JP4603447B2 - Lubrication nozzle - Google Patents

Description

  The present invention relates to a fueling nozzle that is provided at the tip of a hose of a measuring machine installed in a fueling station or the like and supplies fuel to a fuel tank of a vehicle or the like.

  Conventionally, during a refueling operation, a refueling operator removes a refueling nozzle from a predetermined nozzle storage location provided in the main body of the measuring machine, etc., inserts the cylinder tip into the refueling port of the fuel tank, and the nozzle lever of the refueling nozzle (operation Open the valve and perform the refueling operation.

  By opening the valve of the nozzle lever, the valve provided in the liquid passage in the nozzle body of the oil supply nozzle is opened when the valve body is separated from the valve seat. Further, the oil supply means (liquid supply means) such as a pump provided in the measuring machine main body is already activated by removing the oil supply nozzle from a predetermined nozzle storage location.

  By opening the oil supply nozzle, the oil supplied from the oil supply means to the oil supply nozzle through the hose is discharged from the cylinder opening provided on the downstream side of the valve of the oil supply nozzle, and is actually supplied to the fuel tank. Refueling is started.

  On the other hand, the end of refueling is performed when the refueling operator closes the nozzle lever of the refueling nozzle, or when the automatic valve closing mechanism provided in the nozzle main body of the refueling nozzle is activated, The valve body portion of the valve provided on the seat is seated on the valve seat portion and closed.

  If the refueling operator can still perform a small amount of additional refueling after closing the nozzle lever of the refueling nozzle or after the automatic valve closing mechanism provided in the refueling nozzle is activated, the nozzle lever of the refueling nozzle After performing a small valve opening operation to perform a small amount of additional refueling work, aligning the oil amount with an integer, or filling the tank full of fuel tank capacity, and then closing the fuel nozzle, It is designed to be stored in a predetermined nozzle storage location.

  At that time, the oil supply means such as a pump provided in the main body of the measuring machine is stopped when the oil supply nozzle is stored in the nozzle storage place, and the nozzle lever of the oil supply nozzle is closed or automatically closed. When the valve mechanism is activated, it is still in the drive state.

JP-A 63-178996

  By the way, in the conventional oil supply nozzle, the valve body part of the valve provided in the nozzle body is separated from the valve seat part corresponding to the operation amount of the nozzle lever of the oil supply nozzle, and the oil supply corresponding to the amount of separation is performed. The valve opening amount of the nozzle changes directly, and the flow rate of the oil liquid discharged from the cylinder tip opening of the oil supply nozzle is adjusted. Therefore, when performing the small amount of additional refueling operation described above, a delicate nozzle lever operation is required.

  However, when performing this small amount of additional refueling work, the valve body part of the valve provided in the nozzle body is seated on the valve seat part and the oil supply nozzle is closed, and the upstream side of the valve body part (oil liquid On the surface of the supply means side), the supply pressure of the oil is acting by the oil supply means being driven. Therefore, the pressure acting on the upstream side of the valve body (oil supply means side) is higher than the pressure acting on the downstream side of the valve body (the cylinder tip opening side of the oil nozzle). Since the body part has a differential pressure that presses the valve body part in the valve closing direction, it occurs in the valve body part when opening the nozzle lever of the oiling nozzle to perform a small amount of additional oiling work. The nozzle lever must be opened by a small amount against the differential pressure in the valve closing direction.

  However, since the operating force of the nozzle lever resists this differential pressure, it becomes unexpectedly large, the amount of separation of the valve body portion from the valve seat portion at the beginning of the valve opening increases, and the oil discharged from the cylinder tip opening of the oil supply nozzle There was a tendency for the liquid flow rate to increase. Therefore, in order to perform a small amount of additional refueling work, skill is required to perform the delicate nozzle lever operation of the above-described refueling nozzle, and it is difficult for an operator who is unfamiliar with the handling of the weighing machine. There was a problem that. Further, in the worst case, there is a possibility that the oil liquid overflows from the fuel filler opening of the fuel tank.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide an oil supply nozzle that is improved in performance such as operability and safety during a small amount of additional oil supply work.

  In order to solve the above-described problem, the fueling nozzle of the present invention relates to the operation of the nozzle lever of the fueling nozzle, and sets the valve opening amount of the fueling nozzle within a predetermined operation amount range immediately after the start of the valve opening operation. It is characterized in that it can be maintained at a minute constant flow rate regardless of the operation amount of the nozzle lever.

Therefore, fueling nozzle of the present invention includes a nozzle body having an internal fluid passage, a main valve body and away seated against installed et a valve seat in the fluid passage, communicating and blocking the fluid passage, the main valve A sub-valve that communicates with and shuts off the valve passage that is provided to connect the upstream and downstream sides of the main valve body to and from the valve seat provided on the body, and interlocks with the operation of the operation piece The valve stem member is displaced from the valve seat of the main valve body seated on the valve seat in response to the valve opening direction displacement of the valve shaft member interlocked with the valve opening operation of the operation piece. In response to further displacement in the valve opening direction of the valve shaft member after the sub-valve body is separated, the main valve body is separated from the valve seat portion, and the oil supplied from the liquid feeding means is removed. a refueling nozzle for refueling container, inwardly of the abutting portion in the displacement direction on the side of the valve seat to the main valve body and opposite in charge sub-valve body of the valve shaft member A projecting portion having a predetermined height is provided with respect to the contact portion, and the sub-valve element is in contact with the valve seat on the side of the main valve element facing the sub-valve element in the displacement direction of the valve shaft member. A valve shaft that accommodates the projecting portion with a gap of a predetermined area between the projecting portion and the outer peripheral portion of the projecting portion, and has a hole portion in which the valve body passage opens at the back, and interlocks with the valve opening operation of the operation piece In response to the displacement of the member in the valve opening direction, at least a part of the projecting portion is a hole until the sub-valve element is separated from the valve seat and the operation amount of the operation piece before the main valve element is opened. The flow rate of the oil liquid that is accommodated in the portion and flows between the sub-valve element and the valve seat is limited to a predetermined flow rate by the clearance area formed between the outer peripheral portion of the protrusion and the inner wall of the hole. Features.

Further, at least a part of the projecting portion is accommodated in the hole portion even after the open area generated according to the amount of separation between the contact portion and the valve seat by the operation of the operation piece becomes larger than the gap area. The gap area is maintained constant regardless of the displacement of the valve shaft member in the valve opening direction while at least a part of the protruding portion is accommodated in the hole. Features.

  According to the fueling nozzle of the present invention, when performing a small amount of additional fueling, the valve lever of the fueling nozzle is opened within a predetermined operation amount range immediately after the start of the valve opening operation. Since the amount can be kept at a minute constant flow rate regardless of the operation amount of the nozzle lever, even if the customer himself applies it to a self-service gas station that operates the oil nozzle and supplies oil, the operability, Performance such as safety is improved.

An oil supply nozzle according to an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a front sectional view of an oil supply nozzle according to an embodiment of the present invention.
FIG. 2 is an end view of the fueling nozzle shown in FIG. 1 as viewed in the direction of arrows YY.

  The oil supply nozzle 1 of the present embodiment has a nozzle body 3 in which a liquid passage 2 is formed. One end of the liquid passage 2 opens to one side 3A of the nozzle main body 3, and serves as a connection end of a hose extending from a weighing machine main body (not shown). The other end of the liquid passage 2 opens to the other side 3 </ b> B of the nozzle body 3 and serves as a connection end of the discharge pipe 4. A valve portion 5 is provided at an intermediate portion of the liquid passage 2 of the nozzle body 3.

  The valve portion 5 is composed of an annular valve seat portion 6 formed on the inner peripheral wall of the liquid passage 2 of the nozzle body 3, and a main valve 7 that is separated from and seated on the valve seat portion 6. The main valve 7 is disposed in the nozzle body 3 together with a valve shaft member 19 and the like which will be described later from an attachment opening 8 formed in the nozzle body 3. The mounting opening 8 is usually covered with a lid 10 via a seal ring 9.

  The main valve 7 is separated from and seated on the valve seat portion 6 to communicate and block the fluid passage 2, and the valve body passage 14 formed on the main valve body 11 is seated on the main valve body 11. And a sub-valve body 12 that communicates and blocks.

  The main valve body 11 is formed with a valve shaft insertion hole 13 extending in the axial direction at the axial center position, and a plurality of valve body passages 14 are formed so as to surround the valve shaft insertion hole 13. ing. The sub-valve body 12 is disposed on the upstream side of the main valve body 11 with the valve shaft portion 15 passing through the valve shaft insertion hole 13 of the main valve body 11. The sub-valve body 12 is guided by the valve shaft portion 15 through the valve shaft insertion hole 13 of the main valve body 11, and is seated and separated on a ring-shaped valve seat 16 provided in the main valve body 11. Open and close. The valve shaft portion 15 is formed with a rod insertion hole 17 extending in the axial direction.

  A coil-shaped spring member 18 is interposed between the sub-valve body 12 of the valve unit 5 configured as described above and the lid body 10 described above. The spring member 18 urges the sub-valve body 12 so that the sub-valve body 12 is seated on the valve seat 16 of the main valve body 11 and the main valve body 11 is seated on the valve seat portion 6.

Here, a detailed configuration of the valve unit 5 configured as described above will be described with reference to FIG.
FIG. 3 is an enlarged view of the valve portion of the fueling nozzle shown in FIG.
As shown in FIG. 3, on the side of the main valve body 11 on which the axial valve seat 16 is attached, a stepped hole 211 having a larger diameter than the valve shaft insertion hole 13 is formed coaxially with the valve shaft insertion hole 13. Has been. The stepped hole 211 has a larger diameter than the back hole 211b to which the opening hole 211a is connected.

  In the illustrated example, the opening hole 211a is opposite to the end face on the side on which the sub-valve body 12 comes into contact with the valve seat 16 having an inner diameter d0 that is approximately equal to the inner diameter of the inner hole 211b. The end surface on the side is in contact with the stepped portion 211c between the holes 211a and 211b, and is provided internally. On the other hand, the other end side of each of the plurality of pipe passages 212 that are arranged to surround the valve shaft insertion hole 13 and whose one end side communicates with the downstream side of the main valve body 11 is opened in the back side hole portion 211b. ing.

On the other hand, the sub-valve body 12 has a valve shaft portion 15 extending, and a columnar protrusion 221 is coaxial with the valve shaft portion 15 on the side in contact with the valve seat 16 attached to the stepped hole 211 of the main valve body 11. Is formed. The cylindrical protrusion 221 has an outer diameter d2 that is smaller than the inner diameter d0 of the valve seat 16 and larger than the outer diameter d1 of the valve shaft portion 15, and the axial height h is a sub-valve described later. The valve opening stroke of the body 12, that is, the maximum lift amount L 0 of the sub-valve body 12 with respect to the valve seat 16 of the main valve body 11 is appropriately sized. As shown in FIG. 3, when the sub-valve element 12 is seated on the valve seat 16 of the main valve element 11, the protrusion 221 is accommodated in the space in the valve seat 16 of the main valve element 11. It has been configured. When the sub-valve body 12 is separated from the valve seat 16 of the main valve body 11 and lifted from the valve seat 16 by a predetermined amount L (L <L0) smaller than the maximum lift amount L0, the protruding portion 221 It escapes from the space in 16 to the outside.

  Therefore, the valve body passage 14 is in a state in which the protruding portion 221 of the sub-valve body 12 is partly accommodated in the space in the valve seat 16, and the stroke (lift amount) L of the sub-valve body 12 with respect to the main valve body 11. Is smaller than the axial height h of the protruding portion 221, the outer circumferences of the plurality of pipe passages 212, the valve shaft portion 15 of the sub-valve body 12 inserted through the valve shaft insertion hole 13, and the protruding portion 221. It is formed by a gap between the surface and the inner peripheral surface of the back side hole 211b of the stepped hole 211 and the inner peripheral surface of the valve seat 16 provided in the opening side hole 211a.

  On the other hand, in the valve body passage 14, the stroke L of the sub-valve body 12 with respect to the main valve body 11 is in a state where the protruding portion 221 of the sub-valve body 12 is pulled out from the stepped hole 211 of the main valve body 11. In a state where the height h of the protruding portion 221 is larger than the axial height h, the plurality of pipe passages 212, the outer peripheral surface of the valve shaft portion 15 of the sub-valve body 12 inserted through the valve shaft insertion hole 13, and the stepped hole It is formed by a gap between the inner peripheral surface of the rear side hole 211b of 211 and the inner peripheral surface of the valve seat 16 provided in the opening side hole 211a.

  Returning to FIGS. 1 and 2, a valve shaft member 19 is engaged with the valve portion 5. The valve shaft member 19 includes a valve shaft sleeve 20 and a valve shaft rod 22 capable of moving forward and backward in a sleeve hole 21 formed in the valve shaft sleeve 20.

  In the axial direction of the valve shaft sleeve 20, one end side is an insertion rod portion 23 that can be inserted into the rod insertion hole 17 formed in the sub-valve body 12 of the valve portion 5, and the other end side is larger than the insertion rod portion 23. The stepped shape is a sleeve portion 24 having a diameter. The boundary step portion between the insertion rod portion 23 and the sleeve portion 24 is a shoulder portion 25 that can come into contact with the main valve body 11 of the main valve 7. In addition, a sleeve hole 21 opened at the other end of the valve shaft sleeve 20 is formed in the sleeve portion 24 so as to extend in the axial direction.

  In the present embodiment, the insertion rod portion 23 of the valve shaft sleeve 20 is inserted into the rod insertion hole 17 formed in the valve shaft portion 15 of the sub-valve body 12, and the tip side thereof is at the hole bottom portion in the rod insertion hole 17. It is the structure which has contact | abutted. Further, in the state where the main valve body 11 is seated on the valve seat portion 6 and the sub-valve body 12 is seated on the valve seat 16 of the main valve body 11, the insertion rod portion 23 and the sleeve portion 24 of the valve shaft sleeve 20 The shoulder portion 25 of the boundary step portion has a gap L in the axial direction between the main valve body 11 and the valve opening stroke of the sub-valve body 12 with respect to the main valve body 11.

  One end of the valve shaft rod 22 is fitted between the bottom surface of the sleeve hole 21 of the valve shaft sleeve 20 via a spring member 26 so as to be able to advance and retract. The spring member 26 urges the valve shaft rod 22 toward the opening side of the sleeve hole 21 so that the valve shaft sleeve 20 and the valve shaft rod 22 are separated from each other by contraction. Then, the valve shaft sleeve 20 and the valve shaft rod 22 are connected so as to be integrally movable in the axial direction by an engagement rod 27 of an automatic valve closing mechanism 61 described later. The urging force generated by the contraction of the spring member 26 is set smaller than the urging force of the spring member 18.

  The valve shaft member 19 having such a configuration is provided through a valve shaft member insertion hole 28 formed in the nozzle body 3. An insertion rod portion 23 of the valve shaft sleeve 20 in the valve shaft member 19 extends so as to be able to advance and retreat into the liquid passage 2 via a seal member 29, and the rod insertion hole 17 formed in the sub-valve body 12 of the valve portion 5. Is fitted. Further, the other end side of the valve shaft rod 22 in the valve shaft member 19 is projected to the outside of the nozzle body 3, and is in contact with and supported by a nozzle lever 30 pivotally supported by the nozzle body 3.

  The nozzle lever 30 is configured such that a base end 30B is pivotally supported on the other side 3B of the nozzle body 3 and a free end 30A extends to one side 3A of the nozzle body 3. Thereby, the nozzle lever 30 can move the free end 30 </ b> A on the lever operation portion 31 side toward or away from the nozzle body gripping portion 32 on the one side 3 </ b> A of the nozzle body 3 by rotating with respect to the nozzle body 3. ing. The other end of the valve shaft rod 22 is in contact with a portion closer to the support shaft side of the nozzle lever 30. Then, the valve shaft sleeve 20 and the valve shaft rod 22 are engaged with each other via the engaging rod 27 described above, and the valve shaft sleeve 20 and the valve shaft are operated according to the turning operation of the nozzle lever 30. The valve shaft member 19 constituted by the shaft rod 22 slides through the valve shaft member insertion hole 28, and the valve portion 5 opens and closes.

  In addition, the above-described attachment of the nozzle lever 30 to the nozzle body 3 is also performed in the direction in which the free end 30 </ b> A intersects its rotation surface with respect to the base end 30 </ b> B of the nozzle lever 30 (FIG. 1, front and back direction on the paper surface). It can be displaced by a small amount. A lever guard 33 is provided with both ends connected to the one side 3A and the other side 3B of the nozzle body 3 so as to surround the rotatable nozzle lever 30 with a rotation locus. A lever hook 35 having a plurality of step portions 34 on which the free end 30A of the nozzle lever 30 can be placed is attached to the lever guard 33 portion on the side surrounding the rotation locus of the free end 30A of the nozzle lever 30. ing. Thus, the free end 30A of the nozzle lever 30 is placed on any one of the step portions 34, so that it can be held at a desired valve opening position.

  The opening of the nozzle body 3 on the other side 3B, which is the connection end of the discharge pipe 4, guides and supports a valve seat member 36 and a check valve 37 that is separated from and seated on the valve seat member 36. The joint members 38 are coaxially arranged in order from the opening side with the valve seat member 36 at the back side.

  The valve seat member 36 is formed with a valve seat forming hole 39 extending in the axial direction while expanding from one end to the other end and forming a valve seat surface of the check valve 37. The valve seat member 36 is disposed in the opening portion on the other side 3B of the nozzle body 3 with one end face on the side where the small diameter side of the valve seat forming hole 39 is opened as the back side. An annular seal member 40 is provided on one end surface of the valve seat member 36, and the valve seat member 36 is attached to the mounting step 41 formed on the inner peripheral surface of the opening on the other side 3 </ b> B of the nozzle body 3. It is arranged in contact with the step surface. The valve seat member 36 has a stepped structure in which the outer peripheral structure is formed by connecting a large diameter portion and a small diameter portion along the axial direction. The outer diameter of the large diameter portion on the outer peripheral surface of the valve seat member 36 is formed to be smaller than the inner peripheral surface of the opening on the other side 3B of the nozzle body 3. An annular passage 42 can be formed between the inner peripheral surface of the opening of the side 3B. The valve seat member 36 has a negative pressure generating passage 43 having one end opened to the outer annular passage 42 and the other end opened to the tapered valve seat surface of the valve seat forming hole 39. A plurality are formed around the circumference of the surface. The other end side opening of each negative pressure generating passage 43 is a negative pressure generating portion 44 that generates a negative pressure by the venturi effect when the oil liquid opens the check valve 37 and flows through the narrow portion.

The joint member 38 is formed with a liquid hole 45 extending through from the one end to the other end in the axial direction. In the liquid hole 45, a columnar mounting portion 46 is disposed so as to be aligned with the liquid hole 45 and axially supported by a plurality of leg portions 47. The mounting portion 46 has bottomed mounting holes 48 and 49 on both sides in the axial direction. The mounting hole 48 on one end side of the mounting portion 46 is inserted with the valve shaft portion 50 of the check valve 37, and guides and supports the check valve 37 so that it can be detached from the valve seat member 36. A coiled spring member 51 is wound around the valve shaft 50 of the check valve 37 between the mounting portion 46 and the check valve 37 is biased in the seating direction. Further, one end side of the negative pressure compensation pipe 52 is fitted into the attachment hole 49 on the other end side.

  The outer periphery of the end portion of the joint member 38 on the check valve 37 side is formed to have a smaller diameter than the inner peripheral surface of the opening portion on the other side 3B of the nozzle body 3 in the same manner as the large diameter portion of the valve seat member 36 described above. The circumference is formed to be substantially the same diameter as the outer circumference of the small diameter portion of the valve seat member 36 described above. A passage 53 is formed in the leg portion 47 of the joint member 38 to communicate between the outer peripheral portion on the check valve 37 side and the mounting hole 49. The joint member 38 abuts the flange formed in the intermediate portion in the axial direction against the opening end surface of the other side 3B of the nozzle body 3, and the outer peripheral portion between the flange and the aforementioned small diameter portion is the nozzle body. 3 is press-fitted into the opening on the other side 3B and is attached to the nozzle body 3 to position and fix the valve seat member 36. In this state, one end side of the negative pressure compensating pipe 52 is configured to communicate with the annular passage 42 via the passage 53 and the outer peripheral portion of the joint member 38 on the check valve 37 side.

  The negative pressure compensation pipe 52 extends in the discharge pipe 4, and the other end side opens to the outer peripheral surface on the front end side of the discharge pipe 4 to form a liquid level detection hole 54. The annular passage 42 is also communicated with a negative pressure chamber 64 (see FIG. 2) of an automatic valve closing mechanism 61 described later via a passage 55 formed in the nozzle body 3. Thereby, the negative pressure generating part 44, the liquid level detection hole 54, and the negative pressure chamber 64 of the automatic valve closing mechanism 61 described later are configured to communicate with each other via the annular passage 44. Further, a retaining coil 56 for preventing the oil supply nozzle 1 from falling off the oil supply port 1 is wound around the outer periphery of the discharge pipe 4.

Next, the configuration of the automatic valve closing mechanism 61 and the leakage prevention mechanism 62 provided in the nozzle body 3 of the fuel supply nozzle 1 shown in FIGS. 1 and 2 will be described with reference to FIG.
FIG. 4 is an explanatory diagram of assembly of the automatic valve closing mechanism of the fueling nozzle shown in FIGS. 1 and 2.
In FIG. 4, the same parts as those described in FIGS. 1 to 3 are denoted by the same reference numerals.

  In FIG. 2, a valve closing mechanism accommodation hole 60 is formed through the nozzle body 3 so as to cross the valve shaft member insertion hole 28. The valve closing mechanism accommodation hole 60 has an automatic valve closing mechanism 61 for stopping the discharge of the oil from the discharge pipe 4 when a liquid level is detected regardless of the operation state of the nozzle lever 30, and a fueling operation. A leakage prevention mechanism 62 for preventing leakage of oil from the discharge pipe 4 due to an erroneous operation of the nozzle lever 30 at the start is accommodated.

  The automatic valve closing mechanism 61 includes a negative pressure chamber 64 and an atmospheric pressure chamber 65 defined by a diaphragm member 63. In the illustrated example, the diaphragm member 63 is disposed on a flexible diaphragm film 67 having a mounting hole 66 formed in the center of the film, and on the film surface of the diaphragm film 67 on the negative pressure chamber 64 side, and fitted in the center. A spring receiving member 69 in which a joint hole 68 is formed, and a disk-shaped coupling member 72 in which fitting portions 70 and 71 protrude from the both sides in the axial direction, respectively. The diaphragm member 63 is inserted into the fitting hole 68 of the spring receiving member 69 by inserting the fitting portion 70 formed on one side of the coupling member 72 in the axial direction into the mounting hole 66 of the diaphragm film 67. The diaphragm film 67 is integrally sandwiched between the coupling member 72 and the spring receiving member 69.

  The negative pressure chamber 64 is attached to the nozzle body 3 so as to sandwich the peripheral edge portion of the diaphragm film 67 of the diaphragm member 63 disposed so as to cover one side opening of the valve closing mechanism accommodation hole 60 with the nozzle body 3. Further, the inner space of the lid member 73 is formed. Although not shown in the drawing, the negative pressure chamber 64 communicates with the other end of a passage 55 provided at one end described in FIG. In the negative pressure chamber 64, a spring member 74 for restoring the diaphragm member 63 that has been bent due to the negative pressure is provided between the spring receiving member 69 and the bottom of the lid member 73. ing. Thereby, in the atmospheric pressure state in which the negative pressure chamber 64 is not at a negative pressure, the diaphragm member 63 closes the spring receiving member 69 and the coupling member 72 by the biasing force of the spring member 74 as shown in FIG. The valve mechanism accommodation hole 60 is located on the back side, that is, on the leakage prevention mechanism 62 side.

  In addition, a U-shaped moving member 75 as shown in FIG. 4 is tightly attached to the fitting portion 71 formed on the other side in the axial direction of the coupling member 72 in the diaphragm member 63 so as to automatically close the valve. A U-shaped engaging rod guide member 76 constituting the mechanism 61 is integrally attached.

  As shown in FIG. 4, the moving member 75 has a U-shape having a pair of side plate portions 75R and 75L and a connecting plate portion 75C that connects the pair of side plate portions 75R and 75L. The connecting plate portion 75C is formed with an insertion hole 77 through which the fitting portion 71 of the coupling member 72 is inserted, and the pair of side plate portions 75R and 75L are notched portions 78 for preventing contact with other portions. Is formed. Further, the engagement rod guide member 76 has a U-shape having a pair of side plate portions 76R and 76L and a connecting plate portion 76C for connecting the pair of side plate portions 76R and 76L. The connecting plate portion 76C is formed with a convex portion 76c that can be fitted into the insertion hole 77 of the moving member 75, and the convex portion 76c is formed with an insertion hole 79 through which the fitting portion 71 of the coupling member 72 is inserted. ing. Each of the pair of side plate portions 76R and 76L is formed with a guide hole 80 with which the end of the engagement rod 27 is engaged. The guide hole 80 has a long hole shape and restricts the movement of the engagement rod 27 in the axial direction of the insertion hole 79, while the direction orthogonal to the axial direction of the insertion hole 79, that is, the valve shaft member 19. The engagement rod 27 is movable along the axial direction by a predetermined distance, that is, by the valve opening stroke of the main valve body 11 and the sub-valve body 12 constituting the valve portion 5.

  In the illustrated example, the engagement rod guide member 76 has the projection 76 c inserted into the insertion hole 77 of the moving member 75 in a state where the engagement rod 27 is engaged with the pair of guide holes 80 (FIG. 4, step S 01). They are fitted and installed inside the moving member 75 (step S02). In addition, the engagement rod guide member 76 has the insertion hole 79 fitted to the fitting portion 71 of the coupling member 72, and the moving member 75 is closely attached to the coupling member 72, so that the diaphragm member It is attached to 63 integrally (step S03).

  The integrated diaphragm member 63, moving member 75, and engagement rod guide member 76, as shown in FIG. 4, engage the engagement rod 27 of the engagement rod guide member 76 with the valve shaft member 19. The lid member 73 is attached to the nozzle body 3 by screwing so that the peripheral edge portion of the diaphragm film 67 of the diaphragm member 63 is sandwiched between the diaphragm body 63 and the nozzle body 3.

  On the other hand, the valve shaft sleeve 20 and the valve shaft rod 22 constituting the valve shaft member 19 are formed with an engagement hole 81 and an engagement groove 82 that can be engaged with the engagement rod 27 in the middle part in the length direction. ing. The axial hole width of the engagement hole 81 formed in the valve shaft sleeve 20 is substantially equal to the total diameter of the engagement rods 27 and 27. On the other hand, the axial groove width of the engaging groove 82 formed in the valve shaft rod 22 is the valve in the state where both the main valve body 11 and the sub-valve body 12 of the main valve 7 shown in FIG. The distance between the shoulder portion 25 of the shaft sleeve 20 and the main valve body 11 of the main valve 7, that is, the valve opening stroke of the sub-valve body 12 with respect to the main valve body 11, from the hole width in the axial direction of the engagement hole 81. Is also formed large. When the automatic valve closing mechanism 61 and the leakage prevention mechanism 62 are not operating, the engagement held by the guide hole 80 of the engagement rod guide member 76 by the urging force of the spring member 74 as shown in FIG. The combined rods 27 are engaged with both the engagement hole 81 and the engagement groove 82.

  The valve shaft sleeve 20 is formed with a guide hole 83 extending along the axial direction from the opening side of the sleeve hole 21 in the peripheral wall of the sleeve portion 24. A pin 84 is erected on the outer peripheral surface of the valve shaft rod 22 so as to engage with the guide hole 83. As a result, as shown in step S04 of FIG. 4, the valve shaft rod 22 is assembled with the spring member 26 between the bottom surface of the sleeve hole 21 of the valve shaft sleeve 20 so as to be able to advance and retract. At this time, by engaging the pin 84 of the valve shaft rod 22 with the guide hole 83 of the valve shaft sleeve 20, the opening direction of the engagement groove 82 of the valve shaft rod 22 and the engagement hole 81 of the valve shaft sleeve 20 is determined. Can be easily matched. In addition, when the valve shaft sleeve 20 is positioned in the valve shaft member insertion hole 28 from the mounting opening 8 shown in FIG. The guide hole 83 is matched with the pin mounting hole 85 formed through the nozzle body 3 with respect to the valve shaft member insertion hole 28, and pin mounting is performed from the opening of the pin mounting hole 85 on the opposite side to the valve shaft member insertion hole 28. A pin 86 is driven into the hole 85 to project into the guide hole 83. As a result, the engagement groove 82 of the valve shaft rod 22 and the engagement hole 81 of the valve shaft sleeve 20 are arranged opposite to the engagement rods 27, 27 held in the guide hole 80 of the engagement rod guide member 76. Then, the engagement rods 27 and 27 are positioned so as to be engageable with both the engagement hole 81 and the engagement groove 82.

  The cross-sectional shape of the contact portion of the nozzle lever 30 pivotally supported by the nozzle body 3 with the valve shaft rod 22, that is, the other end side of the valve shaft member 19 is in the axial direction of the valve shaft member 19. It has a shape having an inclined surface 87 inclined with respect to an orthogonal plane. The inclined surface 87 is inclined corresponding to the swing direction p1-p2 of the free end 30A of the nozzle lever 30, and from the swing direction p2 side that separates the free end 30A of the nozzle lever 30 from the lever hook 35. The free end 30 </ b> A of the nozzle lever 30 is inclined downward toward the swing direction p <b> 1 that brings the free end 30 </ b> A close to the lever hook 35. The inclination angle ag is determined so that the contact position N1 of the valve shaft rod 22 with respect to the nozzle lever 30 when the free end 30A of the nozzle lever 30 is placed on the step portion 34 of the lever hook 35 is at an oil supply port of a vehicle or the like. When the oil supply nozzle 1 hooked by the retaining coil 56 falls from the oil supply port, the contact is displaced in the swinging direction p2 side based on the fall acceleration or the impact force based on the collision with the site of the gas station. The angle is such that it moves to the position N0.

  On the other hand, the leakage prevention mechanism 62 is configured as shown in FIG. The leakage prevention mechanism 62 has the same configuration as that of the fuel nozzle previously filed by the applicant of the present application as Japanese Patent Application No. 2004-107281, and therefore, the same components are simply denoted by the same reference numerals. .

  The leakage prevention mechanism 62 is provided in the valve closing mechanism accommodation hole 60 formed in the nozzle body 3 on the opposite side to the side where the automatic valve closing mechanism 61 is provided with the valve shaft member 19 interposed therebetween. The leakage prevention mechanism 62 includes a hydraulic chamber 92 and an atmospheric pressure chamber 93 defined by the diaphragm film 91.

  As shown in FIG. 2, the hydraulic chamber 92 and the atmospheric pressure chamber 93 are configured by a unit lid 95 that closes the other opening of the valve closing mechanism accommodation hole 60 and includes a diaphragm housing hole 94 with a bottom. The On the inner peripheral surface of the diaphragm housing hole 94 of the unit lid 95, a step portion 96 is formed for supporting the outer peripheral edge portion of the diaphragm film 91 so as to be able to bend. The diaphragm film 91 is supported and fixed to the step portion 96 by a holding member 98 screwed to the opening side of the diaphragm housing hole 94 through a cylindrical spacer 97. The hydraulic chamber 92 is configured by a bottom side portion of the diaphragm accommodation hole 94 defined by the diaphragm film 91. The fluid pressure chamber 92 is a fluid passage on the upstream side of the valve portion 5 of the nozzle body 3 through a passage 99 extending in the wall portion of the unit lid 95 and a passage 100 formed in the casing of the nozzle body 3. 2 is communicated. As a result, the hydraulic fluid upstream of the valve section 5 is introduced into the hydraulic pressure chamber 92, and the hydraulic pressure upstream of the valve section 5 acts on the diaphragm membrane 91.

  On the other hand, in the atmospheric pressure chamber 93 at the opening portion of the diaphragm housing hole 94 defined by the diaphragm film 91, the piston member 101 for pushing and displacing the diaphragm film 91 is guided by the inner peripheral surface of the spacer 97 and slides. It is provided freely. The piston member 101 has a rod mounting hole 102 formed in the center. The rod 103 is attached to the rod attachment hole 102 so that the rod 103 can be displaced integrally with the piston member 101 by restricting relative movement of both ends of the rod 103 by retaining rings 104. The piston member 101 is restricted from moving toward the opening side of the diaphragm housing hole 94 by a holding member 98 screwed into the opening side of the diaphragm housing hole 94. One end side of the rod 103 is led out of the diaphragm housing hole 94 through a through hole 105 formed in the holding member 98. A coiled spring member 106 is interposed between the piston member 101 and the holding member 98. The spring member 106 has a configuration in which the end face of the piston member 101 is brought into close contact with the diaphragm film 91, and in the contracted state, the diaphragm film 91 and the piston member 101 are urged toward the bottom side of the diaphragm housing hole 94. ing.

  The urging force that urges the diaphragm film 91 and the piston member 101 toward the bottom side of the diaphragm housing hole 94 by the spring member 106 is applied to the guide hole 80 of the engagement rod guide member 76 by the spring member 74 described above. It is set to be larger than the urging force that causes the provided engagement rod 27 to enter the engagement hole 81 of the valve shaft sleeve 20 and the engagement groove 82 of the valve shaft rod 22.

  Further, a moving member operating mechanism 107 is attached to the closing surface 95d of the unit lid 95 that faces the other opening surface of the valve closing mechanism accommodation hole 60. The moving member operating mechanism 107 includes a support member 108 and a link member 109 that is rotatably supported by the support member 108.

  The support member 108 has a U-shape having a pair of side plate portions and a connecting plate portion that connects the pair of side plate portions. The support member 108 is screwed to the closing surface 95 d of the unit lid body 95 so as to be integrally fixed to the unit lid body 95. The support member 108 is disposed in the valve closing mechanism accommodation hole 60 in a state in which the unit lid 95 to which the support member 108 is fixed is attached to the nozzle body 3.

  The link member 109 has a U-shape having a pair of side plate portions and a connecting plate portion for connecting the pair of side plate portions. The link member 109 has a side plate portion provided between the side plate portions of the support member 108, and is pivotally supported by the support member 108 so that its rotation range is restricted.

  In addition, the engagement rod guides engaged with the engagement rods 27 and 27 shown in FIG. 4 are engaged with the side plate portion of the link member 109 that is pivotally supported by the support member 108. A connection shaft loosely fitted in an operating shaft that contacts the front end surfaces 75t and 75t of the side plate portions 75R and 75L of the U-shaped moving member 75 integral with the plate 76, and a shaft insertion hole formed on one end side of the rod 103. The shaft is rotatably attached to the link member 109 such that the shaft is opposed to the support member 108 with respect to the support member 108.

  Thereby, the axial displacement of the piston member 101, that is, the rod 103 is converted into a rotational displacement (swinging displacement) of the link member 109 with respect to the support member 108, and the displacement / proximity displacement of the operating shaft toward the valve shaft member 19 side. It is configured to be converted.

  The moving member actuating mechanism 107 is attached to the unit lid 95 in advance, and the valve closing mechanism accommodation hole on the side opposite to the side where the automatic valve closing mechanism 61 of the nozzle body 3 is provided as a leakage prevention mechanism assembly. 60 is attached. At that time, the link member 109 of the moving member operating mechanism 107 is rotated as described below in relation to the displacement of the diaphragm film 91 due to the differential pressure generated between the hydraulic chamber 92 and the atmospheric chamber 93 described above. It is configured to be displaced.

First, when the hydraulic chamber 92 is in the expanded state, the link member 109 is configured such that the one end side of the rod 103 attached so as to be displaceable integrally with the piston member 101 is interlocked with the displacement of the piston member 101. in response to being displaced so as to approach the 19 side, the link member 109, by sea urchin of the operating shaft is separated from the valve shaft member 19 side, since the rotational displacement relative to the support member 108, the actuating shaft Cannot push the front end surfaces 75t, 75t of the side plate portions 75R, 75L of the moving member 75 against the urging force of the spring member 74.

  Therefore, when the hydraulic chamber 92 is in the expanded state, the operating shaft fixed to the link member 109 so as to be rotatable is the guide hole 80 of the engagement rod guide plate 76 provided integrally with the moving member 75. , 80 is allowed to engage with both the engagement hole 81 of the valve shaft sleeve 20 and the engagement groove 82 of the valve shaft rod 22.

  On the other hand, when the hydraulic chamber 92 is in a contracted state, the link member 109 has one end side of the rod 103 attached to the piston member 101 so as to be displaceable integrally with the displacement of the piston member 101. In response to being displaced away from the valve shaft member 19 side, the link member 109 is rotationally displaced with respect to the support member 108 so as to bring the operating shaft closer to the valve shaft member 19 side. The shafts 117 and 117 push the front end surfaces 75t and 75t of the side plate portions 75R and 75L of the moving member 75 against the urging force of the spring member 74.

  Therefore, when the hydraulic chamber 92 is in the contracted state, the operating shaft fixed to the link member 109 so as to be rotatable is the guide hole 80 of the engagement rod guide plate 76 provided integrally with the moving member 75. , 80 is only allowed to engage with the engagement hole 81 of the valve shaft sleeve 20 and the engagement of the valve shaft rod 22 with the engagement groove 82 is blocked. ing.

  Next, operation | movement of the oil supply nozzle 1 of this Embodiment comprised as mentioned above is demonstrated in relation to the oil supply operation | work.

  First, in the fueling nozzle 1 in which the operation state of the nozzle lever 30 is in the valve closing operation state as shown in FIG. 1, the contact between the valve shaft rod 22 that constitutes the valve shaft member 19 together with the valve shaft sleeve 20 and the nozzle lever 30. The contact portion N is in a position state (the lowermost position state in FIG. 1) that is farthest outward from the nozzle body 3 from the opening of the valve shaft member insertion hole 28 with respect to the axial direction of the valve shaft member 19. . Similarly, the valve shaft sleeve 20 of the valve shaft member 19 is also the most in the axial direction of the valve shaft member 19 due to the biasing force of the spring member 18 acting via the valve shaft portion 15 of the sub-valve body 12 of the valve portion 5. The valve shaft member insertion hole 28 is located near the opening on the nozzle lever 30 side (the lowest position in FIG. 1).

  In this state, the sub-valve body 12 is seated on the valve seat 16 of the main valve body 11 by the biasing force of the spring member 18 and the communication of the valve body passage 14 is cut off. The urging force of the spring member 18 acting through the valve member 5 is seated on the valve seat portion 6 and the valve portion 5 is closed. In the valve closing operation state of the nozzle lever 30, the positional relationship between the engagement groove 82 of the valve shaft rod 22 constituting the valve shaft member 19 and the engagement hole 81 of the valve shaft sleeve 20 with respect to the axial direction of the valve shaft member 19 is Both are positioned on the nozzle lever 30 side end 80a (see FIG. 4) side of the guide hole 80 formed in the engagement rod guide plate 76, and the engagement groove 82 of the valve shaft rod 22 and the valve shaft The engagement hole 81 of the sleeve 20 is superposed.

  On the other hand, in the storage state in which the refueling nozzle 1 is placed on the nozzle hook (corresponding to the nozzle storage location) of the measuring machine, the nozzle switch (nozzle removal detection means) attached to the nozzle hook is in the open state. (Storage detection state). In addition, in response to a detection signal (nozzle storage signal) from the nozzle switch, liquid supply means such as a pump provided in a measuring machine that supplies oil to the oil supply nozzle 1 connected to the tip of the oil supply hose is also driven. It is in a stopped state.

[Fueling nozzle opening operation when the fueling nozzle is retracted]
In the state where the above-described refueling nozzle 1 is in the valve closing operation state and is stored in the nozzle storage place of the measuring machine, the negative pressure chamber 64 of the automatic valve closing mechanism 61 is negative because the oil supply nozzle 1 is in the valve closing operation state. The pressure generating unit 44 cannot generate a negative pressure due to the venturi effect, and the liquid level detection hole 54 at the distal end side of the discharge pipe 4 is not blocked by the oil liquid and is opened to the atmosphere. It has become. As a result, no differential pressure is generated between the negative pressure chamber 64 and the atmospheric pressure chamber 65 of the automatic valve closing mechanism 61 so as to displace the diaphragm member 63 against the urging force of the spring member 74. The U-shaped moving member 75 and the engagement rod guide member 76 which are integrally attached to the engagement member are provided in the guide hole 80 of the engagement rod guide member 76 by the biasing force of the spring member 74. The rod 27 tries to enter the engagement hole 81 of the valve shaft sleeve 20 and the engagement groove 82 of the valve shaft rod 22 which are in the above-described superposed state.

  However, in the fueling nozzle 1 of the present embodiment, the leakage prevention mechanism 62 prevents the engagement rod 27 from entering the engagement groove 82 of the valve shaft rod 22.

  That is, the leakage prevention mechanism 62 stops driving the liquid feeding means such as a pump provided in the measuring machine when the above-described oil supply nozzle 1 is in the valve closing operation state and is stored in the nozzle storage place of the measuring machine. Therefore, the fluid pressure chamber 92 is higher than the fluid pressure in the fluid passage 2 upstream of the valve portion 5 when the fluid feeding means is driven, for example, the pressure when the fluid feeding means is driven. Low pressure is applied. Therefore, the hydraulic pressure chamber 92 and the atmospheric pressure chamber 93 defined by the diaphragm film 91 are contracted and the atmospheric pressure chamber 93 is expanded by the biasing force of the spring member 106.

  That is, the rod 103 is in a moving position state separated from the hydraulic chamber 92 side, that is, the valve shaft member 19 side. As a result, the link member 109 connected to the piston member 101 has its operating shaft engaged with the engagement rods 27 and 27 only in the engagement hole 81 of the valve shaft sleeve 20 in the valve shaft member 19. The moving member 75 integral with the engaging rod guide plate 76 has moved to the valve shaft member 19 side until it comes into contact with the front end surfaces 75t, 75t of the side plate portions 75R, 75L.

Therefore, the automatic valve closing mechanism 61 causes the engagement rods 27 and 27 to enter the engagement groove 82 of the valve shaft rod 22 of the valve shaft member 19 by the biasing force of the spring member 74, and the engagement of the diaphragm member 63 and the engagement member 27. Even if the rod guide plate 76 is pushed, the operating shaft provided in the link member 109 as the moving member operating mechanism 107 of the leakage preventing mechanism 62 is already in contact with the moving member 75, and the spring member 106 of the leakage preventing mechanism 62 Since the urging force is set to be larger than the urging force of the spring member 74 of the automatic valve closing mechanism 61, the operating shaft cannot be moved away from the valve shaft member 19, and the engagement rods 27, 27 Cannot enter the engaging groove 82 of the valve shaft rod 22.

  As a result, when the oil supply nozzle 1 is in the valve closing operation state and stored in the nozzle storage place of the measuring machine, the engagement rod 27 is only the valve shaft sleeve 20 of the valve shaft member 19 as shown by the broken line in FIG. Therefore, the integral connection between the valve shaft sleeve 20 and the valve shaft rod 22 of the valve shaft member 19 is released.

  Therefore, even if the nozzle lever 30 of the fuel supply nozzle 1 is opened while the fuel supply nozzle 1 is stored in the nozzle storage location of the metering machine, the valve shaft rod 22 of the valve shaft member 19 causes the spring member 26 to move. Since it only enters the sleeve hole 21 of the valve shaft sleeve 20 while contracting, the valve portion 5 does not open.

    Therefore, according to the fueling nozzle 1 of the present embodiment, the customer as an unfamiliar fueling operator pulls the nozzle lever 30 of the fueling nozzle 1 and opens the valve at the self-service fueling station. Even if it is removed from the nozzle storage location, the valve portion 5 is not opened by the valve opening operation. Therefore, simultaneously with the removal of the fuel supply nozzle 1 from the nozzle storage location, the supply means such as a pump is activated to supply the fuel supply nozzle 1. The oil liquid can be prevented from leaking from the discharge pipe 4.

[Fueling nozzle opening operation with the oiling nozzle removed]
Next, the operation of the fueling nozzle 1 when the valve opening operation is performed by pulling the nozzle lever 30 of the fueling nozzle 1 after removing the fueling nozzle 1 from the nozzle storage location will be described.

  In this case, with the oil supply nozzle 1 removed from the nozzle hook of the weighing machine, the nozzle switch attached to the nozzle hook is in a closed state (removal detection state), and a detection signal from this nozzle switch (nozzle removal) In response to the signal), liquid feeding means such as a pump provided in the measuring machine is activated to supply the oil liquid to the oil supply nozzle 1. Then, the force generated in the diaphragm membrane 91 itself due to the fluid pressure in the fluid passage 2 upstream of the valve portion 5 in the oil supply nozzle 1 is increased by the oil supplied from the fluid feeding means, and rises to the relief pressure of the fluid feeding means. To do.

  Then, the leakage prevention mechanism 62 causes the engagement rod 27 to engage with the engagement groove 82 of the valve shaft rod 22 due to the increase in the fluid pressure in the fluid passage 2 upstream of the valve portion 5 in the fuel supply nozzle 1 based on the activation of the fluid feeding means. Will be allowed to enter.

  That is, in the leakage prevention mechanism 62, the liquid supply means such as a pump provided in the measuring machine is already activated in a state in which the oil supply nozzle 1 is in the valve closing operation state and is removed from the nozzle storage location of the measuring machine. Therefore, the hydraulic chamber 92 defined by the diaphragm film 91 is in an expanded state, and the atmospheric pressure chamber 93 is in a contracted state.

  In this state, the rod 103 is in a moving position close to the valve shaft member 19 side. Further, the link member 109 connected to the piston member 101 is in a rotating state in which its operating shaft is positioned on the side away from the valve shaft member 19 side.

  Thus, the operating shaft is integrated with the diaphragm member 63 together with the moving member 75 regardless of contact / non-contact with the tip surfaces 75t, 75t (see FIG. 4) of the pair of side plate portions 75R, 75L of the moving member 75. The engagement rods 27, 27 of the engagement rod guide member 76, which are attached to each other, are both the engagement hole 81 of the valve shaft sleeve 20 and the engagement groove 82 of the valve shaft rod 22 in the above-described superposed state. It has been displaced to a position allowing it to engage.

  Therefore, the diaphragm member 63 and the engagement rod guide plate 76 of the automatic valve closing mechanism 61 can be displaced toward the valve shaft member 19 by the biasing force of the spring member 74, and the guide hole of the engagement rod guide plate 76 The engagement rod 27 provided on the valve shaft 80 can be engaged with both the engagement hole 81 of the valve shaft sleeve 20 and the engagement groove 82 of the valve shaft rod 22 in a superposed state. .

  As a result, when the oil supply nozzle 1 is in the valve closing operation state and removed from the nozzle storage location of the metering machine, the engagement rod 27 is connected to the valve shaft sleeve 20 and the valve shaft member 19 as shown by the solid line in FIG. Both the valve shaft rods 22 are engaged, and the valve shaft sleeve 20 of the valve shaft member 19 and the valve shaft rod 22 are integrally connected.

  Therefore, if the nozzle lever 30 of the oil supply nozzle 1 is opened while the oil supply nozzle 1 is removed from the nozzle storage location of the measuring machine and the liquid feeding means such as a pump is already activated, the valve shaft member 19 The valve shaft sleeve 20 and the valve shaft rod 22 are integrally displaced to the valve portion 5 side. Due to this displacement, the valve unit 5 is opened in the order of the sub-valve body 12 and the main valve body 11, and the check valve 37 is opened from the discharge pipe 4 of the fueling nozzle 1 to respond to the valve opening operation amount of the nozzle lever 30. In addition, an oil liquid having a flow rate per unit time is discharged.

  Therefore, according to the fueling nozzle 1 of the present embodiment, at a self-service fueling station, a customer as a fueling operator removes the fueling nozzle 1 from the nozzle storage place without opening the nozzle lever 30. When the nozzle lever 30 is opened after the discharge pipe 4 of the oil supply nozzle 1 is inserted into the oil supply port of the oil supply tank, actual oil supply to the oil supply tank can be started as before.

[Full tank refueling]
After the actual refueling is started, the refueling operator places the free end 30A of the nozzle lever 30 on the step 34 corresponding to the desired valve opening operation amount of the lever hook 35, and opens the nozzle lever 30. If the operation state is maintained, even when the valve opening operation of the nozzle lever 30 is not performed, the full tank fueling or the preset fueling corresponding to the preset value preset in the fueling operation can be completed.

  In the case of full tank refueling, the liquid level detection hole 54 at the front end side of the discharge pipe 4 is closed with oil liquid as in the case of the conventional oil supply nozzle, so that the oil supply nozzle regardless of the operation state of the nozzle lever 30. The automatic discharge of the oil liquid from 1 is stopped.

  That is, when the liquid level detection hole 54 at the distal end side of the discharge pipe 4 is blocked by the oil, the negative pressure generated by the negative pressure generating unit 44 cannot be compensated, and the negative pressure chamber 64 of the automatic valve closing mechanism 61 is not compensated. The negative pressure chamber 64 and the atmospheric pressure chamber 65 defined by the diaphragm member 63 due to the differential pressure generated between the negative pressure chamber 64 and the atmospheric pressure chamber 65 are resisted against the biasing force of the spring member 74. The atmospheric pressure chamber 93 is in an expanded state. As a result, the engagement rod guide member 76 that is integrally attached to the diaphragm member 63 together with the moving member 75 is displaced so as to be separated from the valve shaft member 19 in conjunction with the displacement of the diaphragm member 63. As a result, the engagement rods 27, 27 entering and engaging both the engagement hole 81 of the valve shaft sleeve 20 and the engagement groove 82 of the valve shaft rod 22 are engaged with the engagement groove 82 of the valve shaft rod 22. The valve shaft sleeve 20 is engaged with only the engagement hole 81 of the valve shaft sleeve 20, and the valve shaft sleeve 20 is disengaged from the valve shaft rod 22.

  As a result, the valve shaft rod 22 remains as it is, and only the valve shaft sleeve 20 is supplied from the biasing force of the spring member 18 and the liquid feeding means acting via the valve shaft portion 15 of the sub-valve body 12 of the valve portion 5. The hydraulic pressure moves against the biasing force of the spring member 26 so that the valve shaft member insertion hole 28 moves in the axial direction closest to the nozzle lever 30 side. The valve 7 is closed and the supply of the oil liquid from the oil supply nozzle 1 to the oil supply tank is stopped.

[Additional lubrication]
In addition, according to the oil supply nozzle 1 of the present embodiment, when it is necessary to perform a small amount of additional oil supply after this full tank oil supply, the liquid supply means is still in the drive state, and the hydraulic pressure of the leakage prevention mechanism 62 Since a fluid pressure higher than a predetermined pressure is applied to the chamber 92, once the nozzle lever 30 is returned to the valve closing operation position, the oil supply nozzle 1 can be operated without opening the nozzle lever 30. It becomes the same state as the state removed from the nozzle storage location, and additional refueling can be performed by simply opening the nozzle lever 30 again.

  Next, taking the case of performing a small amount of additional fueling as an example, the manner of operation of the valve portion 5 by the valve opening operation of the nozzle lever 30 in the fueling nozzle 1 of the present embodiment will be described with reference to FIGS. This will be described in detail with reference to FIG.

  FIG. 3 shows a state diagram of the valve portion when the nozzle lever is in the valve closing operation position as shown in FIG.

  FIG. 5 shows a state diagram of the valve section when the sub-valve element starts to open by the valve opening operation of the nozzle lever from the valve section closed state shown in FIG.

  FIG. 6 shows a state diagram of the valve portion when the sub-valve element is fully opened by the valve opening operation of the nozzle lever.

  FIG. 7 shows a state diagram of the valve portion when the main valve body is opened next after the sub-valve body is fully opened by the valve opening operation of the nozzle lever.

  As described above, also in the case of this additional oil supply, the oil supply nozzle 1 is removed from the nozzle storage location of the measuring machine, and the liquid feeding means such as a pump is still driven. When the valve 30 is opened, the valve shaft sleeve 20 and the valve shaft rod 22 of the valve shaft member 19 are integrally displaced in the axial direction toward the valve portion 5 according to the lever operation amount. Due to this axial displacement, the valve section 5 opens in the order of the sub-valve body 12 and the main valve body 11, and the check valve 37 is opened from the discharge pipe 4 of the fueling nozzle 1 to open the valve lever 30. Accordingly, an oil liquid having a flow rate per unit time corresponding to the pressure is discharged.

  At that time, the shoulder 25 of the sub-valve body 12 is moved from the closed state of the valve portion 5 shown in FIG. 3 by the movement of the valve shaft sleeve 20 according to the lever operation amount of the nozzle lever 30. The valve opening operation is performed in the order shown in FIGS.

  At the beginning of the valve opening operation of the nozzle lever 30, the sub-valve body 12 is first seated on the valve seat portion 6 as shown in FIG. 5 by the movement of the valve shaft sleeve 20 according to the lever operation amount of the nozzle lever 30. The main valve body 11 is separated from the valve seat 16. When the sub-valve element 12 is initially separated from the valve seat 16 of the main valve element 11, the columnar protrusion 221 of the sub-valve element 12 has a part of the height h portion in the axial direction thereof. It exists in the state located in the space in the valve seat 16 in the stepped hole 211 in which the valve seat 16 of the valve body 11 was provided.

In this state, for simplification of explanation, the flow resistance is ignored, and the separation distance from the valve seat 16 of the main valve element 11 of the sub-valve element 12, that is, the stroke of the sub-valve element 12 with respect to the main valve element 11 ( Assuming that the lift amount is L, and the sub-valve body 12 is in contact with the inner peripheral side edge (diameter d0) of the valve seat 16 when the valve portion 5 is closed, the sub-valve body 12 is the main valve body. The liquid flow path opening area Ss opened by separating from the 11 valve seats 16 is:
Ss = 2π × d0 × L
Accordingly, the liquid flow path is opened when the sub-valve body 12 is separated from the valve seat 16 of the main valve body 11 in accordance with an increase in the stroke (lift amount) L of the sub-valve body 12 with respect to the main valve body 11 The area Ss increases.

  On the other hand, the columnar protrusion 221 of the sub-valve body 12 has a part of the height h portion in the axial direction when the valve seat 16 of the main valve body 11 is located in the space in the valve seat 16. Regardless of the increase in the liquid flow path opening area Ss due to the increase in the stroke (lift amount) L of the valve body 12 with respect to the main valve body 11, the liquid flow path area through which the oil liquid flowing downstream from the sub valve body 12 passes is: The clearance passage area Sf between the inner peripheral portion of the valve seat 16 and the outer peripheral portion of the columnar protrusion 221 of the sub-valve body 12 is regulated.

In this case, the clearance passage area Sf is defined as d2 (<d0) when the diameter of the cylindrical protrusion 221 is d2.
Sf = π × ((d0) / 2) ² −π × ((d2) / 2) ²
become.

  Accordingly, when the gap passage area Sf is larger than the liquid flow path opening area Ss at the beginning of the opening of the sub-valve body 12, the oil liquid flowing to the downstream side of the main valve body 11 via the opened sub-valve body 12 is used. The amount increases in accordance with the increase in the liquid flow path opening area Ss corresponding to the increase in the stroke (lift amount) L of the sub-valve element 12 with respect to the main valve element 11, but thereafter, the main valve element 11 of the sub-valve element 12. When the liquid flow path opening area Ss becomes greater than or equal to the clearance passage area Sf due to an increase in stroke (lift amount) L (where L <L0, L0: maximum lift amount of the sub-valve body 12), the clearance passage area Sf is reduced. Thus, the amount of the oil flowing to the downstream side of the main valve body 11 through the opened sub-valve body 12 is a liquid flow due to an increase in the stroke (lift amount) L of the sub-valve body 12 with respect to the main valve body 11. Regardless of the increase in the road opening area Ss, the protruding portion of the auxiliary valve body 12 21 is regulated to a predetermined flow rate F based on the gap passage area Sf during the stroke in which the valve seat 16 of the main valve body 11 is located in the space in the valve seat 16 in the stepped hole 211 provided therein. Become.

  Thereafter, the protrusion (221) of the sub-valve body 12 is provided in the stepped hole 211 of the main valve body 11 by increasing the stroke (lift amount) L of the sub-valve body 12 with respect to the main valve body 11 (L <L0). After exiting from the space in the valve seat 16, the outer edge portion of the protrusion 221 of the sub-valve body 12 and the inner peripheral edge portion (diameter d0) of the valve seat 16 from the predetermined flow rate F are The amount of oil that flows downstream of the main valve body 11 through the opened sub-valve body 12 in response to the increase in the liquid flow path opening area Ss ′ accompanying the increase in the stroke (lift amount) L during Will increase.

  Further, when the nozzle lever 30 is further operated to further move the valve shaft sleeve 20 to bring the shoulder 25 into contact with the main valve body 11 as shown in FIG. After that, as the valve shaft sleeve 20 is further moved by the operation of the nozzle lever 30, the main valve body 11 is separated from the valve seat portion 6 as shown in FIG. The amount of oil that flows downstream further increases.

  FIG. 8 is a flow characteristic diagram corresponding to the operation of the nozzle lever in the conventional fueling nozzle.

  FIG. 9 is a flow characteristic diagram corresponding to the operation of the nozzle lever in the fueling nozzle of the present embodiment.

  8 and 9, the horizontal axis represents the operation amount of the nozzle lever 30, that is, the axial stroke of the valve shaft member 19 corresponding to the gripping stroke of the nozzle lever 30, and the vertical axis represents the downstream side of the main valve body 11. The flow rate of the oil liquid flowing through the oil supply, that is, the supply flow rate (discharge flow velocity) from the oil supply nozzle 1 is shown.

  In FIG. 9, the section represented by Lh is such that the columnar protrusion 221 of the sub-valve element 12 is located in the space in the valve seat 16 of the main valve element 11, and the supply flow rate (discharge flow velocity) is substantially the predetermined flow rate F. This is a stroke section in a constant state.

  As is apparent from a comparison between FIGS. 8 and 9, according to the fueling nozzle 1 of the present embodiment, the supply flow rate (discharge flow velocity) increases with respect to the operation amount (grip stroke) of the nozzle lever 30 at the start of additional fueling. The degree of opening of the fueling nozzle can be kept small regardless of the operation amount of the nozzle lever 30 within the predetermined operation amount range Lh immediately after the start of the valve opening operation. Can be maintained at a constant flow rate. As a result, even when the customer himself / herself operates the refueling nozzle 1 and applies it to a self-service refueling station, the operability, safety, and other performances of the refueling nozzle 1 during additional refueling are improved.

  Further, in the fueling nozzle 1 of the present embodiment, as shown in FIGS. 1 and 2, the cross-sectional shape of the contact portion with the other end side of the valve shaft rod 22, that is, the valve shaft member 19 is changed to the lever hook 35. Corresponding to the arrangement, it has a shape having an inclined surface 87 inclined with respect to a plane perpendicular to the axial direction of the valve shaft member 19. Thereby, even when the oil supply nozzle 1 is dropped from the oil supply port during the full tank refueling described above, the fall acceleration caused by the drop of the oil supply nozzle 1, the impact force based on the collision with the surface of the gas station, etc. Is received by the inclined surface 87, the component force can be applied in the direction in which the free end 30A of the nozzle lever 30 placed on the step portion 34 of the lever guard 33 is separated from the step portion 34, The valve portion 5 of the oil supply nozzle 1 is quickly closed by the urging force of the spring member 18 and the hydraulic pressure supplied from the liquid feeding means. Therefore, it is safe even when the oil supply nozzle 1 is dropped from the oil supply port during the above-described full tank oil supply or preset oil supply.

  As described above, the fuel nozzle 1 of the present embodiment is configured, but the fuel nozzle of the present invention is not limited to the above-described configuration.

  For example, the stepped hole 211 of the main valve body 11 and the inner diameter d0 of the valve seat 16 in the valve section 5 of the oil supply nozzle 1 and the diameter d2 and height h of the protrusion 221 formed on the sub-valve body 12 together with the shape thereof In consideration of the maximum lift amount L0 of the sub-valve body 12 with respect to the valve seat 16 of the main valve body 11 in the oil supply nozzle 1, an appropriate oil supply amount (flow velocity) at the time of additional oil supply, and opening at the start of additional oil supply It can be appropriately changed depending on the variation range of the operation stroke L of the nozzle lever 30 during valve operation.

It is front sectional drawing of the oil supply nozzle of one embodiment of this invention. It is the end elevation which looked at the oil supply nozzle shown in FIG. 1 in the YY arrow direction. It is an enlarged view of the valve part of the oil supply nozzle shown in FIG. 2, and is a valve-closing state figure of a valve part. It is assembly | attachment explanatory drawing of the automatic valve closing mechanism of the oil supply nozzle shown in FIG. FIG. 4 is a state diagram of the valve portion when the sub valve body starts to open by the valve opening operation of the nozzle lever from the closed state of the valve portion shown in FIG. 3. It is a state figure of a valve part when a subvalve is fully opened by valve opening operation of a nozzle lever. FIG. 6 is a state diagram of the valve portion when the main valve body is opened next after the sub-valve body is fully opened by the valve opening operation of the nozzle lever. It is a flow rate characteristic figure corresponding to operation of a nozzle lever in the conventional oil supply nozzle. It is a flow rate characteristic figure corresponding to operation of a nozzle lever in an oil supply nozzle of this embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Oil supply nozzle 2 Liquid passage 3 Nozzle main body 4 Discharge pipe 5 Valve part 7 Main valve 11 Main valve body 12 Subvalve body 18 Spring member 19 Valve shaft member 20 Valve shaft sleeve 22 Valve shaft rod 27 Engagement rod 30 Nozzle lever 44 Negative Pressure generating section 52 Negative pressure compensating pipe 61 Automatic valve closing mechanism 62 Leakage preventing mechanism 64 Negative pressure chamber 65 Atmospheric pressure chamber 92 Hydraulic pressure chamber 93 Atmospheric pressure chamber 107 Moving member operating mechanism 211 Stepped hole 221 Protruding portion

Claims (2)

A nozzle body having a liquid passage inside;
A main valve body in which the liquid away seated against installed et a valve seat in the passage, communicating and blocking said fluid passage,
A sub-valve element that is separated from and seated on a valve seat provided in the main valve element, and that communicates and blocks a valve element passage provided to communicate the upstream side and the downstream side of the main valve element;
A valve shaft member that is displaced in conjunction with the operation of the operation piece ;
The sub-valve element is separated from the valve seat of the main valve element seated on the valve seat in response to displacement in the valve opening direction of the valve shaft member interlocked with the valve opening operation of the operation piece. Oil liquid supplied from the liquid feeding means is caused to be seated and in response to further displacement in the valve opening direction of the valve shaft member after the sub-valve body is separated, the main valve body is separated from the valve seat portion. A refueling nozzle for refueling a container,
A protrusion having a predetermined height with respect to the corresponding contact portion is provided inward of a portion of the sub-valve member that contacts the valve seat on the side facing the main valve member in the displacement direction of the valve shaft member. Provided,
On the side of the main valve body facing the sub-valve body in the displacement direction of the valve shaft member, the projecting portion is in an outer peripheral portion of the projecting portion in a state where the sub-valve body is in contact with the valve seat. And having a gap with a predetermined area between and providing a hole where the valve body passage opens in the back,
In response to the valve opening direction displacement of the valve shaft member interlocked with the valve opening operation of the operation piece, the operation piece before the sub valve body is separated from the valve seat and the main valve body is opened. Until the predetermined operation amount, at least a part of the protrusion is accommodated in the hole, and the flow rate of the oil liquid flowing between the sub-valve element and the valve seat is different from that of the outer peripheral portion of the protrusion. An oil supply nozzle characterized by being limited to a predetermined flow rate by a gap area formed between the inner wall of the hole portion . The projecting portion has at least a part of the hole even after an open area generated according to a seating amount between the contact portion and the valve seat by an operation with the operation piece becomes larger than the gap area. The clearance area has a predetermined height so as to be accommodated in the portion, and while the at least part of the projecting portion is accommodated in the hole portion, the clearance area regardless of the displacement of the valve shaft member in the valve opening direction. The refueling nozzle according to claim 1 , wherein is kept constant .

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