JP2022138629A - flow control valve - Google Patents

Abstract

To reduce the influence of abnormal noise NVH (Noise Vibration Harshness) during duty ratio control of a second solenoid valve.SOLUTION: A flow control valve uses a housing in which an inflow passage, an outflow passage, an orifice throttle portion, a valve seat, and an inflow passage side throttle portion are coaxially arranged. Further, the flow control valve has a first valve element that is arranged on the outflow passage side of the valve seat and cooperates with the orifice throttle portion to control the flow volume of fluid, and a second valve element that is arranged on a passage chamber side of the valve seat, contacts with and separates from the valve seat to control the flow volume of the fluid, and a third valve element that is arranged on the inflow passage side of the valve seat and controls the flow volume of the fluid flowing into a passage chamber from the inflow passage. The first valve element and the third valve element can throttle the outflow passage side and the inflow passage side, respectively, by switching a first solenoid valve. Therefore, even if the second valve element is moved between a position where it closes the valve seat and a position where it opens the valve seat by the duty ratio control of a second solenoid valve, the influence of abnormal noise NVH associated with the movement can be reduced.SELECTED DRAWING: Figure 2

Description

The present disclosure relates to a flow control valve that controls the flow rate of a fluid, for example, it is arranged in a purge passage that communicates between a canister and an intake passage downstream of a throttle valve, and is used in a purge valve that controls the flow rate of air flowing through this purge passage. preferred.

With the hybridization of vehicles, there is a demand to allow the vaporized fuel adsorbed in the canister to flow into the intake passage of the engine (purging) in a shorter period of time. On the other hand, along with hybridization, the intake negative pressure of the engine at the time of purging is decreasing (approaching atmospheric pressure).

Therefore, as prior art in Patent Document 1, a first solenoid valve that switches between an ON position that greatly opens the purge passage and an OFF position that narrows the purge passage slightly, and a coil that contacts and separates the valve seat and the valve body. (Japanese Patent Application No. 2020-26491). The flow rate of the purge air is switched by the first solenoid valve, and the flow rate of the purge air is controlled by the second solenoid valve both when the flow rate is large and when the flow rate is small.

However, if the valve seat and the second valve body repeatedly contact and disengage due to the duty ratio control of the second solenoid valve, there is a risk of generating an abnormal noise NVH (Noise Vibration Harshness). It is also transmitted to the intake passage side of the engine.

JP 2008-291916 A

The present disclosure has been made in view of the above points, and an object of the present disclosure is to reduce the influence of abnormal noise NVH during duty ratio control of the second solenoid valve.

A first aspect of the present disclosure is an inflow passage for inflowing fluid, an outflow passage communicating with the intake passage side and outflowing fluid, a passage chamber formed between the outflow passage and the inflow passage, and the passage chamber. an orifice restrictor formed on the outflow passage side to limit the flow rate of fluid; a valve seat formed in the passage chamber; A housing is used in which an outflow passage, an outflow passage, an orifice throttle portion, a valve seat, and an inflow passage side throttle portion are coaxially arranged.

A first aspect of the present disclosure includes a first valve body disposed on the outflow passage side of the valve seat and configured to cooperate with the orifice restrictor to control the flow rate of fluid; and a third valve body arranged on the inflow passage side of the valve seat and controlling the flow rate of fluid flowing into the passage chamber from the inflow passage.

A first aspect of the present disclosure is a first coil that is excited by energization, a first stator core that forms a magnetic circuit when the first coil is energized, and a first coil that is arranged to face the first stator core with a magnetic gap interposed therebetween. and a first moving core that moves due to the excitation of the coil and transmits the displacement accompanying the movement to the first valve body and the third valve body via the rod, and the on position when the first coil is energized and the first coil is non-discharged. A first solenoid valve is used for switching between the off position and the energized state.

The first aspect of the present disclosure is a second coil that is excited by energization, and is arranged to face the second stator core with a magnetic gap interposed therebetween. It has a second moving core for transmission, and is used with a second electromagnetic valve that performs duty ratio control when the second coil is energized and when the second coil is not energized.

In addition, the first aspect of the present disclosure includes a diaphragm arranged in the passage chamber of the housing and providing non-communication between the inflow passage and the outflow passage when the second valve body is in contact with the valve seat. . In addition, the second valve body is provided with a communication hole through which the lot of the first solenoid valve passes.

In the first aspect of the present disclosure, the first valve body is arranged closer to the outflow passage than the second valve body that contacts the valve seat, and the third valve body is arranged closer to the inflow passage than the second valve body. By switching one solenoid valve, the outflow passage side and the inflow passage side can be throttled by the first valve element and the third valve element, respectively. Therefore, even if the second valve element moves between the position where the valve seat is closed and the position where the valve seat is opened by the duty ratio control of the second solenoid valve, the influence of abnormal noise NVH accompanying the movement can be reduced.

In particular, since the first valve body and the third valve body are arranged opposite to each other with the second valve body interposed therebetween, the transition between the ON position and the OFF position of the first solenoid valve is controlled by the first valve body via the lot. It is transmitted to both the second valve body. Therefore, the second valve body is provided with a communication hole through which the lot is passed. In addition, the inflow passage and the outflow passage are not separated from each other while the second valve body is in contact with the valve seat so that the second valve body can connect and disconnect the fluid even if the communication hole is provided. A communicating diaphragm is disposed in the passage chamber of the housing.

In a second aspect of the present disclosure, the first valve body includes a valve body throttle portion that cooperates with the orifice throttle portion to control the fluid flow rate, and a valve body passage portion that allows the fluid to flow. When the first solenoid valve is in the ON position, the first valve body is separated from the orifice throttle section, and the fluid flows through the outer periphery of the valve body throttle section and the valve body passage, and the first solenoid valve is closed. When the first valve body is in the OFF position, the valve body restricting portion of the first valve body contacts the orifice restricting portion, and the fluid flows through the valve body passage portion.

According to the second aspect of the present disclosure, it is possible to switch the flow rate to a small flow rate when the first solenoid valve is in the ON position and the second solenoid valve is in the OFF position.

According to a third aspect of the present disclosure, the first valve body includes a valve body throttle portion that cooperates with the orifice throttle portion to control the fluid flow rate. Then, when the first solenoid valve is in the ON position, the first valve disc throttle portion separates from the orifice throttle portion, and a large amount of fluid flows around the valve disc throttle portion, and the first solenoid valve is in the OFF position. At one time, the first valve body has a configuration in which the valve body restricting portion approaches the orifice restricting portion and the fluid flows at a small flow rate around the outer periphery of the valve body restricting portion.

According to the third aspect of the present disclosure, it is possible to switch between a large flow rate and a small flow rate with the first electromagnetic valve without providing a valve body passage portion in the first valve body, and the configuration of the first valve body is simplified. can be made.

In the fourth aspect of the present disclosure, both the first solenoid valve and the second solenoid valve are arranged on the inflow passage side of the passage chamber. The first solenoid valve and the second solenoid valve can be arranged in an overlapping manner.

In a fifth aspect of the present disclosure, the first solenoid valve is arranged on the outflow passage side of the passage chamber, and the second solenoid valve is arranged on the inflow passage side of the passage chamber. It is possible to increase the degree of freedom of the arrangement position of the first solenoid valve.

According to a sixth aspect of the present disclosure, the valve seat is formed in a ring shape on the inner periphery of the orifice narrowed portion in the passage chamber, and a flow path is formed on the outer periphery of the valve seat to allow the fluid in the passage chamber to flow to the orifice narrowed portion. , the rod is arranged on the inner circumference of the valve seat, and the diaphragm is arranged between the inner circumference of the valve seat and the rod. With the diaphragm, it is possible to ensure a seal with the second valve body seated on the valve seat while allowing the change of the lot. Moreover, since the diaphragm is in contact with the lot, movement of the lot is stabilized.

A seventh aspect of the present disclosure is that the valve seat is configured by a member separate from the orifice restricting portion so as to face the orifice restricting portion, and is connected to the rod of the first solenoid valve to move one moving core of the first solenoid valve. Accordingly, the position is displaced together with the first valve body and the third valve body. Moreover, the valve seat has a disc shape that closes the communication hole of the second valve body.

In the seventh aspect of the present disclosure, it is possible to vary the stroke of the second valve body by displacing the position of the valve seat. When controlling a small flow rate, the stroke of the second valve body can be reduced, and when controlling a large flow rate, the stroke of the second valve body can be increased. Further, since the valve seat is disk-shaped, the valve seat itself can block the fluid flow when the second valve body is seated.

In an eighth aspect of the present disclosure, the diaphragm is arranged on the outer peripheral side of the second valve body so as to close the passage chamber. Fluid leakage from the second solenoid valve can be prevented.

1 is a block diagram illustrating a purge system in which flow control valves of the present disclosure are used; FIG. 1 is a cross-sectional view of a flow control valve according to a first embodiment of the present disclosure; FIG. 3 is a cross-sectional view taken along line III-III of FIG. 2; FIG. FIG. 3 is a cross-sectional view of the flow control valve shown in FIG. 2 in a large flow rate state; FIG. 4 is a cross-sectional view of the flow control valve of the second embodiment of the present disclosure; FIG. 6 is a sectional view of the flow control valve shown in FIG. 5 in a large flow rate state; FIG. 10 is a cross-sectional view of a flow control valve according to a third embodiment of the present disclosure; FIG. 8 is a cross-sectional view of the flow control valve shown in FIG. 7 in a large flow rate state; FIG. 11 is a cross-sectional view of a flow control valve according to a fourth embodiment of the present disclosure; FIG. 10 is a cross-sectional view of the flow control valve shown in FIG. 9 in a large flow rate state;

FIG. 1 illustrates the use of the flow control valve of the present disclosure when used as a purge valve 100 . Purge air containing gasoline volatilized in the fuel tank 10 flows into the canister 13 through the inlet-side purge air passage 11 and the canister 13 adsorbs the gasoline. Purge air containing gasoline from the canister 13 is supplied to the intake pipe 21 of the engine 20 through the outlet side purge air passage 14 . A purge valve 100 controls the flow rate of the purge air flowing through the outlet side purge air passage 14 .

The outlet side purge air passage 14 opens downstream of the throttle valve 25 in the intake pipe 21, and the purge air containing gasoline from the canister 13 is sucked by the negative pressure of the intake air throttled by the throttle valve 25. . The canister 13 is provided with an atmosphere release valve 12 for opening to the atmosphere as required. An air filter 24 removes foreign matter from the air taken into the engine 20 .

On/off control and flow rate control of the purge valve 100 are controlled by the engine control unit 50 . That is, since the gasoline adsorbed in the canister 13 is sucked into the engine 20 together with the gasoline from the fuel tank 10, the engine control unit 50 calculates the optimum engine combustion state and controls the flow rate of the purge valve 100. In addition, the engine control unit 50 controls the on/off of the purge valve 100 in response to information from the vehicle ECU 60 that abnormal noise generated by the control of the purge valve 100 is unlikely to be transmitted to the occupant. For example, when the vehicle is running at high speed, abnormal noise is less likely to be transmitted to the occupants.

The configuration of purge valve 100 is described below with respect to each embodiment.

(First embodiment)
The first solenoid valve 130 includes a first coil 132 wound many times around a first bobbin 131 made of resin such as polybutylene terephthalate PBT. When a drive voltage is received from a connector (not shown) and the first coil 132 is energized, the first coil 132 is excited. A first yoke 133 made of iron is arranged outside the first coil 132 so as to form a magnetic circuit at that time, and a first stator core 134 made of iron is arranged inside the first coil 132 . .

The first stator core 134 has a cylindrical shape, and a cup-shaped first moving core 135 made of iron is movably arranged inside. Since the first stator core 134 is formed with a first narrowed portion 134a for narrowing the magnetic circuit, a first magnetic gap 134b is formed between the first stator core 134 and the first moving core 135, At the time of excitation, the first moving core 135 is attracted upward in the figure in order to reduce the first magnetic gap 134b. The first spring 136 biases the first moving core 135 in a direction opposite to the suction direction. The first spring 136 is arranged between the first moving core 135 and the first spring bearing member 137 .

The second solenoid valve 150 has approximately the same structure as the first solenoid valve 130 . A second bobbin 151 , a second coil 152 , a second yoke 153 , a second stator core 154 and a second moving core 155 are provided.

The second stator core 154 is also formed with a second narrowed portion 154 a for narrowing the magnetic circuit, and a second magnetic gap 154 b is formed between the second stator core 154 and the second moving core 155 . When the second coil 152 is excited, the second moving core 155 is attracted downward in the drawing so as to reduce the second magnetic gap 154b. A second spring 156 biases the second moving core 155 in a direction opposite to the suction direction. The second spring 156 is arranged between the second moving core 155 and the second spring bearing member 157 .

The housing 110 is made of resin such as polybutylene terephthalate PBT, and a passage chamber 160 is formed in the upper portion of FIG. The lower end of the housing 110 is closed by a bottom plate 111, and the bottom plate 111 is formed with an inflow passage 161 to which a hose forming the outlet side purge air passage 14 is connected. The housing 110 including the upper lid plate 112 and the lower bottom plate 111 has a cylindrical shape with a diameter of about 60 mm and a length of about 100 mm. The inflow passage 161 communicates with the passage chamber 160 via the central space 118 of the first solenoid valve 130 and the second solenoid valve 150 . In the passage chamber 160, a cylindrical orifice throttle portion 162 is formed so as to protrude so that the diameter of the intermediate portion is narrowed. A ring-shaped valve seat 163 is arranged at the lower end of the orifice throttle portion 162 in FIG. Although not shown in FIG. 2, the valve seat 163 and the orifice restrictor 162 are connected via an arm. The orifice narrowing portion 162 narrows the passage diameter of the purge air so as to work together with the first valve body 170, which will be described later, to narrow the flow of the purge air.

The orifice narrowed portion 162 communicates with the outflow passage 164 , and the purge air that has flowed into the passage chamber 160 from the inflow passage 161 flows from the outer periphery of the valve seat 163 to the outflow passage 164 via the orifice narrowed portion 162 . A hose forming the outlet side purge air passage 14 is connected to the outflow passage 164 , and the purge air is sucked from the outflow passage 164 through the hose downstream of the throttle valve 25 of the intake pipe 21 . The outflow passage 164, the orifice throttle portion 162, and the valve seat 163 are resin-molded integrally with the cover plate 112. As shown in FIG. The housing 110 has a cylindrical shape and is closed at both ends by being welded to a bottom plate 111 and a cover plate 112 .

The first valve body 170 has a cylindrical shape with a valve body passage portion 171 through which purge air passes. The valve body passage 171 has a cross-sectional area equivalent to a hole with a diameter of about 4 mm. 2 of the outer circumference of the first valve body 170 has a tapered shape that can be seated against the orifice throttle section 162, forming a valve body throttle section 174. As shown in FIG. The first valve body 170 is connected to the first moving core 135 of the first electromagnetic valve 130 via a lot 172 . More specifically, it is connected to the third valve body 190 connected to the first moving core 135 via the lot 172 . As shown in FIG. 3 , the rod 172 and the first valve body 170 are connected via an arm portion 173 . The rod 172 is made of resin or non-magnetic metal such as aluminum, is integrally formed with the first valve body 170, and has substantially the same length as the housing. Also, the diameter of the lot 172 is about 1 to 1.5 millimeters.

A second valve body 180 is arranged in a portion of the passage chamber 160 that faces the valve seat 163 . The second valve body 180 is baked and fixed to the second moving core 155 of the second solenoid valve 150, and is made of an elastic member such as a rubber material in order to obtain sealing performance with the valve seat 163. As shown in FIG. In the present disclosure, fluororubber is used in consideration of gasoline resistance. A communicating hole 185 is formed in the second valve body 180 , and the rod 172 passes through the communicating hole 185 . The communication hole 185 has a cross-sectional area equivalent to a hole with a diameter of about 5 millimeters.

A diaphragm 181 that seals the inner circumference of a ring-shaped valve seat 163 is arranged in the passage chamber 160 . The diaphragm 181 is made of flexible rubber material, and like the second valve body 180, fluorine rubber is used. The inner periphery 182 of the diaphragm 181 is bonded to the rod 172, and the outer periphery 183 is bonded to the valve seat 163 by adhesive or thermocompression. Then, the diaphragm 181 deforms according to the movement of the lot 172 . A second diaphragm 1811 closes the space between the two solenoid valve 150 and the passage chamber 160 of the housing 110 . The second diaphragm 1811 prevents purge air from leaking through the gap between the second stator core 154 and the second moving core 155 of the second electromagnetic valve 150 . The second diaphragm 1811 is also made of fluororubber like the diaphragm 181 . In the present disclosure, the second diaphragm 1811 is also included in the diaphragm that makes the inflow passage 161 and the outflow passage 164 non-communicating with the second valve body 180 in contact with the valve seat 163 .

In FIG. 2, a disc-shaped third valve body 190 made of a resin material such as polybutylene terephthalate PBT is attached to the lower end of the lot 172 . The third valve body 190 is fitted into the cylindrical inflow passage side throttle portion 113 formed in the bottom plate 111 with a gap therebetween when the first electromagnetic valve 130 is in the OFF position. This gap has a cross-sectional area equivalent to a hole with a diameter of about 2 millimeters.

Next, the operation of the purge valve 100 having the above configuration will be described. In the OFF position where the first coil 132 of the first electromagnetic valve 130 is not energized, the first coil 132 is not energized and the first moving core 135 is pulled away from the first stator core 134 by the first spring 136. energized. 2, the first moving core 135 is biased toward the bottom plate 111 of the housing 110 by the first spring 136. As shown in FIG. In this state, the outer circumference of the first valve body 170 is seated on the orifice throttle portion 162 . Therefore, the flow from the passage chamber 160 toward the outflow passage 164 is only through the valve element passage portion 171 of the first valve element 170 . Also, in this state, the third valve body 190 is fitted in the inflow passage side throttle portion 113 with a gap therebetween. Therefore, the purge air flowing into the housing 110 from the inflow passage 161 is restricted by the third valve body 190 and the inflow passage side throttle portion 113 .

Thus, as a result of the air flow path being throttled by both the first valve body 170 and the third valve body 190, the flow rate along which the purge valve 100 flows is small. In the present disclosure, the flow rate is about 60 liters per minute.

With this small flow rate, the flow rate of purge air flowing through the purge valve 100 is further controlled by the second valve body 180 . When the second coil 152 of the second solenoid valve 150 is excited, a magnetic attraction force is generated in the second magnetic gap 154b between the second stator core 154 and the second moving core 155, and this magnetic attraction force acts as the second spring. Since the biasing force of 156 is exceeded, the second moving core 155 moves to the second stator core 154 side. As a result, the second valve body 180 is separated from the valve seat 163 and the purge air in the passage chamber 160 flows into the valve body passage portion 171 of the first valve body 170 . The state of FIG. 2 is a state in which the second coil 152 is energized and the second valve body 180 opens the valve seat 163 .

When the second coil 152 is de-energized from the state shown in FIG. 2, the second moving core 155 is displaced upward in the drawing by the second spring 156 and the second valve body 180 contacts the valve seat 163 . As a result, the flow of purge air from passage chamber 160 to outflow passage 164 is blocked.

The second solenoid valve 150 performs duty ratio control between a fully open state in which the valve seat 163 is opened and a fully closed state in which the valve seat 163 is closed. A state where the duty ratio is 100% is the maximum flow rate when the flow rate is small, and the purge air flow is cut off when the duty ratio is 0%. The time for duty ratio control is about 10 hertz (0.1 seconds), and the ratio between the fully open state and the fully closed state is varied within this time.

The flow rate control of the purge valve 100 when the flow rate is small has been described above. As a result, the first coil 132 is excited, and an attractive force is generated in the first magnetic gap 134 b between the first stator core 134 and the first moving core 135 of the first electromagnetic valve 130 . This attractive force is greater than that of the first spring 136, and the first moving core 135 is pulled upward by about 3 mm as shown in FIG.

The movement of the first moving core 135 is transmitted to the third valve body 190 and also to the first valve body 170 via the lot 172 . Therefore, the first valve body 170 is separated from the orifice throttle portion 162 . As a result, the purge air that has passed through the valve seat 163 flows not only through the valve body passage portion 171 of the first valve body 170 but also through the valve body throttle portion 174 on the outer circumference of the first valve body 170 to flow into the outflow passage 164. becomes. At the same time, the third valve body 190 is further separated from the inflow passage side throttle portion 113, and the flow rate of the purge air flowing between the third valve body 190 and the inflow passage side throttle portion 113 increases. By moving both the first valve body 170 and the third valve body 190, a large amount of purge air can flow. In the present disclosure, purge air flows on the order of 200 liters per minute at high flow rates.

The flow rate of the purge air is controlled by the second solenoid valve 150 even in this state of high flow rate. The duty ratio control is performed in the same manner as the control at the time of small flow rate. That is, the second solenoid valve 150 performs duty ratio control between a fully open state in which the valve seat 163 is opened and a fully closed state in which the valve seat 163 is closed. At a duty ratio of 0%, purge air flow is blocked. FIG. 4 shows a fully open state in which the second solenoid valve 150 opens the valve seat 163 .

However, the control for interrupting the purge air flow is actually performed when the flow rate is small. Therefore, the minimum flow rate of purge air when a large flow rate is applied is not 0%, but the duty ratio is adjusted so that it is about 60 liters per minute, which is the same as the maximum flow rate of purge air when a small flow rate is applied. stipulate. In the present disclosure, the duty ratio is approximately 30%.

In the present disclosure, the control of the purge air flow rate is performed by duty ratio control of the second solenoid valve 150, regardless of whether the control is for a small flow rate or a large flow rate. Here, when the second valve body 180 performs duty ratio control between the fully open position and the fully closed position, the flow of the purge air is repeatedly circulated and blocked in short cycles. This circulation and blockage causes pulsation in the purge air flow.

The pulsation of the purge air is transmitted to the purge valve upstream passage 14A flowing from the canister 13 of the outlet side purge air passage 14 to the purge valve 100, and the purge valve downstream passage 14B flowing from the purge valve 100 to the intake passage 21 downstream of the throttle valve 25. Therefore, the purge air pulsates throughout the outlet-side purge air passage 14, causing noise NVH. Although the degree of abnormal noise NVH varies depending on various conditions, it may be about 60 decibels.

However, in the present disclosure, since both the first valve body 170 and the third valve body 190 narrow the flow path when the flow rate is small, the influence of noise NVH can be suppressed. That is, since the pulsating noise has a large effect on the upstream passage 14A, the effect of the pulsation on the purge valve upstream passage 14A on the canister 13 side is reduced by the cooperation of the third valve body 190 and the inflow passage side throttle portion 113. I am letting At the same time, the influence of pulsation on the purge valve downstream passage 14B on the side of the intake passage 21 is also reduced by the cooperation of the first valve body 170 and the orifice throttle portion 162 .

Even when the flow rate of the purge air is large, the third valve body 190 exists on the upstream side of the purge air. is ready. It is possible to halve the abnormal noise NVH, although it depends on various conditions.

Even if the communication hole 185 for passing the rod 172 is provided in the second valve body 180 , the sealing performance when the second valve body 180 comes into contact with the valve seat 163 is ensured by the diaphragm 181 . That is, the outer circumference of the diaphragm 181 is connected to the valve seat 163, and the inner circumference of the diaphragm 181 is connected to the rod 172. Therefore, when the second valve body 180 is seated on the valve seat 163, the passage chamber 160 and the passage chamber 160 are connected. A diaphragm 181 blocks the flow from the inflow passage 161 .

Here, the third valve body 190 is engaged with the first moving core 135 of the first solenoid valve 130 , and the position of the third valve body 190 is held by the first solenoid valve 130 . The rod 172 has its lower end fixed to the third valve body 190 and its upper end to which the first valve body 170 is attached via an arm portion 173 . Therefore, while the rod 172 is stable when the first valve body 170 is seated as shown in FIG. 2, the rod 172 is cantilevered when the first valve body 170 is removed as shown in FIG. However, in the present disclosure, the diaphragm 181 is joined to the lot 172 on the side of the first valve body 170 from the second valve body 180 in the lot 172, so the movement of the lot 172 is stable even if it is cantilevered. .

(Second embodiment)
In the first embodiment described above, the valve body passage portion 171 is formed in the first valve body 170, and the valve body throttle portion 174 has a shape that can be seated on the orifice throttle portion 162. A simple shape can also be used as in the second embodiment. The first valve body 170 of the second embodiment has a conical shape, and a valve body passage portion is not formed therein. The outer periphery forms the valve body throttle portion 174 , but does not come into contact with the orifice throttle portion 162 .

When the flow rate is low, as shown in FIG. 5, the first coil 132 of the first electromagnetic valve 130 is not energized and is in the OFF position. Therefore, the first moving core 135 is pushed downward by the first spring 136 and the third valve body 190 is held by the bottom plate 111 of the housing 110 . In this state, the third valve body 190 does not block the inflow passage 161 but partially contacts it, so that a small amount of purge air flows through the inflow passage side narrowed portion 113 . In addition, the conical first valve body 1703 also approaches the orifice throttle portion 162, and the flow path between the first valve body 170 and the orifice throttle portion 162 narrows. The gap between them is set so that the purge air flow rate is as small as about 60 liters per minute. In the present disclosure, the cross-sectional area of the gap is set to be approximately 7 square millimeters.

When the flow rate is large, as shown in FIG. 6, the first coil 132 of the first electromagnetic valve 130 is energized to the ON position. As a result, the first moving core 135 is pulled up toward the first stator core 134 side, and the first valve body 170 is also pushed upward through the lot 172 . As a result, the conical first valve body 170 is separated from the orifice throttle portion 162 , and a large flow of purge air flows between the first valve body 170 and the orifice throttle portion 162 . The third valve body 190 is also lifted in the same manner, and a large flow of purge air can flow away from the inflow passage side throttle portion 113 . At this time, the gap between the first valve body 170 and the orifice throttle portion 162 and the gap between the third valve body 190 and the inflow passage side throttle portion 113 are set so as to provide a large flow rate of about 200 liters per minute. In the present disclosure, the cross-sectional area of the gap is set to be approximately 13 square millimeters.

Also in this second embodiment, in addition to the diaphragm 181 closing the space between the valve seat 163 and the lot 172 , the space between the second solenoid valve 150 and the passage chamber 160 of the housing 110 is also blocked by the second diaphragm 1811 . In the present disclosure, the second diaphragm 1811 may be included in the diaphragm that makes the inflow passage 161 and the outflow passage 164 non-communicating with the second valve body 180 in contact with the valve seat 163 . It is similar to the embodiment.

5 and 6 both show a state in which the second solenoid valve 150 is in an excited state and the second valve body 180 is in the fully open position. The duty ratio control of the second solenoid valve 150 is the same as in the first embodiment.

(Third embodiment)
In the above-described embodiments, the first solenoid valve 130 and the second solenoid valve 150 are arranged in one housing 110 and are arranged on the same side with respect to the passage chamber 160 . In the third embodiment, as shown in FIGS. 7 and 8, the housing 110 is separated into a first housing 116 in which the first solenoid valve 130 is arranged and a second housing 115 in which the second solenoid valve 150 is arranged. , a connection housing 114 is interposed therebetween. The inflow passage 161 and passage chamber 160 are formed in the second housing 115 , and the outflow passage 164 is formed in the first housing 116 .

A diaphragm 181 is provided to prevent communication between the inflow passage 161 and the outflow passage 164 through the communication hole 185 of the second valve body 180 through which the lot 172 passes, as in the above-described embodiment. As in the second embodiment, the second diaphragm 1811 prevents purge air from leaking from the gap between the second stator core 154 and the second moving core 155 of the second solenoid valve 150 .

FIG. 7 shows the low flow rate state of the OFF position in which the first coil 132 of the first solenoid valve 130 is de-energized. In this state, the first moving core 135 is pushed downward in the figure by the biasing force of the first spring 136 , and the outer peripheral valve body throttle portion 174 of the first valve body 170 is seated on the orifice throttle portion 162 . there is Therefore, the purge air flows only through the valve body passage portion 171 of the first valve body 170 . Further, when the first valve body 170 is seated, the third valve body 190 enters the inflow passage side throttle portion 113 to limit the flow rate of the purge air flowing in from the inflow passage 161 . The operation is similar to that of the first embodiment shown in FIG. 2, although the location of lot 172 is different.

FIG. 8 shows the high flow condition, in which the first solenoid valve 130 is in the ON position with the first coil 132 energized. As a result, the first moving core 135 is lifted upward in the figure by the magnetic attraction force generated in the first magnetic gap 134b, and the valve body throttle portion 174 on the outer periphery of the first valve body 170 and the valve body passage portion 171 both move. Purge air flows. In addition, the third valve body 190 is also pulled up, leaving the inflow passage side throttle portion 113, and a large flow of purge air flows.

7 and 8 both show a state in which the second valve element 180 is in the fully open position with the second solenoid valve 150 being excited. It is the same as the embodiment and the second embodiment.

(Fourth embodiment)
In the above-described embodiment, the valve seat 163 is fixed inside the orifice throttle portion 162 via the arm portion, but in this fourth embodiment, the valve seat 163 is fixed to the rod 172 . As shown in FIGS. 9 and 10, the valve seat 163 moves integrally with the first valve body 170 and the third valve body 190 as the first moving core 135 moves.

Therefore, in the OFF position of the first solenoid valve 130, which allows a small flow rate, as shown in FIG. is displaced to Therefore, the stroke A of the second valve body 180 at the OFF position is reduced. Since it is sufficient to control a small flow rate at the OFF position, even if the stroke A is small, the purge air flow rate can be sufficiently controlled. As a result of reducing the stroke A, the pulsation caused by the duty ratio control of the second solenoid valve 150 is also suppressed, and the noise NVH is also suppressed. In particular, since the first valve body 170 restricts the outflow passage 164 side and the third valve body 190 restricts the inflow passage 161 side, the abnormal noise NVH suppressing effect is enhanced.

Conversely, when the first solenoid valve 130 is in the ON position where a large flow of purge air flows, as shown in FIG. is also pulled upwards in the figure. As a result, the stroke A between the second valve body 180 and the valve seat 163 also increases. Since the stroke A is increased, it becomes possible to flow a large amount of purge air.

In this fourth embodiment, since the valve seat 163 is fixed to the lot 172, the diaphragm 181 between the lot 172 is unnecessary. The second diaphragm 1811 takes charge of sealing when the second valve body 180 is in contact with the valve seat 163 . The second diaphragm 1811 is shaped to allow a large stroke A at the ON position where a large flow of purge air flows.

Although the valve seat 163 is integrally formed with the rod 172 in this fourth embodiment, the valve seat 163 is treated as one component of the housing 110 in the present disclosure. In other words, the disk-shaped valve seat 163 is arranged in the passage chamber 160 of the housing 110 and displaces its position within the passage chamber 160 according to the displacement of the rod 172 .

(Other embodiments)
The materials and sizes shown in the above disclosure are examples, and can be changed in various ways according to the required performance and the like. In the above disclosure, the second valve body 180 is baked and fixed to the second moving core 155 of the second solenoid valve 150, but a connecting member is interposed between the second moving core 155 and the second valve body 180. may

In addition, the purge valve 100 is a desirable example of use of the flow control valve of the present disclosure, but the present disclosure is widely used as a control valve capable of switching between a large flow rate and a small flow rate and capable of controlling both the large flow rate and the small flow rate. have a use.

100 Purge valve 110 Housing 130 First solenoid valve 150 Second solenoid valve 160 Passage chamber 161 Inflow passage 162 Orifice throttle portion 163 Valve seat 164 Outflow passage 170 First valve body 180 Second valve body 190 Third valve body 185 Communication hole

Claims (8)

An inflow passage for inflowing fluid, an outflow passage for outflowing fluid, a passage chamber formed between the outflow passage and the inflow passage, and a passage chamber formed on the outflow passage side of the passage chamber to limit the flow rate of the fluid. An orifice throttle portion, a valve seat arranged in the passage chamber, and an inflow passage side throttle portion formed on the inflow passage side of the valve seat to limit the flow rate of fluid, wherein the inflow passage, the outflow passage, the a housing in which the orifice throttle portion, the valve seat, and the inflow passage side throttle portion are coaxially arranged;
a first valve body disposed closer to the outflow passage than the valve seat, and cooperating with the orifice restrictor to control the flow rate of fluid flowing out of the passage chamber into the outflow passage;
a second valve body disposed on the passage chamber side of the valve seat and configured to come into contact with and separate from the valve seat to control a fluid flow rate;
a third valve body arranged on the inflow passage side of the valve seat and controlling the flow rate of fluid flowing into the passage chamber from the inflow passage in cooperation with the inflow passage side throttle portion;
a first coil that is excited by energization; a first stator core that forms a magnetic circuit when the first coil is energized; a first moving core that transmits the displacement associated with the first valve body and the third valve body through a rod, the on position when the first coil is energized and the off position when the first coil is not energized; a first solenoid valve for switching between positions;
a second coil that is excited by energization; and a second moving core that is opposed to the second stator core with a magnetic gap therebetween and moves by the excitation of the second coil and transmits the displacement associated with the movement to the second valve body. a second solenoid valve that performs duty ratio control when the second coil is energized and when the second coil is not energized;
a diaphragm disposed in the passage chamber of the housing, wherein the inflow passage and the outflow passage are not communicated with each other when the second valve body is in contact with the valve seat;
A flow control valve, wherein a communication hole through which the rod of the first solenoid valve passes is formed inside the second valve body. The first valve body includes a valve body throttling portion that cooperates with the orifice throttling portion to control a fluid flow rate, and a valve body passage portion that allows the fluid to pass through,
When the first solenoid valve is in the ON position, the first valve body has the valve body restricting portion separated from the orifice restricting portion and the fluid flows through the outer circumference of the valve body restricting portion and the valve body passage,
2. When said first solenoid valve is in said OFF position, said first valve body is characterized in that said valve body restricting portion contacts said orifice restricting portion and fluid flows through said valve body passage portion. The flow control valve described in . The first valve body includes a valve body throttle section that cooperates with the orifice throttle section to control a fluid flow rate,
when the first solenoid valve is in the ON position, the first valve body has the valve body restricting portion separated from the orifice restricting portion and a large amount of fluid flows along the outer periphery of the valve body restricting portion;
When the first solenoid valve is in the off position, the first valve body is characterized in that the valve body restricting portion approaches the orifice restricting portion, and a small amount of fluid flows around the outer periphery of the valve body restricting portion. The flow control valve according to claim 1. The flow control valve according to any one of claims 1 to 3, wherein both the first solenoid valve and the second solenoid valve are arranged on the inflow passage side of the passage chamber. The first solenoid valve is arranged on the outflow passage side of the passage chamber,
The second electromagnetic valve is arranged on the inflow passage side of the passage chamber.
4. The flow control valve according to any one of claims 1 to 3, characterized in that: The valve seat is formed in a ring shape on the inner circumference of the orifice narrowed portion in the passage chamber, and a flow path is formed on the outer circumference of the valve seat to allow the fluid in the passage chamber to flow to the orifice narrowed portion, The rod is arranged on the inner periphery of the valve seat,
The flow control valve according to any one of claims 1 to 5, wherein the diaphragm is arranged between the inner periphery of the valve seat and the lot. The valve seat faces the orifice restricting portion and is composed of a member separate from the orifice restricting portion,
The valve seat is connected to the rod of the first solenoid valve and displaces its position together with the first valve body and the third valve body according to the movement of the first moving core of the first solenoid valve. ,
The flow control valve according to any one of claims 1 to 5, wherein the valve seat has a disk shape that closes the communication hole of the second valve body. The flow control valve according to any one of claims 1 to 7, wherein the diaphragm is arranged on the outer peripheral side of the second valve body so as to close the passage chamber.

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