JP2019211022A - Fluid control valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the sealing property of a fluid control valve by reducing the weight of a shaft forming a valve body. A first valve body (136) and a second valve body (134) are arranged in a valve chamber (67) formed inside a valve casing (56). The first valve body and the second valve body are relatively slidably arranged in the valve chamber in the axial direction. A seal member 163 held by the second valve body is disposed between the first valve body 136 and the second valve body 134. The first valve body includes a shaft portion 157 that constitutes a relative sliding portion with respect to the second valve body, and a flange 156 that abuts and separates from the seal member 163. A spring bearing member 159 is fitted and fixed to the shaft portion 157, and a second valve body 134 is spring-loaded in the flange position direction of the first valve body 136 between the spring bearing member and the second valve body. A spring 161 is arranged in a biased relationship. The shaft portion 157 of the first valve body 136 is formed in a hollow shape. [Selection diagram] Fig. 9

Description

  The present invention relates to a fluid control valve. In particular, the present invention relates to a fluid control valve used in a fuel vapor processing apparatus mounted on a vehicle.

  A vehicle such as an automobile is provided with an evaporated fuel processing device in a fuel supply path from a fuel tank to an engine. A fluid control valve is used in this fuel vapor processing apparatus. This fluid control valve is also commonly referred to as a block valve. A fluid control valve called a block valve has an electric valve and a relief valve (see Patent Document 1 below).

  In the fluid control valve used in the fuel vapor processing apparatus, the electric valve and the relief valve are arranged in combination in the same valve casing. The motor-operated valve is disposed in the main passage in the fuel vapor processing apparatus, and opens and closes the main passage. The relief valve is arranged in a bypass passage with respect to the main passage, and bypasses the abnormal pressure state of the main passage in the state closed by the motor-operated valve to avoid it.

  Therefore, the relief valve includes a positive pressure relief valve mechanism that opens when the pressure in the main passage (in the gasoline tank) is equal to or higher than a predetermined abnormal positive pressure value, and the pressure in the main passage is equal to or lower than a predetermined abnormal negative pressure value. And a negative pressure relief valve mechanism that opens in this case.

  Since the relief valve constitutes the positive pressure relief valve mechanism and the positive pressure relief valve mechanism described above, first, a valve chamber of the relief valve is formed inside the valve casing, and the first valve body and the valve chamber are formed in the valve chamber. A second valve body is disposed. The first valve body and the second valve body are disposed so as to be relatively slidable in the axial direction in the valve chamber, and between the first valve body and the second valve body, A seal member is disposed by being held by the second valve body. The first valve body includes a shaft that forms a relative sliding portion with the second valve body, and a flange that comes into contact with and separates from the seal member. A spring receiving member is fitted and fixed to the shaft, and the second valve body is spring-biased in the flange direction of the first valve body between the spring receiving member and the second valve body. As a relation, the spring is arranged.

JP 2006-121791 A

  By the way, the shaft of the first valve body in the relief valve described above has a solid shape. For this reason, when the mass of the shaft increases and the center of gravity of the shaft is biased toward the spring receiving member, lateral displacement of the first valve body or oscillation is likely to occur when vibration is applied. The sealing performance of the relief valve may be deteriorated. Such a problem is a problem that occurs in a fluid control valve having the same configuration as the relief valve.

  Thus, the present invention has been devised in view of the above points, and the problem to be solved by the present invention is to reduce the mass of the shaft forming the valve body, thereby reducing the weight of the fluid control valve. The purpose is to improve the sealing performance.

  In order to solve the above problems, the fluid control valve according to the present invention takes the following means.

  A first aspect of the present invention is a fluid control valve in which a first valve body and a second valve body are disposed in a valve chamber formed inside a valve casing, the first valve body and The second valve body is disposed so as to be relatively slidable in the axial direction in the valve chamber, and the second valve body is disposed between the first valve body and the second valve body. The first valve body includes a shaft that forms a relative sliding portion with the second valve body, and a flange that contacts and separates from the seal member. A spring receiving member is fitted and fixed to the shaft, and the second valve body is positioned between the spring receiving member and the second valve body in the flange position of the first valve body. A spring is disposed as a spring-biased relationship in the direction, and the shaft of the first valve body is a fluid control valve formed in a hollow shape.

  According to the first aspect, the shaft of the first valve body is formed in a hollow shape. For this reason, first, the material cost for forming the first valve body can be reduced (cost reduction). And since the axial load of the axis | shaft of a 1st valve body can be reduced and the inclination by the dead weight of an axis | shaft can be suppressed, the dispersion | variation in the flow volume at the time of valve opening by a 1st valve body can be reduced. In addition, since the mass of the first valve body is reduced, even if the center of gravity of the first valve body moves toward the spring receiving member and vibration is applied, the lateral displacement of the first valve body and the neck swing Is unlikely to occur. This makes it difficult for deterioration of the sealing performance to occur and improves the sealing performance.

  Further, according to the first aspect of the invention, the shaft of the first valve body is formed in a hollow shape, so that the hollow shaft is elastically deformed when the spring receiving member is fitted and inserted into the shaft. Thus, the press-fit load can be reduced. Thereby, the press fit of the spring receiving member to the shaft of the first valve body can be easily performed. That is, workability can be improved.

  A second aspect of the present invention is the fluid control valve according to the first aspect described above, wherein the spring receiving member includes a first cylindrical portion that is a fitting portion with the first valve body, A second cylindrical portion that is a guide portion of a spring that is radially separated from the first cylindrical portion, a connecting portion that connects one end portions of the two cylindrical portions, and the other end portion of the second cylindrical portion. It is a fluid control valve provided with the flange part which is a seat surface part of the spring formed by bending and extending.

  According to the second aspect, the spring receiving member is integrally formed by connecting the first tube portion, the second tube portion, the connecting portion, and the flange portion. Thereby, even when the 1st cylinder part which is a fitting part with the 1st valve body, and the 2nd cylinder part which is a guide part of a spring are arranged away in the diameter direction, both cylinder parts Since the space is a space, the weight can be reduced. In addition, since the spring receiving member can be formed with a reduced weight, the position of the center of gravity in the fitted state with the shaft of the first valve body can be set to the lower position on the shaft of the first valve body. If the position of the center of gravity is decentered, the influence on the sealing performance can be suppressed. That is, this can also improve the sealing performance.

  According to the second invention, the second cylindrical portion of the spring receiving member is a press-fitting jig when the inner peripheral side of the cylindrical portion engages the spring receiving member with the shaft of the first valve body. Become a guide. In addition, since the outer peripheral side of the cylindrical portion serves as a spring guide and can be used also as the second cylindrical portion, the spring receiving member can be reduced in size and the entire fluid control valve can be reduced in size. Can also be achieved.

  According to the above-described means of the present invention, the sealing performance of the fluid control valve can be improved by reducing the weight of the shaft forming the valve body.

It is a block diagram which shows the evaporative fuel processing apparatus concerning embodiment of this invention. It is a perspective view which shows the external appearance of the sealing valve (fluid control valve) applied to an evaporative fuel processing apparatus. FIG. 3 is a cross-sectional view taken along line III-III in FIG. 2. FIG. 4 is a cross-sectional view taken along line IV-IV in FIG. 3. It is an expanded sectional view which shows the principal part of the motor operated valve which comprises a blocking valve. It is a perspective view which decomposes | disassembles and shows the principal part of a motor operated valve. It is an expanded sectional view of the relief valve which comprises a block valve. It is sectional drawing which decomposes | disassembles and shows the 1st valve body and spring receiving member of a relief valve as a single item. It is sectional drawing which shows a relief valve typically. It is an assembly | attachment figure which shows the state which attaches a spring receiving member to the axis | shaft of a 1st valve body with a press-fit jig | tool.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The fluid control valve 38 of the present embodiment is provided as a blocking valve in the evaporated fuel processing device 12 mounted on a vehicle such as an automobile on which the internal combustion engine (engine) 14 is mounted. The fluid control valve 38 as a block valve in the present embodiment includes an electric valve 52 and a relief valve 54. In the present embodiment, the relief valve 54 corresponds to the fluid control valve 38 in the present invention. Hereinafter, the configuration of the embodiment will be described sequentially.

<Description of Configuration of Evaporative Fuel Processing Device 12>
First, the fuel vapor processing apparatus 12 in which the fluid control valve 38 having the relief valve 54 targeted by the present invention is disposed will be described. FIG. 1 shows the configuration of the evaporated fuel processing device 12. The evaporative fuel processing device 12 is provided in an engine system 10 of a vehicle such as an automobile. The engine system 10 includes an engine 14 and a fuel tank 15 that stores fuel supplied to the engine 14. The fuel tank 15 is provided with an inlet pipe 16. The inlet pipe 16 is a pipe that introduces fuel into the fuel tank 15 from a fuel filler port at the upper end thereof, and a tank cap 17 is detachably attached to the fuel filler port. Further, the breather pipe 18 communicates the inside of the upper end portion of the inlet pipe 16 and the gas layer portion in the fuel tank 15 where the evaporated fuel exists.

  A fuel supply device 19 is provided in the fuel tank 15. The fuel supply device 19 includes a fuel pump 20 that sucks and pressurizes fuel in the fuel tank 15, a center gauge 21 that detects the liquid level of the fuel, and a tank internal pressure that detects a tank internal pressure as a relative pressure to the atmospheric pressure. A sensor 22 and the like are provided. The fuel pumped up from the fuel tank 15 by the fuel pump 20 is supplied to the engine 14 through the fuel supply passage 24. Specifically, after being supplied to a delivery pipe 26 having an injector (fuel injection valve) 25 corresponding to each combustion chamber, the fuel is injected from each injector 25 into the intake passage 27. In the intake passage 27, an air cleaner 28, an air flow meter 29, a throttle valve 30 and the like are provided.

  The evaporative fuel processing device 12 includes a vapor passage 31, a purge passage 32, and a canister 34. One end portion (upstream end portion) of the vapor passage 31 is communicated with the air layer portion in the fuel tank 15. The other end (downstream end) of the vapor passage 31 communicates with the inside of the canister 34. Further, one end (upstream end) of the purge passage 32 communicates with the inside of the canister 34. The other end portion (downstream end portion) of the purge passage 32 communicates with the passage portion on the downstream side of the throttle valve 30 in the intake passage 27. The canister 34 is loaded with activated carbon (not shown) as an adsorbent. The evaporated fuel in the fuel tank 15 is adsorbed by the adsorbent (activated carbon) in the canister 34 through the vapor passage 31.

  An ORVR valve (On Board Refueling Vapor Recovery valve) 35 and a fuel cut-off valve (Cut Off Valve) 36 are provided at the upstream end portion of the vapor passage 31 in the air layer portion in the fuel tank 15.

  A sealing valve 38 is interposed in the vapor passage 31. That is, the vapor passage 31 is divided into a passage portion 31a on the fuel tank 15 side and a passage portion 31b on the canister 34 side in the middle, and a blocking valve 38 is disposed between the passage portions 31a and 31b. The blocking valve 38 of this embodiment corresponds to a fluid control valve of the present invention. The blocking valve 38 includes an electric valve 52 and a relief valve 54. The motor-operated valve 52 adjusts the flow rate of a gas containing evaporated fuel (referred to as “fluid”) flowing through the vapor passage 31 by opening and closing the passage by electrical control. The electric valve 52 is controlled to open and close by a drive signal output from an engine control device (hereinafter referred to as “ECU”) 45. The relief valve 54 is interposed in the middle of a bypass passage (described later) that bypasses the electric valve 52. The relief valve 54 is for maintaining the pressure in the fuel tank 15 at an appropriate pressure when the electric valve 52 is closed. The details of these blocking valves (fluid control valves) 38 will be described later.

  A purge valve 40 is interposed in the purge passage 32. The purge valve 40 is controlled so as to be opened and closed by a valve opening amount corresponding to the purge flow rate calculated by the ECU 45. Further, the purge valve 40 includes, for example, a stepping motor and can adjust the valve opening amount by controlling the stroke of the valve body. The purge valve 40 is an electromagnetic valve in the present embodiment, and includes an electromagnetic solenoid. The purge valve 40 is closed in a non-energized state and opened by energization.

  An atmospheric passage 42 is disposed in the canister 34. The other end of the atmospheric passage 42 is open to the atmosphere. An air filter 43 is interposed in the middle of the air passage 42.

  In addition to the tank internal pressure sensor 22, the electric valve 52 of the blocking valve 38, the purge valve 40, the ECU 45 is connected to a lid switch 46, a lid opener 47, a display device 49, and the like. The lid opener 47 is connected to a lid manual opening / closing device (not shown) that manually opens and closes the lid 48 that covers the fuel filler opening. The lid switch 46 outputs a signal for unlocking the lid 48 to the ECU 45. The lid opener 47 is a lock mechanism of the lid 48, and when the signal for releasing the lock is supplied from the ECU 45, or when the lid manual opening / closing device is opened, the lid opener 47 locks the lid 48. To release.

(Explanation of operation of the evaporated fuel processing device 12)
Next, the basic operation of the evaporated fuel processing device 12 will be described. Under normal conditions, the relief valve 54 of the blocking valve 38 is in a closed state.

<Description of Operation of Evaporative Fuel Treatment Device 12 -Parking->
(1) First, “when the vehicle is parked” will be described. While the vehicle is parked, the motor-operated valve 52 of the block valve 38 is kept closed. Therefore, the evaporated fuel in the fuel tank 15 does not flow into the canister 34. Further, the air in the canister 34 does not flow into the fuel tank 15. At this time, the purge valve 40 is maintained in the closed state. When the motor-operated valve 52 is closed such as when the vehicle is parked, the pressure in the fuel tank 15 is maintained at an appropriate pressure by a relief valve 54 (described later) of the blocking valve 38.

<Description of Operation of Evaporative Fuel Treatment Device 12 -During Traveling->
(2) Next, “during vehicle travel” will be described. During traveling of the vehicle, the ECU 45 executes control for purging the evaporated fuel adsorbed by the canister 34 when a predetermined purge condition is satisfied. In this control, the purge valve 40 is controlled to open and close. When the purge valve 40 is opened, the intake negative pressure of the engine 14 acts in the canister 34 via the purge passage 32. As a result, the evaporated fuel in the canister 34 is burned in the engine 14 by being purged into the intake passage 27 together with the air sucked from the atmospheric passage 42. Further, the ECU 45 opens the electric valve 52 of the block valve 38 only during the purge of the evaporated fuel. Thereby, the tank internal pressure of the fuel tank 15 is maintained at a value near atmospheric pressure.

<Explanation of Operation of Evaporative Fuel Processing Device 12-During Refueling->
(3) Next, “during refueling” will be described. When the lid switch 46 is operated while the vehicle is stopped, the ECU 45 opens the electric valve 52 of the blocking valve 38. At this time, if the tank internal pressure of the fuel tank 15 is higher than the atmospheric pressure, the motor-operated valve 52 of the blocking valve 38 opens, and at the same time, the evaporated fuel in the fuel tank 15 passes through the vapor passage 31 and enters the canister 34. Adsorbed on the adsorbent. This prevents the evaporated fuel from being released into the atmosphere. As a result, the tank internal pressure of the fuel tank 15 decreases to a value near atmospheric pressure. Further, when the tank internal pressure of the fuel tank 15 decreases to a value near atmospheric pressure, the ECU 45 outputs a signal for releasing the lock of the lid 48 to the lid opener 47. Upon receiving the signal, the lid opener 47 releases the lock of the lid 48, so that the lid 48 can be opened. Then, in a state where the lid 48 is opened and the tank cap 17 is opened, the fuel supply to the fuel tank 15 is started. Further, the ECU 45 keeps the motor-operated valve 52 of the blocking valve 38 in an open state until the end of refueling (specifically, the lid 48 is closed). For this reason, during refueling, the evaporated fuel in the fuel tank 15 passes through the vapor passage 31 and is adsorbed by the adsorbent in the canister 34.

<Description of Blocking Valve (Fluid Control Valve) 38>
Next, the blocking valve 38 will be described. FIG. 2 shows an external perspective view of the valve casing 56 that forms the block valve 38. 3 and 4 are sectional views showing the entire configuration of the blocking valve 38, FIG. 3 is a longitudinal sectional view taken along line lll-lll in FIG. 2, and FIG. 4 is a sectional view taken along line lV-lV in FIG. FIG. As shown in FIGS. 3 and 4, the blocking valve 38 includes an electric valve 52 formed in the valve casing 56 and a relief valve 54. Note that the direction indications shown in the drawings illustrating the blocking valve 38 are normally installed under the floor of the vehicle, and thus each direction is determined in accordance with the front, rear, left, right, up and down directions of the vehicle. The arrangement direction of the blocking valve 38 is not specified.

<Description of valve casing 56 and main passage 74>
FIG. 2 shows the appearance of the valve casing 56 that forms the block valve 38. The valve casing 56 is made of resin, and as shown in FIGS. 3 and 4, an electric valve 52 and a relief valve 54 constituting the blocking valve 38 are accommodated in the valve casing 56. Therefore, the valve casing 56 has a first housing cylinder portion 60 for constituting the motor operated valve 52 and a second housing cylinder portion 61 for constituting the relief valve 54. Further, the valve casing 56 includes a first pipe portion 57 and a second pipe portion 58. The first pipe portion 57 and the second pipe portion 58 form a main passage 74 that forms part of the vapor passage 31 (see FIG. 1) in the valve casing 56.

  The first pipe portion 57 and the second pipe portion 58 that form the main passage 74 in the valve casing 56 are formed in a hollow circular tube, and the first pipe portion 57 is disposed in the front-rear direction, and the second pipe portion 58. Are arranged in the left-right direction.

  Further, a bypass passage 90 is formed in the valve casing 56 as a passage for bypassing the main passage 74 (see FIG. 3). A relief valve 54 is disposed in the bypass passage 90. As shown in FIG. 3, the relief valve 54 and the motor-operated valve 52 are communicated with each other by a communication passage 84 to form a bypass passage 90.

  Furthermore, the valve casing 56 has a mounting portion 63 for mounting the blocking valve 38 on the lower surface of the floor of the vehicle. As shown in FIGS. 2 and 3, the attachment portion 63 is formed integrally with the upper portion of the first housing cylinder 60 that forms the motor-operated valve 52, and as shown in FIG. 4, the first housing cylinder is formed. The unit 60 can be attached to the vehicle floor at both the left and right positions. The attachment position is a position offset in the front-rear direction.

  As shown in FIG. 3 and FIG. 4, the first accommodating cylinder portion 60 that forms the motor-operated valve 52 gradually increases in diameter from the front end portion of the first pipe portion 57 toward the front (the left side). It is formed in a stepped cylindrical shape. The 1st pipe part 57 and the 1st accommodating cylinder part 60 are formed concentrically. A valve chamber 65 of the motor-operated valve 52 is formed in the rear end portion of the first housing cylinder portion 60. This is the first valve chamber 65. The second pipe part 58 is formed in a hollow circular tube extending rightward (downward in FIG. 4) from the first valve chamber 65 of the first housing cylinder part 60.

  As shown in FIG. 3, the second housing cylinder part 61 that forms the valve chamber 67 of the relief valve 54 is formed in a bottomed cylindrical shape above the front end part of the first pipe part 57. As can be seen from the illustrated state of FIG. 4, the second accommodating cylinder portion 61 has an outer diameter that is approximately twice the outer diameter of the first pipe portion 57. The axial center of the second housing cylinder 61 is a position on the axial center line of the first pipe portion 57. That is, the second housing cylinder part 61 is installed at a position directly above the first pipe part 57. A valve chamber 67 of the relief valve 54 is formed in the second housing cylinder 61 (see FIG. 3). This valve chamber 67 is defined as a second valve chamber. The second valve chamber 67 of the present embodiment corresponds to the valve chamber of the present invention.

  As shown in FIG. 4, the 1st pipe part 57 and the 2nd pipe part 58 are formed with the same pipe diameter or substantially the same pipe diameter. The insides of both pipe portions 57 and 58 are in communication with each other via the first valve chamber 65. The opening on the first valve chamber 65 side of the first pipe portion 57 is a valve port 71 of the motor operated valve 52. This valve port 71 is defined as a first valve port. The first valve port 71 is formed with an inner diameter that is slightly smaller than the inner diameter of the first pipe portion 57. An edge portion of the first valve port 71 is a valve seat 72. Inside the first pipe portion 57 is a first passage portion 75 extending along the same direction as the axial direction of the first valve port 71. The inside of the second pipe portion 58 is on the opposite side to the first passage portion 75 side (rear side) of the first valve port 71, that is, the front side (left side in FIG. 4), and the axial direction (front-rear direction) of the first passage portion 75. The second passage portion 76 extends in a different direction, that is, along the right side (downward in FIG. 4). An elbow-shaped main passage 74 is formed by the first passage portion 75 and the second passage portion 76.

  As shown in FIG. 3, a stepped portion 78 having a smaller inner diameter is formed concentrically at the lower end portion of the second accommodating cylinder portion 61 that forms the second valve chamber 67 of the relief valve 54. A hollow portion in the stepped portion 78 is a valve port 80 that communicates with the second valve chamber 67 in the second housing cylinder portion 61. The valve port 80 of the relief valve 54 is a second valve port. The second valve port 80 communicates with the first passage portion 75 by passing through the overlapping wall portion between the first pipe portion 57 and the second housing cylinder portion 61. On the end surface (upper end surface) of the stepped portion 78 on the second valve chamber 67 side, a metal annular plate-shaped valve seat 82 is disposed concentrically. The valve seat 82 is embedded and disposed in the stepped portion 78. The valve seat 82 forms the seat surface of the relief valve 54.

<Description of bypass passage 74>
As shown in FIG. 3, a bypass passage 90 that bypasses the main passage 74 is formed in the main passage 74 formed by the first pipe portion 57 and the second pipe portion 58 shown in FIG. The bypass passage 90 is connected to the first valve chamber 65 of the motor-operated valve 52 via the second valve port 80 and the second valve chamber 67 of the relief valve 54 that is branched from the first passage portion 75. Connected via and formed. That is, the bypass passage 90 is formed by bypassing the first valve port 71 of the motor-operated valve 52 in the path of the main passage 74. In the bypass passage 90, an abnormal positive pressure or negative pressure state in the fuel tank when the motor-operated valve 52 in the main passage 74 is in a closed state and the main passage 74 is in a shut-off state is given to the bypass passage 90. This is a passage that is adjusted by relief by control of the relief valve 54 provided.

<Description of Configuration of Motorized Valve 52>
Next, the configuration of the motor operated valve 52 will be described. FIG. 5 is an enlarged cross-sectional view of the motor-operated valve 52, and FIG. 6 is an exploded perspective view. As shown in FIG. 5, the motor-operated valve 52 is accommodated in the first accommodating cylinder portion 60 of the valve casing 56. The electric valve 52 includes an electric motor 92, a valve guide 94, a valve body 96, and a valve spring 98. FIG. 5 shows the open state of the motor operated valve 52.

  The electric motor 92 of the electric valve 52 is a stepping motor in this embodiment. The stepping motor 92 is installed in the first housing cylinder portion 60 with its axial direction as the front-rear direction. The stepping motor 92 has an output shaft 93 that can rotate forward and reverse. The output shaft 93 is directed rearward and is concentrically disposed in the first valve chamber 65 of the first housing cylinder 60. A male screw portion 100 is formed on the outer peripheral surface of the output shaft 93.

  As shown in FIG. 6, the valve guide 94 has a cylindrical tube wall portion 102 and an end wall portion 103 that closes the front end opening of the tube wall portion 102. At the front end of the cylindrical wall portion 102, an overhanging portion 104 that increases the outer diameter is formed in a stepped cylindrical shape. A cylindrical tube shaft portion 105 is formed concentrically at the center portion of the end wall portion 103. The front end opening of the cylindrical shaft portion 105 is closed. As shown in FIG. 5, a female screw portion 106 is formed on the inner peripheral surface of the cylindrical shaft portion 105.

  The valve guide 94 is disposed so as to be movable in the axial direction, that is, the front-rear direction with respect to the first valve chamber 65. The valve guide 94 is prevented from rotating in the direction around the axis by a rotation preventing means (not shown) with respect to the peripheral wall portion (first housing cylinder portion 60) of the first valve chamber 65. The overhanging portion 104 of the valve guide 94 is fitted to the inner wall surface of the first valve chamber 65 with a predetermined gap. The female screw portion 106 of the tube shaft portion 105 is screwed to the male screw portion 100 of the output shaft 93 of the stepping motor 92. Therefore, the valve guide 94 is moved in the axial direction (front-rear direction) based on forward and reverse rotation of the output shaft 93. A feed screw mechanism 110 is configured by the male thread portion 100 of the output shaft 93 and the female thread portion 106 of the valve body 96.

  An auxiliary spring 112 made of a coil spring is interposed between the valve seat 72 of the valve casing 56 and the overhanging portion 104 of the valve guide 94. The auxiliary spring 112 is fitted to the cylindrical wall portion 102. The auxiliary spring 112 suppresses backlash of the feed screw mechanism 110 by always urging the valve guide 94 forward. The rear end surface of the cylindrical wall portion 102 is opposed to the valve seat 72 so as to be able to come into contact therewith.

  As shown in FIG. 6, the valve body 96 includes a cylindrical tubular portion 114 and a valve plate portion 115 that closes the rear end opening of the tubular portion 114. An annular seal member 117 made of a rubber-like elastic material is attached to the valve plate portion 115 (see FIG. 5). This seal member 117 is a first seal member.

  As shown in FIG. 5, the valve body 96 is disposed concentrically in the valve guide 94 and is movable in the front-rear direction. The first seal member 117 is opposed to the valve seat 72 so as to come into contact therewith. A connecting means 120 is provided between the valve guide 94 and the valve body 96 so as to connect both members 94 and 96 so as to be movable within a predetermined range in the axial direction (front-rear direction). As shown in FIG. 6, a plurality of sets (for example, four sets) of connecting means 120 are arranged at equal intervals in the circumferential direction. The connecting means 120 includes an engaging protrusion 122 provided on the cylindrical portion 114 of the valve body 96 and an engaging groove 124 provided on the cylindrical wall portion 102 of the valve guide 94.

  As shown in FIG. 6, the engagement protrusion 122 protrudes outward in the radial direction from the front end portion of the outer peripheral surface of the tubular portion 114 of the valve body 96. A substantially U-shaped groove forming wall 126 is formed in a protruding shape on the inner peripheral surface of the cylindrical wall portion 102 of the valve guide 94. The groove forming wall 126 forms an engaging groove 124 that opens in the cylindrical wall portion 102 and extends in the front-rear direction. One side wall portion of the groove forming wall 126 is connected to the end wall portion 103. An opening 127 is formed between the other side wall portion of the groove forming wall 126 and the end wall portion 103. The engaging protrusion 122 is engaged in the engaging groove 124 from the opening 127 of the groove forming wall 126. Accordingly, the valve body 96 is connected to the valve guide 94 so as to be movable with a predetermined movement amount in the axial direction (front-rear direction) in a state where the valve body 96 is prevented from rotating in the circumferential direction.

  As shown in FIGS. 5 and 6, the valve spring 98 is a coil spring. The valve spring 98 is concentrically interposed between the end wall portion 103 of the valve guide 94 and the valve plate portion 115 of the valve body 96. The valve spring 98 always urges the valve body 96 backward, that is, in the closing direction with respect to the valve guide 94.

<Description of Relief Valve 54 Configuration—Embodiment of Valve Configuration Targeted by Present Invention>
Next, the relief valve 54 will be described. The relief valve is an embodiment of a valve configuration showing a fluid control valve targeted by the present invention. FIG. 7 shows an enlarged cross-sectional view of the relief valve 54. The relief valve 54 has a positive pressure relief valve mechanism 130 and a negative pressure relief valve mechanism 132. The illustrated state of FIG. 7 shows the closed state of both the relief valve mechanisms 130 and 132. As shown in FIG. 7, the relief valve 54 is disposed in the second accommodating cylinder portion 61 of the valve casing 56.

  The relief valve 54 has a positive pressure relief valve mechanism 130 and a negative pressure relief valve mechanism 132 concentrically. The valve member 134 of the positive pressure relief valve mechanism 130 and the valve member 136 of the negative pressure relief valve mechanism 132 are disposed concentrically and vertically movable in the second valve chamber 67 of the second housing cylinder portion 61. Yes. Hereinafter, the valve member 134 of the positive pressure relief valve mechanism 130 is the second valve body, and the valve member 136 of the negative pressure relief valve mechanism 132 is the first valve body.

  The second valve element 134 of the positive pressure relief valve mechanism 130 has an annular plate-like valve plate 138, and an inner cylinder part 139 and an outer cylinder part 140 that form an inner and outer double cylinder shape. . The outer peripheral portion of the valve plate 138 is a valve portion 141 corresponding to the valve seat 82 of the second accommodating cylinder portion 61. This is the first valve portion 141. The first valve portion 141 opens the second valve port 80 when sitting upward from the valve seat 82, and closes the second valve port 80 by sitting on the valve seat 82 from that state.

  The inner cylinder part 139 and the outer cylinder part 140 are erected on the valve plate 138. A connecting portion between the valve plate 138 and the inner cylinder portion 139 has a plurality of communication holes 143 (two are shown in FIG. 7) that penetrate the valve plate 138 in the vertical direction and penetrate the inner cylinder portion 139 in the radial direction. Is formed. A plurality of stopper pieces 145 are formed at equal intervals in the circumferential direction on the lower surface of the outer peripheral edge of the first valve portion 141. The stopper piece 145 contacts the valve seat 82 when the second valve body 134 is closed. Thereby, the valve closing position of the 2nd valve body 134 is prescribed | regulated. An inner peripheral portion of the valve plate 138 serves as a valve seat 147 of the negative pressure relief valve mechanism 132.

  A cap 150 and a retaining member 152 are disposed at the upper end opening of the second housing cylinder 61. The cap 150 is made of resin and has a disk shape. The cap 150 closes the upper end opening of the second housing cylinder 61 by fitting. The retaining member 152 is made of resin and has an annular shape. The retaining member 152 is joined to the upper end portion of the second housing cylinder portion 61 by welding or the like. The retaining member 152 is engaged with the outer peripheral portion of the cap 150. As a result, the cap 150 is prevented from being detached by the retaining member 152.

  A first coil spring 154 is disposed concentrically between the opposing surfaces of the valve plate 138 of the second valve body 134 and the cap 150. The first coil spring 154 biases the second valve body 134 downward, that is, in the valve closing direction. The first coil spring 154 is fitted in the outer cylindrical portion 140 of the second valve body 134.

  The first valve body 136 includes a disk-shaped flange 156 and a long shaft portion 157 having a round cross section. As for the 1st valve body 136, the axial part 157 is fitted in the inner cylinder part 139 of the 2nd valve body 134 from the downward direction. The flange 156 opens the communication hole 143 when being separated from the valve seat 147 of the second valve body 134, and closes the communication hole 143 by sitting on the valve seat 147 from this state. An annular plate-shaped spring receiving member 159 is attached to the distal end portion (upper end portion) of the shaft portion 157. The spring receiving member 159 contacts the inner cylinder portion 139 of the second valve body 134 when the first valve body 136 is opened. Thereby, the maximum valve opening amount of the first valve body 136 is defined.

  A second coil spring 161 is concentrically disposed between the opposing surfaces of the valve plate 138 of the second valve body 134 and the spring receiving member 159. An inner cylinder portion 139 of the second valve element 134 is disposed in the second coil spring 161. The second coil spring 161 biases the first valve body 136 upward, that is, in the valve closing direction. The second coil spring 161 and the first coil spring 154 are arranged in an inner and outer double annular shape. The coil diameter, coil length, and coil wire diameter of the second coil spring 161 are set smaller than the coil diameter, coil length, and coil wire diameter of the first coil spring 154. Therefore, the biasing force of the second coil spring 161 is smaller than the biasing force of the first coil spring 154. The second coil spring 161 of the present embodiment described above corresponds to the spring of the present invention.

  An annular seal member 163 made of a rubber-like elastic material is attached to the lower surface of the valve plate 138 of the second valve body 134 by adhesion or the like. This seal member 163 is a second seal member. The second seal member 163 is formed of a rubber-like elastic material such as rubber, and has both inner and outer seal portions 164 and 165 projecting in an inner and outer double ring shape on the lower surface side. The inner peripheral seal portion 164 faces the flange 156 of the first valve body 136. When the first valve body 136 is closed, the first valve body 136 is urged upward by the urging force of the second coil spring 161, so that the flange 156 elastically contacts the inner peripheral side seal portion 164. That is, they are in close contact. Further, the outer peripheral side seal portion 165 faces the valve seat 82 of the valve casing 56. When the second valve body 134 is closed, the second valve body 134 is urged downward by the urging force of the first coil spring 154, so that the outer peripheral seal portion 165 elastically contacts the valve seat 82. That is, they are in close contact.

<Positive pressure relief valve mechanism 130>
Next, the positive pressure relief valve mechanism 130 (see FIG. 7) will be described. In the positive pressure relief valve mechanism 130, the valve opening pressure on the positive pressure side is set by the first coil spring 154. As a result, when the pressure on the second valve port 80 side (fuel tank side) becomes equal to or higher than the valve opening pressure on the positive pressure side, the second valve element 134 rises against the bias of the first coil spring 154. As a result, the positive pressure relief valve mechanism 130 is opened. At this time, the seal portion 165 on the outer peripheral side is separated from the valve seat 82 and is in a free state.

<Negative pressure relief valve mechanism 132>
Next, the negative pressure relief valve mechanism 132 (see FIG. 7) will be described. In the negative pressure relief valve mechanism 132, the valve opening pressure on the negative pressure side is set by the second coil spring 161. As a result, when the pressure on the second valve port 80 side (fuel tank side) becomes equal to or lower than the valve opening pressure on the negative pressure side, the first valve body 136 descends against the bias of the second coil spring 161. As a result, the negative pressure relief valve mechanism 132 is opened. At this time, the seal portion 164 on the inner peripheral side is relatively separated from the flange 156 of the first valve body 136 and is in a free state.

<Arrangement of blockade valve 38 and main passage 74>
The above-described blocking valve 38 is interposed in the vapor passage 31 in the evaporated fuel processing device 12 (see FIG. 1) mounted on a vehicle (not shown). That is, as shown in FIGS. 3 and 4, the passage portion 31 a on the fuel tank 15 side of the vapor passage 31 is connected to the first pipe portion 57 of the valve casing 56, and the vapor passage 31 is connected to the second pipe portion 58. A passage 31b on the canister 34 side is connected. Thus, both passage portions 31 a and 31 b of the vapor passage 31 are communicated with each other via the main passage 74 of the valve casing 56. For this reason, the main passage 74 constitutes a part of the vapor passage 31. As shown in FIG. 3, the attachment portion 63 of the valve casing 56 is fixed to the fixed side member 167 on the lower floor side of the vehicle by fastening a bolt or the like. As a result, the blocking valve 38 is mounted on the vehicle so that the axis of the relief valve 54 (see FIG. 3) faces in the vertical direction. The second valve port 80 of the relief valve 54 is disposed on the top side with respect to the main passage 74 in a vehicle-mounted state. That is, as shown in FIG. 3, the second valve port 80 is set at a position above the main passage 74 formed by the first pipe portion 57.

<Operation of Motorized Valve 52>
Next, the operation of the motor operated valve 52 in the blocking valve 38 will be described. The operation of the electric valve 52 is performed when the positive pressure relief valve mechanism 130 and the negative pressure relief valve mechanism 132 of the relief valve 54 are closed (see FIG. 3).

<Valve open state of motorized valve 52>
First, the open state of the electric valve 52 will be described. As shown in FIG. 5, in the open state of the electric valve 52, the valve guide 94 and the valve body 96 (including the first seal member 117) are located forward (in FIG. 5) from the valve seat 72 of the first housing cylinder 60. (Upward). Further, the valve body 96 is urged rearward (downward in FIG. 5) by the elasticity of the valve spring 98 with respect to the valve guide 94, and the groove bottom portion (groove formation) of the engagement groove 124 of the valve guide 94 shown in FIG. The engagement protrusion 122 of the valve body 96 is in contact with the front end portion of the wall portion 126. For this reason, the valve guide 94 and the valve body 96 are connected via the connecting means 120.

  Further, the valve guide 94 is stroke-controlled in the axial direction via the feed screw mechanism 110 based on drive control of the stepping motor 92 by the ECU 45 (see FIG. 1). Accordingly, the valve body 96 is moved in the front-rear direction (vertical direction in FIG. 5) together with the valve guide 94, whereby the valve opening amount (lift amount) of the valve body 96 is adjusted. Further, even when the stepping motor 92 is turned off in the valve open state, the valve open state can be maintained by the detent torque of the stepping motor 92, the lead angle of the feed screw mechanism 110, and the like.

  And in the valve opening state of the motor operated valve 52 mentioned above, the main channel | path 74 formed in the valve casing 56 is in a communication state. In other words, the main passage 74 of the first pipe portion 57 connected to the passage portion 31a of the vapor passage 31 on the fuel tank 15 side shown in FIG. 4 and the second passage connected to the passage portion 31b of the vapor passage 31 on the canister 34 side are shown. The pipe portion 58 is in communication with the main passage 74.

<When the electric valve 52 is closed>
Next, the time of the valve closing operation of the electric valve 52 will be described. When the motorized valve 52 is opened (the state shown in FIG. 5), when the stepping motor 92 is closed, the output shaft 93 is rotated in the valve closing direction. As a result, the valve guide 94 and the valve body 96 move rearward via the feed screw mechanism 110. Then, the valve body 96 (specifically, the first seal member 117) is seated on the valve seat 72, and the backward movement of the valve body 96 is restricted. Subsequently, the valve guide 94 moves further rearward. Accordingly, the groove bottom portion (front end portion of the groove forming wall portion 126) of the engagement groove 124 of the valve guide 94 moves forward with respect to the engagement protrusion 122 of the valve body 96 shown in FIG. For this reason, the connection between the valve guide 94 and the valve body 96 by the connecting means 120 is released.

  Then, when the cylindrical wall portion 102 of the valve guide 94 approaches or comes into contact with the valve seat 72 of the valve casing 56, the valve closing operation of the stepping motor 92 is stopped by the ECU 45. This state is a valve closing state. The valve guide 94 is brought close to the valve seat 72 by opening the stepping motor 92 by a predetermined amount after the cylindrical wall portion 102 of the valve guide 94 contacts the valve seat 72 of the valve casing 56. Also good.

<Valve closed state of motorized valve 52>
Next, the closed state of the electric valve 52 will be described. When the motor-operated valve 52 is closed, the valve body 96 is elastically held in a state of being seated on the valve seat 72 of the valve casing 56 by the biasing force of the valve spring 98. In addition, the first seal member 117 elastically seals between the valve body 96 and the valve seat 72. Further, even when the stepping motor 92 is turned off in the closed state, the closed state can be maintained by the detent torque of the stepping motor 92, the lead angle of the feed screw mechanism 110, and the like.

<When the motorized valve 52 is opened>
Next, the opening operation of the electric valve 52 will be described. When the stepping motor 92 is opened in the closed state of the electric valve 52, the output shaft 93 is rotated in the valve opening direction. Thereby, the valve guide 94 is moved forward (opening direction) via the feed screw mechanism 110. Accordingly, the engagement groove 124 of the valve guide 94 moves upward along the engagement protrusion 122 of the valve body 96. As a result, the valve spring 98 and the auxiliary spring 112 extend due to their elastic restoring force. Then, the groove bottom portion of the engagement groove 124 (the front end portion of the groove forming wall portion 126) contacts the engagement protrusion 122 of the valve body 96. Thereby, the relative movement between the valve guide 94 and the valve body 96 is restricted. For this reason, the valve guide 94 and the valve body 96 are connected via the connecting means 120. Subsequently, the valve guide 94 and the valve body 96 are further raised. Along with this, the auxiliary spring 112 extends due to its elastic restoring force. As a result, the valve body 96 (specifically, the first seal member 117) is separated from the valve seat 72 of the valve casing 56, thereby opening the valve (the state shown in FIG. 5).

<Operation of relief valve 54>
Next, the operation of the relief valve 54 will be described based on FIG. Both the valve opening operation of the positive pressure relief valve mechanism 130 and the valve opening operation of the negative pressure relief valve mechanism 132 in the relief valve 54 are performed while the motor-operated valve 52 is closed.

<Valve Opening Operation of Positive Pressure Relief Valve Mechanism 130>
The valve opening operation of the positive pressure relief valve mechanism 130 is performed when a positive pressure higher than the valve opening pressure of the positive pressure relief valve mechanism 130 is generated in the fuel tank 15. That is, when a positive pressure equal to or higher than the valve opening pressure is generated, the second valve body 134 is moved up as described above, the positive pressure relief valve mechanism 130 is opened, and the second valve port 80 and the second valve chamber 67 are opened. Communicate. As a result, the bypass passage 90 is in a communicating state, and the first valve port 71 of the electromagnetic valve 52 in the main passage 74 is in a closed state, and the main passage 74 is shut off via the bypass passage 90. It becomes a communication state. Due to the communication of the bypass passage 90, the fluid from the fuel tank 15 side flows from the first passage portion 75 through the bypass passage 90 and from the second passage portion 76 to the canister 34 side. Thereby, the pressure in the fuel tank 15 can be reduced.

<Valve Opening Operation of Negative Pressure Relief Valve Mechanism 132>
The valve opening operation of the negative pressure relief valve mechanism 132 is performed when a negative pressure equal to or lower than the valve opening pressure of the negative pressure relief valve mechanism 132 is generated in the fuel tank 15. That is, when a negative pressure equal to or lower than the valve opening pressure is generated, the first valve body 136 is lowered and opened as described above, the negative pressure relief valve mechanism 132 is opened, and the second valve port 80 and the second valve The valve chamber 67 communicates. As a result, as in the case of opening the positive pressure relief valve mechanism 130, the bypass passage 90 is in a communicating state, and even if the main passage 74 is in a blocked state, the bypass passage 90 is in a communicating state. Due to the communication of the bypass passage 90, the fluid from the fuel tank 15 side flows from the first passage portion 75 through the bypass passage 90 and from the second passage portion 76 to the canister 34 side. Thereby, the pressure in the fuel tank 15 can be raised.

<Characteristic Configuration of the Present Embodiment-Part 1; Configuration of the Shaft 157 of the First Valve Body 136 in the Relief Valve 54>
The configuration characterized by the present embodiment is first the configuration of the shaft portion 157 of the first valve body 136 in the configuration of the relief valve 54 described above. FIG. 8 is a cross-sectional view showing the first valve body 136 and a spring receiving member 159 having a characteristic configuration to be described later as a single product. As shown in FIG. 8, as described above, the first valve body 136 includes a shaft portion 157 having a round cross section and a long shaft shape, and a disc-shaped flange 156. The shaft portion 157 is formed integrally with one end portion. And the axial part 157 is formed in the hollow shape by which the axial center part was made into the space. Since the first valve body 136 is a steel product, the hollow shape is formed by punching a press in this embodiment. Therefore, as shown in FIG. 8, the upper end of the shaft portion 157 has a bottomed shape, and the lower end portion where the flange 156 is formed has an open shape. The shaft portion 157 may be manufactured by removing the central portion from a solid shape part by cutting or the like. However, press working is cheaper and preferable from the viewpoint of manufacturing cost.

  FIG. 9 is a schematic diagram of the relief valve 54. This schematic diagram shows the relief valve 54 in which the shaft portion 157 of the first characteristic configuration described above has a hollow shape, and the configuration of the relief valve 54 described above is simplified for easy understanding. . For this reason, the same components as those of the relief valve 54 described above are shown with the same reference numerals. That is, the configuration of FIG. 9 is a schematic diagram showing a simplified configuration of the first invention of the present invention.

<Characteristic Configuration of the Present Embodiment-Part 2; Configuration of Spring Receiving Member 159 in Relief Valve 54->
The following configuration characterized by the present embodiment is a configuration of a spring receiving member 159 fitted and attached to the shaft portion 157 of the first valve body 136 having the above-described first characteristic configuration. As shown in FIG. 8, a single spring receiver member 159 is shown in cross section. The spring receiver member 159 includes a first cylindrical portion 170, a second cylindrical portion 172, a connecting portion 174, a flange portion 176, and an upper portion. The cylindrical part 178 is connected and formed integrally. The spring receiving member 159 is also a steel product.

  The first cylindrical portion 170 is a portion that fits with the shaft portion 157 of the first valve body 136 and is formed in a cylindrical shape. The first valve body 136 is fitted and attached to the shaft portion 157 with a tight fit. The second cylinder portion 172 is a cylindrical member that is spaced apart radially outward of the first cylinder portion 170. The second cylindrical portion 172 serves as a guide portion for a second coil spring 161 (see FIG. 7) disposed in parallel with the shaft portion 157 of the first valve member.

  The connecting portion 174 is a portion that connects the first cylindrical portion 170 and one end of the second cylindrical portion 172. In the present embodiment, as shown in FIG. 8, the lower ends of the first cylindrical portion 170 and the second cylindrical portion 172 are connected. The flange portion 176 is formed by bending and extending the other end portion of the second cylindrical portion 172, that is, the upper end portion in FIG. The flange portion 176 is a seat surface portion of the second coil spring 161 (see FIG. 7). The upper cylindrical portion 178 is formed as a cylindrical shape bent upward from the outer peripheral portion of the flange portion 176 as viewed in FIG. The upper cylinder part 178 is a part that plays a role of reinforcement.

<Effects of Feature Configuration (Part 1) of the Present Embodiment>
According to the configuration of the characteristic configuration (part 1) of the present embodiment described above, the following effects are obtained. First, since the shaft portion 157 of the first valve body 136 is formed in a hollow shape, the material cost for forming the first valve body 136 can be reduced (cost reduction). And the axial load of the axial part 157 of the 1st valve body 136 can be reduced, and the inclination by the dead weight of the axial part 157 can be suppressed. Thereby, the dispersion | variation in the flow volume at the time of valve opening by the 1st valve body 136 can be reduced. Further, since the mass of the first valve body 136 becomes small, even if the center of gravity of the first valve body 136 moves upward on the spring receiving member 159 side and vibration is applied, the first valve body 136 is Side slip and neck swing are unlikely to occur, and the sealing performance is unlikely to deteriorate. Thereby, the sealing performance can be improved.

  Further, since the shaft portion 157 is formed in a hollow shape, the spring receiving member 159 can be easily press-fitted into the shaft portion 157. That is, when the spring receiving member 159 is press-fitted and fitted, the hollow shaft portion 157 is elastically deformed, so that the press-fitting load can be reduced, and the spring receiving member is press-fitted into the shaft portion 157 of the first valve body 136. Can be easily performed. That is, workability can be improved. This effect is remarkable in the case of the spring receiving member 159 having the first cylindrical portion 170 shown in the present embodiment, but the same effect is also obtained in the case of the massive spring receiving member 159 shown in FIG.

<Effects of Feature Configuration (Part 2) of the Present Embodiment>
According to the configuration of the spring receiving member 159 of the characteristic configuration (part 2) of the present embodiment described above, the following effects are obtained. First, when the 1st cylinder part 170 which is a fitting site | part with the 1st valve body 136, and the 2nd cylinder part 172 which is a guide site | part of the 2nd coil spring 161 are arrange | positioned away in radial direction. However, since the space between the tube portions 170 and 172 is a space, the weight can be reduced.

  In accordance with the weight reduction of the spring receiving member 159 due to the above effect, in the present embodiment, the position of the center of gravity in the fitted state with the shaft portion 157 of the first valve body 136 is set to the shaft portion 157 of the first valve body 136. It can be in the lower position. For this reason, even if the position of the center of gravity is eccentric, the influence on the sealing performance can be suppressed. That is, this can also improve the sealing performance.

  FIG. 10 shows an assembling process in which the spring receiving member 159 is press-fitted to the shaft portion 157 of the first valve body 136 using the press-fitting jig 180. As shown in FIG. 10, the pressure receiving cylindrical portion 182 disposed on the lower surface portion of the press fitting jig 180 pushes the connecting portion 174 of the spring receiving member 159 downward by the press fitting load, so that the spring receiving member 159 is moved to the shaft portion 157. It is assembled. In this assembly, the inner peripheral surface of the first cylindrical portion 170 of the spring receiving member 159 is press-fitted as a press-fitting surface that is fitted to the shaft portion 157, so that press-fitting dimension accuracy can be obtained. Reference numeral 184 denotes a pedestal, and the flange 156 of the first valve body 136 is placed on the upper surface of the pedestal 184 and assembled.

  Further, the inner peripheral surface of the second cylindrical portion 172 of the spring receiving member 159 functions as a guide for the press-fitting jig 180 at the time of assembly by the pressurizing cylindrical portion 182 of the press-fitting jig 180 described above. The outer peripheral surface functions as a guide for the second coil spring 161. As described above, the second cylindrical portion 172 serves two functions by one part, which contributes to the downsizing of the relief valve 54.

<Effects of other configurations of the present embodiment>
According to the blocking valve (fluid control valve) 38 of the present embodiment, the motor-operated valve 52 and the relief valve 54 are arranged so that their axial directions are different from each other. In other words, the motor-operated valve 52 and the relief valve 54 are arranged such that their axis lines form a twisted positional relationship. Specifically, the motor-operated valve 52 is disposed so that the axial direction is the front-rear direction, and the relief valve 54 is disposed so that the axial direction is the vertical direction. Thereby, the dimension in the direction (vertical direction) along the axial direction of the relief valve 54 can be shortened, and the blockade valve 38 can be made compact.

  In addition, a main passage 74 having a first valve port 71 and a bypass passage 90 having a second valve port 80 are formed in the valve casing 56. For this reason, the electric valve 52 and the relief valve 54 can be integrated, and the blockade valve 38 can be made compact.

<Modification of Embodiment>
While the present invention has been described with respect to specific embodiments, the present invention can be implemented in various other forms.

  For example, the blocking valve (fluid control valve) 38 of the present embodiment is not limited to the evaporated fuel processing device 12 and may be applied to other necessary devices. Moreover, the motor-operated valve 52 and the relief valve 54 should just be arrange | positioned so that a mutual axial direction may become a different direction, The direction is not limited.

DESCRIPTION OF SYMBOLS 12 ... Evaporative fuel processing apparatus 15 ... Fuel tank 31 ... Vapor passage 34 ... Canister 38 ... Sealing valve (fluid control valve)
52 ... Electric valve 54 ... Relief valve 56 ... Valve casing 65 ... First valve chamber 67 ... Second valve chamber 74 ... Main passage 90 ... Bypass passage 130 ... Positive pressure relief valve mechanism 132 ... Negative pressure relief valve mechanism 134 ... Second Valve body 136 ... first valve body 156 ... flange 157 ... shaft 159 ... spring receiving member 161 ... second coil spring (spring)
163 ... Second seal member (seal member)
170 ... 1st cylinder part 172 ... 2nd cylinder part 174 ... Connection part 176 ... Flange part 178 ... Upper cylinder part 180 ... Press-fit jig 182 ... Pressurization cylinder part 184 ... Pedestal

Claims (2)

A fluid control valve in which a first valve body and a second valve body are disposed in a valve chamber formed inside a valve casing,
The first valve body and the second valve body are disposed so as to be relatively slidable in the axial direction in the valve chamber,
Between the first valve body and the second valve body, a seal member is disposed to be held by the second valve body,
The first valve body includes a shaft that forms a relative sliding portion with the second valve body, and a flange that contacts and separates from the seal member,
A spring receiving member is fitted and fixed to the shaft. Between the spring receiving member and the second valve body, the second valve body springs in the flange position direction of the first valve body. A spring is arranged as a biased relationship,
The fluid control valve, wherein the shaft of the first valve body is formed in a hollow shape. The fluid control valve according to claim 1,
The spring receiving member includes a first tube portion that is a fitting portion with the first valve body, and a second tube portion that is a guide portion of a spring that is radially separated from the first tube portion. And a fluid control comprising: a connecting portion that connects one end portions of the two tubular portions; and a flange portion that is a seat portion of a spring formed by bending and extending the other end portion of the second tubular portion. valve.

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