阅读说明：本技术 净化控制阀设备 (Purge control valve apparatus ) 是由 小林康规 井野口哲规 李晔楠 安积凉 于 2020-04-01 设计创作，主要内容包括：本发明提供一种净化控制阀设备。在净化控制阀设备中,净化阀包括设置在壳体内部的第一电磁阀和第二电磁阀。第一电磁阀具有第一阀体,其控制在壳体中流动的蒸发燃料的流速。第二电磁阀具有第二阀体,其控制在壳体中流动的蒸发燃料的流速。上游通道和下游通道串联地布置。第一电磁阀切换第一阀体的落座状态和未落座状态。所述净化阀具有收窄通道,在该收窄通道中,在落座状态和未落座状态中的一种状态下的蒸发燃料的流速小于在落座状态和未落座状态中的另一种状态下的蒸发燃料的流速。(The invention provides a purge control valve apparatus. In the purge control valve apparatus, the purge valve includes a first solenoid valve and a second solenoid valve provided inside the housing. The first electromagnetic valve has a first valve body that controls the flow rate of the evaporated fuel flowing in the housing. The second electromagnetic valve has a second valve body that controls the flow rate of the evaporated fuel flowing in the housing. The upstream and downstream channels are arranged in series. The first solenoid valve switches between a seated state and an unseated state of the first valve body. The purge valve has a narrowed passage in which a flow rate of the evaporated fuel in one of the seated state and the unseated state is smaller than a flow rate of the evaporated fuel in the other of the seated state and the unseated state.)

1. A purge control valve apparatus, comprising:

an inlet (31a) into which the evaporated fuel flowing out of the tank (13) flows;

an outlet port (33a) through which the evaporated fuel flows out toward an engine (2);

a housing (32) having a housing inner passage 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 a flow rate of the evaporated fuel; and

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 a flow rate of the evaporated fuel; wherein

The first internal passage and the second internal passage are arranged in series in the housing internal passage, and

the first solenoid valve and the second solenoid valve are controlled to operate individually,

the first solenoid valve is switched between a seated state in which the first valve body is in contact with a first valve seat and an unseated state in which the first valve body is separated from the first valve seat;

the purge control valve device further includes a constricted passage (31c1, 134b2) in which a flow rate of the evaporated fuel in one of the seated state and the unseated state is smaller than a flow rate of the evaporated fuel in the other of the seated state and the unseated state.

2. A purge control valve apparatus, comprising:

an inlet (31a) into which the evaporated fuel flowing out of the tank (13) flows;

an outlet port (33a) through which the evaporated fuel flows out toward an engine (2);

a housing (32) having a housing inner passage 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 a flow rate of the evaporated fuel; and

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 a flow rate of the evaporated fuel; wherein

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 individually, and

the first solenoid valve is switched between a seated state in which the first valve body is in contact with a first valve seat and an unseated state in which the first valve body is separated from the first valve seat,

the purge control valve apparatus further includes a narrowed passage (31c1, 134b2) in the first internal passage such that a passage cross-sectional area of the first internal passage in one of the seated state and the unseated state is smaller than a passage cross-sectional area of the first internal passage in the other of the seated state and the unseated state.

3. The purge control valve apparatus of claim 1 or 2,

the first internal passage is disposed upstream of the second internal passage.

4. The purge control valve apparatus of claim 1 or 2,

the first solenoid valve includes: a channel that functions as the narrowing channel in the unseated state; and an open passage (34b2), a passage cross-sectional area of the open passage being larger than the narrowed passage, and the evaporated fuel flowing through the open passage in the seated state.

5. The purge control valve apparatus of claim 1 or 2,

the first solenoid valve includes: a passage that becomes the narrowing passage in the seated state; and an open passage (31b2), the open passage having a larger passage cross-sectional area than the narrowed passage, and the evaporated fuel flowing through the open passage in the unseated state.

6. The purge control valve apparatus of claim 1 or 2, further comprising

A second valve adjuster (345) that moves with the first valve body in response to an electromagnetic force and adjusts a displaceable range of the second valve body, wherein

The second valve regulator in the one state brings the second valve body closer to a second valve seat (33c1) than in the other state.

7. The purge control valve apparatus of claim 1 or 2, further comprising

A controller (50) that individually controls the first solenoid valve and the second solenoid valve when increasing the flow rate of the evaporated fuel such that the controller executes a first increase rate mode and a second increase rate mode, respectively, the second increase rate mode having a flow increase rate greater than the first increase rate mode, wherein

The controller controls the first solenoid valve and the second solenoid valve during the first increase rate mode such that the evaporated fuel flows through the narrowed passage, and

the controller controls the first solenoid valve and the second solenoid valve during the second increase rate mode such that the evaporated fuel flows through an open passage (34b2, 31b2) having a larger passage cross-sectional area than the narrowed passage.

8. The purge control valve apparatus of claim 7,

the controller executes the first increase rate mode and then executes the second increase rate mode in flow rate increase control in which the flow rate of the evaporated fuel flowing out of the flow outlet is increased from zero.

9. The purge control valve apparatus of claim 7,

the controller controls the first solenoid valve by energization that opens and closes the first solenoid valve, and controls the second solenoid valve by controlling a duty ratio of a voltage applied to the second solenoid valve, and

the controller is configured to, in control of the second electromagnetic valve,

increasing the duty cycle of the applied voltage in the first increase rate mode,

reducing the duty cycle of the applied voltage when transitioning from the first increase rate mode to the second increase rate mode, and

increasing the duty cycle of the applied voltage in the second increase rate mode.

10. The purge control valve apparatus of claim 7,

the controller individually controls the first solenoid valve and the second solenoid valve, and executes the first increase rate mode when the concentration of the evaporated fuel is known.

11. The purge control valve apparatus of claim 7,

the controller individually controls the first solenoid valve and the second solenoid valve so as to execute the first increase rate mode when a noise generation condition is satisfied.

Technical Field

The present disclosure relates to a purge control valve apparatus (purge control valve device).

Background

As the negative pressure of the low fuel consumption engine decreases and the operating time of the engine of the vehicle such as a hybrid vehicle decreases, a large flow capacity of the purge valve is required. Patent document 1(JP 2008-291916A) discloses a purge valve in which a columnar member is positioned to face a chamber inlet to reduce pulsation entering the input port and reduce a decrease in flow rate.

Disclosure of Invention

Patent document 1 provides a technique for improving flow characteristics, but there is room for improvement. The purge control valve apparatus of the present disclosure has specific flow characteristics in order to improve the flow characteristics.

It is an object of the present disclosure to provide a purge control valve apparatus capable of improving flow characteristics.

According to one aspect of the present disclosure, a purge control valve apparatus includes: an inflow port into which the evaporated fuel flowing out of the tank flows; an outlet port through which the evaporated fuel flows out toward an engine; a housing having an in-housing passage (in-housing) connecting the inflow port and the outflow port; a first electromagnetic valve provided inside the housing and having a first valve body that opens and closes a first internal passage included in the housing internal passage to control a flow rate of the evaporated fuel; and a second electromagnetic valve provided inside the housing and having a second valve body that opens and closes a second internal passage included in the housing internal passage to control a flow rate of the evaporated fuel. 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 individually. The first solenoid valve switches between a seated state (seated state) in which the first valve body contacts the first valve seat and an unseated state (unseated state) in which the first valve body is separated from the first valve seat. The purge control valve apparatus further includes a constricted passage (narrow passage) in which a flow rate of the evaporated fuel in one of the seated state and the unseated state is smaller than a flow rate of the evaporated fuel in the other of the seated state and the unseated state.

Therefore, the evaporated fuel flowing through the constricted passage has a smaller flow rate in the one state and a larger flow rate in the other state. The seated state and the unseated state may be switched such that the one state is selected when it is desired to obtain a small flow rate characteristic or suppress pulsation, and the other state is selected when it is desired to secure a flow rate. Therefore, the purge control valve apparatus can improve flow characteristics.

According to another aspect of the present disclosure, a purge control valve apparatus includes: an inflow port into which the evaporated fuel flowing out of the tank flows; an outlet port through which the evaporated fuel flows out toward an engine; a housing having a housing inner passage connecting the inflow port and the outflow port; a first electromagnetic valve provided inside the housing and having a first valve body that opens and closes a first internal passage included in the housing internal passage to control a flow rate of the evaporated fuel; and a second electromagnetic valve provided inside the housing and having a second valve body that opens and closes a second internal passage included in the housing internal passage to control a flow rate of the evaporated fuel. The first internal passage and the second internal passage are arranged in series in a housing internal passage. The first solenoid valve and the second solenoid valve are controlled to operate individually. The first solenoid valve is switched between a seated state in which the first valve body is in contact with a first valve seat and an unseated state in which the first valve body is separated from the first valve seat. The purge control valve apparatus further includes a narrowed passage in the first internal passage such that a passage cross-sectional area of the first internal passage in one of the seated state and the unseated state is smaller than a passage cross-sectional area of the first internal passage in the other of the seated state and the unseated state.

Therefore, by the narrowed passage that reduces the passage cross-sectional area of the first internal passage, the flow speed of the evaporated fuel in the one state can be smaller than that in the other state. Therefore, the one state is selected when it is desired to obtain a small flow rate characteristic or suppress pulsation, and the other state is selected when it is desired to secure a flow rate. Therefore, the passage cross-sectional area of the first internal passage can be switched. Therefore, the purge control valve apparatus can improve flow characteristics.

Drawings

The details of one or more implementations are set forth in the accompanying drawings and the description below. Other features and advantages will be apparent from the description and drawings, and from the claims.

Fig. 1 is a schematic diagram showing an evaporated fuel treatment apparatus including a purge control valve device according to a first embodiment.

Fig. 2 is a sectional view showing the operation of the purge control valve apparatus according to the first embodiment at a first increase rate.

Fig. 3 is a sectional view showing the operation of the purge control valve apparatus according to the first embodiment at the second increase rate.

Fig. 4 is a flowchart showing the control of the purge control valve apparatus.

Fig. 5 is a diagram showing flow rate control of the purge control valve apparatus.

Fig. 6 is a sectional view showing the operation of the purge control valve apparatus according to the second embodiment at a first increase rate.

Fig. 7 is a sectional view showing the operation of the purge control valve apparatus according to the second embodiment at the second increase rate.

Fig. 8 is a flowchart showing the control of the purge control valve apparatus.

Fig. 9 is a sectional view showing the operation of the purge control valve apparatus according to the third embodiment at the first increase rate.

Fig. 10 is a sectional view showing the operation of the purge control valve apparatus according to the third embodiment at the second increase rate.

Fig. 11 is a sectional view showing the operation of the purge control valve apparatus according to the fourth embodiment at the first increase rate.

Fig. 12 is a sectional view showing the operation of the purge control valve apparatus according to the fifth embodiment at the first increase rate.

Fig. 13 is a sectional view showing the operation of the purge control valve apparatus according to the sixth embodiment at the first increase rate.

Detailed Description

Hereinafter, embodiments for implementing the present disclosure will be described with reference to the accompanying drawings. In each embodiment, portions corresponding to elements described in the foregoing embodiments are denoted by the same reference numerals, and redundant explanation may be omitted. While only a part of the configuration is described in each form, the other forms described above may be applied to other parts of the configuration. If there is no particular hindrance to combining the components of the respective embodiments, the components of the respective embodiments may be combined not only in the combinations explicitly described in the embodiments but also in combinations not explicitly described in the embodiments.

(first embodiment)

A first embodiment will be described with reference to fig. 1 to 5. The purge control valve device is used in an evaporated fuel treatment apparatus 1, and the evaporated fuel treatment apparatus 1 is an evaporated fuel purge system mounted on a vehicle. The purge valve 3 is an embodiment of a purge control valve apparatus. As shown in fig. 1, the evaporated fuel processing device 1 supplies gas such as HC gas in the fuel adsorbed by the canister 13 to the intake passage of the engine 2. Therefore, the release of the evaporated fuel from the fuel tank 10 to the outside air is prevented. The evaporated fuel processing apparatus 1 includes: an intake system of the engine 2, which constitutes an intake passage of the engine 2 as an internal combustion engine; and an evaporated fuel purge system that supplies evaporated fuel to an intake system of the engine 2.

The evaporated fuel introduced into the intake passage of the engine 2 by the intake pressure is mixed with the combustion fuel supplied to the engine 2 from an injector or the like, and is combusted in the combustion chamber of the engine 2. The engine 2 mixes at least the combustion fuel and the vaporized fuel desorbed from the canister 13 and burns the mixture. In the intake system of the engine 2, an intake pipe 21 forming an intake passage is connected to an intake manifold 20. In this intake system, a throttle valve 25 and an air filter 24 are provided in an intake pipe 21.

The fuel tank 10 and the canister 13 in the evaporated fuel purge system are connected to each other through a pipe 11 forming a vapor passage. The canister 13 and the intake pipe 21 in the evaporated fuel purge system are connected to each other through the purge valve 3 and the pipe 14 forming the purge passage. A purge pump may be disposed in the purge passage. The air filter 24 is provided in an upstream portion of the intake duct 21, and traps dust, dirt, and the like in the intake air. The throttle valve 25 is an intake air amount adjusting valve that adjusts the amount of intake air flowing into the intake manifold 20 by adjusting the opening degree of the inlet of the intake manifold 20. Intake air passes through the intake passage and flows into the intake manifold 20. Then, the intake air is mixed with combustion fuel injected from an injector or the like at a predetermined air-fuel ratio to be combusted in the combustion chamber.

The fuel tank 10 is a container for storing fuel such as gasoline. The fuel tank 10 is connected to an inflow portion of a canister 13 through a pipe 11 forming a vapor passage. An ORVR valve 15 is provided in the fuel tank 10. The ORVR valve 15 prevents evaporated fuel in the fuel tank 10 from being discharged from the fuel inlet to the outside air during refueling. The ORVR valve 15 is a float valve that displaces in accordance with the fuel level. When the amount of fuel in the fuel tank 10 is small, the ORVR valve 15 opens, and 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 due to the buoyancy of the fuel, thereby preventing the evaporated fuel from flowing out toward the canister 13.

The tank 13 is a container sealed with an adsorbent such as activated carbon. The canister 13 absorbs the evaporated fuel generated in the fuel tank 10 through the vapor passage and temporarily adsorbs the evaporated fuel to the adsorbent. The tank 13 is provided with a valve module 12 either integrally or through piping. The valve module 12 includes a tank shut-off valve and an internal pump. The canister closing valve opens and closes a suction portion for sucking in fresh air from the outside. Since the tank 13 includes the tank closing valve, atmospheric pressure can be introduced into the tank 13. The canister 13 can easily release (i.e., purge) the evaporated fuel adsorbed to the adsorbent by the fresh air drawn in.

The purge valve 3 is a purge control valve apparatus including a plurality of valve bodies that open and close an in-housing passage in a housing as a part of a purge passage. The purge control valve apparatus has a plurality of solenoid valves therein. The purge valve 3 can allow and prevent the evaporated fuel from being supplied from the canister 13 to the engine 2.

During running of the vehicle, when the controller 50 performs control such that the inflow port 31a communicates with the outflow port 33a, a pressure difference is generated between the atmospheric pressure in the tank 13 and the negative pressure in the intake manifold 20, which is generated by the suction action of the piston. This pressure difference causes the vapor fuel adsorbed to canister 13 to be drawn to intake manifold 20 through the purge passage, purge valve 3, and intake pipe 21.

The evaporated fuel drawn into the intake manifold 20 is mixed with the original combustion fuel supplied to the engine 2 from an injector or the like, and is combusted in the cylinder of the engine 2. In the cylinder of the engine 2, an air-fuel ratio, which is a mixture ratio of combustion fuel and intake air, is controlled to a predetermined air-fuel ratio set in advance. The controller 50 controls the first solenoid valve 34 by energizing and de-energizing the first solenoid valve 34. The controller 50 controls the second solenoid valve 35 by controlling the duty ratio of energization. The adjustment of the purge amount of the evaporated fuel is achieved by the appropriate control of the first solenoid valve 34 and the second solenoid valve 35 by the controller 50, so that a predetermined air-fuel ratio is maintained.

The controller 50 includes at least one processing unit (CPU) and at least one storage unit as a storage medium storing programs and data. The controller 50 is provided by a microcontroller including a computer readable storage medium. The storage medium is a non-transitory tangible storage medium that stores the computer-readable program in a non-transitory manner. A semiconductor memory, or a magnetic disk or the like may serve as the storage medium. The controller 50 may be provided by a set of computer resources linked by a computer or data communication device. When the controller 50 executes the program, the program causes the controller 50 to function in accordance with the description provided herein and causes the controller 50 to perform the methods described herein.

The means and/or functions provided by the controller 50 may be provided by software recorded in a physical storage device and a computer that can execute the software, software only, hardware only, or some combination thereof. For example, when the controller 50 is provided by an electronic circuit as hardware, the controller 50 may be provided by a digital circuit including a plurality of logic circuits or analog circuits.

In recent years, the negative pressure in the engine tends to decrease due to a decrease in fuel consumption, and the operating time of the engine of a vehicle such as a hybrid vehicle tends to decrease. Therefore, the purge valve 3 can have a performance capable of adjusting the fuel at a large flow rate. 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 tank 13 increases. The increase in the range of the pressure fluctuation may cause the pipe to vibrate due to the pulsation and generate noise in the vehicle. Furthermore, such a large flow of the purge valve 3 may cause a wobbling sound (hunting sound) of the ORVR valve 15. A pipe 14 connecting the purge valve 3 and the tank 13 is provided, for example, below the floor of the vehicle compartment. Therefore, noise due to vibration of the pipe and a rattling sound of the ORVR valve 15 are easily transmitted to the vehicle compartment. The evaporated fuel processing apparatus 1 has the effect of reducing the range of pressure fluctuation in the flow path to the tank 13 and reducing the wobbling sound of the ORVR valve 15. When the flow rate of the purge valve 3 increases, the accuracy of the flow rate control decreases, and therefore the accuracy of the concentration learning (concentration learning) of the evaporated fuel tends to decrease. The evaporated fuel treatment apparatus 1 has an effect of ensuring accuracy of knowledge of the evaporated fuel concentration.

Next, the configuration of the purge valve 3 will be described. The purge valve 3 includes 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 inside the purge valve 3 in the direction from the upstream side to the downstream side. In the drawing, the upstream side is denoted by "US". In the drawing, the downstream side is denoted by "DS". The first solenoid valve 34 and the second solenoid valve 35 are arranged in the displacement direction of the valve body of the purge valve 3 or in the axial direction of the valve body. In the drawings, the axial direction is denoted by "AD". The first solenoid valve 34 is located upstream of the second solenoid valve 35. The first electromagnetic valve 34 opens and closes the first internal passage in the purge valve 3, and adjusts the passage cross-sectional area of the first internal passage. The second electromagnetic valve 35 opens and closes the second internal passage in the purge valve 3, and adjusts the passage cross-sectional area of the second internal passage. The channel cross-sectional area is a cross-sectional area of the channel cut along a plane orthogonal to a flow direction of the fluid in the channel.

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, not in parallel, in the internal passage in the housing. In the present embodiment, the first internal passage is an upstream passage in the casing internal passage, and the second internal passage is a downstream passage in the casing internal passage. Hereinafter, the first internal passage is replaced by an upstream passage, and the second internal passage is replaced by a downstream passage.

The purge valve 3 includes an inflow housing 31, an outflow housing 33, and an intermediate housing 32 as housings. The inflow housing 31, the intermediate housing 32, and the outflow housing 33 are formed of, for example, a resin material. The inflow housing 31 includes an inflow port 31a into which the evaporated fuel flows from the tank 13. The inflow port 31a is connected to the pipe 14 forming the purge passage of the evaporated fuel processing apparatus 1. The inflow port 31a communicates with the tank 13 through a pipe 14 connected to the inflow port 31 a. The inflow housing 31 includes a flange 31b, and the flange 31b is joined to a flange 32b of the intermediate housing 32 by welding or bonding.

The inflow port 31a is a part of a tubular portion having a fluid inflow passage 31al therein, and is located at an upstream end of the inflow housing 31. The downstream portion of the tubular portion has a pipe diameter that increases in a direction toward the downstream side, and an inflow chamber is formed inside the downstream portion. The inflow chamber has a larger passage cross-sectional area than the passage in the inflow port 31a located upstream of the inflow chamber. The passage cross-sectional area of the inflow chamber increases in a direction toward the downstream side. The downstream end of the tubular portion is integrally formed with a flange 31b that projects radially outward.

The flange 31b has a first valve seat 31b1 on a downstream surface of the flange 31 b. In the seated state of the first solenoid valve 34, the first valve body 34b contacts the first valve seat 31b 1. The flange 31b is provided with a flow path narrowing wall 31c projecting downstream from the downstream surface of the flange 31 b. The flow path narrowing wall 31c is located radially outward of the plate 34b1, and a gap is formed between the flow path narrowing wall 31c and the outer peripheral edge of the plate 34b 1. The flow path narrowing wall 31c may surround the entire peripheral edge or a part of the peripheral edge of the plate 34b 1.

As shown in fig. 2, the gap between the outer peripheral edge of the plate 34b1 and the flow path narrowing wall 31c forms a narrowing passage 31c1 through which fluid flows 31c1 when the first valve body 34b is in the unseated state. The purge valve 3 includes a narrowed passage 31c1, and the narrowed passage 31c1 reduces the passage cross-sectional area of the first internal passage to be smaller than the passage cross-sectional area in the seated state of the first valve body 34 b.

The narrowed passage 31c1 forms a passage having a passage cross-sectional area smaller than that of the through-hole 34b 2. The constricted passage 31c1 is configured such that fluid does not flow through the constricted passage 31c1 in the seated state of the first valve body 34 b. When the fluid flows at the first increasing rate shown in fig. 5, the narrowed passage 31c1 corresponds to the upstream passage of the purge valve 3 through which the fluid flows. When fluid flows at a first rate of increase in the unseated state shown in fig. 2, the first valve body 34b contacts the stationary core 343. The unseated state shown in fig. 2 can be said to be a state in which the first valve body 34b is seated on the fixed core 343. Therefore, the fluid flows through the constricted passage 31c1, but not through the through hole 34b 2.

The intermediate housing 32 includes a cylindrical portion 32a extending in the axial direction, and flanges 32b and 32c provided at different ends of the cylindrical portion 32a in the axial direction. The flange 32b is a portion radially protruding from the upstream end of the cylindrical portion 32 a. The flange 32c is a portion that protrudes radially from the downstream end of the cylindrical portion 32 a.

The intermediate housing 32 accommodates a first solenoid valve 34 and a second solenoid valve 35. Inside the intermediate housing 32, a first solenoid valve 34 is provided in the upstream region, and a second solenoid valve 35 is provided in the downstream region. The inner peripheral surface of the intermediate housing 32 and the outer peripheral surface of the first solenoid valve 34 or the second solenoid valve 35 define an intermediate passage 32a1 therebetween. The intermediate passage 32a1 is a cylinder passage that is located between the upstream passage and the downstream passage in the purge valve 3, and is located outside the first solenoid valve 34 and the second solenoid valve 35. The intermediate passage 32al has a passage cross-sectional area larger than that of the upstream passage and the downstream passage in the purge valve 3.

The outflow housing 33 is provided with an outflow port 33a through which the evaporated fuel flows out to the intake pipe 21; and a tubular portion 33c located upstream of the outflow port 33 a. The outlet port 33a and the tubular portion 33c are coaxially provided. The outflow port 33a communicates with the inside of the intake pipe 21 through a pipe connected to the outflow port 33 a. The outflow housing 33 includes a flange 33b, and the flange 33b is joined to the flange 32c of the intermediate housing 32 by welding or bonding. The flange 33b is a portion radially protruding from the upstream end of the outflow port 33 a.

The outflow port 33a is a tubular portion having a fluid outflow passage 33al therein, and is located at the downstream end of the outflow housing 33. The outflow port 33a and the tubular portion 33c are connected by a flange 33 b. A second valve seat 33c1 is provided at the upstream end of the tubular portion 33 c. The space between the second valve seat 33c1 and the second valve body 35b corresponds to a downstream passage of the purge valve 3, through which the fluid flows toward the outflow passage 33a 1. The upstream end of the passage in the tubular portion 33c communicates with the downstream passage of the purge valve 3. The downstream end of the passage in the tubular portion 33c communicates with the outflow passage 33a 1. The tubular portion 33c has a pipe diameter that decreases in a direction toward the upstream end thereof. The passage cross-sectional area of the passage in the tubular portion 33c decreases in the direction toward the upstream end.

The purge valve 3 has an inflow port 31a into which the fluid flows from the outside; and an outflow port 33a from which the fluid flows out to the outside. All the fluid that has flowed into the inflow channel 31a1 flows through the upstream channel, the intermediate channel 32a1, and the downstream channel in this order, and then flows out to the outflow channel 33 al. The first solenoid valve 34 and the second solenoid valve 35 each include a solenoid and a valve body, and form magnetic circuits, respectively. The first solenoid valve 34 and the second solenoid valve 35 are configured such that energization of their coils is individually controlled by the controller 50.

The first solenoid valve 34 includes a first valve body 34b and a first solenoid 34a, and the first solenoid 34a generates electromagnetic force to displace the first valve body 34 b. The first valve body 34b is capable of adjusting 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 an unseated state in which the first valve body 34b is separated from the first valve seat 31b 1. In the unseated state of the first valve body 34b, the flow rate of the fluid increases at a small rate of increase, which is the first rate of increase shown in the graph of fig. 5. In the case where the first rate of increase mode is executed, the first valve body 34b is maintained in the unseated state.

The first solenoid valve 34 shown in fig. 3 is controlled in a seated state in which the first valve body 34b is in contact with the first valve seat 31b 1. In the seated state of the first valve body 34b, the flow rate of the fluid increases at a second rate of increase that is greater than the first rate of increase shown in the graph of fig. 5. In the case where the second rate of increase mode is executed, the first valve body 34b is maintained in the seated state. When no voltage is applied, the first solenoid valve 34 is controlled to a seated state, and when voltage is applied, the first solenoid valve 34 is controlled to an unseated state. The first solenoid valve 34 is a normally open valve that controls a small flow by narrowing the upstream passage when voltage is applied, and controls a large flow by fully opening the upstream passage when voltage is not applied. The flow increase rate is, for example, an increase in flow rate per unit time, or an increase in flow rate per unit displacement of the valve body.

The first solenoid 34a includes a coil 340, a bobbin 341, a movable core 342, a fixed core 343, a yoke 36, a shaft 353b, and a spring 344. The center axis of the first solenoid 34a corresponds to the center axis of the first electromagnetic valve 34 and the center axis of the purge valve 3. The shaft 353b is a part of the axial support 353. The axial support 353 comprises an annular plate 353a located at the downstream end of the axial support 353; and a shaft 353b extending from the inner circumferential edge of the annular plate 353a to the upstream side in the axial direction. The axial support 353 coaxially supports the first solenoid 34a and the second solenoid 35 a.

The movable core 342 is made of a material through which a magnetic force (magnetism) passes, for example, a magnetic material. The movable core 342 has a cup-shaped body with a bottom. The movable core 342 is disposed around the spring 344, and the spring 344 is disposed inside the movable core 342. The spring 344 is disposed between the shaft 353b and the movable core 342. The spring 344 provides an urging force to move the movable core 342 in a direction away from the shaft 353 b. The spring 344 provides an urging force to move the movable core 342 toward the first valve seat 31b 1.

The first valve body 34b has a valve element formed of an elastically deformable material such as rubber. The valve element of the first valve body 34b has an annular shape around the entire circumference of the upstream and downstream surfaces of the plate 34b 1. The plate 34b1 is provided integrally with the upstream end of the movable core 342. The upstream surface of the plate 34b1 faces the first valve seat 31b1 in the axial direction. The second valve body 35b is provided at the downstream end of the movable core 352, and is integral with the movable core 352. The plate 34b1 is provided with a plurality or one through hole 34b 2. As shown in fig. 3, when the first valve body 34b is in the seated state, the through hole 34b2 forms an open passage through which fluid may flow. The purge valve 3 includes an open passage that increases the passage cross-sectional area of the first internal passage to be larger than the passage cross-sectional area in the unseated state of the first valve body 34 b. As shown in FIG. 2, when the first valve body 34b is in the unseated state, the through-holes 34b2 form a passage through which fluid does not flow. When the fluid flows at the second increasing rate shown in fig. 5, the through hole 34b2 corresponds to the upstream passage of the purge valve 3 through which the fluid flows.

The fixed core 343 slidably supports the movable core 342, and the movable core 342 is moved in the axial direction against the urging force of the spring 344 by electromagnetic force. The fixed core 343 is provided integrally with the bobbin 341, the coil 340, the yoke 36, and the axial support 353. The fixed core 343, the movable core 342, the first valve body 34b, the coil 340, and the yoke 36 are coaxial.

The bobbin 341 is formed of an insulating material and has a function of insulating the coil 340 from other components. The fixed core 343, the movable core 342, the shaft 353b, and the yoke 36 are made of a material that transmits magnetism. The yoke 36 includes a cylindrical portion 361 having opposite open ends in the axial direction, and an annular plate 362 having an annular shape and provided on an inner circumferential surface of the cylindrical portion 361. The annular plate 362 is located between the coil 340 and the other coil 350. When the coil 340 is energized, a magnetic circuit indicated by a dotted line around the coil 340 in fig. 2 is formed. The magnetic circuit generates an electromagnetic force that attracts the movable core 342 toward the axis 353 b. The electromagnetic force switches the first valve body 34b from the seated state to the unseated state. The magnetic circuit in the first solenoid valve 34 is formed by a magnetic force passing through the fixed core 343, the movable core 342, the shaft 353b, the annular plate 362, and the cylindrical portion 361. The first valve body 34b is driven in accordance with the balance between the electromagnetic force generated when the coil 340 is energized and the urging force of the spring 344, thereby switching between the seated state and the unseated state.

The housing is provided with a first connector having terminals for energizing the coil 340 of the first solenoid valve 34. The terminals built in the first connector are current-carrying terminals electrically connected to the coil 340. The first connector is connected to a power connector for supplying power from a power supply unit or a current controller. The first connector and the power source connector are connected, and the terminal is electrically connected to the controller 50. Accordingly, the current supplied to the coil 340 can be controlled.

The second solenoid valve 35 includes a second valve body 35b and a second solenoid 35a, and the second solenoid 35a generates electromagnetic force to displace the second valve body 35 b. The second valve body 35b is capable of opening and closing the downstream passage of the purge valve 3. In fig. 2 and 3, the second solenoid valve 35 is controlled to an unseated state in which the second valve body 35b is separated from the second valve seat 33c 1.

The second electromagnetic valve 35 is a normally closed valve that is controlled to a closed state in which the downstream passage is closed when no voltage is applied, and is controlled to an open state in which the downstream passage is open when a voltage is applied. The controller 50 performs energization of the coil 350 of the second solenoid valve 35 by controlling the duty ratio (i.e., the ratio of the period of energization on to the period of one cycle). The controller 50 controls the duty ratio in a range of 0% to 100%. According to the duty energization control, the flow rate of the evaporated fuel flowing through the downstream passage in the purge valve 3 is changed in proportion to the duty. The second solenoid valve 35 is controlled such that the duty ratio is gradually increased from 0% to 100% when the first increase rate mode shown in the graph of fig. 5 is implemented. The second solenoid valve 35 is controlled such that when the second increase rate mode shown in the graph of fig. 5 is implemented, the duty ratio is changed from a predetermined percentage: x% is gradually increased to 100%. X% is any value set between 0% and 100%. X% may be set to a value capable of ensuring the continuity of the flow rate change from the first increase rate mode to the second increase rate mode as shown in fig. 5.

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

The movable core 352 is made of a material through which a magnetic force passes, for example, a magnetic material. The movable core 352 has a cup-shaped body with a bottom. The movable core 352 is disposed around the spring 354, and the spring 354 is disposed inside the movable core 352. The spring 354 is disposed between the shaft member 355 and the movable core 352. The shaft member 355 is fixed and press-fitted into the axial support 353. The spring 354 provides an urging force to move the movable core 352 in a direction away from the shaft member 355. The spring 354 provides an urging force to move the movable core 352 toward the second valve seat 33c 1. The second valve body 35b is formed of an elastically deformable material such as rubber. The second valve body 35b is provided integrally with the downstream end of the movable core 352.

The axial support 353 slidably supports the movable core 352, and the movable core 352 is moved in the axial direction against the urging force of the spring 354 by electromagnetic force. The axial support 353 is provided integrally with the bobbin 351, the coil 350, the yoke 36 and the shaft member 355. The axial support 353, the movable core 352, the second valve body 35b, the coil 350, and the yoke 36 are coaxial.

The bobbin 351 is formed of an insulating material and has a function of insulating the coil 350 from other components. The axial support 353, the movable core 352, and the yoke 36 are made of a material that transmits magnetism. When the coil 340 is energized, a magnetic circuit indicated by a dotted line around the coil 350 in fig. 2 and 3 is formed. The magnetic circuit generates an electromagnetic force that attracts the movable core 352 toward the shaft member 355. The electromagnetic force switches the second valve body 35b from the seated state to the unseated state. The magnetic circuit in the second solenoid valve 35 is formed by magnetic force passing through the annular plate 353a, the movable core 352, the shaft 353b, the annular plate 362, and the cylindrical portion 361. The second valve body 35b is driven in accordance with the balance between the electromagnetic force generated when the coil 350 is energized and the urging force of the spring 354, thereby switching between the seated state and the unseated state.

The housing is provided with a second connector having terminals for energizing the coil 350 of the second solenoid valve 35. The terminals built in the second connector are current-carrying terminals electrically connected to the coil 350. The second connector is connected to a power connector for supplying power from the power supply unit or the current controller. The second connector and the power source connector are connected, and the terminal is electrically connected to the controller 50. Accordingly, the current supplied to the coil 350 can be controlled.

Next, the operation of the purge valve controller will be described with reference to the flowchart of fig. 4. The controller 50 executes the process according to the flowchart of fig. 4. The flowchart starts when the evaporated fuel is caused to flow to the engine 2. The second solenoid valve 35 is controlled by energization of a duty cycle, which is gradually increased from 0%.

When the flowchart starts, it is determined in step S100 whether the controller 50 is in a state in which the evaporated fuel concentration is known. When it is determined in step S100 that it is in the state of learning the concentration, the controller 50 determines in step S120 whether the first electromagnetic valve 34 is energized. When it is determined in step S120 that the first electromagnetic valve 34 is in the energized state, the process returns to step S100, and the determination process of step S100 is performed. When it is determined in step S120 that the first electromagnetic valve 34 is not in the energized state, the first electromagnetic valve 34 is controlled in the energized state in step S125, and then the determination process of step S100 is performed.

When it is determined in step S100 that the controller 50 is not in a state of learning the density, the controller 50 determines in step S110 whether the noise generation condition is satisfied. The noise generation condition is a preset condition in which noise is expected to be generated due to pressure fluctuation in the passage of the evaporated fuel or the wobbling sound of the ORVR valve 15. For example, the noise generation condition may be set to be satisfied when the current vehicle speed is equal to or lower than a predetermined speed. In this case, the controller 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 a vehicle Electronic Control Unit (ECU)60 that controls the running of the vehicle and controls a cooling system required for the running of the vehicle, and the vehicle speed information is output from the vehicle ECU60 to the controller 50. The predetermined speed is preferably set based on experimental results or empirical rules, and is set as a vehicle speed at which noise is overwhelmed by a running sound and is difficult to be recognized by a passenger in the vehicle compartment. Therefore, when the current vehicle speed is lower than the predetermined speed, the noise generation condition is satisfied. Therefore, it is possible to suppress noise that may be generated when the vehicle speed is low and the running sound is low.

For example, when the vehicle is stopped, running at a low speed or in an idling state of the engine 2, the controller 50 determines in step S110 that the noise generation condition is satisfied. When 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 performed.

In the flow returning from step S120 to step S100, and in the flow returning to step S100 after step S125 is executed, the first increase rate mode in fig. 5 is executed. In the first increase rate mode, since the increase rate of the flow rate of the fluid is small, the accuracy of knowing the evaporated fuel concentration can be improved. According to the first increase rate mode, the flow rate variation in a small flow rate range can be reduced as compared with a solenoid valve in which the flow rate increase rate is constant. Further, in the first increase rate mode, a small flow rate can be implemented, so that pulsation can be reduced and an effect of suppressing noise can be obtained. Further, in the first increase rate mode, since the fluid flow rate is reduced, the hunting of the ORVR valve 15 is reduced, and the effect of suppressing noise is obtained.

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

When it is determined in step S140 that the first electromagnetic valve 34 is not in the energized state, the process returns to step S100, and the determination process of step S100 is performed. When it is determined in step S140 that the first solenoid valve 34 is in the energized state, the controller 50 controls the first solenoid valve 34 in the de-energized state in step S150. In step S160, the controller 50 reduces the duty ratio of the second solenoid valve 35 to a predetermined value X%, and returns to step S100. The controller 50 performs control such that the duty ratio of the second solenoid valve 35 is gradually increased from a predetermined value toward 100%. The processes of steps S150 and S160 can smoothly switch the flow rate of the fluid controlled by the purge valve 3 from the first increase rate mode to the second increase rate mode as shown in fig. 5.

In this flowchart, when the first solenoid valve 34 is not in the energized state, the second increase rate mode shown in fig. 5 is executed. In the second increase rate mode, an increase in the flow rate is promoted so as to reduce the flow velocity resistance of the upstream passage. According to the second increase rate mode, the flow rate variation in a large flow rate range can be increased as compared with a solenoid valve in which the flow rate increase rate is constant. For this reason, in a state where noise is unlikely to be generated, the fluid flow rate can be rapidly increased, so that the output requirement of the engine 2 can be satisfied. According to the control according to the flowchart of fig. 4, it is possible to provide a flow control capable of suppressing noise caused by pulsation in the case where a large flow rate as shown in fig. 5 is achieved.

Further, when the current rotation speed of the engine 2 is lower than the predetermined rotation speed, the controller 50 may determine that the noise generation condition is satisfied in step S110. If such a determination process is employed, the predetermined rotation speed is preferably set based on experimental results or empirical rules, and is set to a vehicle speed at which noise is overwhelmed by engine sound and is difficult to recognize by a passenger. The noise generation condition is satisfied when the current rotation speed of the engine 2 is lower than a predetermined rotation speed. Therefore, when the engine speed is small and quiet, noise caused by pressure fluctuation or the like can be reduced.

The operational effects of the purge control valve apparatus exemplified by the purge valve 3 of the first embodiment will be described. The purge control valve apparatus includes a housing having a housing inner passage connecting an inflow port 31a and an outflow port 33 a. The purge control valve apparatus includes: a first electromagnetic valve 34 that opens and closes the first internal passage to control the flow rate of the evaporated fuel; and a second electromagnetic valve 35 that opens and closes the second internal passage to control the flow rate of the evaporated fuel. 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 controlled to operate individually. The first solenoid valve 34 is switched between a seated state in which the first valve body 34b is in contact with the first valve seat 31b1 and an unseated state in which the first valve body 34b is separated from the first valve seat 31b 1. The purge control valve device has a constricted passage 31c1 in which the flow rate of the evaporated fuel in one of the seated state and the unseated state is smaller than the flow rate of the evaporated fuel in the other of the seated state and the unseated state 31c 1.

Therefore, it is possible to provide the purge control valve device including the narrowed passage 31c1, in which the evaporated fuel flowing through 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 may be switched between the seated state and the unseated state such that the purge control valve device is set to the one state when it is desired to obtain a small flow rate characteristic or suppress pulsation, and is set to the other state when it is desired to secure a flow rate. As described above, a small flow characteristic and a large flow characteristic can be obtained, and a purge control valve apparatus capable of improving the flow characteristic can be obtained.

The purge control valve device includes the narrowed passage 31c1 such that the passage cross-sectional area of the first internal passage in one of the seated state and the unseated state of the first valve body is smaller than the passage cross-sectional area of the first internal passage in the other seated state. Therefore, it is possible to provide a purge control valve device including the narrowed passage 31c1, in which the passage cross-sectional area of the first internal passage is larger in the other state and smaller in the one state. The purge control valve device may switch the passage cross-sectional area of the first internal passage such that the purge control valve device is set to the one state when it is desired to obtain a small flow rate characteristic or suppress pulsation, and is set to the other state when it is desired to secure a flow rate. In the purge control valve apparatus, a small flow characteristic and a large flow characteristic can be obtained, and the purge control valve apparatus can improve the flow characteristic.

In the purge control valve apparatus, the first internal passage is provided upstream of the second internal passage. According to this configuration, in the case inner passage, the opening degree of the upstream passage can be changed, and the downstream passage can be opened and closed. Therefore, it is possible to provide a purge control valve apparatus in which the pressure loss can be reduced and the configuration and control of the second electromagnetic valve 35 can be simplified.

The purge valve 3 includes: a channel that functions as a narrowing channel in an unseated state; and an open passage having a passage cross-sectional area larger than that of the narrowed passage, and through which the evaporated fuel flows in a seated state. According to the purge valve 3, it is possible to provide a purge control valve device in which the evaporated fuel flowing through the constricted passages in the unseated state has a small flow rate in the unseated state, and the evaporated fuel flows through the open passages at a large flow rate in the seated state. The purge valve 3 can be switched between a seated state and an unseated state such that the purge valve 3 is set to the unseated state when it is desired to suppress pulsation, and the purge valve 3 is set to the seated state when it is desired to secure a flow rate. The purge valve 3 provides a purge control valve apparatus that can achieve pulsation suppression and flow rate assurance.

When increasing the flow rate of the evaporated fuel, the controller 50 individually controls the first solenoid valve 34 and the second solenoid valve 35 to perform a first increase rate mode and a second increase rate mode, in which the increase rate is greater than the first increase rate mode, respectively. The controller 50 controls the first solenoid valve 34 and the second solenoid valve 35 in a first increase rate mode such that the evaporated fuel flows through the constricted passage. The controller 50 controls the first solenoid valve 34 and the second solenoid valve 35 in the second increase rate mode such that the evaporated fuel flows through the open passage having a larger passage cross-sectional area than the narrowed passage. According to this control, it is possible to provide a purge control valve apparatus that can achieve pulsation suppression and flow rate assurance by switching the first increase rate mode and the second increase rate mode at appropriate timings. The purge valve 3 can obtain a wide range of flow rates and can improve flow rate characteristics.

In the flow rate increase control in which the flow rate of the evaporated fuel flowing out from the flow outlet 33a increases from zero, the controller 50 executes the first increase rate mode, and then executes the second increase rate mode. According to this control, it is possible to provide a purge control valve apparatus that can suppress pulsation of fluid and hunting of the ORVR valve 15 from the start of purge and can exhibit large purge performance.

The controller 50 controls the first solenoid valve 34 by opening and closing energization of the first solenoid valve 34, and controls the second solenoid valve 35 by controlling the duty ratio of the applied voltage. The controller 50 controls the second solenoid valve so as to increase the duty ratio of the applied voltage in the first increase rate mode. The controller 50 reduces the duty cycle of the applied voltage once when switching from the first increase rate mode to the second increase rate mode. Then, the controller 50 controls the second solenoid valve 35 to increase the duty ratio in the second increase rate mode. Therefore, at the time of switching from the first increase rate mode to the second increase rate mode, purge control in which the flow rate of the evaporated fuel flowing out from the outflow port 33a does not greatly change can be performed.

The controller 50 individually controls the first solenoid valve 34 and the second solenoid valve 35 to execute the first increase rate mode when the concentration of the evaporated fuel is known. According to this control, the evaporated fuel concentration learning can be performed with a small flow rate variation. Therefore, it is possible to provide a purge control valve apparatus that can achieve pulsation suppression and flow volume assurance, and also can improve the accuracy of concentration learning.

The controller 50 individually controls the first solenoid valve 34 and the second solenoid valve 35 to execute the first increase rate mode when a noise generation condition that can be expected is satisfied. According to this control, the first increase rate mode can be executed in a state where noise due to pulsation or oscillation of the ORVR valve 15 is likely to occur. Therefore, it is possible to provide a purge control valve apparatus that can suppress noise more effectively and achieve a sufficient flow rate.

(second embodiment)

A second embodiment will be described with reference to fig. 6 to 8. The purge valve 103 according to the second embodiment is different from the first embodiment in the first electromagnetic valve 134. The first electromagnetic valve 134 is a normally closed valve that controls a small flow by narrowing the upstream passage when no voltage is applied, and controls a large flow by fully opening the upstream passage when a voltage is applied. The second solenoid valve 135 has the same configuration and the same operation as the second solenoid valve 35. Configurations, actions, and effects not specifically described in the second embodiment are the same as those in the first embodiment, and only differences from the first embodiment will be described below. The description of the first embodiment with respect to the first solenoid valve 34 may be applied to the second embodiment by replacing the first solenoid valve 34 with the first solenoid valve 134. The description of the second solenoid valve 35 in the first embodiment can be applied to the second embodiment by replacing the second solenoid valve 35 with the second solenoid valve 135.

Next, the configuration of the purge valve 103 will be described. The purge valve 103 includes a first solenoid valve 134 and a second solenoid valve 135 disposed inside the housing. The first solenoid valve 134 and the second solenoid valve 135 are arranged inside the purge valve 103 in the direction from the upstream side to the downstream side. The first solenoid valve 134 and the second solenoid valve 135 are arranged in the displacement direction of the valve body of the purge valve 103 or in the axial direction of the valve body. The first solenoid valve 134 is located upstream of the second solenoid valve 135. The first electromagnetic valve 134 adjusts the passage cross-sectional area of the upstream passage in the purge valve 103. The second electromagnetic valve 135 adjusts the passage cross-sectional area of the downstream passage in the purge valve 103.

In the seated state of the first solenoid valve 134, the first valve body 34b contacts the first valve seat 31b 1. The flange 31b of the inflow housing 131 is not provided with the flow path narrowing wall 31c of the first embodiment. Therefore, the purge valve 103 does not include the narrowing passage 31c1 of the first embodiment.

The plate 134b1 is provided integrally with the upstream end of the movable core 342. The upstream surface of the plate 134b1 faces the first valve seat 31b1 in the axial direction. The plate 134b1 is provided with a plurality of or one through holes 134b 2. As shown in fig. 6, when the first valve body 34b is in the seated state, the through hole 134b2 forms a flow passage through which fluid can flow. As shown in FIG. 7, when the first valve body 34b is in the unseated state, the through-holes 134b2 form passages through which fluid does not flow. When the fluid flows at the first increasing rate shown in fig. 5, the through hole 134b2 corresponds to the upstream passage of the purge valve 103 through which the fluid flows.

The through hole 134b2 forms a passage having a smaller passage cross-sectional area than the passage 31b2 formed between the first valve body 34b and the first valve seat 31b1 in the unseated state shown in fig. 7. When the first valve body 34b is in the seated state, the through-hole 134b2 forms a constricted passage through which fluid flows. The purge valve 103 includes a narrowed passage that reduces the passage cross-sectional area of the first internal passage to be smaller than the passage cross-sectional area in the unseated state of the first valve body 34 b. The through-hole 134b2 is configured such that fluid does not flow through the through-hole 134b2 in the unseated state of the first valve body 34 b. When the fluid flows at the first increasing rate shown in fig. 5, the through hole 134b2 corresponds to the upstream passage of the purge valve 103 through which the fluid flows. The through hole 134b2 serves as a narrowing passage through which the evaporated fuel flows in a first increasing rate mode. The passage 31b2 forms an open passage through which vaporized fuel flows when the first valve body 34b is in the unseated state. The purge valve 103 includes an open passage that increases the passage cross-sectional area of the first internal passage to be larger than the passage cross-sectional area in the seated state of the first valve body 34 b. The passage 31b2 serves as an open passage through which the evaporated fuel flows in the second increase rate mode.

The first solenoid valve 134 and the second solenoid valve 135 each include a solenoid and a valve body, and form magnetic circuits, respectively. The first solenoid valve 134 and the second solenoid valve 135 are configured such that energization of their coils is individually controlled by the controller 50.

The first solenoid valve 134 includes a first valve body 34b and a first solenoid 34a, and the first solenoid 34a generates electromagnetic force to displace the first valve body 34 b. The first valve body 34b is capable of adjusting 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 31b 1. In the seated state of the first valve body 34b, the flow rate of the fluid increases at a small rate of increase, which is the first rate of increase shown in the graph of fig. 5. The first solenoid valve 134 shown in fig. 7 is controlled in an unseated state in which the first valve body 34b is separated from the first valve seat 31b 1. In the unseated state of the first valve body 34b, the flow rate of the fluid increases at a second rate of increase that is greater than the first rate of increase shown in the graph of fig. 5. When voltage is applied, the first solenoid 134 is controlled in an unseated state, and when voltage is not applied, the first solenoid 34 is controlled in a seated state.

In fig. 6 and 7, the second solenoid valve 135 is controlled in an unseated state in which the second valve body 35b is separated from the second valve seat 33c 1. The second electromagnetic valve 135 is a normally closed valve that is controlled to a closed state in which the downstream passage is closed when no voltage is applied, and is controlled to an open state in which the downstream passage is open when a voltage is applied. The controller 50 controls the duty cycle to energize the coil 350 of the second solenoid valve 135.

Next, the operation of the purge valve controller will be described with reference to the flowchart of fig. 8. The controller 50 executes the process according to the flowchart of fig. 8. The second solenoid valve 135 is controlled by energizing with a duty cycle, wherein the duty cycle is gradually increased 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 thereof in the first embodiment is incorporated herein.

When it is determined in step S200 that the controller 50 is in a state of learning the concentration, the controller 50 determines in step S220 whether the first solenoid valve 134 is not energized, i.e., in a deenergized state. When it is determined in step S220 that the first solenoid valve 134 is in the deenergized state, the process returns to step S200, and the determination process of step S200 is performed. 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 in the de-energized state in step S225, and then the determination process of step S200 is performed.

When it is determined in step S200 that the controller 50 is not in a state of learning the density, and it is determined in step S210 that the noise generation condition is satisfied, the determination process of S220 is performed. In the flow returning from step S220 to step S200, and in the flow returning to step S200 after step S225 is executed, the first increase rate mode in fig. 5 is executed. In the first increase rate mode, since the increase rate of the flow rate of the fluid is small, the accuracy of knowing the evaporated fuel concentration can be improved. In the first increase rate mode, the flow velocity of the fluid can be reduced, so that pulsation can be reduced and an effect of suppressing noise can be obtained. In the first increase rate mode, since the fluid flow rate is reduced, the oscillation of the ORVR valve 15 is reduced, and the effect of suppressing noise is obtained.

When it is determined in step S230 that the duty ratio has reached 100%, it is determined in step S240 whether the first solenoid valve 134 is in the deenergized state. When it is determined in step S240 that the first electromagnetic valve 134 is not in the deenergized state, the process returns to step S200, and the determination process of step S200 is performed. When it is determined in step S240 that the first solenoid valve 134 is in the deenergized state, the controller 50 controls the first solenoid valve 134 to be in the energized state in step S250. In step S260, the controller 50 reduces the duty ratio of the second solenoid valve 135 to a predetermined value X%, and returns to step S200. The controller 50 performs control such that the duty ratio of the second solenoid valve 135 is gradually increased from a predetermined value toward 100%. The processes of steps S250 and S260 may smoothly transition the fluid flow rate controlled by the purge valve 103 from the first increase rate mode to the second increase rate mode as shown in fig. 5.

In this flowchart, when the first solenoid valve 134 is not in the deenergized state, the second increase rate mode shown in fig. 5 is executed. In the second increase rate mode, in order to facilitate a large amount of control, the flow rate variation in a large flow rate range may be increased as compared to a solenoid valve in which the flow rate increase rate is constant. According to the control according to the flowchart of fig. 8, it is possible to provide a flow control capable of suppressing noise caused by pulsation in the case where a large flow rate as shown in fig. 5 is achieved.

The apparatus of the second embodiment comprises: a channel that functions as a narrowing channel in a seated state; and an open passage having a passage cross-sectional area larger than that of the narrowed passage, and through which the evaporated fuel flows in an unseated state. According to the purge valve 103, it is possible to provide a purge control valve device in which the evaporated fuel flowing through the constricted passages in the seated state has a small flow rate in the unseated state, and the evaporated fuel flows through the open passages at a large flow rate in the unseated state. The purge valve 103 can be switched between a seated state and an unseated state so that the purge valve 103 is set to the seated state when it is desired to suppress pulsation, and the purge valve 3 is set to the unseated state when it is desired to secure a flow rate. The purge valve 103 provides a purge control valve apparatus that can achieve improvement of small flow characteristics, pulsation suppression, and securing of a large flow rate. The purge valve 103 can obtain a wide range of flow rates and can improve flow rate characteristics.

(third embodiment)

The purge valve 203 of the third embodiment will be described with reference to fig. 9 to 10. The purge valve 203 differs from the first embodiment in that the purge valve 203 includes a second valve regulator 345 that moves in the axial direction together with the first valve body 34 b. The second valve regulator 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 regulator 345 may limit the movable distance of the movable core 352 of the second solenoid valve 235 in the unseated direction. The second valve regulator 345 moves integrally with the first valve body 34b in response to the electromagnetic force, and has a function of changing the displaceable range of the second valve body 35 b. Further, the second valve adjuster 345 and the movable core 342 may be configured as a single component.

The first solenoid valve 234 is a normally open valve, and controls a small flow by narrowing the upstream passage when voltage is applied, and controls a large flow by fully opening the upstream passage when voltage is not applied. The second solenoid valve 235 is a normally closed valve similar to the second solenoid valve 35. Configurations, actions, and effects not specifically described in the third embodiment are the same as those in the first embodiment, and only differences from the first embodiment will be described below.

Next, the configuration of the purge valve 203 will be described. The purge valve 203 includes a first solenoid valve 234 and a second solenoid valve 235 disposed inside the housing. The first solenoid valve 234 and the second solenoid valve 235 are arranged inside the purge valve 203 in the direction from the upstream side to the downstream side. The first solenoid valve 234 and the second solenoid valve 235 are arranged in the displacement direction of the valve body of the purge valve 203 or in the axial direction of the valve body. The first solenoid valve 234 is located upstream of the second solenoid valve 235. The first electromagnetic valve 234 adjusts the passage cross-sectional area of the upstream passage in the purge valve 203. The second electromagnetic valve 235 adjusts the passage cross-sectional area of the downstream passage in the purge valve 203.

The first solenoid valve 234 and the second solenoid valve 235 each include a solenoid and a valve body, and form magnetic circuits, respectively. The first solenoid valve 234 and the second solenoid valve 235 are configured such that energization of their coils is individually controlled by the controller 50. The first solenoid valve 234 includes a first valve body 34b and a first solenoid 234a, and the first solenoid 234a generates electromagnetic force to displace the first valve body 34 b. 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 an unseated state in which the first valve body 34b is separated from the first valve seat 31b 1. The first valve body 34b is controlled to be in an unseated state so as to implement a first rate of increase mode. The state shown in fig. 9 shows a state where the first increase rate mode shown in fig. 5 starts. The first solenoid valve 234 shown in fig. 10 is controlled to a seated state in which the first valve body 34b is in contact with the first valve seat 31b 1. The first valve body 34b is controlled to be in a seated state so as to implement the second rate of increase mode. The state shown in fig. 10 shows a state where the second increase rate mode shown in fig. 5 starts. When voltage is applied, the first solenoid valve 234 is controlled in an unseated state, and when voltage is not applied, the first solenoid valve 34 is controlled in a seated state.

The second valve regulator 345 is located closer to the second valve seat 33c1 together with the movable core 342 in the unseated state of the first valve body 34b than in the seated state shown in fig. 10. Therefore, the movable core 352 is located at a position closer to the second valve seat 33c1 in the unseated state of the first valve body 34b than in the seated state shown in fig. 10. The displaceable range within which the second valve body 35b can be displaced by the electromagnetic force is smaller in the unseated state of the first valve body 34b than in the seated state of the first valve body 34 b. The amount of stroke by which the second valve body 35b is displaceable to be seated in the unseated state of the first valve body 34b that performs the first rate-of-increase mode is shorter than in the seated state that performs the second rate-of-increase mode. The passage cross-sectional area of the second internal passage in the purge valve 203 is larger in fig. 10 than in fig. 9. The second valve regulator 345 brings the second valve body 35b closer to the second valve seat 33c1 in one state where the narrowed passage 31c1 is formed than in the other state.

In fig. 9 and 10, the second solenoid valve 235 is controlled in an unseated state in which the second valve body 35b is separated from the second valve seat 33c 1. The second electromagnetic valve 235 is a normally closed valve that is controlled to a closed state in which the downstream passage is closed when no voltage is applied, and is controlled to an open state in which the downstream passage is open when a voltage is applied. The controller 50 controls the duty cycle to energize the coil 350 of the second solenoid valve 235.

The first solenoid 234a includes a coil 340, a bobbin 341, a movable core 342, a fixed core 346, a yoke 347, a shaft 37c, and a spring 344. The center axis of the first solenoid 234a corresponds to the center axis of the first solenoid valve 234 and the center axis of the purge valve 203. The central axis of the first solenoid 234a is also the central axis of the second valve regulator 345. The shaft 37c supports the second valve regulator 345 to be slidable in the axial direction. The shaft 37c has a cylindrical body. The shaft 37c supports the second valve adjuster 345 to be slidable in the axial direction, so that the inner circumferential surface of the shaft 37c slides on the outer circumferential surface of the second valve adjuster 345. The second valve regulator 345 is formed of, for example, metal, resin, or the like.

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

The spring 344 is disposed between the shaft 37c and the movable core 342. The spring 344 provides an urging force to move the movable core 342 in a direction away from the shaft 37 c. The axial support 37 is made of, for example, metal or resin.

The fixed core 346 slidably supports the movable core 342, and the movable core 342 is moved in the axial direction against the urging force of the spring 344 by electromagnetic force. The fixed core 346 includes: a cylindrical portion 346b having opposite open ends in the axial direction; and an annular plate 346a having a flange shape and provided at an upstream end of the cylindrical portion 346 b. The inner peripheral surface of the cylindrical portion 346b slidably supports the movable core 342. The coil 340 is wound around the outer circumferential surface of the cylindrical portion 346b via a bobbin 341. The annular plate 346a is engaged with the outer cylindrical portion 37a of the axial support member 37. The fixed core 346 is provided integrally with the bobbin 341, the coil 340, the yoke 347 and the axial support 37. The yoke 347 includes a cylindrical portion 347b and an annular plate 347a, the annular plate 347a extending from an inner peripheral surface of a downstream end of the cylindrical portion 347b toward the center. The fixed core 346, the movable core 342, the first valve body 34b, the coil 340, and the yoke 347 are coaxial.

The fixed core 346, the movable core 342, and the yoke 347 are made of a material that transmits magnetic force. When the coil 340 is energized, a magnetic circuit indicated by a dotted line around the coil 340 in fig. 9 is formed. The magnetic circuit generates an electromagnetic force that attracts the movable core 342 toward the shaft 37 c. The electromagnetic force switches the first valve body 34b of the first solenoid valve 234 from the seated state to the unseated state. The magnetic circuit in the first solenoid valve 234 is formed by magnetic force passing through the annular plate 346a, the movable core 342, the cylindrical portion 346b, the annular plate 347a, and the cylindrical portion 347 b. The first valve body 34b, the movable core 342, and the second valve regulator 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 235a, and the second solenoid 235a generates electromagnetic force to displace the second valve body 35 b. The controller 50 controls the duty cycle to energize the coil 350 of the second solenoid valve 235. The second solenoid valve 235 is controlled such that the duty ratio is gradually increased from 0% to 100% when the first increase rate mode is implemented. The second solenoid valve 235 is controlled such that the duty ratio is gradually increased from the predetermined percentage X% to 100% when the second increase rate mode is implemented.

The second solenoid 235a includes a coil 350, a bobbin 351, a movable core 352, a fixed core 356, a yoke 357, a shaft 37c, and a spring 354. The center axis of the second solenoid 235a corresponds to the center axis of the second solenoid valve 235 and the center axis of the purge valve 203. The central axis of the second solenoid 235a is also the central axis of the second valve regulator 345. A spring 354 is provided between the shaft 37c and the movable core 352. The spring 354 provides an urging force to move the movable core 352 in a direction away from the shaft 37 c.

The fixed core 356 slidably supports the movable core 352, and the movable core 352 moves in the axial direction against the urging force of the spring 354 by electromagnetic force. The stationary core 356 includes a cylindrical portion 356b having opposite open ends in the axial direction, and an annular plate 356a having a flange shape and disposed at an upstream end of the cylindrical portion 356 b. The inner peripheral surface of the cylindrical portion 356b slidably supports the movable core 352. The coil 350 is wound around the outer circumferential surface of the cylindrical portion 356b via the bobbin 351. The annular plate 356a engages the outer cylindrical portion 37a of the axial support 37. The fixed core 356 is provided integrally with the bobbin 351, the coil 350, the yoke 357, and the axial support 37. The yoke 357 includes a cylindrical portion 357b and an annular plate 357a, the annular plate 357a extending from an inner peripheral surface of a downstream end of the cylindrical portion 357b toward the center. The fixed core 356, the movable core 352, the second valve body 35b, the coil 350, and the yoke 357 are coaxial.

The fixed core 356, the movable core 352, and the yoke 357 are made of a material that transmits magnetic force. When the coil 340 is energized, a magnetic circuit indicated by a dotted line around the coil 350 in fig. 9 and 10 is formed. The magnetic circuit generates an electromagnetic force that attracts the movable core 352 toward the shaft 37 c. The electromagnetic force switches the second valve body 35b of the second solenoid valve 235 from the seated state to the unseated state. The magnetic circuit in the second solenoid valve 235 is formed by magnetic force passing through the annular plate 356a, the movable core 352, the cylindrical portion 356b, the annular plate 357a, and the cylindrical portion 357 b. 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 controller 50 controls the purge valve 203 by executing the processing according to the flowchart of fig. 4, similarly to the first embodiment. The description of the processing according to the flowchart of fig. 4 in the first embodiment is incorporated herein 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 operational effects of the purge control valve apparatus exemplified by the purge valve 203 of the third embodiment will be described. The purge valve 203 includes: a channel that functions as a narrowing channel in an unseated state; and an open passage having a passage cross-sectional area larger than that of the narrowed passage, and through which the evaporated fuel flows in a seated state. According to the purge valve 203, it is possible to provide a purge control valve device in which the evaporated fuel flowing through the constricted passages in the unseated state has a small flow rate in the unseated state, and the evaporated fuel flows through the open passages at a large flow rate in the seated state. The purge valve 203 can be switched between a seated state and an unseated state so that the purge control valve device is set to one state when it is desired to obtain a small flow rate characteristic or suppress pulsation, and to the other state when it is desired to secure a flow rate. As described above, the purge valve 203 can obtain a small flow characteristic and a large flow characteristic, and the purge valve 203 provides a purge control valve apparatus capable of improving the flow characteristic.

The purge valve 203 includes a second valve adjuster 345 that changes an axial distance between the second valve body 35b and the second valve seat 33c1 according to the seated state and the unseated state of the first valve body 34 b. According to this configuration, the amount of stroke that the second valve body 35b can move to seat is smaller in the first rate-of-increase mode than in the second rate-of-increase mode. Therefore, it is possible to achieve precise flow rate variation and smooth flow rate variation in the first increase rate mode. The purge valve 203 helps to smoothly transition the fluid flow rate from the first increase rate mode to the second increase rate mode and helps to increase the linearity of the flow rate variation. These effects may help to reduce the range of pressure fluctuations in the flow path to the canister 13 and reduce the rattle of the ORVR valve 15.

(fourth embodiment)

The purge valve 303 of the fourth embodiment will be described with reference to fig. 11. The purge valve 303 differs from the purge valve 3 of the first embodiment in that the flow direction of the fluid inside the apparatus is reversed.

Regarding the purge valve 303, the configuration, action, and effect not specifically described in the fourth embodiment are the same as those in the first embodiment, and only the difference from the first embodiment will be described below. In the purge valve 303, the second electromagnetic valve 35 and the first electromagnetic valve 34 are arranged inside the apparatus in the direction from the upstream side to the downstream side. In the purge valve 303, the outlet 33a of the first embodiment serves as an inlet, and the inlet 31a of the first embodiment serves as an outlet. In a fourth embodiment, the second internal passage is an upstream passage in the casing internal passage, and the first internal passage is a downstream passage in the casing internal passage.

(fifth embodiment)

The purge valve 403 of the fifth embodiment will be described with reference to fig. 12. The purge valve 403 is different from the purge valve 103 of the second embodiment in that the flow direction of the fluid inside the apparatus is reversed.

Regarding the purge valve 403, the configuration, action, and effect not specifically described in the fifth embodiment are the same as those in the second embodiment, and only the difference from the first embodiment will be described below. In the purge valve 403, the second solenoid valve 135 and the first solenoid valve 134 are arranged inside the apparatus in the direction from the upstream side to the downstream side. In the purge valve 403, the outlet 33a of the second embodiment serves as an inlet, and the inlet 31a of the second embodiment serves as an outlet. In the fifth embodiment, the second internal passage is an upstream passage in the casing internal passage, and the first internal passage is a downstream passage in the casing internal passage.

(sixth embodiment)

The purge valve 503 in the sixth embodiment will be described with reference to fig. 13. The purge valve 503 is different from the purge valve 203 of the third embodiment in that the flow direction of the fluid inside the apparatus is reversed.

Regarding the purge valve 503, the configuration, action, and effect not specifically described in the sixth embodiment are the same as those in the third embodiment, and only the difference from the first embodiment will be described below. In the purge valve 503, the second solenoid valve 235 and the first solenoid valve 234 are arranged inside the apparatus in the direction from the upstream side to the downstream side. In the purge valve 503, the outlet 33a of the third embodiment serves as an inlet, and the inlet 31a of the third embodiment serves as an outlet. In a sixth embodiment, the second internal passage is an upstream passage in the casing internal passage, and the first internal passage is a downstream passage in the casing internal passage.

(other embodiments)

The disclosure in this specification is not limited to the illustrated embodiments. The present disclosure encompasses the illustrated embodiments and variations based on the embodiments made by those skilled in the art. For example, the present disclosure is not limited to the combinations of components and elements shown in the embodiments, and may be implemented in various modifications. The present disclosure may be implemented in various combinations. The present disclosure may have additional parts that may be added to the embodiments. This disclosure covers the omission of components and elements of the embodiments. The present disclosure encompasses substitutions and combinations of components, elements, and/or the like between one embodiment and another embodiment. The scope of the disclosed technology is not limited to the description of the embodiments. The technical scope disclosed is indicated by the description in the claims, and should be understood to include all modifications within the meaning and scope equivalent to the description in the claims.

The purge control valve apparatus in the specification includes a first solenoid valve that controls a flow on an upstream side, and a second solenoid valve that controls a flow on a downstream side in a passage connecting an inflow port and an outflow port. The purge control valve apparatus is not limited to the configuration having one inflow port and one outflow port. The purge control valve device may have a configuration including a plurality of inflow ports and a plurality of outflow ports. The purge control valve means may have an arrangement having one inflow port and a plurality of outflow ports. The purge control valve device may have an arrangement with a plurality of inflow ports and one outflow port.

As described in the fourth to sixth embodiments, the purge control valve apparatus in the specification is configured such that the first solenoid valve forming the narrowed passage is located downstream of the second solenoid valve. In this configuration, the first internal passage connected in series with the second internal passage is arranged downstream of the second internal passage.

While the disclosure has been described with reference to various exemplary embodiments thereof, it is to be understood that the disclosure is not limited to the disclosed embodiments and constructions. To the contrary, the disclosure is intended to cover various modifications and equivalent arrangements. In addition, while the various elements of the disclosure are shown in various example combinations and configurations, other combinations and configurations, including more, less or only a single element, are also within the spirit of the disclosure.