JP2021038738A - Purge control valve device - Google Patents

Abstract

To provide a purge control valve device capable of improving flow characteristics.SOLUTION: A purge valve 3 includes a first solenoid valve 34 and a second solenoid valve 35 inside of a housing. The first solenoid valve 34 has a first valve element 34b controlling a flow rate of an evaporated fuel flowing down in an upstream-side passage in the housing. The second solenoid valve 35 has a second valve element 35b for controlling a flow rate of an evaporated fuel flowing down in a downstream-side passage in the housing. The upstream-side passage and the downstream-side passage are disposed in series in a housing internal passage. The first solenoid valve 34 switches a seated state and a separated state with respect to the first valve element 34b. The purge valve 3 has a throttle passage 31c1 to make the flow rate of the evaporated fuel flowing down in the separated state, smaller than the flow rate of the evaporated fuel flowing down in the seated state.SELECTED DRAWING: Figure 2

Description

The disclosure herein relates to a purge control valve device.

Due to the low negative pressure of the engine due to the fuel efficiency of the engine and the reduction of the operating time of the engine of hybrid vehicles, there is a demand for a purge valve capable of a large flow rate. Patent Document 1 discloses a purge valve that suppresses a decrease in flow rate while reducing pulsation invading the input port by providing a pillar member at a position facing the chamber inlet.

Japanese Unexamined Patent Publication No. 2008-291916

Patent Document 1 provides one technique for improving the flow rate characteristics, but there is room for improvement with respect to further improvement of the flow rate characteristics. The purge control valve device disclosed in this specification is an improvement of the prior art with a unique flow rate characteristic in order to improve the flow rate characteristic.

An object disclosed in this specification is to provide a purge control valve device capable of improving the flow rate characteristics.

The plurality of aspects disclosed herein employ different technical means to achieve their respective objectives. Further, the scope of claims and the reference numerals in parentheses described in this section are examples showing the correspondence with the specific means described in the embodiment described later as one embodiment, and limit the technical scope. is not it.

One of the disclosed purge control valve devices is an inflow port (31a) into which the evaporative fuel spilled from the canister (13) flows in, an outflow port (33a) in which the evaporative fuel flows out toward the engine (2), and the like. A housing (32) having a housing internal passage connecting the inflow port and the outflow port, and a first internal passage provided inside the housing to open and close the first internal passage included in the housing internal passage to control the flow rate of evaporated fuel. A first solenoid valve (34; 134; 234) having one valve body (34b) and a second solenoid valve (34; 134; 234) provided inside the housing are opened and closed in the second internal passage included in the housing internal passage to control the flow rate of fuel vapor. A second solenoid valve (35; 135; 235) having a second valve body (35b) is provided.
The first internal passage and the second internal passage are arranged in series in the housing internal passage, and are arranged in series.
The first solenoid valve and the second solenoid valve are controlled to operate separately.
The first solenoid valve switches between a seated state in which the first valve body contacts the valve seat portion (31b1) and a separated state in which the first solenoid valve is separated from the valve seat portion.
It is provided with a throttle passage (31c1; 134b2) in which the flow rate of the evaporated fuel flowing down in one of the seated state and the unseat state of the first valve body is smaller than the flow rate of the evaporated fuel flowing down in the other state. ..

According to this device, the evaporative fuel flowing down the throttle passage becomes a small flow rate in one state, and a large flow rate of the evaporative fuel can flow down in the other state. This makes it possible to switch between the seated state and the unoccupied state so that one state is set when a small flow rate characteristic or a pulsation suppressing effect is desired, and the other state is set when a flow rate is to be secured. In this way, the purge control valve device can improve the flow rate characteristics.

One of the disclosed purge control valve devices is an inflow port (31a) into which the evaporative fuel spilled from the canister (13) flows in, an outflow port (33a) in which the evaporative fuel flows out toward the engine (2), and the like. A housing (32) having a housing internal passage connecting the inflow port and the outflow port, and a first internal passage provided inside the housing to open and close the first internal passage included in the housing internal passage to control the flow rate of evaporated fuel. A first solenoid valve (34; 134; 234) having one valve body (34b) and a second solenoid valve (34; 134; 234) provided inside the housing are opened and closed in the second internal passage included in the housing internal passage to control the flow rate of fuel vapor. A second solenoid valve (35; 135; 235) having a second valve body (35b) is provided.
The first internal passage and the second internal passage are arranged in series in the housing internal passage, and are arranged in series.
The first solenoid valve and the second solenoid valve are controlled to operate individually, and the first solenoid valve is in a seated state where the first solenoid valve contacts the valve seat portion (31b1) and is separated from the valve seat portion. Switch between states,
Of the seated state and the unseat state in the first valve body, the flow path crossing area of the first internal passage in one state is smaller than the flow path crossing area of the first internal passage in the other state (31c1; 134b2) is provided.

According to this device, a small flow rate of evaporated fuel can flow down in one state than in the other state by the throttle passage that reduces the flow path cross-sectional area of the first internal passage. As a result, it is possible to switch the flow path crossing area of the first internal passage by setting it to one state when it is desired to obtain a small flow rate characteristic or a pulsation suppressing effect, and setting it to the other state when it is desired to secure a flow rate. .. This purge control valve device can improve the flow rate characteristics.

It is a block diagram of the evaporative fuel processing apparatus provided with the purge control valve apparatus of 1st Embodiment. It is sectional drawing which shows the operation in the 1st increase rate region about the purge control valve device of 1st Embodiment. It is sectional drawing which shows the operation in the 2nd increase rate region. It is a flowchart explaining control which concerns on a purge control valve apparatus. It is a figure explaining the flow rate control which concerns on the purge control valve device. It is sectional drawing which shows the operation in the 1st increase rate region about the purge control valve device of 2nd Embodiment. It is sectional drawing which shows the operation in the 2nd increase rate region. It is a flowchart explaining control which concerns on a purge control valve apparatus. It is sectional drawing which shows the operation in the 1st increase rate region about the purge control valve device of 3rd Embodiment. It is sectional drawing which shows the operation in the 2nd increase rate region. It is sectional drawing which shows the operation in the 1st increase rate region about the purge control valve device of 4th Embodiment. It is sectional drawing which shows the operation in the 1st increase rate region about the purge control valve device of 5th Embodiment. It is sectional drawing which shows the operation in the 1st increase rate region about the purge control valve device of 6th Embodiment.

Hereinafter, a plurality of modes for carrying out the present disclosure will be described with reference to the drawings. In each form, the same reference numerals may be attached to the parts corresponding to the items described in the preceding forms, and duplicate explanations may be omitted. When only a part of the configuration is described in each form, the other forms described above can be applied to the other parts of the configuration. Not only the combination of the parts that clearly indicate that the combination is possible in each embodiment, but also the combination of the embodiments even if it is not specified if there is no particular problem in the combination. It is also possible.

(First Embodiment)
The first embodiment will be described with reference to FIGS. 1 to 5. The purge control valve device is used in the evaporative fuel processing device 1 which is an evaporative fuel purging system mounted on a vehicle. The purge valve 3 is an example of a purge control valve device. As shown in FIG. 1, the evaporative fuel processing device 1 supplies HC gas or the like in the fuel adsorbed on the canister 13 to the intake passage of the engine 2. This makes it possible to prevent the evaporated fuel from the fuel tank 10 from being released into the atmosphere. The evaporative fuel processing device 1 includes an intake system of the engine 2 that constitutes an intake passage of the engine 2 that is an internal combustion engine, and an evaporative fuel purge system that supplies the evaporated fuel to the intake system of the engine 2.

The evaporated fuel introduced into the intake passage by the intake pressure of the engine 2 is mixed with the combustion fuel supplied to the engine 2 from the injector or the like and burned in the combustion chamber of the engine 2. The engine 2 mixes and burns at least the evaporated fuel desorbed from the canister 13 and the combustion fuel. In the intake system of the engine 2, the intake pipe 21 constituting the intake passage is connected to the intake manifold 20. This intake system is further configured by providing a throttle valve 25, an air filter 24, and the like in the middle of the intake pipe 21.

In the evaporative fuel purge system, the fuel tank 10 and the canister 13 are connected by a pipe 11 constituting a vapor passage. In the evaporative fuel purge system, the canister 13 and the intake pipe 21 are connected to each other via a pipe 14 constituting a purge passage and a purge valve 3. Further, a purge pump may be provided in the middle of the purge passage. The air filter 24 is provided in the upstream portion of the intake pipe 21 and captures dust, dust, etc. in the intake pipe. The throttle valve 25 is an intake air amount adjusting valve that adjusts the opening degree of the inlet portion of the intake manifold 20 to adjust the amount of intake air flowing into the intake manifold 20. The intake air passes through the intake air passage, flows into the intake manifold 20, is mixed with the combustion fuel injected from the injector or the like so as to have a predetermined air-fuel ratio, and is burned in the combustion chamber.

The fuel tank 10 is a container for storing fuel such as gasoline. The fuel tank 10 is connected to the inflow portion of the canister 13 by a pipe 11 forming a vapor passage. The ORVR valve 15 is provided in the fuel tank 10. The ORVR valve 15 prevents the evaporated fuel in the fuel tank 10 from being discharged into the atmosphere from the fuel filler port during fuel refueling. The ORVR valve 15 is a float valve whose position is displaced according to the liquid level of the fuel. When the fuel in the fuel tank 10 is low, the ORVR valve 15 is opened, and the vapor is discharged from the fuel tank 10 to the canister 13 by the pressure at the time of refueling. When a predetermined amount or more of fuel is present in the fuel tank 10, the ORVR valve 15 is closed by the buoyancy of the fuel to prevent the evaporated fuel from flowing out to the canister 13.

The canister 13 is a container in which an adsorbent such as activated carbon is sealed. The canister 13 takes in the evaporated fuel generated in the fuel tank 10 through the vapor passage and temporarily adsorbs it to the adsorbent. The canister 13 is provided with a valve module 12 integrally or via a duct portion. The valve module 12 includes a canister closed valve and an internal pump. The canister close valve opens and closes the suction section for sucking in fresh air from the outside. By providing the canister 13 with a canister close valve, atmospheric pressure can be applied to the inside of the canister 13. The canister 13 can easily desorb, that is, purge the evaporated fuel adsorbed on the adsorbent by the sucked fresh air.

The purge valve 3 is a purge control valve device including a plurality of valve bodies that open and close the passage inside the housing in the housing that is a part of the purge passage. The purge control valve device has a plurality of solenoid valves inside. The purge valve 3 can allow and block the supply of evaporative fuel from the canister 13 to the engine 2.

When the control device 50 controls the inflow port 31a and the outflow port 33a so as to communicate with each other when the vehicle is traveling, the negative pressure in the intake manifold 20 generated by the suction action of the piston and the atmospheric pressure applied to the canister 13 There is a difference. Due to this pressure difference, the vapor fuel adsorbed in the canister 13 flows through the purge passage and the purge valve 3 and is sucked into the intake manifold 20 through the intake pipe 21.

The evaporated fuel sucked into the intake manifold 20 is mixed with the original combustion fuel supplied from the injector or the like to the engine 2 and burned in the cylinder of the engine 2. In the cylinder of the engine 2, the air-fuel ratio, which is the mixing ratio of the combustion fuel and the intake air, is controlled to be a predetermined air-fuel ratio. The control device 50 controls the first solenoid valve 34 by turning on and off the energization. The control device 50 controls the duty energization of the second solenoid valve 35. The control device 50 properly controls the first solenoid valve 34 and the second solenoid valve 35 to adjust the purging amount of the evaporated fuel so that a predetermined air-fuel ratio is maintained.

The control device 50 has at least one arithmetic processing unit (CPU) and at least one memory device as a storage medium for storing programs and data. The control device 50 is provided, for example, by a microcomputer having a storage medium that can be read by a computer. A storage medium is a non-transitional substantive storage medium that stores a computer-readable program non-temporarily. The storage medium may be provided by a semiconductor memory, a magnetic disk, or the like. The control device 50 may be provided by a single computer, or a set of computer resources linked by a data communication device. The program, when executed by the control device 50, causes the control device 50 to function as the device described herein and to perform the method described herein.

The means and / or functions provided by the control device 50 can be provided by software recorded in a substantive memory device and a computer, software only, hardware only, or a combination thereof that executes the software. For example, if the control device 50 is provided by an electronic circuit that is hardware, it can be provided by a digital circuit or an analog circuit that includes a large number of logic circuits.

In recent years, the purge valve 3 is required to have a performance capable of adjusting a large flow rate due to a decreasing tendency of engine negative pressure due to low fuel consumption and a decreasing tendency of engine operating time of a hybrid vehicle or the like. If an attempt is made to increase the flow rate of the purge valve 3, the fluctuation range of the pressure in the flow path connecting the purge valve 3 and the canister 13 may become large. The increase in the pressure fluctuation range causes vibration of the piping due to pulsation, which causes noise in the vehicle. Further, with the realization of a large flow rate of the purge valve 3, a fluttering noise of the ORVR valve 15 may be generated. The pipe 14 connecting the purge valve 3 and the canister 13 is provided, for example, under the floor in the vehicle interior. Therefore, the noise caused by the vibration of the piping and the fluttering sound of the ORVR valve 15 are easily transmitted to the vehicle interior. Therefore, the evaporative fuel processing device 1 has an effect of suppressing the pressure fluctuation width in the flow path on the canister side and the fluttering noise of the ORVR valve 15. Further, when trying to increase the flow rate of the purge valve 3, the accuracy of the flow rate control is lowered, so that the accuracy of the concentration learning of the evaporated fuel tends to be lowered. Therefore, the evaporative fuel processing device 1 has an effect of ensuring the accuracy of learning the concentration of the evaporative fuel.

The configuration of the purge valve 3 will be described. The purge valve 3 has a first solenoid valve 34 and a second solenoid valve 35 provided inside the housing. The first solenoid valve 34 and the second solenoid valve 35 are arranged so as to line up from the upstream side to the downstream side inside the purge valve 3. The upstream side is shown by US in the drawings. The downstream side is shown by DS in the drawings. The first solenoid valve 34 and the second solenoid valve 35 are arranged along the displacement direction in which the valve body of the purge valve 3 is displaced or the axial direction of the valve body. The axial direction is indicated by AD in the drawings. The first solenoid valve 34 is located on the upstream side of the second solenoid valve 35. The first solenoid valve 34 opens and closes the first internal passage in the purge valve 3 to adjust the flow path cross-sectional area in the first internal passage. The second solenoid valve 35 opens and closes the second internal passage in the purge valve 3 to adjust the flow path cross-sectional area in the second internal passage. The flow path cross-sectional area is the cross-sectional area of the passage when the passage is cut at a plane orthogonal to the direction in which the fluid flows.

The first internal passage and the second internal passage are passages included in the housing internal passage. The first internal passage and the second internal passage are arranged in series rather than in parallel in the internal passage in the housing. In this embodiment, the first internal passage is the upstream passage in the housing internal passage, and the second internal passage is the downstream passage in the internal passage in the housing. Hereinafter, the first internal passage will be replaced with the upstream passage, and the second internal passage will be replaced with the downstream passage.

The purge valve 3 includes an inflow side housing 31, an outflow side housing 33, and an intermediate housing 32 as housings. The inflow side housing 31, the intermediate housing 32, and the outflow side housing 33 are made of, for example, a resin material. The inflow side housing 31 includes an inflow port 31a into which the evaporated fuel from the canister 13 flows in. The inflow port 31a is connected to a pipe 14 forming a purge passage in the evaporative fuel processing device 1. The inflow port 31a communicates with the canister 13 via the connected pipe 14. The inflow side housing 31 includes a flange portion 31b that is joined to the flange portion 32b of the intermediate housing 32 by welding or adhesion.

The inflow port 31a is a part of a tubular portion having a fluid inflow passage 31a1 inside, and is located at an upstream end portion of the inflow side housing 31. The diameter of the downstream portion of this tubular portion increases as it goes downstream, and an inflow side chamber chamber is formed inside the downstream portion. The inflow side chamber chamber has a larger passage crossing area than the passage in the inflow port 31a located upstream, and the passage crossing area becomes larger toward the downstream. A flange portion 31b that protrudes radially is integrally formed at the downstream end of the tubular portion.

The flange portion 31b has a first valve seat portion 31b1 on the downstream side surface. The first valve seat portion 31b1 comes into contact with the first valve body 34b in the seated state of the first solenoid valve 34. The flange portion 31b is provided with a flow path narrowing wall 31c that projects from the downstream surface toward the downstream. The flow path narrowing wall 31c is located outside the disc-shaped portion 34b1 and is provided so as to form a gap with the outer peripheral edge of the disc-shaped portion 34b1. The flow path narrowing wall 31c may be provided so as to surround the entire circumference of the outer peripheral edge of the plate-shaped portion 34b1, or may be partially provided.

As shown in FIG. 2, the gap between the outer peripheral edge of the disc-shaped portion 34b1 and the flow path throttle wall 31c constitutes a throttle passage 31c1 through which the fluid flows down when the first valve body 34b is unseat. The purge valve 3 includes a throttle passage 31c1 that makes the flow path cross-sectional area of the first internal passage smaller than the seated state of the first valve body 34b.

The throttle passage 31c1 constitutes a passage having a passage crossing area smaller than that of the through hole 34b2. The throttle passage 31c1 is configured so that the fluid does not flow down when the first valve body 34b is seated. The throttle passage 31c1 corresponds to the upstream passage in the purge valve 3 through which the fluid flows down when the first increase rate region shown in FIG. 5 is implemented. The first valve body 34b is in contact with the fixed core 343 when the seated state is shown in FIG. 2 and the first increase rate region is carried out. It can be said that the seated state shown in FIG. 2 is a state in which the first valve body 34b is seated on the fixed core 343. With this configuration, the fluid flows down the throttle passage 31c1 and does not flow down the through hole 34b2.

The intermediate housing 32 includes a tubular portion 32a extending in the axial direction, and flange portions 32b and flange portions 32c provided at both ends in the axial direction of the tubular portion 32a. The flange portion 32b is a portion that radially protrudes in the radial direction at the upstream end portion of the tubular portion 32a. The flange portion 32c is a portion that radially protrudes in the radial direction at the downstream end portion of the tubular portion 32a.

The intermediate housing 32 houses the first solenoid valve 34 and the second solenoid valve 35. Inside the intermediate housing 32, a first solenoid valve 34 is provided on the upstream side, and a second solenoid valve 35 is provided on the downstream side. An intermediate passage 32a1 is provided between the inner peripheral surface of the intermediate housing 32 and the outer peripheral surface of the first solenoid valve 34 and the second solenoid valve 35. The intermediate passage 32a1 is a tubular passage located outside the first solenoid valve 34 and the second solenoid valve 35 between the upstream passage and the downstream passage in the purge valve 3. The intermediate passage 32a1 is a passage in the purge valve 3 having a larger passage crossing area than the upstream passage and the downstream passage.

The outflow side housing 33 includes an outflow port 33a for flowing out the evaporated fuel toward the intake pipe 21, and a tubular portion 33c on the upstream side of the outflow port 33a. The outflow port 33a and the tubular portion 33c are provided coaxially. The outflow port 33a communicates with the intake pipe 21 via a connected pipe. The outflow side housing 33 includes a flange portion 33b that is joined to the flange portion 32c of the intermediate housing 32 by welding or adhesion. The flange portion 33b is a portion that radially protrudes in the radial direction at the upstream end portion of the outflow port 33a.

The outflow port 33a is a tubular portion having a fluid outflow passage 33a1 inside, and is located at the downstream end of the outflow side housing 33. The outflow port 33a and the tubular portion 33c are connected by a flange portion 33b. A second valve seat portion 33c1 is provided at the upstream end of the tubular portion 33c. The space between the second valve seat portion 33c1 and the second valve body 35b corresponds to a downstream passage in the purge valve 3 through which the fluid flows toward the outflow passage 33a1. The passage in the tubular portion 33c communicates with the upstream passage in the purge valve 3 at the upstream end and communicates with the outflow passage 33a1 at the downstream end. The tubular portion 33c is formed so that the pipe diameter becomes smaller toward the upstream end. The passage crossing area of the passage in the tubular portion 33c becomes smaller toward the upstream end.

The purge valve 3 includes one inflow port 31a into which the fluid flows in from the outside and one outflow port 33a in which the fluid flows out to the outside. All of the fluid flowing into the inflow passage 31a1 flows through the upstream passage, the intermediate passage 32a1, and the downstream passage in this order, and then flows out to the outflow passage 33a1. The first solenoid valve 34 and the second solenoid valve 35 each include a separate solenoid portion and a valve body, and form a separate magnetic circuit. The first solenoid valve 34 and the second solenoid valve 35 have a configuration in which the energization of the coil portion is individually controlled by the control device 50.

The first solenoid valve 34 includes a first valve body 34b and a first solenoid unit 34a that generates an electromagnetic force that displaces the first valve body 34b. The first valve body 34b can adjust the flow path resistance in the upstream passage in the purge valve 3. The first solenoid valve 34 shown in FIG. 2 is controlled in a seated state in which the first valve body 34b is separated from the first valve seat portion 31b1. The unseat state of the first valve body 34b is controlled in order to carry out the first increase rate region in which the flow rate increase rate of the fluid is small as shown in the graph of FIG. The first valve body 34b is maintained in a seated state while performing the mode of the first increase rate region.

The first solenoid valve 34 shown in FIG. 3 is controlled to be in a seated state in which the first valve body 34b is in contact with the first valve seat portion 31b1. The seated state of the first valve body 34b is controlled in order to carry out the second increase rate region in which the flow rate increase rate of the fluid is larger than the first increase rate region as shown in the graph of FIG. The first valve body 34b is maintained in a seated state while performing the mode of the second increase rate region. The first solenoid valve 34 is a valve that is controlled to be in a seated state when a voltage is not applied and to be in a seated state when a voltage is applied. The first solenoid valve 34 is a normally open type valve that narrows the upstream passage when a voltage is applied to perform small flow rate control, and opens the upstream passage to perform large flow control when no voltage is applied. The flow rate increase rate is, for example, the amount of increase in the flow rate per unit time or the amount of increase in the flow rate per unit displacement of the valve body.

The first solenoid portion 34a includes a coil portion 340, a bobbin 341, a movable core 342, a fixed core 343, a yoke 36, a shaft portion 353b, a spring 344, and the like. The central axis of the first solenoid portion 34a corresponds to the central axis of the first solenoid valve 34 and the central axis of the purge valve 3. The shaft portion 353b is a part of the shaft support member 353. The shaft support member 353 includes an annular plate portion 353a located at the downstream end portion and a shaft portion 353b extending axially from the inner peripheral edge of the annular plate portion 353a toward the upstream side. The shaft support member 353 coaxially supports the first solenoid portion 34a and the second solenoid portion 35a.

The movable core 342 is made of a material that conducts magnetism, for example, a magnetic material. The movable core 342 is a bottomed cup-shaped body. The movable core 342 is provided so as to surround the spring 344 installed inside the movable core 342. The spring 344 is provided between the shaft portion 353b and the movable core 342. The spring 344 provides an urging force that moves the movable core 342 away from the shaft portion 353b. The spring 344 provides an urging force for moving the movable core 342 toward the first valve seat portion 31b1.

The first valve body 34b has a valve portion made of an elastically deformable material such as rubber. The valve portion of the first valve body 34b is provided in an annular shape over the entire circumference on each of the upstream side surface and the downstream side surface of the disc-shaped portion 34b1. The disc-shaped portion 34b1 is integrally provided at the upstream end portion of the movable core 342. The upstream side surface of the disc-shaped portion 34b1 is a surface that faces the first valve seat portion 31b1 in the axial direction. The second valve body 35b is provided at the downstream end of the movable core 352 and is integrated with the movable core 352. The plate-shaped portion 34b1 is provided with a plurality of or a single through hole 34b2. As shown in FIG. 3, the through hole 34b2 constitutes an open passage through which the fluid can flow down when the first valve body 34b is seated. The purge valve 3 includes an open passage that makes the flow path cross-sectional area of the first internal passage larger than that of the first valve body 34b in the unseat state. As shown in FIG. 2, the through hole 34b2 constitutes a flow path through which the fluid does not flow down when the first valve body 34b is seated away. The through hole 34b2 corresponds to the upstream passage in the purge valve 3 through which the fluid flows down when the second increase rate region shown in FIG. 5 is implemented.

The fixed core 343 slidably supports a movable core 342 that moves in the axial direction against the urging force of the spring 344 by an electromagnetic force. The fixed core 343 is integrally provided on the bobbin 341, the coil portion 340, the yoke 36, and the shaft support member 353. The fixed core 343, the movable core 342, the first valve body 34b, the coil portion 340, and the yoke 36 are installed so that their axes are coaxial.

The bobbin 341 is formed of an insulating material and has a function of insulating the coil portion 340 from other portions. The fixed core 343, the movable core 342, the shaft portion 353b, and the yoke 36 are made of a material that allows magnetism to pass through. The yoke 36 includes a tubular portion 361 in which both ends in the axial direction are open, and an annular disc portion 362 provided in an annular shape on the inner peripheral surface of the tubular portion 361. The annular plate portion 362 is located between the coil portion 340 and the coil portion 350. When the coil portion 340 is energized, the magnetic circuit shown by the broken line in FIG. 2 is formed. This magnetic circuit generates an electromagnetic force that attracts the movable core 342 to the shaft portion 353b. The first valve body 34b switches from the seated state to the unseat state by this electromagnetic force. The magnetic circuit in the first solenoid valve 34 is formed by magnetism passing through a fixed core 343, a movable core 342, a shaft portion 353b, an annular plate portion 362, and a tubular portion 361. The first valve body 34b is driven according to the balance between the electromagnetic force generated when the coil portion 340 is energized and the urging force of the spring 344, and switches between the seated state and the unseat state.

The housing is provided with a first connector having a built-in terminal for energizing the coil portion 340 of the first solenoid valve 34. The terminal built in the first connector is an energizing terminal that is electrically connected to the coil portion 340. A power supply side connector for supplying electric power from the power supply unit or the current control device is connected to the first connector. The current that energizes the coil unit 340 can be controlled by the configuration in which the first connector and the power supply side connector are connected and the terminal is electrically connected to the control device 50 or the like.

The second solenoid valve 35 includes a second valve body 35b and a second solenoid unit 35a that generates an electromagnetic force that displaces the second valve body 35b. The second valve body 35b is a valve body capable of opening and closing the downstream passage in the purge valve 3. The second solenoid valve 35 shown in FIGS. 2 and 3 is controlled in a seated state in which the second valve body 35b is separated from the second valve seat portion 33c1.

The second solenoid valve 35 is a normally closed type valve controlled to be in a closed state in which the downstream passage is closed when no voltage is applied and in an open state in which the downstream passage is opened when a voltage is applied. The control device 50 controls the ratio of the energization on time to the time of one cycle, that is, the duty ratio, to energize the coil portion 350 of the second solenoid valve 35. The control device 50 controls the duty ratio in the range of 0% to 100%. Due to the duty energization control, the flow rate of the evaporated fuel flowing through the downstream passage in the purge valve 3 changes in proportion to the duty ratio. The second solenoid valve 35 is controlled so that the duty ratio gradually increases from 0% to 100% when the first increase rate region shown in the graph of FIG. 5 is implemented. The second solenoid valve 35 is controlled so that the duty ratio gradually increases from a predetermined value of X% to 100% when the second increase rate region shown in the graph of FIG. 5 is being implemented. X% is any value set between 0% and 100%. As shown in FIG. 5, X% is preferably set to a value that can ensure the continuity of the flow rate change from the first increase rate region to the second increase rate region.

The second solenoid portion 35a includes a coil portion 350, a bobbin 351 and a movable core 352, a yoke 36, an annular plate portion 353a, a shaft portion 353b, a spring 354, and the like. The annular plate portion 353a is a component corresponding to the fixed core 343 in the first solenoid portion 34a. The central axis of the second solenoid portion 35a corresponds to the central axis of the second solenoid valve 35 and the central axis of the purge valve 3.

The movable core 352 is made of a material that conducts magnetism, for example, a magnetic material. The movable core 352 is a bottomed cup-shaped body. The movable core 352 is provided so as to surround the spring 354 installed inside the movable core 352. The spring 354 is provided between the shaft-shaped member 355 and the movable core 352. The shaft-shaped member 355 is fixed in a state of being press-fitted into the shaft support member 353. The spring 354 provides an urging force that moves the movable core 352 away from the shaft-like member 355. The spring 354 provides an urging force for moving the movable core 352 toward the second valve seat portion 33c1. The second valve body 35b is made of an elastically deformable material such as rubber. The second valve body 35b is integrally provided at the downstream end of the movable core 352.

The shaft support member 353 slidably supports a movable core 352 that moves in the axial direction against the urging force of the spring 354 by an electromagnetic force. The shaft support member 353 is integrally provided on the bobbin 351, the coil portion 350, the yoke 36, and the shaft-shaped member 355. The shaft support member 353, the movable core 352, the second valve body 35b, the coil portion 350, and the yoke 36 are installed so that their axes are coaxial with each other.

The bobbin 351 is formed of an insulating material and has a function of insulating the coil portion 350 from other portions. The shaft support member 353, the movable core 352, and the yoke 36 are made of a material that conducts magnetism. When the coil portion 350 is energized, the magnetic circuit shown by the broken line in FIGS. 2 and 3 is formed. This magnetic circuit generates an electromagnetic force that attracts the movable core 352 to the shaft-shaped member 355. The second valve body 35b switches from the seated state to the unseat state by this electromagnetic force. The magnetic circuit in the second solenoid valve 35 is formed by magnetism passing through the annular plate portion 353a, the movable core 352, the shaft portion 353b, the annular plate portion 362, and the tubular portion 361. The second valve body 35b is driven according to the balance between the electromagnetic force generated when the coil portion 350 is energized and the urging force of the spring 354, and switches between the seated state and the unseat state.

The housing is provided with a second connector having a built-in terminal for energizing the coil portion 350 of the second solenoid valve 35. The terminal built in the second connector is an energizing terminal that is electrically connected to the coil portion 350. A power supply side connector for supplying electric power from the power supply unit or the current control device is connected to the second connector. The current that energizes the coil unit 350 can be controlled by the configuration in which the second connector and the power supply side connector are connected and the terminal is electrically connected to the control device 50 or the like.

The operation of the purge valve control device will be described with reference to the flowchart of FIG. The control device 50 executes the process according to the flowchart of FIG. This flowchart starts when the evaporated fuel flows down toward the engine 2. The second solenoid valve 35 is controlled by a duty energization that gradually increases the duty ratio from 0%.

When this flowchart is started, the control device 50 determines whether or not the concentration of the evaporated fuel is learned in step S100. If it is determined in step S100 that the concentration learning is being performed, the control device 50 determines in step S120 whether or not the first solenoid valve 34 is in the energized state. If it is determined in step S120 that the first solenoid valve 34 is in the energized state, the process returns to step S100 again, and the determination process of step S100 is executed. If it is determined in step S120 that the first solenoid valve 34 is not in the energized state, the first solenoid valve 34 is controlled to be in the energized state in step S125, and the determination process of step S100 is executed.

If it is determined in step S100 that the concentration learning is not performed, the control device 50 determines in step S110 whether or not the noise generation condition is satisfied. The noise generation condition is a preset condition that can be assumed to generate noise due to pressure fluctuation in the passage through which the evaporated fuel flows and the generation of the fluttering noise of the ORVR valve 15. The noise generation condition can be set, for example, to be satisfied when the current vehicle speed is equal to or lower than a predetermined speed. In this case, the control device 50 acquires the current vehicle speed based on the vehicle speed information detected by the vehicle speed sensor 61. The vehicle speed sensor 61 outputs vehicle speed information to the vehicle ECU 60 that controls the traveling of the vehicle and the cooling system required for the traveling of the vehicle, and the vehicle speed information is output from the vehicle ECU 60 to the control device 50. The predetermined speed is preferably set based on experimental results or empirical rules, and is set to a vehicle speed at which the noise is drowned out by the running noise and is difficult for the occupants in the vehicle interior to recognize. By setting the condition for generating noise when the current vehicle speed is lower than the predetermined speed, it is possible to suppress the noise that tends to be generated when the vehicle speed is low and the running noise is low.

For example, when the vehicle is stopped, the vehicle is running at a low speed, the engine 2 is idling, or the like, the control device 50 determines that the noise generation condition is satisfied in step S110. If it is determined in step S110 that the noise generation condition is satisfied, the process proceeds to step S120, and the determination process of step S120 is executed.

The flow returning from step S120 to step S100, and the flow returning to step S100 after executing step S125 implements the mode of the first increase rate region of FIG. In the mode of the first increase rate range, the flow rate increase rate of the fluid is small, so that the concentration learning accuracy of the evaporated fuel can be improved. According to the mode of the first increase rate region, the flow rate change in the small flow rate region can be made smaller than that of the solenoid valve in which the flow rate increase rate is constant. Further, in the mode of the first increase rate range, a small flow rate can be performed, so that the effect of reducing pulsation and suppressing noise can be obtained. Further, in the mode of the first increase rate range, the fluid flow rate is suppressed, so that the effect of reducing the fluttering of the ORVR valve 15 and suppressing the noise can be obtained.

If it is determined in step S110 that the noise generation condition is not satisfied, the control device 50 determines whether or not the duty ratio of the second solenoid valve 35 has reached 100% in step S130. If it is determined in step S130 that the duty ratio has not reached 100%, the process returns to step S100 and the determination process of step S100 is executed. When it is determined in step S130 that the duty ratio has reached 100%, it is determined in step S140 whether or not the first solenoid valve 34 is in the energized state.

If it is determined in step S140 that the first solenoid valve 34 is not in the energized state, the process returns to step S100 and the determination process of step S100 is executed. If it is determined in step S140 that the first solenoid valve 34 is in the energized state, the control device 50 controls the first solenoid valve 34 in the non-energized state in step S150. In step S160, the control device 50 reduces the duty ratio of the second solenoid valve 35 to X%, which is a predetermined value, and returns to step S100. The control device 50 executes control in which the duty ratio of the second solenoid valve 35 is gradually increased from a predetermined value toward 100%. By the processing of steps S150 and S160, the fluid flow rate controlled by the purge valve 3 can be smoothly shifted from the first increase rate region to the second increase rate region as shown in FIG.

When the first solenoid valve 34 is not energized in the flowchart, the mode of the second increase rate range shown in FIG. 5 is executed. In the mode of the second increase rate range, the flow rate resistance of the upstream passage is reduced, so that the flow rate is increased. According to the mode of the second increase rate region, the flow rate change in a large flow rate region can be made larger than that of the solenoid valve in which the flow rate increase rate is constant. Therefore, the fluid flow rate can be increased quickly in a state where noise is unlikely to be generated, and the operation satisfying the output requirement of the engine 2 can be realized. According to the control according to the flowchart of FIG. 4, as shown in FIG. 5, it is possible to provide a flow rate control capable of suppressing noise caused by pulsation and the like and increasing the flow rate.

Further, the control device 50 may determine in step S110 that the noise generation condition is satisfied when the current rotation speed of the engine 2 is lower than the predetermined rotation speed. When this determination process is adopted, the predetermined number of revolutions is preferably set based on experimental results or empirical rules, and is set to such a number of revolutions that the noise is drowned out by the engine sound and is difficult for the occupant to recognize. And. By setting the condition for generating noise when the current engine speed is lower than the predetermined engine speed, the noise caused by pressure fluctuations and the like becomes noise when the engine speed is small and quiet. It can be suppressed.

The operation and effect brought about by the purge control valve device exemplified by the purge valve 3 of the first embodiment will be described. The purge control valve device includes a housing having a housing internal passage connecting the inflow port 31a and the outflow port 33a. The purge control valve device includes a first solenoid valve 34 that opens and closes the first internal passage to control the flow rate of the evaporated fuel, and a second solenoid valve 35 that opens and closes the second internal passage to control the flow rate of the evaporated fuel. Be prepared. The first internal passage and the second internal passage are arranged in series in the housing internal passage. The first solenoid valve 34 and the second solenoid valve 35 are configured to be controlled so as to operate individually. The first solenoid valve 34 switches between a seated state in which the first valve body 34b is in contact with the first valve seat portion 31b1 and a separated state in which the first valve seat portion 31b1 is separated from the first valve seat portion 31b1. The purge control valve device has a throttle passage 31c1 in which the flow rate of the evaporated fuel flowing down in one of the seated state and the unseat state is smaller than the flow rate of the evaporated fuel flowing down in the other state.

According to this, it is possible to provide a purge control valve device including a throttle passage 31c1 in which the evaporated fuel flowing down the first internal passage has a large flow rate in the other state and a small flow rate in the one state. The purge control valve device is set to one state when you want to obtain small flow rate characteristics or to suppress pulsation, and to the other state when you want to secure the flow rate. Can be switched. In this way, a purge control valve device capable of obtaining small flow rate characteristics and large flow rate characteristics and improving the flow rate characteristics can be obtained.

In the purge control valve device, the flow path crossing area of the first internal passage in one of the seated state and the unseat state in the first valve body is smaller than the flow path crossing area of the first internal passage in the other state. It has a throttle passage 31c1. According to this, it is possible to provide a purge control valve device including a throttle passage 31c1 in which the flow path cross-sectional area of the first internal passage is large in the other state and small in the one state. The purge control valve device is set to one state when it is desired to obtain a small flow rate characteristic or to suppress pulsation, and is set to the other state when it is desired to secure a flow rate. The cross-sectional area can be switched. The purge control valve device can acquire a small flow rate characteristic and a large flow rate characteristic, and can improve the flow rate characteristic.

In the purge control valve device, the first internal passage is arranged on the upstream side of the second internal passage. According to this configuration, among the internal passages of the housing, a configuration in which the flow path is variable on the upstream side and a configuration in which the flow path is opened and closed on the downstream side can be adopted. This makes it possible to provide a purge control valve device capable of suppressing pressure loss and simplifying the configuration and control of the second solenoid valve 35.

The purge valve 3 includes a passage that functions as a throttle passage when the seat is off, and an open passage through which the evaporated fuel flows down when the passage crossing area is larger than that of the throttle passage and the seat is seated. According to the purge valve 3, it is possible to provide a purge control valve device in which the evaporative fuel flowing down the throttle passage in the seated state has a small flow rate, and the evaporative fuel flowing down the open passage in the seated state has a large flow rate. The purge valve 3 can be switched between a seated state and a seated state so as to be set in a seated state when it is desired to suppress pulsation and to be set in a seated state when it is desired to secure a flow rate. The purge valve 3 provides a purge control valve device capable of both suppressing pulsation and securing a flow rate.

The control device 50 separately executes the mode of the first increase rate region and the mode of the second increase rate region in which the flow rate increase rate is larger than that of the first increase rate region with respect to the increase in the flow rate of the evaporated fuel. The solenoid valve 34 and the second solenoid valve 35 are individually controlled. The control device 50 controls the first solenoid valve 34 and the second solenoid valve 35 so that the evaporated fuel flows down the throttle passage in the mode of the first increase rate region. The control device 50 controls the first solenoid valve 34 and the second solenoid valve 35 so that the evaporated fuel flows down the open passage having a passage crossing area larger than that of the throttle passage in the mode of the second increase rate region. According to this control, it is possible to provide a purge control valve device capable of achieving both pulsation suppression and flow rate securing by switching between the mode in the first increase rate range and the mode in the second increase rate range at an appropriate timing. The purge valve 3 can obtain a wide range of flow rates and can improve the flow rate characteristics.

In the flow rate increase control in which the flow rate of the evaporated fuel flowing out from the outflow port 33a is increased from the zero state, the control device 50 executes the mode of the first increase rate range and then sets the mode of the second increase rate range. carry out. According to this control, it is possible to provide a purge control valve device capable of suppressing pulsation and fluttering of the ORVR valve 15 from the start of purging, and further exhibiting a large flow rate performance of purging.

The control device 50 controls the first solenoid valve 34 by turning on and off the energization, and controls the second solenoid valve 35 by controlling the duty ratio of the applied voltage. The control device 50 controls the second solenoid valve so as to increase the duty ratio of the applied voltage in the mode of the first increase rate region. The control device 50 temporarily lowers the duty ratio of the applied voltage when shifting from the mode in the first increase rate region to the mode in the second increase rate region, and then temporarily reduces the duty ratio of the applied voltage in the mode in the second increase rate region. The second solenoid valve 35 is controlled so as to rise. According to this, when shifting from the mode of the first increase rate region to the mode of the second increase rate region, it is possible to carry out purge control in which the flow rate of the evaporated fuel flowing out from the outflow port 33a does not fluctuate significantly.

The control device 50 individually controls the first solenoid valve 34 and the second solenoid valve 35 so that the mode of the first increase rate region is executed when the concentration learning of the evaporated fuel is performed. According to this control, the concentration learning of the evaporated fuel can be carried out in a state where the flow rate change is small. As a result, it is possible to provide a purge control valve device that can achieve both pulsation suppression and flow rate securing, and further improve the accuracy of concentration learning.

The control device 50 individually controls the first solenoid valve 34 and the second solenoid valve 35 so that the mode of the first increase rate region is executed when the noise generation condition in which noise can be assumed is satisfied. According to this control, the mode of the first increase rate region can be executed in a state where noise due to pulsation or fluttering of the ORVR valve 15 can be generated. This makes it possible to provide a purge control valve device that can suppress noise more efficiently and secure a flow rate.

(Second Embodiment)
The second embodiment will be described with reference to FIGS. 6 to 8. The purge valve 103 of the second embodiment is different from the first solenoid valve 134 of the first embodiment. The first solenoid valve 134 is a normally closed type valve that narrows the upstream passage when no voltage is applied to perform small flow rate control, and opens the upstream passage to perform large flow control when a voltage is applied. The second solenoid valve 135 has the same configuration and the same operation as the second solenoid valve 35. The configurations, actions, and effects that are not particularly described in the second embodiment are the same as those in the first embodiment, and only the differences will be described below. The description regarding the first solenoid valve 34 in the first embodiment can be incorporated in the second embodiment by replacing the first solenoid valve 34 with the first solenoid valve 134. The description regarding the second solenoid valve 35 in the first embodiment can be incorporated in the second embodiment by replacing the second solenoid valve 35 with the second solenoid valve 135.

The configuration of the purge valve 103 will be described. The purge valve 103 has a first solenoid valve 134 and a second solenoid valve 135 provided inside the housing. The first solenoid valve 134 and the second solenoid valve 135 are arranged so as to line up from the upstream side to the downstream side inside the purge valve 103. The first solenoid valve 134 and the second solenoid valve 135 are aligned along the displacement direction in which the valve body of the purge valve 103 is displaced or the axial direction of the valve body. The first solenoid valve 134 is located on the upstream side of the second solenoid valve 135. The first solenoid valve 134 adjusts the flow path cross-sectional area in the upstream passage in the purge valve 103. The second solenoid valve 135 adjusts the flow path cross-sectional area in the downstream passage in the purge valve 103.

The first valve seat portion 31b1 comes into contact with the first valve body 34b in the seated state of the first solenoid valve 134. The flange portion 31b of the inflow side housing 131 is not provided with the flow path narrowing wall 31c as in the first embodiment. Therefore, the purge valve 103 does not include the throttle passage 31c1 of the first embodiment.

The disc-shaped portion 134b1 is integrally provided at the upstream end portion of the movable core 342. The upstream side surface of the disc-shaped portion 134b1 is a surface that faces the first valve seat portion 31b1 in the axial direction. The plate-shaped portion 134b1 is provided with a plurality of or a single through hole 134b2. As shown in FIG. 6, the through hole 134b2 constitutes a flow path through which the fluid can flow down when the first valve body 34b is seated. As shown in FIG. 7, the through hole 134b2 constitutes a flow path through which the fluid does not flow down when the first valve body 34b is seated away. The through hole 134b2 corresponds to the upstream passage in the purge valve 103 through which the fluid flows down when the first increase rate region shown in FIG. 5 is implemented.

The through hole 134b2 constitutes a passage having a smaller passage crossing area than the passage 31b2 formed between the first valve body 34b and the first valve seat portion 31b1 in the seated state shown in FIG. The through hole 134b2 constitutes a throttle passage through which the fluid flows down when the first valve body 34b is seated. The purge valve 103 includes a throttle passage that makes the flow path cross-sectional area of the first internal passage smaller than that of the first valve body 34b in the unseat state. The through hole 134b2 is configured so that the fluid does not flow down when the first valve body 34b is seated away. The through hole 134b2 corresponds to the upstream passage in the purge valve 103 through which the fluid flows down when the first increase rate region shown in FIG. 5 is implemented. The through hole 134b2 functions as a throttle passage through which the evaporated fuel flows down in the mode of the first increase rate region. The passage 31b2 constitutes an open passage through which the evaporated fuel flows down when the first valve body 34b is in the unseat state. The purge valve 103 includes an open passage that makes the flow path cross-sectional area of the first internal passage larger than the seated state of the first valve body 34b. The passage 31b2 functions as an open passage through which the evaporated fuel flows down in the mode of the second increase rate region.

The first solenoid valve 134 and the second solenoid valve 135 each include a separate solenoid portion and a valve body to form a separate magnetic circuit. The first solenoid valve 134 and the second solenoid valve 135 have a configuration in which the energization of the coil portion is individually controlled by the control device 50.

The first solenoid valve 134 includes a first valve body 34b and a first solenoid unit 34a that generates an electromagnetic force that displaces the first valve body 34b. The first valve body 34b can adjust the flow path resistance in the upstream passage in the purge valve 103. The first solenoid valve 134 shown in FIG. 6 is controlled in a seated state in which the first valve body 34b is in contact with the first valve seat portion 31b1. The seated state of the first valve body 34b is controlled in order to carry out the first increase rate region in which the flow rate increase rate of the fluid is small as shown in the graph of FIG. The first solenoid valve 134 shown in FIG. 7 is controlled in a seated state in which the first valve body 34b is separated from the first valve seat portion 31b1. The unseat state of the first valve body 34b is controlled in order to carry out the second increase rate region in which the flow rate increase rate of the fluid is larger than the first increase rate region as shown in the graph of FIG. The first solenoid valve 134 is a valve that is controlled to be in a seated state when a voltage is applied and in a seated state when a voltage is not applied.

The second solenoid valve 135 shown in FIGS. 6 and 7 is controlled in a seated state in which the second valve body 35b is separated from the second valve seat portion 33c1. The second solenoid valve 135 is a normally closed type valve controlled to be in a closed state in which the downstream passage is closed when no voltage is applied and in an open state in which the downstream passage is opened when a voltage is applied. The control device 50 controls the duty ratio to energize the coil portion 350 of the second solenoid valve 135.

The operation of the purge valve control device will be described with reference to the flowchart of FIG. The control device 50 executes the process according to the flowchart of FIG. The second solenoid valve 135 is controlled by a duty energization that gradually increases the duty ratio from 0%. S200, S210, S230, and S260 shown in FIG. 8 are the same processes as S100, S110, S130, and S160 shown in FIG. 4, and the description of the first embodiment is incorporated.

If it is determined in step S200 that the concentration learning is being performed, the control device 50 determines in step S220 whether or not the first solenoid valve 134 is in the non-energized state. When it is determined in step S220 that the first solenoid valve 134 is in the non-energized state, the process returns to step S200 and the determination process of step S200 is executed. When it is determined in step S220 that the first solenoid valve 134 is in the energized state, the first solenoid valve 134 is controlled to be in the non-energized state in step S225, and the determination process in step S200 is executed.

If it is determined in step S200 that the density learning is not performed, and if it is determined in step S210 that the noise generation condition is satisfied, the determination process of step S220 is executed. The flow returning from step S220 to step S200, and the flow returning to step S200 after executing step S225 implements the mode of the first increase rate region of FIG. In the mode of the first increase rate range, the flow rate increase rate of the fluid is small, so that the concentration learning accuracy of the evaporated fuel can be improved. In the mode of the first increase rate range, the fluid flow rate is suppressed, so that the effect of reducing pulsation and suppressing noise can be obtained. In the mode of the first increase rate range, the fluid flow rate is suppressed, so that the effect of reducing the fluttering of the ORVR valve 15 and suppressing the noise can be obtained.

When it is determined in step S230 that the duty ratio has reached 100%, it is determined in step S240 whether or not the first solenoid valve 134 is in the non-energized state. If it is determined in step S240 that the first solenoid valve 34 is not in the non-energized state, the process returns to step S200 and the determination process of step S200 is executed. If it is determined in step S240 that the first solenoid valve 134 is in the non-energized state, the control device 50 controls the first solenoid valve 134 in the energized state in step S250. In step S260, the control device 50 reduces the duty ratio of the second solenoid valve 135 to X%, which is a predetermined value, and returns to step S200. The control device 50 executes control in which the duty ratio of the second solenoid valve 135 is gradually increased from a predetermined value toward 100%. By the processing of steps S250 and S260, the fluid flow rate controlled by the purge valve 103 can be smoothly shifted from the first increase rate region to the second increase rate region as shown in FIG.

When the first solenoid valve 134 is not in the non-energized state in the flowchart, the mode of the second increase rate range shown in FIG. 5 is executed. In the mode of the second increase rate region, since the increase in the flow rate is promoted, the flow rate change in the large flow rate region can be made larger than that of the solenoid valve in which the flow rate increase rate is constant. According to the control according to the flowchart of FIG. 8, as shown in FIG. 5, it is possible to provide a flow rate control capable of suppressing noise caused by pulsation and the like and increasing the flow rate.

The device of the second embodiment includes a passage that serves as a throttle passage when the seat is seated, and an open passage through which the evaporated fuel flows down when the passage crossing area is larger than that of the throttle passage and the seat is separated. According to the purge valve 103, it is possible to provide a purge control valve device in which the evaporated fuel flowing down the throttle passage in the seated state has a small flow rate and a large flow rate of the evaporated fuel flows down in the open passage in the unseat state. The purge valve 103 can switch between a seated state and a seated state so as to set the seated state when it is desired to suppress pulsation and to set the seated state when it is desired to secure the flow rate. The purge valve 103 provides a purge control valve device that realizes a small flow rate characteristic, a pulsation suppressing effect, and a large flow rate securing. The purge valve 103 can obtain a wide range of flow rates and can improve the flow rate characteristics.

(Third Embodiment)
The purge valve 203 of the third embodiment will be described with reference to FIGS. 9 to 10. The purge valve 203 is different from the first embodiment in that it includes a second valve body regulating member 345 that moves in the axial direction integrally with the first valve body 34b. The second valve body regulating member 345 is coupled to the movable core 342 of the first solenoid valve 234 and is displaced in the axial direction together with the movable core 342. The second valve body regulating member 345 can limit the distance that the movable core 352 of the second solenoid valve 235 can move in the seating direction. The second valve body regulating member 345 moves integrally with the first valve body 34b in response to an electromagnetic force, and exerts a function of varying the displaceable width of the second valve body 35b. Further, the second valve body regulating member 345 and the movable core 342 may be configured as one component.

The first solenoid valve 234 is a normally open type valve that narrows the upstream passage when a voltage is applied to perform small flow rate control, and opens the upstream passage when a voltage is not applied to perform large flow control. The second solenoid valve 235 is a normally closed type valve like the second solenoid valve 35. The configurations, actions, and effects that are not particularly described in the third embodiment are the same as those in the first embodiment, and only the differences will be described below.

The configuration of the purge valve 203 will be described. The purge valve 203 has a first solenoid valve 234 and a second solenoid valve 235 provided inside the housing. The first solenoid valve 234 and the second solenoid valve 235 are arranged so as to line up from the upstream side to the downstream side inside the purge valve 203. The first solenoid valve 234 and the second solenoid valve 235 are aligned along the displacement direction in which the valve body of the purge valve 203 is displaced or the axial direction of the valve body. The first solenoid valve 234 is located on the upstream side of the second solenoid valve 235. The first solenoid valve 234 adjusts the flow path cross-sectional area in the upstream passage in the purge valve 203. The second solenoid valve 235 adjusts the flow path cross-sectional area in the downstream passage in the purge valve 203.

The first solenoid valve 234 and the second solenoid valve 235 each include a separate solenoid portion and a valve body, and form a separate magnetic circuit. The first solenoid valve 234 and the second solenoid valve 235 have a configuration in which the energization of the coil portion is individually controlled by the control device 50. The first solenoid valve 234 includes a first valve body 34b and a first solenoid unit 234a that generates an electromagnetic force that displaces the first valve body 34b. The first valve body 34b can adjust the flow path resistance in the upstream passage in the purge valve 203.

The first solenoid valve 234 shown in FIG. 9 is controlled in a seated state in which the first valve body 34b is separated from the first valve seat portion 31b1. The seated state of the first valve body 34b is controlled to carry out the first rate of increase region. The state shown in FIG. 9 indicates a state in which the mode of the first increase rate shown in FIG. 5 is started. The first solenoid valve 234 shown in FIG. 10 is controlled to be in a seated state in which the first valve body 34b is in contact with the first valve seat portion 31b1. The seated state of the first valve body 34b is controlled to carry out the second rate of increase region. The state shown in FIG. 10 indicates a state in which the mode of the second increase rate shown in FIG. 5 is started. The first solenoid valve 234 is a valve that is controlled to be in a seated state when a voltage is applied and to a seated state when a voltage is not applied.

In the unseat state of the first valve body 34b, the second valve body regulating member 345 together with the movable core 342 is located closer to the second valve seat portion 33c1 than in the seated state shown in FIG. As a result, the movable core 352 is located closer to the second valve seat portion 33c1 than in the seated state shown in FIG. In the unseat state of the first valve body 34b, the displaceable width in which the second valve body 35b can be displaced by the action of electromagnetic force is smaller than that in the seated state of the first valve body 34b. In the seated state of the first valve body 34b that implements the mode of the first increase rate, the stroke amount that can be moved until the second valve body 35b is seated is shorter than that of the seated state that implements the mode of the second increase rate. The flow path cross-sectional area in the second internal passage in the purge valve 203 is larger in the state shown in FIG. 10 than in the state shown in FIG. The second valve body regulating member 345 brings the second valve body 35b closer to the second valve seat portion 33c1 in one state in which the throttle passage 31c1 is formed than in the other state.

The second solenoid valve 235 shown in FIGS. 9 and 10 is controlled in a seated state in which the second valve body 35b is separated from the second valve seat portion 33c1. The second solenoid valve 235 is a normally closed type valve controlled to be in a closed state in which the downstream passage is closed when no voltage is applied and in an open state in which the downstream passage is opened when a voltage is applied. The control device 50 controls the duty ratio to energize the coil portion 350 of the second solenoid valve 235.

The first solenoid portion 234a includes a coil portion 340, a bobbin 341, a movable core 342, a fixed core 346, a yoke 347, a shaft portion 37c, a spring 344, and the like. The central axis of the first solenoid portion 234a corresponds to the central axis of the first solenoid valve 234 and the central axis of the purge valve 203. The central axis of the first solenoid portion 234a is also the central axis of the second valve body regulating member 345. The shaft portion 37c slidably supports the second valve body regulating member 345 in the axial direction. The shaft portion 37c is a tubular body. The shaft portion 37c slidably supports the second valve body regulating member 345 so that its inner peripheral surface slides on the outer peripheral surface of the second valve body regulating member 345. The second valve body regulating member 345 is formed of, for example, metal, resin, or the like.

The shaft portion 37c is a part of the shaft support member 37. The shaft support member 37 includes a shaft portion 37c, an outer cylinder portion 37a having an outer diameter larger than that of the shaft portion 37c, and an annular plate portion 37b connecting the shaft portion 37c and the outer cylinder portion 37a. The outer cylinder portion 37a coaxially supports the first solenoid portion 234a and the second solenoid portion 235a. The shaft support member 37 is fixed to, for example, a housing in the purge valve 203. An intermediate passage 32a1 is provided between the inner peripheral surface of the intermediate housing 32 and the outer peripheral surface of the outer cylinder portion 37a.

The spring 344 is provided between the shaft portion 37c and the movable core 342. The spring 344 provides an urging force that moves the movable core 342 away from the shaft portion 37c. The shaft support member 37 is made of, for example, resin.

The fixed core 346 slidably supports a movable core 342 that moves in the axial direction against the urging force of the spring 344 by an electromagnetic force. The fixed core 346 includes a tubular portion 346b in which both ends in the axial direction are open, and an annular plate portion 346a provided in a flange shape at the upstream end portion of the tubular portion 346b. The tubular portion 346b slidably supports the movable core 342 on the inner peripheral surface. A coil portion 340 is wound around the outer peripheral surface of the tubular portion 346b via a bobbin 341. The outer cylinder portion 37a of the shaft support member 37 is engaged with the annular plate portion 346a. The fixed core 346 is integrally provided on the bobbin 341, the coil portion 340, the yoke 347, and the shaft support member 37. The yoke 347 includes a tubular portion 347b and an annular plate portion 347a extending from the inner peripheral surface of the downstream end portion of the tubular portion 347b toward the center. The fixed core 346, the movable core 342, the first valve body 34b, the coil portion 340, and the yoke 347 are installed so that their axes are coaxial.

The fixed core 346, the movable core 342, and the yoke 347 are made of a material that conducts magnetism. When the coil portion 340 is energized, the magnetic circuit shown by the broken line in FIG. 9 is formed. This magnetic circuit generates an electromagnetic force that attracts the movable core 342 to the shaft portion 37c. The first valve body 34b of the first solenoid valve 234 switches from the seated state to the unseat state by this electromagnetic force. The magnetic circuit in the first solenoid valve 234 is formed by magnetism passing through the annular plate portion 346a, the movable core 342, the tubular portion 346b, the annular plate portion 347a, and the tubular portion 347b. The first valve body 34b, the movable core 342, and the second valve body regulating member 345 are driven in the axial direction according to the balance between the electromagnetic force generated at the time of energization and the urging force of the spring 344.

The second solenoid valve 235 includes a second valve body 35b and a second solenoid unit 235a that generates an electromagnetic force that displaces the second valve body 35b. The control device 50 controls the duty ratio to energize the coil portion 350 of the second solenoid valve 235. The second solenoid valve 235 is controlled so that the duty ratio gradually increases from 0% to 100% when the mode of the first increase rate region is performed. The second solenoid valve 235 is controlled so that the duty ratio gradually increases from a predetermined value of X% to 100% when the mode of the second increase rate region is executed.

The second solenoid portion 235a includes a coil portion 350, a bobbin 351 and a movable core 352, a fixed core 356, a yoke 357, a shaft portion 37c, a spring 354 and the like. The central axis of the second solenoid portion 235a corresponds to the central axis of the second solenoid valve 235 and the central axis of the purge valve 203. The central axis of the second solenoid portion 235a is also the central axis of the second valve body regulating member 345. The spring 354 is provided between the shaft portion 37c and the movable core 352. The spring 354 provides an urging force that moves the movable core 352 away from the shaft portion 37c.

The fixed core 356 slidably supports a movable core 352 that moves in the axial direction against the urging force of the spring 354 by an electromagnetic force. The fixed core 356 includes a tubular portion 356b that opens at both ends in the axial direction, and an annular plate portion 356a provided in a flange shape at the upstream end portion of the tubular portion 356b. The tubular portion 356b slidably supports the movable core 352 on the inner peripheral surface. A coil portion 350 is wound around the outer peripheral surface of the tubular portion 356b via a bobbin 351. The outer cylinder portion 37a of the shaft support member 37 is engaged with the annular plate portion 356a. The fixed core 356 is integrally provided on the bobbin 351, the coil portion 350, the yoke 357, and the shaft support member 37. The yoke 357 includes a tubular portion 357b and an annular plate portion 357a extending from the inner peripheral surface of the downstream end portion of the tubular portion 357b toward the center side. The fixed core 356, the movable core 352, the second valve body 35b, the coil portion 350, and the yoke 357 are installed so that their axes are coaxial.

The fixed core 356, the movable core 352, and the yoke 357 are made of a material that conducts magnetism. When the coil portion 350 is energized, the magnetic circuit shown by the broken line in FIGS. 9 and 10 is formed. This magnetic circuit generates an electromagnetic force that attracts the movable core 352 to the shaft portion 37c. The second valve body 35b of the second solenoid valve 235 switches from the seated state to the unseat state by this electromagnetic force. The magnetic circuit in the second solenoid valve 235 is formed by magnetism passing through the annular plate portion 356a, the movable core 352, the tubular portion 356b, the annular plate portion 357a, and the tubular portion 357b. The second valve body 35b and the movable core 352 are driven in the axial direction according to the balance between the electromagnetic force generated at the time of energization and the urging force of the spring 354.

The control device 50 controls the purge valve 203 by executing the process according to the flowchart of FIG. 4, as in the first embodiment. The description of the process according to the flowchart of FIG. 4 in the first embodiment is incorporated by replacing the first solenoid valve 34 and the second solenoid valve 35 with the first solenoid valve 234 and the second solenoid valve 235.

The operation and effect brought about by the purge control valve device exemplified by the purge valve 203 of the third embodiment will be described. The purge valve 203 includes a passage that serves as a throttle passage when the seat is off, and an open passage through which the evaporated fuel flows down when the passage crossing area is larger than that of the throttle passage and the seat is seated. According to the purge valve 203, it is possible to provide a purge control valve device in which the evaporated fuel flowing down the throttle passage in the seated state has a small flow rate, and the evaporated fuel flowing down in the open passage in the seated state has a large flow rate. The purge valve 203 is switched between a seated state and a seated state so as to be set to one state when it is desired to obtain a small flow rate characteristic or to suppress pulsation, and to be set to the other state when it is desired to secure a flow rate. Becomes possible. As described above, the purge valve 203 provides a purge control valve device capable of acquiring a small flow rate characteristic and a large flow rate characteristic to improve the flow rate characteristic.

The purge valve 203 includes a second valve body regulating member 345 that changes the axial distance between the second valve body 35b and the second valve seat portion 33c1 according to the seated state and the seated state of the first valve body 34b. According to this configuration, the stroke amount that can be moved until the second valve body 35b is seated can be made smaller in the mode of the first increase rate than in the mode of the second increase rate. As a result, it is possible to realize a fine flow rate change and a smooth flow rate change in the mode of the first increase rate. The purge valve 203 contributes to the smooth transition of the fluid flow rate from the first increase rate region to the second increase rate region, and contributes to enhancing the linearity of the flow rate change. According to this effect, it is possible to contribute to suppressing the pressure fluctuation width in the flow path on the canister side and the fluttering noise of the ORVR valve 15.

(Fourth Embodiment)
The purge valve 303 of the fourth embodiment will be described with reference to FIG. The purge valve 303 is different from the purge valve 3 of the first embodiment in that the direction in which the fluid flows is opposite to that in the device.

The purge valve 303 has the same configuration, operation, and effect as those of the first embodiment, which are not particularly described in the fourth embodiment, and only the differences will be described below. The purge valve 303 is arranged so that the second solenoid valve 35 and the first solenoid valve 34 are lined up from the upstream side to the downstream side inside the apparatus. In the purge valve 303, the outflow port 33a of the first embodiment functions as an inflow port, and the inflow port 31a of the first embodiment functions as an outflow port. In the fourth embodiment, the second internal passage is the upstream passage in the housing internal passage, and the first internal passage is the downstream passage in the internal passage in the housing.

(Fifth Embodiment)
The purge valve 403 of the fifth embodiment will be described with reference to FIG. The purge valve 403 is different from the purge valve 103 of the second embodiment in that the direction in which the fluid flows is opposite to that in the device.

The purge valve 403 has the same configuration, operation, and effect as those of the second embodiment, which are not particularly described in the fifth embodiment, and only the differences will be described below. The purge valve 403 is arranged so that the second solenoid valve 135 and the first solenoid valve 134 are lined up from the upstream side to the downstream side inside the apparatus. In the purge valve 403, the outflow port 33a of the second embodiment functions as an inflow port, and the inflow port 31a of the second embodiment functions as an outflow port. In the fifth embodiment, the second internal passage is the upstream passage in the housing internal passage, and the first internal passage is the downstream passage in the internal passage in the housing.

(Sixth Embodiment)
The purge valve 503 of the sixth embodiment will be described with reference to FIG. The purge valve 503 is different from the purge valve 203 of the third embodiment in that the direction in which the fluid flows is opposite to that in the device.

The purge valve 503 is the same as the third embodiment in terms of configuration, operation, and effect which are not particularly described in the sixth embodiment, and only the differences will be described below. The purge valve 503 is arranged so that the second solenoid valve 235 and the first solenoid valve 234 are lined up from the upstream side to the downstream side inside the apparatus. In the purge valve 503, the outflow port 33a of the third embodiment functions as an inflow port, and the inflow port 31a of the third embodiment functions as an outflow port. In the sixth embodiment, the second internal passage is the upstream passage in the housing internal passage, and the first internal passage is the downstream passage in the internal passage in the housing.

(Other embodiments)
Disclosure of this specification is not limited to the illustrated embodiments. The disclosure includes exemplary embodiments and modifications by those skilled in the art based on them. For example, the disclosure is not limited to the combination of parts and elements shown in the embodiment, and can be implemented in various modifications. Disclosure can be carried out in various combinations. The disclosure can have additional parts that can be added to the embodiment. The disclosure includes parts and elements of the embodiment omitted. Disclosures include replacements or combinations of parts, elements between one embodiment and another. The technical scope disclosed is not limited to the description of the embodiments. The technical scope disclosed is indicated by the description of the scope of claims, and should be understood to include all modifications within the meaning and scope equivalent to the description of the scope of claims.

A purge control valve device capable of achieving the object disclosed in the specification includes a first solenoid valve that controls the flow rate on the upstream side and a second solenoid valve that controls the flow rate on the downstream side in the passage connecting the inflow port and the outflow port. Be prepared. The purge control valve device that can achieve the purpose is not limited to the form including one inflow port and one outflow port. The purge control valve device that can achieve the purpose may be configured to include a plurality of inflow ports and a plurality of outflow ports. The purge control valve device that can achieve the object may be configured to include one inflow port and a plurality of outflow ports. The purge control valve device that can achieve the object may be configured to include a plurality of inflow ports and one outflow port.

As described in the fourth to sixth embodiments, the purge control valve device capable of achieving the object disclosed in the specification has the first solenoid valve forming the throttle passage on the downstream side of the second solenoid valve. Including those having a configuration to be arranged in. In the case of this configuration, the first internal passage arranged in series with the second internal passage is arranged on the downstream side of the second internal passage.

2 ... Engine, 13 ... Canister, 31a ... Inflow port 31b1 ... First valve seat (valve seat), 31b2 ... Passage (open passage)
31c1 ... throttle passage, 32 ... intermediate housing (housing), 33a ... outflow port 34,134,234 ... first solenoid valve, 35,135,235 ... second solenoid valve 34b ... first valve body, 34b2 ... through hole ( Open passage)
35b ... 2nd valve body, 134b2 ... Through hole (drawing passage)

Claims (11)

The inflow port (31a) into which the evaporated fuel spilled from the canister (13) flows in, and
An outflow port (33a) through which evaporative fuel flows toward the engine (2),
A housing (32) having a passage inside the housing connecting the inflow port and the outflow port,
A first solenoid valve (34; 134; 234) provided inside the housing and having a first valve body (34b) that opens and closes a first internal passage included in the housing internal passage to control the flow rate of evaporated fuel. )When,
A second solenoid valve (35; 135; 235) provided inside the housing and having a second valve body (35b) that opens and closes a second internal passage included in the housing internal passage to control the flow rate of evaporated fuel. )When,
With
The first internal passage and the second internal passage are arranged in series in the housing internal passage.
The first solenoid valve and the second solenoid valve are controlled to operate separately.
The first solenoid valve switches between a seated state in which the first valve body is in contact with the valve seat portion (31b1) and a separated state in which the first solenoid valve is separated from the valve seat portion.
A throttle passage (31c1; 134b2) in which the flow rate of the evaporated fuel flowing down in one of the seated state and the unseat state of the first valve body is smaller than the flow rate of the evaporated fuel flowing down in the other state. ) A purge control valve device. The inflow port (31a) into which the evaporated fuel spilled from the canister (13) flows in, and
An outflow port (33a) through which evaporative fuel flows toward the engine (2),
A housing (32) having a passage inside the housing connecting the inflow port and the outflow port,
A first solenoid valve (34; 134; 234) provided inside the housing and having a first valve body (34b) that opens and closes a first internal passage included in the housing internal passage to control the flow rate of evaporated fuel. )When,
A second solenoid valve (35; 135; 235) provided inside the housing and having a second valve body (35b) that opens and closes a second internal passage included in the housing internal passage to control the flow rate of evaporated fuel. )When,
With
The first internal passage and the second internal passage are arranged in series in the housing internal passage.
The first solenoid valve and the second solenoid valve are controlled to operate separately.
The first solenoid valve switches between a seated state in which the first valve body is in contact with the valve seat portion (31b1) and a detached state in which the first solenoid valve is separated from the valve seat portion.
Of the seated state and the unseat state in the first valve body, the flow path crossing area of the first internal passage in one state is smaller than the flow path crossing area of the first internal passage in the other state. A purge control valve device including a throttle passage (31c1; 134b2). The purge control valve device according to claim 1 or 2, wherein the first internal passage is arranged on the upstream side of the second internal passage. The first solenoid valve has a passage that functions as the throttle passage when the seat is off, and an open passage (34b2) through which the evaporated fuel flows down when the passage crossing area is larger than that of the throttle passage and the seat is in the seated state. ), The purge control valve device according to any one of claims 1 to 3. The first solenoid valve has a passage that becomes the throttle passage when the seated state and an open passage (31b2) through which the evaporated fuel flows down when the passage crossing area is larger than that of the throttle passage and the seated state. The purge control valve device according to any one of claims 1 to 3, further comprising. A second valve body regulating member (345) that moves integrally with the first valve body in response to an electromagnetic force to regulate the displaceable width of the second valve body is provided.
The second valve body regulating member is any one of claims 1 to 4, wherein the second valve body is brought closer to the valve seat portion (33c1) in the one state than in the other state. The purge control valve device according to one item. With respect to the increase in the flow rate of the evaporated fuel, the mode of the first increase rate region and the mode of the second increase rate region in which the flow rate increase rate is larger than that of the first increase rate region are separately executed with the first solenoid valve. A control device (50) for individually controlling the second solenoid valve is provided.
The control device controls the first solenoid valve and the second solenoid valve so that the evaporated fuel flows down the throttle passage in the mode of the first increase rate region, and controls the first solenoid valve and the second solenoid valve in the mode of the second increase rate region. Any of claims 1 to 4, which controls the first solenoid valve and the second solenoid valve so that the evaporated fuel flows down an open passage (34b2; 31b2) having a passage crossing area larger than that of the throttle passage. The purge control valve device according to one item. In the flow rate increase control in which the flow rate of the evaporated fuel flowing out from the outflow port is increased from the zero state, the control device executes the mode of the first increase rate range and then increases the flow rate of the second increase rate range. The purge control valve device according to claim 7, wherein the mode is performed. The control device controls the first solenoid valve by turning on and off the energization, and controls the second solenoid valve by controlling the duty ratio of the applied voltage.
The control device controls the second electromagnetic valve so as to increase the duty ratio of the applied voltage in the mode of the first increase rate region, and from the mode of the first increase rate region to the second increase rate region. Claim 7 or claim, wherein the duty ratio of the applied voltage is once lowered at the time of transition to the mode, and then the second electromagnetic valve is controlled so as to increase the duty ratio of the applied voltage in the mode of the second increase rate region. Item 8. The purge control valve device according to Item 8. From claim 7, the control device individually controls the first solenoid valve and the second solenoid valve so that the mode of the first increase rate region is executed when the concentration learning of the evaporated fuel is performed. The purge control valve device according to any one of claims 9. A claim that the control device individually controls the first solenoid valve and the second solenoid valve so as to execute the mode of the first increase rate region when the noise generation condition in which noise can be assumed is satisfied. The purge control valve device according to any one of claims 7 to 10.

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