the liquid port, reduce the number of times of liquid supply stop, and shorten the fuel supply time.

  The best mode for carrying out the present invention will be described below with reference to the drawings.

  FIG. 1 is a block diagram schematically showing an embodiment of a fuel supply apparatus according to the present invention. As shown in FIG. 1, the fuel supply device 11 is installed in a liquid supply station, and a liquid supply hose 15 connected to a liquid supply nozzle 13 is pulled out on the side surface of the apparatus main body 12. The liquid supply nozzle 13 is usually hooked on a nozzle hook 14 provided on the side surface of the apparatus main body 12. For example, when the vehicle arrives at the liquid supply station, the driver removes the liquid supply nozzle 13 from the nozzle hook 14 and inserts it into the liquid supply port 16a of the fuel tank 16 of the vehicle to supply liquid.

  As will be described later, the liquid supply nozzle 13 has a valve mechanism whose valve opening is adjusted by rotating the nozzle lever, a negative pressure generator that generates a negative pressure by the flow rate of oil, and one end that communicates with the negative pressure generator. A suction pipe (liquid level detection pipe) that sucks air with the other end having an air inlet opening near the tip of the discharge pipe, and negative pressure when the air inlet is closed due to liquid level rising due to liquid supply And a liquid level detection mechanism that performs a valve closing operation.

  The liquid supply nozzle 13 has a liquid supply hose 15 connected to a joint provided on the side surface of the nozzle body. The liquid supply hose 15 is connected to a liquid supply line (fuel supply system) 20 in the apparatus main body 12. It is connected. The liquid supply pipe 20 extends to the underground tank 21 and is inserted in the middle of which a pump 22, a flow meter 24, and a flow rate adjustment valve 27 are disposed.

  The flow rate adjusting valve 27 is a valve that adjusts the flow rate of the oil supplied to the liquid supply nozzle 13 and is continuously adjusted to a valve opening degree according to the frequency and duty of the drive signal output from the control circuit 25. It consists of a solenoid valve. The flow rate adjusting valve 27 has a solenoid that drives the valve body, and by applying an electromagnetic force in the valve opening direction to the valve body according to a duty ratio per cycle of a drive signal input to the solenoid, The valve opening is adjusted so that the discharge amount of the flow rate to be obtained is obtained.

  In addition, a liquid supply amount indicator 26 for displaying a liquid supply amount obtained by integrating the instantaneous flow rate measured by the flow meter 24 is disposed on the front surface of the apparatus main body 12. The nozzle switch 14 a of the nozzle hook 14, the pump motor 22 a of the pump 22, the flow rate pulse transmitter 24 a of the flow meter 24, and the liquid supply amount indicator 26 are connected to the control circuit 25.

  When the liquid supply nozzle 13 is removed from the nozzle hook 14 and a signal from the nozzle switch 14a is input, the control circuit 25 starts the pump motor 22a of the pump 22 and pumps up the oil in the underground tank 21, When the flow rate discharged from the liquid supply nozzle 13 is constant over a predetermined time, the valve opening degree of the flow rate adjustment valve 27 is controlled so that the constant flow rate becomes the maximum discharge flow rate.

  Further, the liquid supply nozzle 13 is configured such that the valve opening degree of the built-in valve is adjusted by the operation position of the nozzle lever. When the nozzle lever of the liquid supply nozzle 13 is operated, liquid supply to the fuel tank 16 is started, and a flow rate pulse is output from the flow rate pulse transmitter 24 a of the flow meter 24 to the control circuit 25.

  The control circuit 25 integrates the flow rate pulses output from the flow rate pulse transmitter 24a to display the supply amount on the supply amount indicator 26, and performs full tank supply control or preset supply control. Further, the control circuit 25 determines a predetermined time in which an elapsed time from when the fuel supply by the liquid level detection of the liquid supply nozzle 13 is stopped before the fuel supply by the liquid supply nozzle 13 is restarted before the full tank is detected. Control means for adjusting the valve opening degree of the flow rate adjusting valve 27 so that the maximum discharge flow rate that can be discharged from the liquid supply nozzle 13 is smaller than the flow rate immediately before the liquid supply is stopped.

  As will be described later, the control means includes a discharge stop detection means for detecting that fuel discharge from the liquid supply nozzle 13 has stopped based on a flow rate measured by the flow meter 24, and a flow rate measured by the flow meter 24. The discharge resumption detecting means for detecting that the fuel discharge from the liquid supply nozzle 13 has been resumed, and the elapsed time from when the discharge stop is detected by the discharge stop detecting means until the discharge restart is detected by the discharge resumption detecting means. Time measuring means, determination means for determining whether or not the elapsed time measured by the time measuring means is shorter than a predetermined time specified in advance, and an elapsed time shorter than the predetermined time specified in advance by the determination means Is determined, the flow rate adjusting valve 2 so that the maximum discharge flow rate that can be discharged from the liquid supply nozzle 13 is smaller than the flow rate immediately before the fuel supply stop mechanism stops the fuel supply. And a valve opening degree adjustment control means for adjusting the degree of valve opening.

  Further, as will be described later, the valve opening adjustment control means supplies liquid when the flow rate measured by the flowmeter 24 immediately before the discharge stop detection is detected by the discharge stop detection means is greater than or equal to a predetermined flow rate. The valve opening degree of the flow rate adjusting valve 27 is adjusted so that the maximum discharge flow rate that can be discharged from the nozzle 13 is smaller than the flow rate immediately before the fuel supply is stopped by the automatic valve closing mechanism 71 (fuel supply stop mechanism). The valve opening adjustment control means adjusts the valve opening of the flow rate adjusting valve 27 when the supply amount of fuel supplied from the liquid supply nozzle 13 to the fuel tank 16 is less than a predetermined supply amount. .

  2 (A) to 2 (C) show the change (drive signal) of the voltage applied to the solenoid of the flow regulating valve 27 comprising a continuously variable solenoid valve according to the duty value (30%, 50%, 100%). FIG. As shown in FIG. 2A, when the duty is set to 30%, the ON time A per cycle of the signal time B is A = B × 30/100. As shown in FIG. 2B, when the duty is set to 50%, the ON time A per cycle of the signal time B is A = B × 50/100. Further, as shown in FIG. 2C, when the duty is set to 100%, the ON time A per cycle of the signal time B is A = B × 100/100. Therefore, as the duty value of the drive signal applied to the solenoid of the flow rate adjusting valve 27 is increased, the valve opening degree of the flow rate adjusting valve 27 is increased, and the valve body 42 is fully opened at a duty of 100%.

  Here, the configuration of the liquid supply nozzle 13 will be described. FIG. 3 is a longitudinal sectional view of the liquid supply nozzle. FIG. 4 is a cross-sectional view of the liquid supply nozzle. As shown in FIGS. 3 and 4, the liquid supply nozzle 13 is provided with a grip 32 that is gripped during a liquid supply operation at the rear part of the nozzle body 33. The nozzle body 33 has an inflow port 33a to which the hose joint 34 is coupled on the left side surface, and an oil passage 33b communicated with the inflow port 33a inside.

  The hose joint 34 includes an elbow 34a that is rotatably fitted to the nozzle body 33, a joint 34b that is rotatably fitted to the other end of the elbow 34a, and a hose joint 34c that is connected to the joint 34b. Become. And the liquid supply hose 15 pulled out from the apparatus main body 12 is connected to the hose coupling 34c.

  A valve seat member 35 having a valve seat 35 a on which the main valve element 41 is seated is attached to the end of the nozzle body 33 on the front end side. A pipe connection member 37 to which the discharge pipe 36 is connected is inserted into the valve seat member 35.

  An oil passage 39 is formed in the valve seat member 35 and the pipe connection member 37. In the oil passages 33 b and 39, a liquid supply valve mechanism 43 including a negative pressure generator 40 and a main valve body 41 is accommodated.

  Further, the liquid supply nozzle 13 is provided with a nozzle lever 46 so as to be rotatable in front of the grip 32. The grip 32 includes a grip 32a, a first lever guard 32b surrounding the nozzle lever 46 on the front side, and a second lever guard mounted between the end of the grip 32 and the first lever guard 32b. 32c.

  The nozzle lever 46 is formed in the same shape as that of a pistol trigger, and has a curved portion 46b whose upper end is rotatably supported by a shaft 46a and whose lower end is curved in an arc shape.

  The negative pressure generating portion 40 described above is configured to generate a negative pressure corresponding to the discharge amount of the oil liquid provided in the valve seat member 35, and includes a passage 44 that opens to the inner wall of the tapered portion of the oil passage 39; The passage 44 is opened away from the inner wall when supplying liquid, and the valve body 47 is in contact with the inner wall by the pressing force of the coil spring 45 when the supply is stopped to close the opening portion of the passage 44 and the oil passage 39.

  The valve body 47 has a tapered contact portion that contacts the inner wall and closes the oil flow path 39, and is slidably inserted into a central hole formed in the pipe connection member 37. An air suction pipe 53 is inserted into the internal passage 36 a of the discharge pipe 36. One end of the air suction pipe 53 is connected to communicate with an air introduction hole 54 provided at the tip of the discharge pipe 36, and the other end of the air suction pipe 43 is a downstream passage formed in the pipe connection member 37. 49.

  The air introduction hole 54 functions as a liquid level detection mechanism at the time of full liquid supply, and communicates with the passage 44 via the air suction pipe 53, the passage 49, and the annular passage 55. The passage 44 communicates with the oil flow path 39 downstream of the valve seat 35a so as to suck air by the negative pressure generated by the negative pressure generating unit 40.

Then, the valve seat 35a is opened and oil is discharged to the discharge pipe 36, and a negative pressure is generated in the negative pressure generating part 40 due to the venturi effect, whereby the air sucked from the air introduction hole 54 is As shown in FIG. 4, the gas is introduced into the diaphragm chamber 58 through the suction pipe 53, the passage 49, the annular passage 55, and the passage 56.
To the passage 44 communicated with the central hole 39 and supplied to the annular passage 55 formed on the outer periphery of the valve seat member 35 and the pipe connection member 37. The annular passage 55 communicates with the other end of the passage 44 communicated with the oil passage 39.

  Next, the negative pressure generating unit 40 and the liquid supply valve mechanism 43 constituting the automatic valve closing mechanism (fuel supply stop mechanism) 71 will be described. When the nozzle lever 46 of the liquid supply nozzle 13 is operated in the C direction and the liquid supply valve mechanism 43 is opened, the valve body 47 is pressed in the A direction by the fluid pressure to open the valve and liquid supply is started.

  Thereby, the oil liquid passes through the oil flow path 39 and is discharged to the discharge pipe 36. At that time, the negative pressure generating unit 40 generates a venturi effect, that is, a negative pressure corresponding to the flow rate of the oil liquid, and the air in the passage 44 that opens to the inner wall of the oil passage 39 is sucked into the oil passage 39. Is done. While the air introduction hole 54 is not blocked by the oil liquid, the negative pressure generated in the diaphragm chamber 58 is small, but when the air introduction hole 54 is blocked by the oil liquid, the inside of the diaphragm chamber 58 is small. The negative pressure increases. Therefore, the diaphragm 74 is pulled up by this negative pressure. As a result, the main valve element 41 of the valve mechanism 43 is closed, and the discharge of the oil from the liquid supply nozzle 13 is stopped.

  Further, the valve shaft unit 60 that supports the main valve body 41 of the liquid supply valve mechanism 43 is slidably fitted with a front shaft 61, a rear shaft 62, and a sleeve 70 (sub valve drive unit). It has a triple structure and is housed in the nozzle body 33. A rear shaft 62 is slidably inserted into a hollow portion of the front shaft 61 formed in a cylindrical shape. The front shaft 61 and the rear shaft 62 are pivotally supported by bearings 63a and 63b provided in the nozzle body 33 so as to be slidable in the A and B directions, and by the spring force of the coil springs 64, 65 and 72. The main valve body 41 is pressed against the valve seat member 35.

  The front shaft 61 has a guide rod 61a inserted into a guide hole 41b formed inside a sub-flow channel 41a that penetrates the main valve body 41 at one end, and a disk-like shape that protrudes radially from the outer periphery of the guide rod 61a. A secondary valve body 61b. A coil spring 64 is in contact with the back surface of the sub-valve body 61 b, and the sub-valve body 61 b is seated on a sub-valve seat 41 c formed on the back side of the main valve body 41 by the spring force of the coil spring 64.

  Further, as shown in FIG. 3, the front shaft 61 includes a shaft hole 61d into which the rear shaft 62 is slidably inserted in the axial direction (A and B directions), a shaft hole 61d, and an oil passage. 39, a communication hole 61e communicating with 39, a small hole 61f penetrating to the outer peripheral side orthogonal to the shaft hole 61d, and a valve portion 68 formed inside the shaft hole 61d.

  The valve portion 68 functions as a pressure relief valve for releasing the pressure when the valve is closed, and includes a seal member 69 mounted inside the shaft hole 61d and a rear shaft 62 that contacts the seal member 69. It is comprised from the edge part 62a. The rear shaft 62 is urged in the A direction by the spring force of the coil spring 65 and is pressed against the seal member 69. Therefore, the valve portion 68 is normally closed, and when the main valve body 41 is closed as described later, the valve portion 68 is opened and the pressure of the oil passage 33b formed in the nozzle body 33 is reduced downstream. This is a pressure relief valve that escapes to the oil passage 39 on the side.

  Further, a sleeve 70 is fitted on the outer periphery of the front shaft 61 so as to be slidable in the axial direction. The sleeve 70 includes a large-diameter portion 70a that contacts a step portion 61g formed on the outer periphery of the front shaft 61, and a small-diameter cylindrical portion 70b that extends in the B direction from the large-diameter portion 70a.

  The large-diameter portion 70a of the sleeve 70 is pressed in the A direction by the spring force of the coil spring 72. When the pressing force due to the hydraulic pressure of the oil passage 33b is increased by the spring force of the coil spring 72, the large diameter portion 70a Moving. Therefore, the sleeve 70 operates so as to drive the sub-valve body 61b of the front shaft 61 in the valve closing direction when the hydraulic pressure in the oil flow path 33b decreases.

  On the outer periphery of the front shaft 61, the rear shaft 62, and the sleeve 70, recesses 61h, 62b, and 70c that are locked by a locking mechanism described later are formed. When these recesses 61h, 62b, and 70c are arranged at the same position, the front shaft 61, the rear shaft 62, and the sleeve 70 are integrally locked.

  The rear shaft 62 is provided with an insertion hole 62c through which the nozzle lever 46 is inserted. The upper end of the nozzle lever 46 protrudes in a semicircular shape with a contact portion 46c inserted through an insertion hole 62c that drives the valve mechanism 43 to open and close. Therefore, when the nozzle lever 46 is turned in the C direction, the front shaft 61, the rear shaft 62, and the sleeve 70 integral with the main valve body 41 are displaced in the valve opening direction (B direction).

  As a result, the oil supplied to the supply nozzle 13 via the supply hose 15 passes through the oil passages 33b and 39 and is supplied from the discharge pipe 36 to the supply port of the fuel tank.

  The automatic valve closing mechanism 71 is a mechanism that performs a valve closing operation by detecting the liquid level at the time of full liquid supply, a diaphragm chamber 58 that communicates with the passage 56, a diaphragm 74 that is mounted on the diaphragm chamber 58, and a diaphragm 74. The engaging member 75 is connected to the central portion of the first engaging portion 75 and engages with the recesses 61h, 62b, and 70c, the coil spring 67 that biases the diaphragm 74, and the lid 69 that closes the diaphragm chamber 58.

  The diaphragm 74 is fixed by a diaphragm presser 73 whose outer peripheral edge is pressed by a lid 69, and the central portion thereof is displaced in the E and F directions in accordance with the pressure change of the diaphragm chamber 58.

  The locking member 75 is fastened to the center portion of the diaphragm 74 by the coupling member 84 and is displaced in the E and F directions according to the pressure difference acting on the diaphragm 74. Further, the locking member 75 has a U-shaped cross section when viewed from the front so as to straddle the cylindrical portion 70 b of the sleeve 70.

  A pair of locking pins 76 extending in the vertical direction are slidably mounted in the A and B directions at both ends of the locking member 75 formed in a U-shape. The locking pin 76 integrally couples the front shaft 61, the rear shaft 62, and the sleeve 70 by fitting into the front shaft 61, the rear shaft 62, and the recesses 61h, 62b, and 70c of the sleeve 70, and the front side. The shaft 61 is locked with respect to the rear shaft 62.

  The diaphragm chamber 58 communicates with the oil flow path 39 of the negative pressure generating unit 40 via the passages 56, 55, 44 described above, and communicates with the suction pipe 53 via the passages 56, 55, 49. . At the time of liquid supply, the negative pressure generated by the negative pressure generator 40 is introduced into the suction pipe 53 via the passages 56, 55, and 49, and is sucked from the air introduction hole 54 provided at the tip of the discharge pipe 36. Air is supplied to the suction pipe 53 and the passages 49, 55, 44.

  Therefore, the pressure in the diaphragm chamber 58 is constant during the liquid supply, and does not change until the air introduction hole 54 is blocked by the liquid level rising the liquid supply port and the air supply from the suction pipe 53 is stopped. At this time, the diaphragm 74 provided in the diaphragm chamber 58 is biased in the F direction by the spring force of the coil spring 77, and the locking pin 76 of the locking member 75 is connected to the front shaft 61, the rear shaft 62, and the sleeve 70. Are held at the valve shaft locking position to be engaged with the recesses 61h, 62b, and 70c.

  Further, the rear shaft 62 in the liquid supply is locked at the valve opening position where the nozzle lever 36 is displaced in the B direction by the valve opening operation, and the front shaft 61 is moved to the rear via the pin 65a of the locking member 75. Locked to the side shaft 62.

  Here, when the air introduction hole 54 of the discharge pipe 36 is closed by the liquid surface or bubbles generated on the liquid surface, air suction from the air introduction hole 54 is blocked and the liquid level is detected. That is, air supply from the suction pipe 53 to the negative pressure generating unit 40 is stopped, and air in the diaphragm chamber 58 is sucked into the negative pressure generating unit 40 through the passages 56, 55, and 44.

  As a result, the air pressure in the diaphragm chamber 58 is reduced, and the central portion of the diaphragm 74 is displaced in the E direction against the spring force of the coil spring 77. Thus, the locking pin 76 of the locking member 75 provided on the diaphragm 74 is separated from the front shaft 61, the rear shaft 62, and the recesses 61h, 62b, and 70c of the sleeve 70, and the front shaft 51 and the sleeve 70 are locked. Is released. The front shaft 61 is closed in the direction A by the spring force of the coil spring 64 to bring the main valve body 41 into contact with the valve seat member 35. Thus, the oil passages 33b and 39 are blocked by the main valve body 41 and the supply of the oil liquid is stopped.

  Here, the operation of the liquid supply nozzle 13 when supplying liquid to the fuel tank of the vehicle will be described with reference to FIGS.

  Before the liquid supply operation, the liquid supply nozzle 13 is hooked on the nozzle hook 14 and the nozzle switch 14a is turned on. At this time, as shown in FIG. 6, the valve mechanism 43 of the liquid supply nozzle 13 is held in a closed state with the main valve body 41 abutting against the valve seat 35 a of the valve seat member 35. The sub valve body 61b is also seated on a sub valve seat 41c formed on the back side of the main valve body 41, and the valve portion 68 is in a closed state.

  As shown in FIG. 3, an operator who performs a liquid supply operation (a worker at a liquid supply station or a driver in the case of the self-service method) removes the liquid supply nozzle 13 from the nozzle hook 14 and supplies the liquid supply nozzle 13. The discharge pipe 36 is inserted into the liquid supply port 16 a of the fuel tank 16. Accordingly, when the nozzle switch 14a is turned on, the pump 22 is activated and the liquid can be supplied.

  As shown in FIG. 6, when the operator grips the grip portion 32 a of the grip 32 of the liquid supply nozzle 13 and pulls the curved portion 46 b of the nozzle lever 46 in the C direction, the valve shaft unit 60 opens in the valve opening direction ( The main valve body 41 of the valve mechanism 43 opens away from the valve seat member 35.

  At this time, the locking pin 76 of the locking member 75 provided on the diaphragm 74 is engaged with the front shaft 61, the rear shaft 62, and the recesses 61h, 62b, and 70c of the sleeve 70. The side shaft 62 and the sleeve 70 are integrally coupled. Further, the main valve body 41 is opened, and the sub-valve body 61b is separated from the sub-valve seat 41c of the main valve body 41 by the hydraulic pressure in the oil passage 33b and is held at the valve-opening position.

  While the main valve body 41 is separated from the valve seat member 35, the oil liquid fed by the pump 22 passes through the oil passages 33b and 39 and opens the valve body 47 as shown by arrows in FIG. Then, the fuel is discharged from the discharge pipe 36 to the fuel tank 16 of the vehicle. Thus, when the valve body 47 is opened, the flow rate of the oil is increased, and a negative pressure is generated in the negative pressure generator 40. Thereby, the air in the air introduction hole 54 of the discharge pipe 36 is sucked into the negative pressure generating unit 40.

  When the liquid level rises from the liquid supply nozzle 13 to the fuel tank 16 and the liquid level rises, and eventually rises to the liquid supply port 16a, bubbles generated on the liquid level reach the tip of the discharge pipe 36.

  When the oil liquid closes the air introduction hole 54 of the discharge pipe 36, air suction from the air introduction hole 54 is shut off, the main valve body 41 shown in FIG. 7 is closed, and the valve portion 68 is opened. . That is, air supply from the suction pipe 53 to the negative pressure generating unit 40 is stopped, and air in the diaphragm chamber 58 is sucked into the negative pressure generating unit 40 through the passages 56, 55, and 44.

  Therefore, the air pressure in the diaphragm chamber 58 is reduced, and the central portion of the diaphragm 74 is displaced in the E direction against the spring force of the coil spring 77. As a result, the locking pin 76 of the locking member 75 provided on the diaphragm 74 is separated from the recesses 61 h and 62 b of the front shaft 61 and the rear shaft 62 to release the locking of the front shaft 61. The locking pin 76 of the locking member 75 is engaged only with the recess 70c of the sleeve 70 located on the outermost periphery.

  The front shaft 61 released from the engagement as described above is closed in the valve closing direction (A direction) by the spring force of the coil spring 64 and the spring force of the coil spring 72 pressing the large diameter portion 70a of the sleeve 70 in the A direction. The main valve body 41 is brought into contact with the valve seat 35a of the valve seat member 35 by sliding. Thus, the oil passages 33b and 39 are blocked by the main valve body 41 and the supply of the oil liquid is stopped.

  Here, immediately after the main valve body 41 is closed, since the hydraulic pressure pressurized by the pump 22 remains in the oil flow path 33b and the liquid supply hose 15, it is inserted into the oil flow path 33b. The large diameter portion 70 a of the sleeve 70 is slid in the B direction against the spring force of the coil spring 72.

  In addition, since the rear shaft 62 maintains the valve opening state of the nozzle lever 46, the rear shaft 62 is maintained in a state of moving in the valve opening direction (direction B), and the end portion 62 a is connected to the valve portion 98. It is separated from the seal member 69. Therefore, the valve portion 68 is opened, and the oil in the oil flow path 33b and the liquid supply hose 15 flows out to the oil flow path 39 through the small hole 61f and the communication hole 61e. The liquid hose 15 is depressurized.

  Next, the oil pressure between the oil passage 33 b and the liquid supply hose 15 flows out downstream of the main valve body 41 through the small hole 61 f of the front shaft 61, thereby reducing the fluid pressure in the oil passage 33 b. Then, the liquid supply nozzle 13 is in the state shown in FIG. That is, when the valve seat 35a is closed by the main valve body 41 by the valve closing operation of the automatic valve closing mechanism 71, the discharge of the oil liquid stops and the valve body 47 is closed by the spring force of the coil spring 45. Air suction by the negative pressure generator 40 is stopped.

  Therefore, the pressure of the diaphragm chamber 58 to which air is supplied to the diaphragm chamber 58 returns to the atmospheric pressure, and the diaphragm 74 returns to the F direction by the spring force of the coil spring 77. At the same time, the sleeve 70 moves in the direction A by the bias of the coil spring 72.

  As a result, the locking member 75 fixed to the central portion of the diaphragm 74 moves to a locking position for locking the valve shaft unit 60, and the locking pin 76 of the front shaft 61 and the sleeve 70 except for the rear shaft 62. Engages with the recesses 61h and 70c. Therefore, the rear shaft 62 is not locked by the locking pin 76 and is maintained in a movable state with respect to the front shaft 61.

  Further, since the flow rate adjustment valve 27 is opened even after the automatic valve closing operation based on the bubble detection, the sub-valve body 61b of the liquid supply nozzle 13 is opened. That is, when the oil liquid pressurized by the pump 22 is supplied to the liquid supply hose 15 and the oil flow path 33b, the liquid pressure in the oil flow path 33b rises, so that the large diameter portion 70a of the sleeve 70 becomes the liquid pressure. It is pressed and slides in the B direction.

  At this time, since the locking pin 76 is engaged with the front shaft 61 and the recesses 61 h and 70 c of the sleeve 70, the front shaft 61 slides in the B direction together with the sleeve 70.

  Accordingly, the sub valve body 61b of the front shaft 61 moves away from the sub valve seat 41c of the main valve body 41 to the valve opening position. As a result, the oil supplied to the oil flow path 33 b passes through the sub flow path 41 a formed inside the main valve body 41 and is discharged to the oil flow path 39. Thus, a small amount of oil liquid is additionally supplied to the liquid supply port 16 a of the fuel tank 16.

  When the liquid level in the fuel tank 16a rises and bubbles generated on the liquid level again block the air introduction hole 54 of the discharge pipe 36, the sub valve body is closed by the valve closing operation of the automatic valve closing mechanism 71 described above. When 61b contacts the sub valve seat 41c of the main valve body 41 to close the sub flow path 41a, the first additional liquid supply is completed.

  Here, a liquid supply operation pattern using the liquid supply nozzle 13 having the automatic valve closing mechanism 71 will be described. 8A and 8B are diagrams showing a conventional liquid supply operation pattern, in which FIG. 8A is a graph showing a flow rate change, FIG. 8B is a graph showing a valve opening degree of the flow rate adjusting valve 27, and FIG. 8C is an operation position of the nozzle lever 46. It is a graph to show.

  In FIG. 8A, as indicated by the alternate long and short dash line, the flow rate change due to the normal full tank liquid supply continues stably. Here, in the conventional liquid supply process, as shown in FIG. 8B, the valve opening degree of the flow rate adjusting valve 27 is reduced by reducing the valve opening degree every time the liquid supply is stopped. The maximum flow rate that can be discharged from the nozzle 13 is reduced. For this reason, as shown by a solid line in FIG. 8A, when the liquid level detection mechanism is activated by the rebound of the oil in the liquid supply port at time T1 immediately after the start of liquid supply, the operator moves the nozzle lever 46. When the liquid supply is resumed by re-gripping, even if the main valve body 41 of the liquid supply nozzle 13 is fully opened, the maximum dischargeable flow rate is reduced by the valve opening degree of the flow rate adjustment valve 27.

  Furthermore, when the nozzle operator stops the supply of liquid and restarts the supply in the same manner as described above at times T2 and T3 after the supply of liquid stops, the maximum flow rate that can be discharged from the supply nozzle 13 is changed to the flow rate adjustment valve 27 each time. It is throttled by the valve opening degree. Thus, in the prior art, whenever the liquid supply stops, the cause of the liquid supply stop is caused by, for example, the operator releasing the nozzle lever 46, and the liquid supply with a reduced flow rate is necessary. Even if this is not the case, the maximum flow rate of the oil liquid that can be discharged from the liquid supply nozzle 13 is limited, so that the liquid supply time is extended accordingly.

  9A and 9B are diagrams showing a liquid supply operation pattern according to the present invention. FIG. 9A is a graph showing a change in flow rate, FIG. 9B is a graph showing a valve opening degree of the flow rate adjusting valve 27, and FIG. It is a graph which shows a position.

  As shown in FIG. 9A, when the oil liquid closes the air introduction hole 54 of the discharge pipe 36 immediately after the start of liquid supply, the automatic valve closing mechanism 71 is closed by detecting the liquid level of the liquid level detecting mechanism. The liquid supply is stopped by this. Thereafter, when resuming the liquid supply, the operator operates the nozzle lever 46 of the liquid supply nozzle 13 in the valve opening direction. Thereby, the liquid supply is resumed.

  The present invention is characterized in that the flow rate is controlled based on the time (elapsed time t) from the supply stop to the supply restart.

  Here, how to set the elapsed time t will be described. First, when it is clear that the fuel tank 16 is not filled with fuel, such as when the automatic valve closing mechanism 71 of the liquid supply nozzle 13 is closed immediately after the start of liquid supply, the driver still has to Immediately operate the nozzle lever 46 to the valve open position by determining that the fuel tank 16 is not filled with fuel (the cause of the operation of the liquid level detection mechanism is that caused by the rebound of the oil in the liquid supply port). Then restart the supply. For this reason, the elapsed time t1 in this case is relatively short. On the other hand, when the automatic valve closing mechanism 71 is closed by the liquid level detection operation of the liquid supply nozzle 13, the driver determines that the liquid supply is stopped by the liquid level detection, and the liquid supply port 16a of the fuel tank 16 is determined. Consider whether or not to supply additional liquid by looking into the interior. Then, since it is determined that additional liquid supply is to be performed, the nozzle lever 46 of the liquid supply nozzle 13 is operated to the valve opening position. In this case, the elapsed time t2 is a case where the liquid supply is resumed immediately after the start of the liquid supply. It will be longer than the elapsed time t1.

  Therefore, the elapsed time t from when the liquid supply is stopped to when the liquid supply is restarted is counted and compared with a preset specified time t0 (in this embodiment, the specified time t is t1 <t0 <t2). As a result, it is possible to determine whether or not the stoppage of liquid supply immediately before the additional fuel supply is based on the operation of the liquid level detection mechanism due to the fuel in the fuel tank 16 being filled.

  The elapsed times t1 and t2 are determined by investigating the actual liquid supply operation of the worker. In this embodiment, the elapsed time t1 is, for example, about t1 = 1 to 3 seconds. The elapsed time t2 is assumed to be about t2 = 5 to 7 seconds longer than the elapsed time t1, and the specified time t0 is set to 4 seconds.

  In FIG. 9B, as indicated by the solid line or broken line, when the automatic valve closing mechanism 71 restarts the liquid supply after the valve closing operation, the following control is performed as indicated by the solid line. Do. First, it is determined whether the time (elapsed time t) from the supply stop to the supply restart is smaller than the predetermined time t0. If the elapsed time t is smaller than the predetermined time t0, the flow rate adjustment valve 27 The maximum flow rate that can be discharged from the liquid supply nozzle 13 is reduced by reducing the valve opening degree by one or two stages, thereby suppressing the splashing of the oil at the liquid supply port 16a. Therefore, in this embodiment, it is possible to prevent the automatic valve closing mechanism 71 from being actuated (liquid supply stop operation) due to the rebound of the oil liquid, thereby shortening the liquid supply time. When the elapsed time t is larger than the predetermined time t0, the maximum flow rate that can be discharged from the liquid supply nozzle 13 without reducing the valve opening degree of the flow rate adjustment valve 27 as shown by the broken line in FIG. 9A. The liquid supply time can be shortened by enabling the liquid supply without reducing.

  Here, the main control process executed by the control circuit 25 of the fuel supply device 11 will be described with reference to the flowchart of FIG. In S11 of FIG. 10, it is checked whether the nozzle switch 14a is off. In S11, when the nozzle switch 14a is OFF, it is determined that the liquid supply nozzle 13 is removed from the nozzle hook 14 and the liquid supply operation is performed, and the process proceeds to S12. In S12, the flow regulating valve 27 composed of a continuously variable electromagnetic valve is opened, and the pump 22 is activated in S13.

  The liquid supply nozzle 13 is inserted into the liquid supply port 16a of the fuel tank 16 and the nozzle lever 46 is operated to the valve opening position. The main valve body 41 of the liquid supply nozzle 13 is opened, and liquid is fed by the pump 22. Fuel is supplied to the fuel tank 16. Subsequently, in S14, the valve opening degree of the flow rate adjusting valve 27 is adjusted to control the discharge amount discharged from the liquid supply nozzle 13. This discharge amount control is a process of a flowchart shown in FIG. 11 described later, and the description thereof is omitted here.

  Thereby, the supply amount discharged from the liquid supply nozzle 13 is measured by the flow meter 24. Therefore, in S15, the flow rate pulse from the flow meter 24 is integrated to calculate the supply amount (supply amount), and in S16, the calculated supply amount (supply amount) is displayed on the supply amount indicator 26.

  In the next S17, it is determined whether or not the liquid supply nozzle 13 has been returned to the nozzle hook 14, and when the nozzle switch 14a is OFF (in the case of NO), the liquid supply nozzle 13 is removed from the nozzle hook 14 and the nozzle switch 14a is turned off. It is determined that the liquid supply operation is being performed, and the process returns to S14. In S17, when the nozzle switch 14a is off (in the case of YES), since the liquid supply nozzle 13 has been returned to the nozzle hook 14, it can be determined that the liquid supply has ended, and the process goes to S18. Then, the flow rate adjusting valve 27 composed of a continuously variable electromagnetic valve is closed. Then, it progresses to S19 and the pump 22 is stopped. This completes the control process for the current liquid supply operation.

  Next, the discharge amount control process (the process of S14 of FIG. 10) executed by the control circuit 25 of the fuel supply device 11 will be described with reference to the flowchart of FIG. In S21 of FIG. 11, the flow rate pulses from the flow meter 24 are integrated to check whether the flow rate is zero or more. In S21, when the flow rate is zero or more (in the case of YES), the process proceeds to S22, and it is checked whether or not the current integrated flow rate is higher than a predetermined integrated flow rate set in advance. In S22, when the current integrated flow rate is larger than the predetermined integrated flow rate set in advance (in the case of YES), the operation of the automatic valve closing mechanism 71 caused by the continued liquid supply is continued in the fuel tank 16. In other words, the process is terminated without performing control to reduce the maximum flow rate that can be discharged from the liquid supply nozzle 13.

  In S22, when the current integrated flow rate is smaller than the predetermined integrated flow rate set in advance (in the case of NO), the process proceeds to S23.

  In S23, it is checked whether or not the liquid supply is stopped (flow rate = 0) (discharge stop detection means). If the liquid supply is stopped (flow rate = 0) (in the case of YES), the process proceeds to S24 and immediately before the liquid supply is stopped. It is checked whether or not the flow rate is equal to or higher than a predetermined flow rate set in advance. The predetermined flow rate in S24 is a flow rate at which the automatic valve closing mechanism 71 can be closed. In S24, the flow rate measured by the flow meter 24 is the valve closing mechanism of the automatic valve closing mechanism 71 of the liquid supply nozzle 13. It is determined whether or not the flow rate is higher than the possible operation. In S24, when the flow rate immediately before stopping the liquid supply is equal to or higher than a predetermined flow rate set in advance (in the case of YES), the liquid supply is performed at a flow rate at which the automatic valve closing mechanism 71 of the liquid supply nozzle 13 can be closed. The process proceeds to S25.

  In S25, a liquid supply stop time, which is an elapsed time t from the liquid supply stop, is started (timer operation) (timer means). Subsequently, in S26, it is determined whether or not the measured liquid supply stop time is equal to or longer than a predetermined time (for example, 4 seconds) set in advance (determination means). In S26, when the measured liquid supply stop time is longer than a predetermined time (for example, 4 seconds) set in advance (in the case of YES), as described above, the liquid supply nozzle 13 by the normal full tank detection is used. It is determined that the valve closing operation of the automatic valve closing mechanism 71 has been performed, and the process proceeds to S27 to stop the time measurement of the liquid supply stop time (stop the counting) and reset the time measured (the count value is zero). Then, the process returns to S22.

  In S26, when the measured liquid supply stop time is less than a predetermined time (for example, 4 seconds) set in advance (in the case of NO), the current liquid supply stop is the oil in the liquid supply port. It is determined that there is a possibility that the automatic valve closing mechanism 71 has been operated due to the rebound of the liquid and the liquid supply has been stopped, and the process proceeds to S28, where it is checked whether or not the liquid supply has been restarted (discharge restart detection means). In S28, when the flow rate measured by the flow meter 24 is greater than zero (in the case of YES), it is determined that the liquid supply has been resumed by operating the nozzle lever 46 of the liquid supply nozzle 13 to the valve opening position, and S29. Proceed to If the flow rate measured by the flow meter 24 is zero, the process proceeds to S26 described above.

  In S29, the valve opening degree of the flow rate adjusting valve 27 is adjusted so that the maximum flow rate discharged from the liquid supply nozzle 13 is less than the flow rate immediately before the liquid supply is stopped (valve opening adjustment control means). For example, the valve opening degree of the flow rate adjusting valve 27 composed of a continuously variable electromagnetic valve is adjusted so that the maximum flow rate discharged from the liquid supply nozzle 13 is 90% of the flow rate immediately before the liquid supply is stopped. Thereby, since the maximum flow rate discharged from the liquid supply nozzle 13 is reduced by 10%, the rebound of the oil liquid in the liquid supply port 16a is reduced, and the liquid level detection mechanism of the liquid supply nozzle 13 is detected before the full tank is detected. Can be prevented from detecting.

  Accordingly, the number of times of liquid supply stop due to the rebound of the oil before the full tank is detected by the liquid supply nozzle 13 is reduced, and the valve opening is not throttled (the flow rate is reduced) when the liquid supply is stopped. Time can be shortened.

  Thereafter, the process proceeds to S27, where the liquid supply stop time is stopped (count is stopped), the time is reset (count value is zero), and the process returns to S22. Then, when the liquid supply by the liquid supply nozzle 13 is resumed, the process again proceeds to the process of S22 described above, and the process ends when the current integrated flow rate exceeds a predetermined integrated flow rate set in advance. .

  If the liquid supply is not stopped in S23, and if the flow rate immediately before the liquid supply is stopped is less than the predetermined flow rate set in advance in S24, the process returns to S22 and the processes in S22 to S24 are repeated.

FIG. 12 is a flowchart for explaining a modification of the discharge amount control process (the process of S14 of FIG. 10) executed by the control circuit 25 of the fuel supply device 11. In FIG. 12, S21 to S28 are the same processing as in FIG. In S29a, the valve opening degree of the flow rate adjustment valve 27 composed of a continuously variable electromagnetic valve is adjusted to 90% immediately before the supply of liquid is stopped (valve opening degree adjusting control means). As a result, the flow rate discharged from the liquid supply nozzle 13 is reduced by 10% at the maximum, so that the rebound of the oil liquid in the liquid supply port 16a is reduced and the liquid level of the liquid supply nozzle 13 is detected before the full tank is detected. It is possible to prevent the mechanism from performing a detection operation.
Even if the valve opening degree of the flow rate adjusting valve 27 is reduced to 90%, the flow rate does not decrease if the maximum discharge amount of the liquid supply nozzle 13 is equal to or less than the flow rate of the flow rate adjusting valve 27. In this case, by stopping the liquid supply by the automatic valve closing mechanism 71 of the liquid supply nozzle 13 again, the rebound of the oil liquid in the liquid supply port 16a is reduced, and the liquid of the liquid supply nozzle 13 is detected before the full tank is detected. It is possible to prevent the surface detection mechanism from performing a detection operation.

  In the above embodiment, the apparatus for supplying an oil liquid such as gasoline or light oil has been described as an example. However, the present invention is not limited to this, and other fuels (for example, CNG, LNG, LPG, hydrogen, etc.) are used. Of course, the present invention can also be applied to the fuel supply device to be supplied.

  Further, in the above embodiment, the air introduction hole 54 sucked by the negative pressure generating unit 40 accompanying the liquid supply is provided at the tip of the liquid supply nozzle 13 as a liquid level detection unit (liquid level sensor). A negative pressure is introduced into the diaphragm chamber 58 that unlocks the main valve body 41 by being blocked by the liquid level, and the main valve body 41 is unlocked to release the main valve body by the automatic valve closing mechanism 71. Although the configuration in which the valve closing operation (liquid supply stop) 41 is performed is taken as an example, the present invention is not limited to this. For example, an ultrasonic sensor or an optical sensor for detecting the liquid level at the tip of the liquid supply nozzle 13 is used. Of course, the main valve element 41 may be unlocked based on the liquid level detection signals output from these sensors.

It is a block diagram which shows typically one Example of the fuel supply apparatus by this invention. It is a figure which shows the change (drive signal) of the voltage applied to the solenoid of the flow regulating valve 27 which consists of a continuously variable solenoid valve according to the value (30%, 50%, 100%) of duty. It is a longitudinal cross-sectional view of a liquid supply nozzle. It is a cross-sectional view of a liquid supply nozzle. It is a cross-sectional view showing the valve mechanism of the liquid supply nozzle in which the main valve body is closed. It is a cross-sectional view showing the valve mechanism of the liquid supply nozzle in which the main valve body is opened. It is a transverse cross section showing valve closing operation by an automatic valve closing mechanism. It is a figure which shows the conventional liquid supply operation | movement pattern, (A) is a graph which shows flow volume change, (B) is a graph which shows the valve opening degree of the flow regulating valve 27, (C) is a graph which shows the operation position of the nozzle lever 46. is there. 4A and 4B are diagrams illustrating a liquid supply operation pattern according to the present invention, in which FIG. 5A is a graph showing a change in flow rate, FIG. 5B is a graph showing a valve opening degree of the flow control valve 27, and FIG. It is. 4 is a flowchart for explaining a main control process executed by a control circuit 25 of the fuel supply device 11. 4 is a flowchart for explaining a discharge amount control process executed by a control circuit 25 of the fuel supply device 11. 7 is a flowchart for explaining a modified example of the discharge amount control process executed by the control circuit 25 of the fuel supply device 11.

Explanation of symbols

DESCRIPTION OF SYMBOLS 11 Fuel supply device 13 Supply nozzle 14 Nozzle hook 14a Nozzle switch 16 Fuel tank 16a Supply port 20 Supply line 22 Pump 24 Flow meter 25 Control circuit 26 Supply amount indicator 27 Flow rate adjustment valve 35 Valve seat member 36 Discharge Pipe 40 Negative pressure generating part 41 Main valve body 43 Valve mechanism 46 Nozzle lever 47 Valve body 54 Air introduction hole 58 Diaphragm chamber 60 Valve shaft unit 71 Automatic valve closing mechanism 74 Diaphragm 76 Locking pin

Claims (4)

A fuel supply system having a nozzle for supplying fuel to the fuel supply body;
A flow meter for measuring the flow rate of fuel supplied from the fuel supply system;
A liquid level detection mechanism that is provided in the nozzle and detects a liquid level of the fuel supplied to the fuel supply body;
A fuel supply stop mechanism that is provided in the nozzle and stops the fuel supply from the nozzle when the liquid level is detected by the liquid level detection mechanism;
A flow rate adjusting valve provided in the fuel supply system for adjusting the flow rate of fuel discharged from the nozzle;
In a fuel supply device having
Maximum discharge that can be discharged from the nozzle when the elapsed time from when the fuel supply from the nozzle is stopped by the fuel supply stop mechanism to when the fuel supply by the nozzle is restarted is shorter than a predetermined time. A fuel supply apparatus comprising: control means for adjusting a valve opening degree of the flow rate adjusting valve so that a flow rate is decreased from a flow rate immediately before the fuel supply stop mechanism by the fuel supply stop mechanism. The fuel supply device according to claim 1,
The control means includes
A discharge stop detecting means for detecting that fuel discharge from the nozzle has stopped based on a flow rate measured by the flow meter;
A discharge resumption detecting means for detecting that the discharge of fuel from the nozzle is resumed from the flow rate measured by the flow meter;
Time measuring means for measuring an elapsed time from when discharge stop is detected by the discharge stop detecting means to when discharge restart is detected by the discharge restart detecting means;
Determining means for determining whether or not the elapsed time measured by the time measuring means is shorter than a predetermined time specified in advance;
When the determining means determines that the elapsed time is shorter than a predetermined time, the maximum discharge flow rate that can be discharged from the nozzle is less than the flow rate immediately before the fuel supply stop mechanism stops the fuel supply. Valve opening adjustment control means for adjusting the valve opening of the flow regulating valve so as to
A fuel supply device comprising: The fuel supply device according to claim 2,
The valve opening adjustment control means can discharge from the nozzle when the flow rate measured by the flow meter is equal to or higher than a predetermined flow rate immediately before the discharge stop detection unit detects the discharge stop. The fuel supply device, wherein the valve opening degree of the flow rate adjusting valve is adjusted so that a maximum discharge flow rate is smaller than a flow rate immediately before the fuel supply stop mechanism by the fuel supply stop mechanism. The fuel supply device according to claim 2 or 3,
The valve opening adjustment control means adjusts the valve opening of the flow rate adjusting valve when the supply amount of fuel supplied from the nozzle to the fuel supply body is less than a predetermined supply amount. A fuel supply device.

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