JP7009313B2 - Fluid control valve - Google Patents

Description

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

Vehicles such as automobiles are equipped with an evaporative fuel treatment device in the fuel supply path from the fuel tank to the engine. A fluid control valve is used in this evaporative fuel processing device. This fluid control valve is also commonly referred to as a shutoff valve. The fluid control valve referred to as a shutoff valve has an electric valve and a relief valve (see Patent Document 1 below).

In the fluid control valve used in the evaporative fuel treatment device, the motorized valve and the relief valve are arranged in combination in the same valve casing. The motorized valve is arranged in the main passage of the evaporative fuel processing device, and opens and closes the flow path of the main passage. The relief valve is arranged in the bypass passage with respect to the main passage, and is designed to bypass and avoid the abnormal pressure state of the main passage in the state of being closed by the electric valve.

Therefore, the relief valve has a positive pressure relief valve mechanism that opens when the pressure in the main passage (inside the gasoline tank) is equal to or higher than the predetermined abnormal positive pressure value, and the relief valve has a positive pressure relief valve mechanism in which the pressure in the main passage is equal to or lower than the predetermined abnormal negative pressure value. It is equipped with a negative pressure relief valve mechanism that opens the valve in the case of.

The positive pressure relief valve mechanism has the following configuration. A valve chamber of a cylindrical relief valve is formed in the valve casing, and the valve body is arranged in the valve chamber so as to be movable in the axial direction. A seat body is arranged in the vicinity of the valve port, which is the inlet to the valve chamber on the inner surface of the valve chamber, and the flow path is opened and closed by the proximity separation between the valve body and the seat body.

In the positive pressure relief valve mechanism, a gap is formed between the inner cylinder surface of the tubular valve chamber and the outer peripheral portion of the valve body in the flow path at the time of valve opening, and this gap is used as the flow path. This gap becomes a flow path of the bypass passage, and the fluid flows.

In addition, the seat body disposed in the vicinity of the valve opening, which is the inflow port to the valve chamber, is arranged in an exposed state at the portion that is close to and separated from the valve body, but the other portions are valves that form the valve chamber. It is buried in the casing.

Japanese Unexamined Patent Publication No. 2016-121791

By the way, the flow path of the positive pressure relief valve mechanism in the above-mentioned relief valve is formed by the gap formed between the inner cylinder surface of the tubular valve chamber and the outer peripheral portion of the valve body. This gap may cause the valve body to be biased in one direction on the inner cylinder surface of the valve chamber. This bias changes along the inner peripheral surface due to the flow of fluid. This change in the bias of the valve body becomes a so-called rampage phenomenon of the valve body, and noise may be generated. Further, in the rampage phenomenon of the valve body, there is a problem that the valve body is tilted in the flow direction due to the existence of the gap which becomes the flow path, and the flow amount thereof changes. That is, there is a problem that the distribution control at the time of opening the positive pressure relief valve mechanism is not performed accurately.

Further, in the above-mentioned positive pressure relief valve mechanism, there is a problem that distribution control is not performed accurately due to the following phenomenon in the arrangement of the seat body on the valve casing. That is, in order to improve the sealing property with the valve body, the sheet body is embedded in the valve casing as a sheet body having good surface roughness and flatness by insert molding or the like. In this case, due to the difference in the coefficient of thermal expansion between the seat body and the valve casing, the two are separated from each other at the interface, and a minute gap is generated. Through this minute gap, the fluid leaks and circulates both when the valve is closed and when the valve is opened. Due to this leaked distribution, there is a problem that distribution control is not performed accurately.

As a measure to prevent the above-mentioned leakage and distribution, there is a method of applying a primer (seal material) to the sheet body to ensure adhesion before insert molding the sheet body. However, when this method is used, there is a problem of increasing the cost.

Therefore, the present invention was devised to solve the above-mentioned problems, and the problem to be solved by the present invention is to accurately control the flow of the fluid control valve.

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

The first invention of the present invention is a tubular valve chamber formed by a valve casing, a valve body arranged in the valve chamber, and a valve port serving as an inflow port to the valve chamber on the inner surface of the valve chamber. It is a fluid control valve provided with a seat body arranged in the vicinity and configured to open and close the flow path by the proximity separation of the valve body and the seat body, and the opening and closing of the flow path is the valve body. In the valve casing, the inner peripheral surface forming the tubular valve chamber has three or more ribs formed in the axial direction within at least 120 degree intervals. It is a fluid control valve which is formed of the above-mentioned rib and is arranged so that the valve body is slidably guided in the axial direction by the rib.

According to the first invention, ribs are formed on the inner peripheral surface of the valve chamber and are arranged in the axial direction between the inner peripheral surface of the tubular valve chamber and the outer peripheral portion of the valve body. The ribs are formed at three or more locations in the circumferential direction and at least within an interval of 120 degrees. Due to the arrangement of the ribs, a gap serving as a flow path is uniformly formed over the entire circumferential direction between the inner peripheral surface of the valve chamber and the outer peripheral portion of the valve body. Further, since the outer peripheral portion of the valve body slides and moves in the axial direction along the rib formed in the axial direction, it is possible to prevent the valve body from being biased or violent or tilting during valve opening flow. Will be done. As a result, the fluid always flows evenly through the flow path in this gap, so that the flow control is performed with high accuracy. In addition, noise generated by rampage can be prevented or suppressed.

The second invention of the present invention is the fluid control valve of the first invention described above, wherein the seat body and the valve casing are made of different materials having different thermal expansion rates, and the seat body and the valve casing are described. At the interface of the housing, there is a part where the two are in contact with each other due to the difference in thermal expansion rate during the first temperature state to seal, and the two are in a second temperature state different from the first temperature state. It is a fluid control valve in which the parts that are in contact with each other due to the difference in thermal expansion rate and the parts to be sealed are set separately.

According to the second invention, the seat body and the valve casing are made of different materials having different thermal expansion rates. Then, by utilizing the difference in the thermal expansion rate of both members, for example, at the site where the two members are in contact with each other to seal in the first temperature state in the high temperature state, and between the two in the second temperature state in the low temperature state, for example. Is in contact and the part to be sealed is set separately. As a result, a part of the interface between the seat body and the valve casing is surely sealed in both the first temperature state and the second temperature state in different temperature states. Therefore, it is possible to prevent or suppress the leakage and circulation of the fluid through the interface between the two. As a result, the flow control of the fluid control valve can be accurately performed.

The third aspect of the present invention is the fluid control valve of the first invention or the second invention described above, wherein the valve casing is made of resin and the seat body is made of metal. ..

According to the third invention, the valve casing is made of resin and the sheet body is made of metal. Since the resin and the metal have different thermal expansion rates, the above-mentioned second invention can be appropriately carried out.

A fourth aspect of the present invention is the above-mentioned third fluid control valve, wherein the seat body has a washer-shaped flange portion which is a sealing surface with the valve body and an axial direction from the outer periphery of the flange portion. It has a first tubular portion extending along the above, and the first tubular portion is a fluid control valve embedded in the valve casing.

According to the fourth invention, the first tubular portion formed in the axial direction is provided, and the first tubular portion is embedded in the valve casing. As a result, the surface facing portion of the valve casing on either the inner peripheral surface side or the outer peripheral surface side of the first tubular portion becomes a portion where sealing is performed in the first temperature state or the second temperature state. Become. Therefore, it is possible to prevent or suppress fluid leakage that occurs through the interface between the valve casing and the sealing body in the first temperature state and the second temperature state.

A fifth aspect of the present invention is the fluid control valve of the fourth aspect described above, wherein the seat body further has a second tubular portion extending along the axial direction from the inner circumference of the flange portion. , A fluid control valve in which the outer peripheral surface of the second tubular portion is in contact with the valve casing.

According to the fifth aspect of the invention, a second tubular portion extending in the axial direction from the inner circumference of the flange portion in the fourth aspect of the invention is formed, and the outer peripheral surface thereof is in contact with the valve casing. As a result, the space between the outer peripheral surface of the second tubular portion and the facing surface of the valve casing also becomes a portion for sealing in the first temperature state or the second temperature state. Therefore, in addition to the above-mentioned fourth invention, fluid leakage generated through the above-mentioned interface can be prevented or suppressed.

The sixth invention of the present invention is the fluid control valve of the third invention described above, wherein the seat body has a washer-shaped first flange portion which is a sealing surface with the valve body, and the first flange portion. It is formed from a washer-shaped second flange portion axially separated from the flange portion of the above, and a connecting portion connecting the first flange portion and the second flange portion, and is formed from the first flange of the sheet body. It is a fluid control valve in which a part of the valve casing formed of resin is filled and formed between the portion and the second flange portion.

According to the sixth invention, in the seat body, the first flange portion, the second flange portion, and the connecting portion are formed in a U-shaped cross section, and a valve casing is formed between the U-shaped cross sections. It is composed of a resin to be filled. As a result, the space between the U-shaped cross-section sheet body and the facing surface of the resin filled between them is a part where sealing is performed in the first temperature state or a part where sealing is performed in the second temperature state. Become. Therefore, it is possible to prevent or suppress fluid leakage that occurs through the interface between the valve casing and the sealing body in the first temperature state and the second temperature state.

According to the above-mentioned means of the present invention, the flow control of the fluid control valve can be performed with high accuracy.

It is a block diagram which shows the evaporative fuel processing apparatus which concerns on embodiment of this invention. It is a perspective view which shows the appearance of the shutoff valve (fluid control valve) applied to the evaporative fuel processing apparatus. FIG. 2 is a cross-sectional view taken along the line III-III in FIG. FIG. 3 is a cross-sectional view taken along the line IV-IV of FIG. It is an enlarged sectional view which shows the main part of the electric valve which constitutes a shut-off valve. It is a perspective view which shows the main part of the electric valve by disassembling. It is an enlarged sectional view of the relief valve which constitutes a shut-off valve. It is a perspective view which shows the state which the rib is formed on the inner peripheral surface of the 2nd valve chamber. It is a top view which shows the arrangement interval of the ribs arranged in the 2nd valve chamber. It is a top view for demonstrating the action effect of a rib. It is a side view which shows the operating state of the 1st valve body. It is a top view which shows the operating state which the 1st valve body was biased to the left direction in the absence of a rib. It is a schematic diagram which shows the operating state in the state of FIG. 13 that the 1st valve body. It is a top view which shows the operating state which the 1st valve body was biased to the right direction in the absence of a rib. It is a schematic diagram which shows the operating state in the state of FIG. 14 that the 1st valve body. It is sectional drawing which shows the 1st embedded form of a valve seat (seat body). It is sectional drawing which shows the 2nd embedded form of a valve seat. It is sectional drawing which shows the 3rd embedded form of a valve seat. It is sectional drawing which shows the 4th embedded form of a valve seat. FIG. 16 is a half-cut perspective view of a single valve seat shown in FIG. It is sectional drawing which shows typically the operation state at the time of temperature rise in the 2nd embedded form of the valve seat shown in FIG. It is sectional drawing which shows typically the operation state at the time of temperature drop in the 2nd embedded form of the valve seat shown in FIG. It is sectional drawing which shows typically the operation state at the time of temperature rise in the 3rd embedded form of the valve seat shown in FIG. It is sectional drawing which shows typically the operation state at the time of temperature drop in the 3rd embedded form of the valve seat shown in FIG.

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 evaporative fuel processing device 12 mounted on a vehicle such as an automobile equipped with an internal combustion engine (engine) 14. The fluid control valve 38 as a sealing valve in the present embodiment includes an electric valve 52 and a relief valve 54. The relief valve 54 corresponds to the fluid control valve 38 in the present invention. Hereinafter, the configurations of the embodiments will be sequentially described.

<Structure explanation of evaporative fuel processing device 12>
First, the evaporative fuel processing apparatus 12 in which the fluid control valve 38 having the relief valve 54, which is the object of the present invention, is arranged will be described. FIG. 1 shows the configuration of the evaporative fuel processing device 12. The evaporative fuel processing device 12 is provided in the engine system 10 of a vehicle such as an automobile. The engine system 10 includes an engine 14 and a fuel tank 15 for storing 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 the fuel filler port at the upper end thereof, and a tank cap 17 is detachably attached to the fuel filler port. Further, the upper end portion of the inlet pipe 16 and the air layer portion in the fuel tank 15 in which the evaporated fuel exists are communicated with each other by the breather pipe 18.

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

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

In the air layer portion in the fuel tank 15, 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 of the vapor passage 31.

A block valve 38 is interposed in the middle of 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 arranged between the passage portions 31a and 31b. The sealing valve 38 of this embodiment corresponds to the fluid control valve of the present invention. The shutoff valve 38 includes an electric valve 52 and a relief valve 54. The motorized valve 52 adjusts the flow rate of a gas (referred to as “fluid”) containing evaporative fuel flowing through the vapor passage 31 by opening and closing the passage by electrical control. The motorized valve 52 is open / closed controlled by a drive signal output from an engine control device (hereinafter referred to as “ECU”) 45. Further, 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 keeping the pressure in the fuel tank 15 at an appropriate pressure when the electric valve 52 is closed. The details of these sealing valves (fluid control valves) 38 will be described later.

A purge valve 40 is interposed in the middle of the purge passage 32. The purge valve 40 is open / closed controlled, so-called purge controlled, with a valve opening amount according to the purge flow rate calculated by the ECU 45. Further, the purge valve 40 is provided with a stepping motor, for example, and the valve opening amount can be adjusted by controlling the stroke of the valve body. The purge valve 40 is a solenoid valve in the present embodiment, is provided with a solenoid solenoid, is closed in a non-energized state, and is opened by energization.

The canister 34 is provided with an atmospheric passage 42. The other end of the atmospheric passage 42 is open to the atmosphere. Further, an air filter 43 is interposed in the middle of the atmospheric passage 42.

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

(Explanation of operation of evaporative fuel processing device 12)
Next, the basic operation of the evaporative fuel processing apparatus 12 will be described.

<Operation explanation of evaporative fuel processing device 12-parking->
(1) First, [the vehicle is parked] will be described. While the vehicle is parked, the motorized valve 52 of the sealing valve 38 is maintained in the closed state. Therefore, the evaporated fuel of 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 electric valve 52 is closed, such as when the vehicle is parked, the pressure inside the fuel tank 15 is maintained at an appropriate pressure by the relief valve 54 (described later) of the closing valve 38.

<Explanation of operation of evaporative fuel processing device 12-running->
(2) Next, [while the vehicle is running] will be described. While the vehicle is running, the ECU 45 executes control to purge the evaporated fuel adsorbed on 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 purged into the intake passage 27 together with the air sucked from the atmospheric passage 42, and is burned by the engine 14. Further, the ECU 45 opens the electric valve 52 of the shutoff valve 38 only while purging the evaporated fuel. As a result, the tank internal pressure of the fuel tank 15 is maintained at a value near the atmospheric pressure.

<Operation explanation 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 electric 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. It is adsorbed by the adsorbent. This prevents the evaporated fuel from being released into the atmosphere. Along with this, the tank internal pressure of the fuel tank 15 drops to a value near the atmospheric pressure. Further, when the tank internal pressure of the fuel tank 15 drops to a value near the atmospheric pressure, the ECU 45 outputs a signal for releasing the lock of the lid 48 to the lid opener 47. When the lid opener 47 that receives the signal unlocks the lid 48, the lid 48 can be opened. Then, with the lid 48 opened and the tank cap 17 opened, refueling to the fuel tank 15 is started. Further, the ECU 45 keeps the motorized valve 52 of the shutoff valve 38 in the open state until the end of refueling (specifically, the lid 48 is closed). Therefore, at the time of refueling, the evaporated fuel in the fuel tank 15 is adsorbed on the adsorbent in the canister 34 through the vapor passage 31.

<Explanation of blocking valve (fluid control valve) 38>
Next, the sealing valve 38 will be described. FIG. 2 shows an external perspective view of the valve casing 56 forming the sealing valve 38. 3 and 4 are cross-sectional views showing the overall configuration of the block valve 38, FIG. 3 is a vertical cross-sectional view taken along the line lll-lll of FIG. 2, and FIG. 4 is a cross-sectional view taken along the line lV-lV of FIG. It is a cross-sectional view of. As shown in FIGS. 3 and 4, the shutoff valve 38 includes an electric valve 52 formed in the valve casing 56 and a relief valve 54. In the direction indication shown in each drawing showing the block valve 38, since the block valve 38 is usually installed under the floor of the vehicle, each direction is determined corresponding to the front-rear, left-right, up-down directions of the vehicle. , The arrangement direction of the sealing valve 38 is not specified.

<Explanation of valve casing 56 and main passage 74>
FIG. 2 shows the appearance of the valve casing 56 forming the sealing 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 sealing valve 38 are housed inside the valve casing 56. Therefore, the valve casing 56 has a first accommodating cylinder portion 60 for forming the electric valve 52 and a second accommodating cylinder portion 61 for forming the relief valve 54. Further, the valve casing 56 is provided with 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 forming a part of the vapor passage 31 (see FIG. 1) in the valve casing 56.

In the valve casing 56, the first pipe portion 57 and the second pipe portion 58 forming the main passage 74 are formed in a hollow circular tubular shape, the first pipe portion 57 is arranged in the front-rear direction, and the second pipe portion 58 is formed. Are arranged in the left-right direction.

Further, the valve casing 56 is formed with a bypass passage 90 as a passage that bypasses the main passage 74 (see FIG. 3). A relief valve 54 is arranged in the bypass path 90. Then, as shown in FIG. 3, the relief valve 54 and the electric valve 52 are communicated with each other by the communication passage 84 to form the bypass passage 90.

Further, 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 mounting portion 63 is integrally formed above the first accommodating cylinder portion 60 forming the motorized valve 52, and as shown in FIG. 4, the first accommodating cylinder It can be attached to the vehicle floor at the left and right sides of the portion 60. The mounting position is offset in the front-rear direction.

As shown in FIGS. 3 and 4, the diameter of the first accommodating cylinder portion 60 forming the motorized valve 52 is gradually increased from the front end portion of the first pipe portion 57 toward the front (same as above, to the left). It is formed in a stepped cylindrical shape. The first pipe portion 57 and the first accommodating cylinder portion 60 are formed concentrically. A valve chamber 65 of the motorized valve 52 is formed in the rear end portion of the first accommodating cylinder portion 60. This is referred to as the first valve chamber 65. The second pipe portion 58 is formed in a hollow circular tubular shape extending to the right (downward in FIG. 4) from the first valve chamber 65 of the first accommodating cylinder portion 60.

As shown in FIG. 3, the second accommodating cylinder portion 61 forming the valve chamber 67 of the relief valve 54 is formed in a bottomed cylindrical shape on the upper side of the front end portion of the first pipe portion 57. As can be seen from the illustrated state of FIG. 4, the second accommodating cylinder portion 61 has an outer diameter approximately twice the outer diameter of the first pipe portion 57. The axis center of the second accommodating cylinder portion 61 is located on the axis center line of the first pipe portion 57. That is, the second accommodating cylinder portion 61 is installed at a position directly above the first pipe portion 57. A valve chamber 67 of the relief valve 54 is formed in the second accommodating cylinder portion 61 (see FIG. 3). This valve chamber 67 is referred to 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 first pipe portion 57 and the second pipe portion 58 are formed to have the same pipe diameter or substantially the same pipe diameter. The insides of both pipe portions 57 and 58 communicate 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 the valve port 71 of the motorized valve 52. This valve port 71 is used as the first valve port. The first valve port 71 is formed with an inner diameter slightly smaller than the inner diameter of the first pipe portion 57. The rim of the first valve opening 71 is a valve seat 72. The inside of the first pipe portion 57 is a first passage portion 75 extending in the same direction as the axial direction of the first valve port 71. The inside of the second pipe portion 58 is on the side opposite 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-back direction) of the first passage portion 75. It is a second passage portion 76 extending along a direction different from that of the above, that is, to the right (lower side in FIG. 4). The elbow-shaped main passage 74 is formed by the first passage portion 75 and the second passage portion 76.

As shown in FIG. 3, stepped portions 78 for reducing the inner diameter are concentrically formed at the lower end portion of the second accommodating cylinder portion 61 forming the second valve chamber 67 of the relief valve 54. The hollow portion in the stepped portion 78 is a valve port 80 communicating with the second valve chamber 67 in the second accommodating cylinder portion 61. The valve port 80 of the relief valve 54 is used as the second valve port. The second valve port 80 communicates with the first passage portion 75 by penetrating the overlapping wall portion between the first pipe portion 57 and the second accommodating cylinder portion 61. Metallic ring plate-shaped valve seats 82 are concentrically arranged on the end surface (upper end surface) of the stepped portion 78 on the second valve chamber 67 side. The valve seat 82 is embedded and arranged in the stepped portion 78. The valve seat 82 forms the seat surface of the relief valve 54. As can be understood from the description of the 0th embodiment, the valve seat 82 of the present embodiment corresponds to the seat body of the present invention.

<Explanation of bypass passage 90>
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 passes through the second valve port 80 and the second valve chamber 67 of the relief valve 54 arranged by branching the first passage portion 75, and provides a communication passage 84 to the first valve chamber 65 of the motorized valve 52. It is formed by being connected via. That is, the bypass passage 90 is formed by bypassing the first valve port 71 of the motorized valve 52 in the path of the main passage 74. In the bypass passage 90, the electric valve 52 in the main passage 74 is in the closed state, and the abnormal positive pressure or negative pressure state in the fuel tank when the main passage 74 is in the shutoff state is transferred to the bypass passage 90. It is a passage that is released and adjusted by the control of the relief valve 54 provided.

<Structure explanation of motorized valve 52>
Next, the configuration of the motorized valve 52 will be described. FIG. 5 is an enlarged cross-sectional view of the motorized valve 52, and FIG. 6 is an exploded perspective view. As shown in FIG. 5, the motorized valve 52 is housed in the first storage tube 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. Note that FIG. 5 shows the valve open state of the motorized 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 accommodating 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 backward. The output shaft 93 is directed rearward and is concentrically arranged in the first valve chamber 65 of the first accommodating cylinder portion 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 cylinder wall portion 102 and an end wall portion 103 that closes the front end opening of the cylinder wall portion 102. At the front end of the cylinder wall 102, an overhanging portion 104 having a large outer diameter is formed in a stepped cylindrical shape. Cylindrical cylinder shaft portions 105 are concentrically formed in the central portion of the end wall portion 103. The front end opening of the cylinder shaft portion 105 is closed. As shown in FIG. 5, a female threaded portion 106 is formed on the inner peripheral surface of the tubular shaft portion 105.

The valve guide 94 is arranged so as to be movable in the axial direction, that is, in the front-rear direction with respect to the inside of the first valve chamber 65. The valve guide 94 is prevented from rotating in the axial direction with respect to the peripheral wall portion (first accommodating cylinder portion 60) of the first valve chamber 65 by a detent means (not shown). 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 threaded portion 106 of the tubular shaft portion 105 is screwed to the male threaded portion 100 of the output shaft 93 of the stepping motor 92. Therefore, the valve guide 94 is moved in the axial direction (front-back direction) based on the forward / reverse rotation of the output shaft 93. The feed screw mechanism 110 is configured by the male screw portion 100 of the output shaft 93 and the female screw 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 cylinder wall portion 102. The auxiliary spring 112 suppresses the backlash of the feed screw mechanism 110 by constantly urging the valve guide 94 forward. The rear end surface of the cylinder wall portion 102 faces the valve seat 72 so as to be in contact with the valve seat 72.

As shown in FIG. 6, the valve body 96 has a cylindrical tubular portion 114 and a valve plate portion 115 that closes the rear end opening of the tubular portion 114. An annular sealing 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 referred to as a first seal member.

As shown in FIG. 5, the valve body 96 is arranged concentrically and movably in the front-rear direction in the valve guide 94. The first seal member 117 faces the valve seat 72 so as to be in contact with the valve seat 72. Between the valve guide 94 and the valve body 96, a connecting means 120 for connecting both members 94 and 96 so as to be movable within a predetermined range in the axial direction (front-rear direction) is provided. As shown in FIG. 6, a plurality of sets (for example, four sets) of the connecting means 120 are arranged at equal intervals in the circumferential direction. The connecting means 120 is composed of an engaging projection 122 provided on the tubular portion 114 of the valve body 96 and an engaging groove 124 provided on the tubular wall portion 102 of the valve guide 94.

As shown in FIG. 6, the engaging 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 cylinder wall portion 102 of the valve guide 94. The groove forming wall 126 forms an engaging groove 124 that opens in the tubular 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 projection 122 is engaged in the engaging groove 124 from the opening 127 of the groove forming wall 126. As a result, the valve body 96 is movably connected to the valve guide 94 in the axial direction (front-back direction) with a predetermined amount of movement while the valve body 96 is stopped rotating in the circumferential direction.

As shown in FIGS. 5 and 6, the valve spring 98 is composed of 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 rearward, that is, in the closing direction with respect to the valve guide 94.

<Structure Description of Relief Valve 54-Embodiment of Valve Configuration Targeted by the Present Invention->
Next, the configuration of the relief valve 54 will be described. The present relief valve is an embodiment of a valve configuration indicating 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 a valve closed state for both the relief valve mechanisms 130 and 132. As shown in FIG. 7, the relief valve 54 is arranged 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 arranged concentrically and vertically in the second valve chamber 67 of the second accommodating cylinder portion 61. There is. Hereinafter, the valve member 134 of the positive pressure relief valve mechanism 130 will be the first valve body, and the valve member 136 of the negative pressure relief valve mechanism 132 will be the second valve body. The second valve chamber 67 in the present embodiment corresponds to the valve chamber of the present invention, and the first valve body 134 of the present embodiment corresponds to the valve body of the present invention.

The first valve body 134 of the positive pressure relief valve mechanism 130 has an annular plate-shaped valve plate 138 and an inner and outer double-cylindrical inner cylinder portion 139 and an outer cylinder portion 140 concentrically. .. 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 referred to as the first valve portion 141. The first valve portion 141 opens the second valve port 80 when it leaves the valve seat 82 upward, and closes the second valve port 80 by sitting on the valve seat 82 from that state.

The inner cylinder portion 139 and the outer cylinder portion 140 are erected on the valve plate 138. At the connection portion between the valve plate 138 and the inner cylinder portion 139, a plurality of communication holes 143 (two are shown in FIG. 7) penetrating the valve plate 138 in the vertical direction and penetrating the inner cylinder portion 139 in the radial direction are provided. It 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 portion of the first valve portion 141. The stopper piece 145 comes into contact with the valve seat 82 when the first valve body 134 is closed. Thereby, the valve closing position of the first valve body 134 is defined. The inner peripheral portion of the valve plate 138 is the valve seat 147 of the negative pressure relief valve mechanism 132.

A cap 150 and a retaining member 152 are arranged at the upper end opening of the second accommodating cylinder portion 61. The cap 150 is made of resin and is formed in a disk shape. The cap 150 closes the upper end opening of the second accommodating cylinder portion 61 by fitting. The retaining member 152 is made of resin and is formed in an annular shape. The retaining member 152 is joined to the upper end of the second accommodating cylinder 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 coming off by the retaining member 152.

The first coil spring 154 is concentrically arranged between the valve plate 138 of the first valve body 134 and the facing surface of the cap 150. The first coil spring 154 urges the first valve body 134 downward, that is, in the valve closing direction. The first coil spring 154 is fitted in the outer cylinder portion 140 of the first valve body 134.

The second valve body 136 has a disk-shaped flange 156 and a long-axis-shaped shaft 157 having a round cross section. The shaft 157 of the second valve body 136 is fitted into the inner cylinder portion 139 of the first valve body 134 from below. The flange 156 opens the communication hole 143 when it leaves the valve seat 147 of the first valve body 134 downward, and closes the communication hole 143 by sitting on the valve seat 147 from that state. A ring plate-shaped spring receiving member 159 is attached to the tip end portion (upper end portion) of the shaft 157. The spring receiving member 159 comes into contact with the inner cylinder portion 139 of the first valve body 134 when the second valve body 136 is opened. Thereby, the maximum valve opening amount of the second valve body 136 is defined.

The second coil spring 161 is concentrically arranged between the valve plate 138 of the first valve body 134 and the facing surface of the spring receiving member 159. The inner cylinder portion 139 of the first valve body 134 is arranged in the second coil spring 161. The second coil spring 161 urges the second 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 / outer double annular shape. The coil diameter, coil length, and coil wire diameter of the second coil spring 161 are set to be smaller than the coil diameter, coil length, and coil wire diameter of the first coil spring 154. Therefore, the urging force of the second coil spring 161 is smaller than the urging force of the first coil spring 154.

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

<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 first valve body 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, becomes a free state, and opens the valve.

<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 second valve body 136 descends against the urging 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 second valve body 136, becomes a free state, and opens the valve.

<Arrangement of blocking valve 38 and main passage 74, etc.>
The above-mentioned sealing valve 38 is interposed in the vapor passage 31 in the evaporative fuel processing device 12 (see FIG. 1) mounted on the vehicle (not shown). That is, as shown in FIGS. 3 and 4, the passage portion 31a 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. The passage portion 31b on the canister 34 side is connected. As a result, both passage portions 31a and 31b of the vapor passage 31 are communicated with each other via the main passage 74 of the valve casing 56. Therefore, the main passage 74 constitutes a part of the vapor passage 31. Further, as shown in FIG. 3, the mounting portion 63 of the valve casing 56 is fixed to the fixing side member 167 on the underfloor side of the vehicle by fastening bolts or the like. As a result, the sealing 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 arranged on the top side of the main passage 74 in the 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 motorized valve 52 in the sealing valve 38 will be described. The operation of the motorized 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 in a closed state (see FIG. 3).

<Valve open state of motorized valve 52>
First, the valve open state of the motorized valve 52 will be described. As shown in FIG. 5, in the valve open state of the motorized valve 52, the valve guide 94 and the valve body 96 (including the first seal member 117) are forward from the valve seat 72 of the first accommodating cylinder portion 60 (in FIG. 5). Up) away. 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. 6 is formed. The engagement protrusion 122 of the valve body 96 is in contact with the front end portion of the wall portion 126). Therefore, 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 the drive control of the stepping motor 92 by the ECU 45 (see FIG. 1). As a result, the valve body 96 is moved in the front-rear direction (vertical direction in FIG. 5) together with the valve guide 94, so that the valve opening amount (lift amount) of the valve body 96 is adjusted. Further, even if the energization of 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.

Then, in the valve open state of the motorized valve 52 described above, the main passage 74 formed in the valve casing 56 is in a communicating state. That is, 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 portion 31b connected to the passage portion 31b of the vapor passage 31 on the canister 34 side. It is in a state of communication with the main passage 74 of the pipe portion 57.

<Valve closure operation of motorized valve 52>
Next, the valve closing operation of the motorized valve 52 will be described. When the stepping motor 92 is closed in the valve open state (state of FIG. 5) of the motorized valve 52, 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 rearward movement of the valve body 96 is restricted. Subsequently, the valve guide 94 moves further backward. Along with this, 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 projection 122 of the valve body 96 shown in FIG. Therefore, the connection between the valve guide 94 and the valve body 96 by the connecting means 120 is released.

Then, when the cylinder 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 the valve closed state. After the cylinder wall portion 102 of the valve guide 94 comes into contact with the valve seat 72 of the valve casing 56, the stepping motor 92 is operated to open the valve by a predetermined amount so that the valve guide 94 is brought close to the valve seat 72. May be good.

<Valve closed state of motorized valve 52>
Next, the closed state of the motorized valve 52 will be described. In the closed state of the motorized valve 52, 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 urging force of the valve spring 98. Further, the valve body 96 and the valve seat 72 are elastically sealed by the first sealing member 117. Further, even if the energization of the stepping motor 92 is turned off in the valve closed state, the valve 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.

<Valve opening operation of the motorized valve 52>
Next, the valve opening operation of the motorized valve 52 will be described. When the stepping motor 92 is opened in the closed state of the motorized valve 52, the output shaft 93 is rotated in the valve opening direction. As a result, the valve guide 94 is moved forward (opening direction) via the feed screw mechanism 110. Along with this, the engagement groove 124 of the valve guide 94 moves upward along the engagement projection 122 of the valve body 96. Along with this, the valve spring 98 and the auxiliary spring 112 extend due to their elastic restoring force. Then, the groove bottom portion (front end portion of the groove forming wall portion 126) of the engaging groove 124 abuts on the engaging projection 122 of the valve body 96. As a result, the relative movement between the valve guide 94 and the valve body 96 is restricted. Therefore, 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 expands 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, so that the valve is opened (state in FIG. 5).

<Activation of relief valve 54>
Next, the operation of the relief valve 54 will be described with reference to FIG. 7. The valve opening operation of the positive pressure relief valve mechanism 130 and the valve opening operation of the negative pressure relief valve mechanism in the relief valve 54 are both performed in the closed state of the electric valve 52.

<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 equal to or 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 higher than the valve opening pressure is generated, the first valve body 134 moves upward as described above, the positive pressure relief valve mechanism 130 opens, and the second valve port 80 and the second valve chamber 67 Communicate. As a result, the bypass passage 90 is in a communicating state, and even if the first valve port 71 of the solenoid valve 52 in the main passage 74 is in the closed state and the main passage 74 is in the closed state, the bypass passage 90 is used. 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. As a result, 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 second valve body 136 descends to open the valve, the negative pressure relief valve mechanism 132 opens, and the second valve port 80 and the second valve port 80 and the second valve open. The valve chamber 67 communicates. As a result, the bypass passage 90 is in a communicating state, and even if the main passage 74 is blocked, the bypass passage 90 is in a communicating state, as in the case of opening the positive pressure relief valve mechanism 130. 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. As a result, the pressure in the fuel tank 15 can be increased.

<Characteristic configuration of this embodiment>
In the closed valve (fluid control valve) of the above-described embodiment, the configuration characterized by the present invention is incorporated in the relief valve 54. The contents will be described below.

<Characteristic configuration of the present embodiment-1; rib 180 formed in the second valve chamber 67>
As shown in FIGS. 8 and 9, the configuration characterized by this embodiment is such that the rib 180 is first formed on the inner peripheral surface 67A of the second valve chamber 67 of the relief valve 54 described above. FIG. 8 is a perspective view showing a state in which the rib 180 is formed on the inner peripheral surface 67A of the second valve chamber 67, and FIG. 9 is a top view showing the arrangement interval of the rib 180. As shown in FIG. 7, in the second valve chamber 67 of the relief valve 54, as described above, the cylindrical portion 150A of the resin cap 150 is fitted to the upper position in the resin second accommodating cylinder portion 61. Is formed. The outer peripheral portion of the first valve body 134 of the relief valve 54 is moved up and down within the range of the inner peripheral surface of the second accommodating cylinder portion 61 in the lower portion of the second valve chamber 67 in which the cylindrical portion 150A of the cap 150 is not arranged. It is designed to move. The vertical movement of the first valve body 134 causes the positive pressure relief valve mechanism 130 to open and close.

The rib 180 is formed on the inner peripheral surface 67A of the second valve chamber 67 within the range of vertical movement of the first valve body 134 described above. The formation state of the rib 180 is shown in FIGS. 8 and 9. The rib 180 is integrally formed with the second accommodating cylinder portion 61, and is made of resin. As shown in FIG. 9, the ribs 180 are arranged at equal intervals on the inner peripheral surface 67A of the second valve chamber 67. In this embodiment, eight ribs 180 are arranged at equal intervals of 45 degrees. As shown in FIG. 8, the rib 180 is formed in the axial direction of the second valve chamber 67. The axial direction in which the rib 180 is arranged is the same as the moving direction in which the first valve body 134 moves up and down.

The outer peripheral portion 134A of the first valve body 134 is configured to slide and move in the vertical direction along the rib 180 due to the arrangement of the rib 180 formed on the inner peripheral surface 67A of the second valve chamber 67 described above. .. Therefore, a gap is formed between the inner peripheral surface 67A of the second valve chamber 67 and the outer peripheral portion 134A of the first valve body 134 due to the presence of the rib 180. This gap serves as a flow path when the positive pressure relief valve mechanism 130 is opened, and the fluid flows through the gap. In the present embodiment, since the ribs 180 are evenly arranged at intervals of 45 degrees, the flow path is uniformly formed around the inner peripheral surface 67A of the second valve chamber 67. This is because if the number of ribs 180 is 3 or more and the distance between them is within 120 degrees, the gaps are evenly formed without biasing the first valve body 134.

<Action and effect by the characteristic configuration (No. 1) of this embodiment>
According to the configuration in which the rib 180 is provided on the inner peripheral surface 67A of the second valve chamber 67 described above, the positive pressure relief valve mechanism 130 can be opened and distributed without causing so-called rampage in the first valve body 134. can. Therefore, distribution control can be performed with high accuracy. 10 and 11 are diagrams schematically shown for explaining the action and effect of the feature configuration of the present embodiment. 10 is a top view, and FIG. 11 is a side view showing an operating state of the first valve body 134.

According to the characteristic configuration of the present embodiment as shown in FIG. 10, the ribs 180 evenly arranged on the inner peripheral surface 67A of the second valve chamber 67 allow distribution during valve opening distribution in the positive pressure relief valve mechanism 130. The gap is uniformly formed on the outer periphery of the first valve body 134. As a result, as shown in FIG. 11, when the fluid flows through the gap around the outer periphery of the first valve body 134, the first valve body 134 is vertically oriented in parallel along the rib 180 as indicated by a white arrow. Since it moves to, there is no bias. Therefore, the gaps on the outer circumference formed uniformly are uniformly distributed, and the distribution is performed with high accuracy. Further, according to the present embodiment, as will be described later, the violence of the first valve body 134 can be prevented or suppressed, so that the generation of noise associated therewith can also be prevented or suppressed.

FIGS. 12 to 15 are shown for comparison with the action and effect of the characteristic configuration of the present embodiment described above, and are the case of the configuration in which the ribs are not arranged as in the present embodiment. 12 and 13 show a case where the first valve body 134 is biased to the left and the right side of the first valve body 134 is tilted upward as seen in the figure. 14 and 15 show a case where the first valve body 134 is biased to the right and the left side of the first valve body 134 is tilted upward as seen in the figure.

In the states of FIGS. 12 and 13, the ribs are not arranged on the inner peripheral surface 67A of the second valve chamber 67, so that the first valve body 134 has a difference in the acting force that flows through the fluid flow gap. The state of moving to the left is shown (see FIG. 12). In this state, as shown in FIG. 13, the first valve body 134 is in a cantilever state with the left side as a fulcrum, and the right side is tilted upward as shown by a white arrow. In this state, as shown in FIGS. 12 and 13, the fluid flows only from the right side of the first valve body 134. Therefore, there is a problem that the distribution accuracy becomes unstable.

Contrary to the above, the states of FIGS. 14 and 15 show a state in which the first valve body 134 moves to the right due to a difference in the acting force or the like flowing through the flow gap of the fluid (see FIG. 14). In this state, as shown in FIG. 15, the first valve body 134 is in a cantilever state with the right side as a fulcrum, and the left side is tilted upward as shown by a white arrow. In this state, as shown in FIGS. 14 and 15, the fluid flows only from the left side of the first valve body 134. Therefore, there is a problem that the distribution accuracy becomes unstable.

The states of FIGS. 12 and 13 and the states of FIGS. 14 and 15 change along the circumference of the inner peripheral surface 67A of the second valve chamber 67 due to the acting force flowing through the flow gap of the fluid. .. This change occurs in the second valve chamber 67 as a rampage phenomenon of the first valve body 134, and causes a problem of generating noise.

<Characteristic configuration of the present embodiment-Part 2; Configuration of the valve seat (seat body) 82 in the relief valve 54 embedded in the valve casing 56>
As shown in FIG. 7, the following configuration characterized by the present embodiment is a valve of a valve seat 82 that constitutes a sealing portion for opening and closing the relief valve 54 with a first valve body 134 in the positive pressure relief valve mechanism 130. It is a configuration embedded in the casing 56. As described in the configuration of the relief valve 54 described above, the valve seat 82 is arranged at a position in the vicinity of the second valve port 80 which is the inflow port to the second valve chamber 67 on the inner surface of the second valve chamber 67. .. The valve seat 82 is embedded in the valve casing 56 and arranged. The valve casing 56 and the valve seat 82 are made of different materials having different thermal expansion rates. In this embodiment, the valve casing 56 is made of resin and the valve seat 82 is made of metal.

In the present embodiment, in the configuration in which the valve seat 82 is embedded in the valve casing 56, since both are formed of different materials, an interface is formed between the two members 82 and 56. At the interface between the two members 82 and 56, the interface between the two members 82 and 56 is in a sealed state at different temperature states due to the difference in the thermal expansion rate of the two members 82 and 56. It is said that.

For example, in the first temperature state of the high temperature state, the interface portion at the set position between the two members 82 and 56 is in a strong contact pressure state due to the difference in the thermal expansion rate, and the interface portion is in the sealed state. It is a buried structure that has a certain part. Then, in the second temperature state, which is different from the first temperature state, for example, in the low temperature state, the interface portion at the position separately set between the two members 82 and 56 has a strong contact pressure due to the difference in the thermal expansion rate. It is a buried structure having a portion where the interface portion is in a sealed state and is in a sealed state. In the following description, the portion to be sealed in the first temperature state in the high temperature state will be referred to as the H portion, and the portion to be sealed in the second temperature state in the low temperature state will be referred to as the C portion. In the present embodiment, the position of the interface portion where the H portion portion is set and the position of the interface portion where the C portion portion is set are different positions of the interface portion.

There are various forms of embedding the valve seat 82 in the valve casing 56 described above. The form will be described in sequence below.

First, the first buried form will be described. The first burial form is shown in FIG. This form is the same as the form of the configuration incorporated in the relief valve 54 shown in FIG. 7. FIG. 20 shows a half-cut perspective view of the valve seat 82 alone. As shown in FIG. 20, the valve seat 82 in this form has a U-shaped cross-sectional opening arranged downward, and has a washer-shaped flange portion 82A and a first tubular portion 82B. , It is composed of a second tubular portion 82C. The flange portion 82A is formed in the shape of a washer of a flat plate, and the upper surface thereof is a sealing surface with the first valve body 134. The first tubular portion 82B is formed by bending the outer peripheral side of the flange portion 82A downward and extending downward in the axial direction. The second tubular portion 82C is formed by bending the inner peripheral side of the flange portion 82A downward and extending downward in the axial direction. The flange portion 82A, the first tubular portion 82B, and the second tubular portion 82C are made of metal and are integrally formed by press molding.

As shown in FIG. 16, the valve seat 82 of the first embedded form is embedded in a resin valve casing 56. Specifically, only the lower surface portion 82Aa is embedded in the planar flange portion 82A. Both sides of the inner peripheral surface 82Ba and the outer peripheral surface 82Bb are embedded in the first tubular portion 82B arranged downward in the axial direction. Then, only the outer peripheral surface 82Cb is embedded in the second tubular portion 82C. Since the thermal expansion rate of the resin forming the valve casing 56 is larger than that of the metal forming the valve seat 82, the sealing portion in this form is as follows. That is, the inner peripheral surface 82Ba of the first tubular portion 82B is the H portion portion, and the outer peripheral surface 82Bb is the C portion portion. Further, the outer peripheral surface 82Cb of the second tubular portion 82C serves as a C portion.

Next, the second buried form will be described. The second buried form is shown in FIG. In the following description, the parts recognized as the same parts in the form of the valve seat 82 are designated by the same reference numerals, and the description thereof may be omitted. The valve seat 82 in the second embedded form has an L-shaped cross section, and is composed of a washer-shaped flange portion 82A and a third tubular portion 82D. The flange portion 82A is the same as the first embedded form described above, and is formed in the shape of a washer of a flat plate, and the upper surface thereof is a sealing surface with the first valve body 134. The third tubular portion 82D is arranged so that the outer peripheral side of the flange portion 82A is bent upward and extends upward in the axial direction. The flange portion 82A and the third tubular portion 82D are made of metal and are integrally formed by press molding.

The burying of the valve seat 82 in the resin valve casing 56 in the second burying form is as follows. Only the lower surface portion 82Aa is embedded in the planar flange portion 82A. Both sides of the inner peripheral surface 82Da and the outer peripheral surface 82Db are embedded in the third tubular portion 82D disposed upward in the axial direction. Then, the sealing portion of the interface in this second buried form is as follows. The inner peripheral surface 82Da of the third tubular portion 82D is the H portion portion, and the outer peripheral surface 82Db is the C portion portion.

Next, the third buried form will be described. The third buried form is shown in FIG. The valve seat 82 in the third embedded form has a crank-shaped cross section, and is composed of a washer-shaped flange portion 82A, a second tubular portion 82C, and a third tubular portion 82D. This third buried form is a combination of the first buried form and the second buried form described above. That is, the flange portion 82A is the same as the first and second embedded forms described above, and is formed in the shape of a washer of a flat plate, and the upper surface thereof is a sealing surface with the first valve body 134. The second tubular portion 82C is arranged so that the inner peripheral side of the flange portion 82A is bent downward and extends downward in the axial direction. The third tubular portion 82D is arranged so that the outer peripheral side of the flange portion 82A is bent upward and extends upward in the axial direction. The flange portion 82A, the second tubular portion 82C, and the third tubular portion 82D are made of metal and integrally formed by press molding.

The state of burying the valve seat 82 in the resin valve casing 56 in the third buried form is as follows: the flange portion 82A, the second tubular portion 82C, and the third tubular portion in the first and second buried forms described above. Same as 82D. Therefore, the sealing portion of the interface in this third buried form is as follows. The outer peripheral surface 82Bb of the second tubular portion 82C is the C portion portion, the inner peripheral surface 82Da of the third tubular portion 82D is the H portion portion, and the outer peripheral surface 82Db is the C portion portion.

Next, the fourth buried form will be described. The fourth buried form is shown in FIG. The valve seat 82 of the fourth embedded form is formed in a U-shaped cross section, and includes a first flange portion 82E, a second flange portion 82F, and a connection portion 82G. The first flange portion 82E is a portion corresponding to the flange portion 82A in the above-mentioned first buried form to the third buried form, and is formed in the shape of a washer of a flat plate, and the upper surface thereof is the first valve body 134. It is a sealing surface with. The second flange portion 82F is also formed in the shape of a washer of a flat plate, and is arranged in parallel with the first flange portion 82E, axially separated from the first flange portion 82E and downward as seen in FIG. There is. The connecting portion 82G is a portion that connects the inner peripheral portion of the first flange portion 82E and the inner peripheral portion of the second flange portion 82F, and is a second cylinder in the above-mentioned first buried form and the third buried form. It is a part corresponding to the part 82C.

The configuration of the valve seat 82 embedded in the resin valve casing 56 in the fourth embedded form is as follows. The resin forming the valve casing 56 is filled and embedded between the lower surface portion 82Ea of the first flange portion 82E and the upper surface portion 82Fb of the second flange portion 82F and in the lower surface portion 82F of the second flange portion 82F. Will be done. As a result, the sealing portion of the interface in this fourth buried form becomes as follows. The lower surface portion 82Ea of the first flange portion 82E is the H portion portion, the upper surface portion 82Fb of the second flange portion 82F is also the H portion portion, and the outer peripheral surface 82Gb of the connection portion 82G is the C portion portion.

<Action and effect by the characteristic configuration (No. 2) of this embodiment>
According to the characteristic configuration (No. 2) of the present embodiment described above, the valve seat 82 and the valve casing 56 use materials having different thermal expansion rates. As a result, when the temperature is different, for example, when the temperature rises or falls, the interface is sealed at different interface points (H site point or C site point) between the two members 82 and 56. That is, due to the difference in the thermal expansion rate, the contact pressure between the portion of the valve seat 82 and the portion of the valve casing 56 at the interface portion becomes stronger, and the flow of the fluid is sealed. As a result, the interface between the valve seat 82 and the valve casing 56 is sealed, and the fluid flow control in the positive pressure relief valve mechanism 130 is performed with high accuracy.

The above-mentioned action and effect will be described as typical examples of the case of the second buried form shown in FIG. 17 and the case of the third buried form shown in FIG. 21 and 22 are the case of the second buried form, and FIGS. 23 and 24 are the case of the third buried form. In any of the present embodiments, the valve seat 82 is made of metal and the valve casing 56 is made of resin. The thermal expansion rate and heat shrinkage rate of resin are larger than those of metal.

First, the case of the second buried form shown in FIGS. 21 and 22 will be described. FIG. 21 shows a case where the temperature rises, and FIG. 22 shows a case where the temperature drops. When the temperature rises in FIG. 21, the resin valve casing 56 has a larger thermal expansion rate than the metal valve seat 82, so that the valve seat 82 is radially outward in the third tubular portion 82D (FIG. 21). The expansion (extension) to the right (to the right) is larger in the expansion of the valve casing 56 around it than in the third tubular portion 82D, as shown by the arrow. Therefore, the interface between the inner peripheral surface 82Da of the third tubular portion 82D and the surface of the valve casing 56 facing the inner peripheral surface 82Da is in a contact state with a strong contact pressure and seals the flow of fluid. That is, the interface between the two is sealed. This state is the above-mentioned H site, which is one of the first temperature state and the second temperature state referred to in the present invention.

On the contrary, in the case of the temperature drop shown in FIG. 22, since the heat shrinkage rate of the resin valve casing 56 is larger than that of the metal valve seat 82, the radial direction of the third cylinder portion 82D of the valve seat 82 As for the inward contraction (to the left when viewed in FIG. 22), the contraction of the valve casing 56 around the third tubular portion 82D is larger as shown by the arrow. Therefore, the interface between the outer peripheral surface 82Db of the third tubular portion 82D and the surface of the valve casing 56 facing the outer peripheral surface 82Db is in a contact state with a strong contact pressure and seals the flow of fluid. That is, the interface between the two is sealed. This state is the C-point portion described above, and is the state of either the first temperature state or the second temperature state referred to in the present invention.

Next, the case of the third buried form shown in FIGS. 23 and 24 will be described. FIG. 23 shows the case where the temperature rises, and FIG. 24 shows the case where the temperature drops. The third tubular portion 82D of the valve seat 82 in the third embedded form has the same form as the third tubular portion 82D in the above-mentioned second buried form, and has the same effect and effect, so duplicate description will be omitted. Therefore, the second tubular portion 82C will be described. In the state at the time of temperature rise shown in FIG. 23, since the thermal expansion rate of the resin valve casing 56 is larger than that of the metal valve seat 82, the valve seat 82 is radially outward (outside) in the second tubular portion 82C. The expansion (extension) to the right (to the right when viewed in FIG. 23) is larger in the expansion of the valve casing 56 around the second tubular portion 82C as shown by the arrow. Therefore, it does not function as a seal.

On the contrary, in the case of the temperature drop shown in FIG. 24, since the heat shrinkage rate of the resin valve casing 56 is larger than that of the metal valve seat 82, the radial direction of the second cylinder portion 82C of the valve seat 82 As for the inward contraction (to the left when viewed in FIG. 24), the contraction of the valve casing 56 around the second tubular portion 82C is larger as shown by the arrow. Therefore, the interface between the outer peripheral surface 82Cb of the second tubular portion 82C and the surface of the valve casing 56 facing the outer peripheral surface 82Cb is in a contact state with a strong contact pressure and seals the flow of fluid. That is, the interface between the two is sealed. Therefore, in the third buried mode, the interface is sealed even in the second tubular portion 82C when the temperature drops. This state is the above-mentioned C portion, and is the state of either the first temperature state or the second temperature state referred to in the present invention.

<Effects of other configurations of this embodiment>
According to the sealing valve (fluid control valve) 38 of the present embodiment, the electric valve 52 and the relief valve 54 are arranged so that their axial directions are different from each other. That is, the motorized valve 52 and the relief valve 54 are arranged so that their axes are twisted to each other. Specifically, the motorized valve 52 is arranged so that the axial direction is the front-rear direction, and the relief valve 54 is arranged so that the axial direction is the vertical direction. As a result, the dimension of the relief valve 54 in the axial direction (vertical direction) can be shortened, and the sealing valve 38 can be made compact.

Further, the valve casing 56 is formed with a main passage 74 having a first valve port 71 and a bypass passage 90 having a second valve port 80. Therefore, the motorized valve 52 and the relief valve 54 can be integrated to make the sealing valve 38 compact.

<Modified example of the embodiment>
Although the present invention has been described above with respect to specific embodiments, the present invention can also be implemented in various other embodiments.

For example, the cross-sectional shape of the rib 180 formed on the inner peripheral surface 67A of the second valve chamber 67 may be a shape in which the first valve body 134 can be slidably moved in the axial direction, and is half as in the present embodiment. Not limited to a round shape.

Further, the number of ribs 180 to be arranged may be 3 or more, and the arrangement interval may be 120 degrees or less. The point is that the first valve body 134 may be arranged so as not to be biased. However, from the viewpoint of the balance of the arrangement configuration, it is preferable that the ribs 180 are evenly spaced.

Further, the form of embedding the valve seat 82 in the valve casing 56 may be such that the above-mentioned so-called H portion and C portion are formed at the interface of the constituent material due to the difference in the thermal expansion rate of the constituent material.

Further, the constituent materials of the valve seat 82 and the valve casing 56 are not limited to metal and resin, and both members may have different thermal expansion rates.

Further, the blocking valve (fluid control valve) 38 of the present embodiment is not limited to the evaporative fuel processing device 12, and may be applied to other necessary devices. Further, the motorized valve 52 and the relief valve 54 may be arranged so that their axial directions are different from each other, and the directions are not limited.

12 ... Evaporated fuel processing device 15 ... Fuel tank 31 ... Vapor passage 34 ... Canister 38 ... Seal valve (fluid control valve)
52 ... Electric valve 54 ... Relief valve 56 ... Valve casing 65 ... First valve chamber 67 ... Second valve chamber (valve chamber)
74 ... Main passage 80 ... Second valve port (valve port)
82 ... Valve seat (seat body)
82A ... Flange portion 82B ... First cylinder portion 82C ... Second cylinder portion 82D ... Third cylinder portion 82E ... First flange portion 82F ... Second flange portion 82G ... Connection portion 90 ... Bypass passage 130 ... Positive Pressure relief valve mechanism 132 ... Negative pressure relief valve mechanism 134 ... First valve body (valve body)
136 ... Second valve body 180 ... Rib

Claims (7)

A tubular valve chamber formed by the valve casing, a valve body arranged in the valve chamber, and a seat body arranged in the vicinity of the valve opening which is an inlet to the valve chamber on the inner surface of the valve chamber. A fluid control valve that is configured to open and close the flow path by the proximity separation between the valve body and the seat body.
The flow path is opened and closed by moving the valve body in the axial direction.
In the valve casing, on the inner peripheral surface forming the tubular valve chamber, three or more ribs formed in the axial direction are formed within at least 120 degree intervals, and the ribs cause the valve body to be shafted. It is arranged so that it slides and guides in the direction .
The seat body and the valve casing are made of different materials having different thermal expansion rates.
At the interface between the seat body and the valve casing, a portion where the two are in contact with each other due to a difference in thermal expansion rate during the first temperature state to perform sealing, and a second portion different from the first temperature state. A fluid control valve in which the two are in contact with each other due to the difference in thermal expansion rate when the temperature is in the above state, and the parts to be sealed are set separately . The fluid control valve according to claim 1.
A fluid control valve in which the valve casing is made of resin and the seat body is made of metal . The fluid control valve according to claim 2 .
The sheet body has a washer-shaped flange portion that is a sealing surface with the valve body, and a first tubular portion extending along the axial direction from the outer periphery of the flange portion, and the first tubular portion is the said. A fluid control valve embedded in the valve casing . The fluid control valve according to claim 3 .
The seat body further has a second tubular portion extending along the axial direction from the inner circumference of the flange portion, and the outer peripheral surface of the second tubular portion is in contact with the valve casing . The fluid control valve according to claim 2 .
The sheet body has a washer-shaped first flange portion which is a sealing surface with the valve body, a washer-shaped second flange portion axially separated from the first flange portion, and the first flange portion. It is formed from a connecting part that connects the flange part and the second flange part.
A fluid control valve in which a part of the valve casing formed of resin is filled and formed between a first flange portion and a second flange portion of the seat body . A tubular valve chamber formed by the valve casing, a valve body arranged in the valve chamber, and a seat body arranged in the vicinity of the valve opening which is an inlet to the valve chamber on the inner surface of the valve chamber. A fluid control valve that is configured to open and close the flow path by the proximity separation between the valve body and the seat body.
The flow path is opened and closed by moving the valve body in the axial direction.
In the valve casing, on the inner peripheral surface forming the tubular valve chamber, three or more ribs formed in the axial direction are formed within at least 120 degree intervals, and the ribs cause the valve body to be shafted. It is arranged so that it slides and guides in the direction.
The valve casing is made of resin, and the seat body is made of metal .
The sheet body has a washer-shaped flange portion that is a sealing surface with the valve body, and a first tubular portion extending along the axial direction from the outer periphery of the flange portion, and the first tubular portion is the said. A fluid control valve embedded in the valve casing. A tubular valve chamber formed by the valve casing, a valve body arranged in the valve chamber, and a seat body arranged in the vicinity of the valve opening which is an inlet to the valve chamber on the inner surface of the valve chamber. A fluid control valve that is configured to open and close the flow path by the proximity separation between the valve body and the seat body.
The flow path is opened and closed by moving the valve body in the axial direction.
In the valve casing, on the inner peripheral surface forming the tubular valve chamber, three or more ribs formed in the axial direction are formed within at least 120 degree intervals, and the ribs cause the valve body to be shafted. It is arranged so that it slides and guides in the direction.
The valve casing is made of resin, and the seat body is made of metal.
The sheet body has a washer-shaped first flange portion which is a sealing surface with the valve body, a washer-shaped second flange portion axially separated from the first flange portion, and the first flange portion. It is formed from a connecting part that connects the flange part and the second flange part.
A fluid control valve in which a part of the valve casing formed of resin is filled and formed between a first flange portion and a second flange portion of the seat body.

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