JP2021050692A - Purge control valve device - Google Patents

Abstract

To provide a purge control valve device which can inhibit reduction of a flow rate of a large flow side passage and achieves pulsation suppression at a low flow rate.SOLUTION: A housing internal passage includes a small flow side passage in which an evaporative fuel flowing from an inflow passage 31a1 into an inflow side chamber 31b flows to a second internal passage 43b. The small flow side passage includes a small contracted passage 31e1 provided at a position where the evaporative fuel flowing down from the inflow side chamber 31b to a first internal passage 43a does not pass. The small flow side passage includes a second communication passage 316 which allows the second internal passage 43b and the inflow side chamber 31b to communicate with each other at the upstream side of the second internal passage 43b. The contracted passage 31e1 has a passage cross sectional area smaller than that of the inflow side chamber 31b. The contracted passage 31e1 is provided at an upstream side partition wall 31e which partitions the second communication passage 316 from the inflow side chamber 31b.SELECTED DRAWING: Figure 9

Description

The disclosure herein relates to a purge control valve device.

Patent Document 1 discloses a purge control valve device having two solenoid valves built-in and having an on-off passage for opening and closing each solenoid valve.

Japanese Patent No. 5717876

In the purge control valve device, it is required to suppress noise caused by pulsation such as pressure fluctuation. On the other hand, the flow rate performance is also an important function for the purge control valve device. Therefore, the purge control valve device is required to have both pulsation countermeasures and flow rate performance.

One of the purposes disclosed in this specification is to provide a purge control valve device capable of suppressing a decrease in the flow rate of the flow rate on the large flow rate side and suppressing pulsation at a small flow rate.

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

One of the disclosed purge control valve devices is an inflow port (31a) having an inflow passage (31a1) into which the evaporative fuel spilled from the canister (13) flows in, and the evaporative fuel flows out toward the engine (2). A housing (31, 32, 33) having an outflow port (32a), an inflow port and an outflow port, and a housing internal passage connecting the inflow port and the outflow port, and a housing (31, 32, 33) provided inside the housing, the first. A first solenoid unit (37) that generates an electromagnetic force that displaces a first valve body (42a) that can open and close the internal passage (43a), and a passage crossing area that is provided inside the housing and is larger than that of the first internal passage. The second solenoid unit (38) that generates an electromagnetic force that displaces the second valve body (42b) that can open and close the second internal passage (43b) formed in a small size, and the evaporated fuel that flows out from the inflow passage flow in. An inflow side chamber chamber (31b) provided inside the housing is provided so that the first internal passage and the second internal passage can flow down separately.
The housing internal passage includes a large flow rate side flow path in which the evaporated fuel flowing from the inflow passage into the inflow side chamber chamber flows down to the first internal passage and a small flow rate side flow path in which the evaporated fuel flows down to the second internal passage.
The small flow rate side passage is provided at a position where the evaporated fuel flowing down from the inflow side chamber chamber to the first internal passage does not pass, and a throttle passage (31e1; 31f1) having a passage crossing area smaller than that of the upstream passage is provided. include.

According to this device, among the passages that branch from the inflow side chamber chamber to the large flow rate side flow rate and the small flow rate side flow rate, the throttle passage is included in the small flow rate side flow path that does not correspond to the large flow rate side flow rate. To be equipped. With the configuration related to this throttle passage, pulsation at the time of a small flow rate can be suppressed without affecting the flow rate on the large flow rate side. The purge control valve device can suppress a decrease in the flow rate of the flow rate on the large flow rate side and suppress pulsation at a small flow rate.

It is a block diagram of the evaporative fuel processing apparatus provided with the purge control valve apparatus of 1st Embodiment. It is a partial cross-sectional view of the purge control valve device which looked at the 3rd attachment part from the front. It is a rear view of the purge control valve device. It is a side view of the purge control valve device which looked at the 2nd attached part from the front. It is a side view of the purge control valve device which saw the 1st attached part from the front. It is an external view of the purge control valve device seen from the inflow side housing side. It is an external view of the purge control valve device seen from the outflow side housing side. It is a schematic diagram which shows the positional relationship of two solenoid valves, an inflow port and an outflow port. It is sectional drawing in the IX-IX cross section of FIG. FIG. 5 is a cross-sectional view taken along the line XX of FIG. It is sectional drawing in the cross section of XI-XI of FIG. It is a figure which shows the drawing passage provided in the inflow side housing. It is a perspective view which shows the diaphragm passage in 2nd Embodiment. It is sectional drawing of the inflow side housing of 2nd Embodiment.

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

(First Embodiment)
The first embodiment will be described with reference to FIGS. 1 to 12. The purge control valve device is used in the evaporative fuel processing device 1 which is an evaporative fuel purging system mounted on a vehicle. The purge valve 3 is an example of a purge control valve device. As shown in FIG. 1, the evaporative fuel processing device 1 supplies HC gas or the like in the fuel adsorbed on the canister 13 to the intake passage of the engine 2. This makes it possible to prevent the evaporated fuel from the fuel tank 10 from being released into the atmosphere. The evaporative fuel processing device 1 includes an intake system of the engine 2 that constitutes an intake passage of the engine 2 that is an internal combustion engine, and an evaporative fuel purge system that supplies the evaporated fuel to the intake system of the engine 2.

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

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

The fuel tank 10 is a container for storing fuel such as gasoline. The fuel tank 10 is connected to the inflow portion of the canister 13 by a pipe 11 forming a vapor passage. The canister 13 is a container in which an adsorbent such as activated carbon is sealed. The canister 13 takes in the evaporated fuel generated in the fuel tank 10 through the vapor passage and temporarily adsorbs it to the adsorbent.

The canister 13 is integrally provided with a valve module 12, or is provided via a duct portion. The valve module 12 includes a canister closed valve and an internal pump. The canister close valve opens and closes the suction section for sucking in fresh air from the outside. The internal pump is a pump capable of releasing gas to the atmosphere and inhaling the atmosphere. By providing the canister 13 with a canister close valve, atmospheric pressure can be applied to the inside of the canister 13. The canister 13 can easily desorb, that is, purge the evaporated fuel adsorbed on the adsorbent by the sucked fresh air.

The purge valve 3 is a purge control valve device including a valve body that opens and closes an internal passage that is a part of the purge passage. The purge control valve device has a plurality of solenoid valves inside. The purge valve 3 can allow and block the supply of evaporative fuel from the canister 13 to the engine 2. The configuration of the purge valve 3 will be described. The purge valve 3 has a solenoid valve that opens and closes each of a plurality of internal passages provided inside the housing. The purge valve 3 includes one inflow port 31a and one outflow port 32a. The inflow port 31a communicates with the canister 13 via the connected pipe 14. The inflow port 31a has an inflow passage 31a1 into which the evaporated fuel flowing out from the canister 13 flows in. The outflow port 32a communicates with the intake pipe 21 via a connected pipe. The outflow port 32a has an outflow passage 32a1 in which the evaporated fuel flows out toward the engine 2. Inside the purge valve 3, two internal passages branching on the downstream side of the inflow port 31a are provided. These two internal passages are further downstream and are concentrated in the outflow port 32a. Each of the two internal passages is a passage that is individually opened and closed by a solenoid valve.

When the purge valve 3 is opened by the control device while the vehicle is traveling, a difference between the negative pressure in the intake manifold 20 generated by the suction action of the piston and the atmospheric pressure applied to the canister 13 occurs. Due to this pressure difference, the vapor fuel adsorbed in the canister 13 flows through the purge passage and the purge valve 3 and is sucked into the intake manifold 20 through the intake pipe 21.

The evaporated fuel sucked into the intake manifold 20 is mixed with the original combustion fuel supplied from the injector or the like to the engine 2 and burned in the cylinder of the engine 2. In the cylinder of the engine 2, the air-fuel ratio, which is the mixing ratio of the combustion fuel and the intake air, is controlled to be a predetermined air-fuel ratio. The control device adjusts the purge amount of the evaporated fuel so that the predetermined air-fuel ratio is maintained even if the evaporated fuel is purged by controlling the purge valve 3 with duty energization.

As shown in FIGS. 2 and 8, the purge valve 3 includes a first solenoid valve 37 and a second solenoid valve 38 as an example of a plurality of solenoid valves. Each of the first solenoid valve 37 and the second solenoid valve 38 is composed of similar components. Each of the first solenoid valve 37 and the second solenoid valve 38 has a solenoid portion 41, a valve body 42, and a tubular portion 331. The first solenoid valve 37 includes a first valve body 42a and a first solenoid unit that generates an electromagnetic force that displaces the first valve body 42a. The first valve body 42a can open and close the first internal passage 43a communicating with the inside of one tubular portion 331. The second solenoid valve 38 includes a second valve body 42b and a second solenoid portion that generates an electromagnetic force that displaces the second valve body 42b. The second valve body 42b can open and close the second internal passage 43b communicating with the other tubular portion 331. A valve seat 332 is provided at the end of the tubular portion 331 so that the valve body is seated in the closed state and separated in the open state. The first solenoid valve 37 and the second solenoid valve 38 are, for example, normally closed type valves controlled to be in a closed state in which the internal passage is closed when no voltage is applied and in an open state in which the internal passage is opened when a voltage is applied.

The solenoid portion 41 of each solenoid valve includes a coil portion 410, a bobbin 411, a fixed core 413, a movable core 412, a shaft member 415, a spring 414, and the like. The solenoid portion 41 is covered with a coating portion formed of a resin material. The covering is integrally formed with the housing. It can be said that the solenoid portion 41 is resin-molded by the covering portion. The central axis of the solenoid unit 41 is also the central axis of the solenoid valve. Since the solenoid portion 41 has a higher specific gravity than the housing, the solenoid portion tends to vibrate with respect to an external force.

The movable core 412 is made of a material that conducts magnetism, for example, a magnetic material. The movable core 412, which is a tubular body, surrounds the shaft member 415 and the spring 414 in a state of being interpolated from the open end. The valve body 42 is made of an elastically deformable material such as rubber. The valve body 42 is attached to the movable core 412 so as to sandwich the head of the movable core 412 from both sides between the base portion and the valve portion, and is integrated with the movable core 412.

The fixed core 413 slidably supports a movable core 412 that moves in the axial direction against the urging force of the spring 414 by an electromagnetic force. The spring 414 has a tubular portion of the movable core 412 in a state where one end in the axial direction is in contact with the shaft member 415 fixed to the fixed core 413 and the other end in the axial direction is in contact with the head of the movable core 412. It is provided inside. Therefore, the spring 414 provides an urging force to move the movable core 412 toward the valve seat 332. The fixed core 413 fixes the shaft member 415 and is assembled to the bobbin 411. The fixed core 413, the shaft member 415, the movable core 412, and the valve body 42 are installed so that their axes are coaxial. The shaft member 415 is formed of, for example, nylon or nylon reinforced by containing glass fiber. The fixed core 413 and the movable core 412 are made of a material that allows magnetism to pass through. The fixed core 413 is formed of, for example, a carbon steel wire for cold heading. Each solenoid valve opens and closes the internal passage 43 by driving the valve body 42 according to the balance between the electromagnetic force generated when the coil portion 410 is energized and the urging force of the spring 414.

The housing is provided with a connector 31c extending from the solenoid portion 41 side of the first solenoid valve 37 in a direction orthogonal to the central axis of the solenoid portion 41. The housing is provided with a connector 31d extending from the solenoid portion 41 side of the second solenoid valve 38 in a direction orthogonal to the central axis of the solenoid portion 41. Each connector has a built-in terminal for energizing the coil portion 410. The connector is a resin molded portion that supports a terminal that penetrates the bottom of the housing and projects outward. The terminal is an energizing terminal that is electrically connected to the coil portion 410. A power supply side connector for supplying power from a power supply unit or a current control device is connected to the connector. When the connector and the power supply side connector are connected and the terminal is electrically connected to the current control device or the like, the purge valve 3 can control the current energizing the coil portion 410.

As shown in FIGS. 2 to 11, the purge valve 3 includes an inflow side housing 31, an outflow side housing 32, and a seat valve member 33 as housings. The inflow side housing 31, the outflow side housing 32, and the seat valve member 33 are made of a resin material. The inflow side housing 31 includes an inflow port 31a into which the evaporated fuel from the canister 13 flows in, and an inflow side chamber chamber 31b provided downstream of the inflow port 31a. The inflow side housing 31 is provided with a flange portion that is joined to the flange portion of the outflow side housing 32 by welding or adhesion. The inflow side housing 31 and the outflow side housing 32 are integrally joined by overlapping the flange portions of both with the outer peripheral edge of the seat valve member 33 sandwiched between them. The flange portion of the inflow side housing 31 is a portion that radially protrudes from the outer peripheral edge of the downstream opening located at the downstream end portion of the inflow side housing 31.

The inflow port 31a is a tubular portion having an inflow passage for fluid inside, and is located at an upstream end portion of the inflow side housing 31. The inflow port 31a is connected to a pipe 14 forming a purge passage in the evaporative fuel processing device 1, and communicates with the canister 13 via the pipe 14.

The inflow side chamber chamber 31b communicates with the inflow passage 31a1 at the upstream end, which has a smaller passage crossing area than the inflow side chamber chamber 31b. The inflow passage 31a1 and the inflow side chamber chamber 31b are provided so as to line up in the inflow direction of the fluid in the inflow passage 31a1. The downstream end of the inflow passage 31a1 is a chamber chamber inflow portion 31a2 facing the inflow side chamber chamber 31b. As shown in FIGS. 9 and 10, the upstream end of the first internal passage 43a is located in the inflow direction in which the evaporated fuel flows down the inflow passage 31a1 rather than the chamber chamber inflow portion 31a2. The inflow direction is a direction along the axial direction of the inflow port 31a. The inflow side chamber chamber 31b communicates with the first internal passage 43a and the second internal passage 43b downstream of the inflow side chamber chamber 31b. The passage crossing area in the inflow port 31a is the cross-sectional area when the inflow port 31a is cut by a plane orthogonal to the central axis of the passage. The passage crossing area of the inflow side chamber chamber 31b is the cross-sectional area when the inflow side chamber chamber 31b is cut by a plane orthogonal to the central axis of the passage formed by the inflow side chamber chamber 31b. The passage crossing area of the passage in the purge valve 3 sharply increases when the passage in the inflow port 31a advances to the inflow side chamber chamber 31b. The inflow side chamber chamber 31b provides a chamber volume that suppresses the pulsation that occurs in the purge valve 3.

The inflow side housing 31 includes a first side wall 311, a second side wall 312, a third side wall 313, and a fourth side wall 314. The inflow side housing 31 includes a connecting wall portion that faces the downstream opening and connects these side walls. As shown in FIG. 6, the connecting wall portion is a wall portion that covers the axial end portions of the first solenoid valve 37 and the second solenoid valve 38 and the inflow side chamber chamber 31b. The inflow port 31a is located closer to the outflow side housing 32 than the connecting wall portion. The inflow port 31a is located inside the connecting wall portion without protruding outward. The inflow port 31a extends along the connecting wall, the third side wall 313, and the fourth side wall 314. The inflow port 31a is provided so that the height dimension of the inflow side housing 31 from the flange portion is lower than that of the connecting wall portion.

The first side wall 311 and the second side wall 312 face each other. The third side wall 313 and the fourth side wall 314 face each other. The first side wall 311 connects the third side wall 313 and the fourth side wall 314 adjacent to each other. The second side wall 312 connects the third side wall 313 and the fourth side wall 314 adjacent to each other. The connector 31c and the connector 31d extend outward from the third side wall 313.

The inflow side housing 31 accommodates the first solenoid valve 37 and the second solenoid valve 38. As shown in FIG. 6, the first solenoid valve 37 and the second solenoid valve 38 are arranged side by side in the inflow side housing 31 on one side closer to the third side wall 313. The first solenoid valve 37 and the second solenoid valve 38 are arranged along the third side wall 313. The first solenoid valve 37 is arranged so as to be adjacent to both the first side wall 311 and the third side wall 313. The second solenoid valve 38 is arranged so as to be adjacent to both the second side wall 312 and the third side wall 313. The inflow port 31a and the inflow side chamber chamber 31b are arranged in the inflow side housing 31 on the other side opposite to the first solenoid valve 37 and the second solenoid valve 38. The inflow port 31a and the inflow side chamber chamber 31b are arranged so as to be arranged in the alignment direction of the first solenoid valve 37 and the second solenoid valve 38. The inflow side chamber chamber 31b is formed between the fourth side wall 314 and the first solenoid valve 37 and the second solenoid valve 38.

The seat valve member 33 has two tubular portions 331. Each of the two tubular portions 331 has a shape protruding from both sides of the plate-shaped portion 333. The tubular portion 331 has an upstream-side protruding portion that protrudes to the upstream side or the valve body side, and a downstream-side protruding portion that protrudes to the downstream side or the outflow port 32a side. The outer peripheral edge of the plate-shaped portion 333 is a portion sandwiched between the inflow side housing 31 and the outflow side housing 32. The plate-shaped portion 333 of the seat valve member 33 is a partition wall portion that separates the inflow side housing 31 side and the outflow side housing 32 side in the purge valve 3. The two tubular portions 331 are a first tubular portion 331a located on the first solenoid valve 37 side and a second tubular portion 331b located on the second solenoid valve 38 side.

The first tubular portion 331a has an internal first internal passage 43a and a first valve seat 332a of the first valve body 42a formed at the tip thereof. The second tubular portion 331b has an internal second internal passage 43b and a second valve seat 332b of the second valve body 42b formed at the tip thereof. These two valve seats 332 are located inside the inflow side housing 31. The downstream end portion 331a1 of the first tubular portion 331a and the downstream end portion 331b1 of the second tubular portion 331b are located inside the outflow side housing 32.

As shown in FIGS. 9 and 10, the upstream end of the second internal passage 43b is located on the side opposite to the inflow direction of the fluid in the inflow passage 31a1 with respect to the chamber chamber inflow portion 31a2. The upstream end of the second internal passage 43b is located on the side opposite to the side where the first internal passage 43a is located with respect to the chamber chamber inflow portion 31a2 in the inflow direction of the fluid.

The first internal passage 43a is a passage in which the flow rate of the fluid flowing down is larger than that of the second internal passage 43b. The housing internal passage includes a large flow rate side passage through which the evaporated fuel flows down into the first internal passage 43a and a small flow rate side passage through which the evaporated fuel flows down into the second internal passage 43b. The large flow rate side flow path is a flow path through which the evaporated fuel flows down in the order of the inflow passage 31a1, the inflow side chamber chamber 31b, the first connecting passage 315, and the first internal passage 43a. The small flow rate side flow path is a flow path through which the evaporated fuel flows down in the order of the inflow passage 31a1, the inflow side chamber chamber 31b, the second connecting passage 316, and the second internal passage 43b. The inflow side chamber chamber 31b is a common passage in the large flow rate side flow path and the small flow rate side flow rate. The evaporated fuel is divided from the inflow side chamber chamber 31b into a flow path that flows down to the first internal passage 43a and a flow path that flows down to the second internal passage 43b.

The first connecting passage 315 is a passage connecting the first internal passage 43a and the inflow side chamber chamber 31b on the upstream side of the first internal passage 43a. The first connecting passage 315 is a large flow rate side connecting passage provided in the large flow rate side flow path. The first connecting passage 315 is a passage provided closer to the inflow passage 31a1 than the first solenoid portion. A filter member 44 having a filter media unit or a net unit supported by the filter frame unit 44a is installed in the first connecting passage 315. The filter member 44 of the first connecting passage 315 collects foreign matter contained in the evaporated fuel before flowing down from the inflow side chamber chamber 31b and flowing down to the first internal passage 43a.

The second connecting passage 316 is a passage connecting the second internal passage 43b and the inflow side chamber chamber 31b on the upstream side of the second internal passage 43b. The second connecting passage 316 is a small flow side connecting passage provided in the small flow side flow path. The second connecting passage 316 is a passage provided closer to the inflow passage 31a1 than the second solenoid portion. The second connecting passage 316 is formed so that the passage crossing area is smaller than that of the first connecting passage 315 and the inflow side chamber chamber 31b, respectively. With this configuration, when the evaporated fuel flows from the inflow side chamber chamber 31b into the second connecting passage 316, it flows down from the wide passage to the narrow passage, so that the pressure loss becomes large. A filter member 44 having a filter media unit or a net unit supported by the filter frame unit 44a is installed in the second connecting passage 316. The filter member 44 of the second connecting passage 316 collects foreign matter contained in the evaporated fuel before flowing down from the inflow side chamber chamber 31b and flowing down to the second internal passage 43b.

As shown in FIGS. 9 to 11, the first internal passage 43a and the second internal passage 43b are located on one side in the orthogonal direction orthogonal to the inflow direction of the fluid. The inflow passage 31a1 is located on the other side of the housing in the orthogonal direction. The orthogonal direction is a direction orthogonal to both the coupling direction of the inflow side housing 31 and the outflow side housing 32 and the inflow direction. The bonding direction is also the stacking direction of the inflow side housing 31 and the outflow side housing 32.

The outflow port 32a is located between the inflow port 31a and the first internal passage 43a and the second internal passage 43b in the orthogonal direction. According to this configuration, the evaporated fuel can flow down the flow path in the orthogonal direction for a long time in the flow path from the inflow side chamber chamber 31b to the first internal passage 43a and the second internal passage 43b. Since the flow path in the orthogonal direction can be configured to be long, the flow path resistance in the large flow rate side flow path and the small flow rate side flow path can be suppressed, which can contribute to securing the flow rate. The downstream end of the first internal passage 43a is provided at a position closer to the upstream end of the outflow passage 32a1 than the downstream end of the second internal passage 43b. With this configuration, the flow path resistance of the large flow rate side flow path can be suppressed more than the flow rate resistance of the small flow rate side flow rate even in the flow path on the outflow passage 32a1 side. Therefore, it is possible to contribute to securing a large flow rate in the purge valve 3.

As shown in FIGS. 9 and 12, the purge valve 3 includes a throttle passage 31e1 that further increases the flow path resistance in the small flow rate side flow path. The housing internal passage includes a throttle passage 31e1 that communicates the inflow side chamber chamber 31b and the second connecting passage 316. The throttle passage 31e1 constitutes a passage upstream of the second connecting passage 316 and having a passage crossing area smaller than that of the second connecting passage 316. The purge valve 3 includes an upstream partition wall 31e that partitions the inflow side chamber chamber 31b and the second connecting passage 316 in the direction in which the solenoid portions are arranged. The upstream side partition wall 31e is a wall portion protruding from the inner wall surface of the inflow side housing 31. The throttle passage 31e1 is formed by a recess or a hole provided in the upstream partition wall 31e. The throttle passage 31e1 may be provided by a hole penetrating the upstream partition wall 31e.

Further, the purge valve 3 may be configured to include an inflow port in which the inflow direction of the fluid in the inflow passage 31a1 in the inflow port 31a is opposite to that of the first embodiment. The inflow port in this case is provided on the inflow side housing 31 on the side opposite to the inflow port 31a. According to this configuration, the pressure loss in the large flow rate side flow path of the purge valve 3 can be increased.

When the evaporated fuel flows down from the inflow side chamber chamber 31b to the second connecting passage 316, it collides with the upstream side partition wall 31e, so that the pressure loss becomes large. The evaporated fuel that collides with the upstream partition wall 31e flows to the throttle passage 31e1 side along the upstream partition wall 31e, and the narrow throttle passage 31e1 further gives a pressure loss. The purge valve 3 is provided with the upstream side partition wall 31e and the throttle passage 31e1 so that the pressure loss is further concentrated in the small flow rate side flow path.

The purge valve 3 has a configuration in which the pressure loss is concentrated in the flow rate on the small flow rate side in the flow path from the inflow passage 31a1 to the internal passage in which the opening degree of each valve body is adjusted. The purge valve 3 provides a flow path configuration in which the flow path does not bend in the opposite direction or passes through an extremely narrow flow path for the large flow rate side flow path. The purge valve 3 provides a flow path configuration in which the flow rate resistance is larger than that of the large flow rate side flow rate by having the flow rate in the opposite direction with respect to the small flow rate side flow rate.

As shown in FIG. 11, the outflow side housing 32 surrounds the downstream side protruding portion protruding from the plate-shaped portion 333 of the seat valve member 33 in the two tubular portions 331. The first tubular portion 331a and the second tubular portion 331b have a shape extending along each other. The downstream protruding portion of the first tubular portion 331a is longer than the downstream protruding portion of the second tubular portion 331b. The first tubular portion 331a is configured such that the axial length from the valve seat to the downstream end portion 331a1 is longer than that of the second tubular portion 331b. The downstream end portion 331a1 is located at a position separated from the plate-shaped portion 333 of the seat valve member 33 from the downstream end portion 331b1. The first tubular portion 331a forms an internal passage longer than the second tubular portion 331b.

The outflow side housing 32 includes an outflow port 32a for flowing out the evaporated fuel toward the intake pipe 21 and an outflow side chamber chamber 32b provided on the upstream side of the outflow port 32a. The flange portion of the outflow side housing 32 is a portion that radially protrudes from the outer peripheral edge of the upstream opening located at the upstream end portion of the outflow side housing 32. The outflow side chamber chamber 32b communicates with the outflow passage 32a1 in the outflow port 32a, which has a smaller passage crossing area than the outflow side chamber chamber 32b at the downstream end. The outflow side chamber chamber 32b connects the outflow port 32a with the first internal passage 43a and the second internal passage 43b inside the housing.

The outflow port 32a is a tubular portion having a fluid outflow passage inside, and is located at the downstream end of the outflow side housing 32. The outflow port 32a communicates with the intake pipe 21 via a connected pipe. The outflow port 32a is preferably located closer to the inflow side housing 31 than the outermost wall portion forming the outflow side housing 32. The outflow port 32a is located inside the outermost wall portion without protruding outward. The outflow port 32a is arranged so as to be arranged in the alignment direction of the first solenoid valve 37 and the second solenoid valve 38. The outflow port 32a extends toward the tip along the same direction as the inflow port 31a. The outflow port 32a is provided so that the height dimension of the outflow side housing 32 from the flange portion is equal to or lower than the outermost wall portion of the outflow side housing 32.

The purge valve 3 is fixed to the vehicle side member by a fixing means such as a bolt via a plurality of attached portions. For example, a female screw portion to be screwed into a bolt is embedded in a vehicle side member. The purge valve 3 has a first attachment portion 34 that projects outward from the first side wall 311 of the inflow side housing 31. The first mounted portion 34 is provided with a mounting hole penetrating in the coupling direction in which the inflow side housing 31 and the outflow side housing 32 are overlapped with each other. The mounting hole of the first mounted portion 34 is a through hole for inserting a fixing means such as a bolt to be coupled to the vehicle side member. The first attached portion 34 is arranged at a position biased to one side in the inflow side housing 31. The first mounting portion 34 is arranged laterally in the inflow side housing 31 so as to be aligned with the first solenoid valve 37.

The purge valve 3 has a second attachment portion 35 that projects outward from the second side wall 312 of the inflow side housing 31. The second attachment portion 35 is provided with an attachment hole penetrating in the coupling direction in which the inflow side housing 31 and the outflow side housing 32 are overlapped with each other. The mounting hole of the second mounted portion 35 is a through hole for inserting a fixing means such as a bolt to be coupled to the vehicle side member. The second attached portion 35 is arranged at a position biased to one side in the arrangement direction of the solenoid portions in the inflow side housing 31. The second mounting portion 35 is arranged laterally in the inflow side housing 31 so as to be aligned with the second solenoid valve 38. The first mounted portion 34, the first solenoid portion, the second solenoid portion, and the second mounted portion 35 are arranged so as to overlap each other in the alignment direction of the first solenoid portion and the second solenoid portion.

The purge valve 3 has a third attachment portion 36 that projects outward from the third side wall 313 of the inflow side housing 31. The third attached portion 36 is located on one side of the inflow side housing 31, and is provided on the third side wall 313 adjacent to the first attached portion 34 and the second attached portion 35. The third mounting portion 36 is provided with a mounting hole that penetrates in the coupling direction in which the inflow side housing 31 and the outflow side housing 32 are overlapped with each other. The mounting hole of the third mounted portion 36 is a through hole for inserting a fixing means such as a bolt to be coupled to the vehicle side member.

The second solenoid valve 38 is configured so that the fluid flow rate flowing through the fully opened second internal passage 43b is the smallest among the plurality of solenoid valves. The first solenoid valve 37 is configured so that the flow rate of the fluid flowing through the fully opened first internal passage 43a is larger than that of the second solenoid valve 38. In the purge valve 3, the first solenoid valve 37 is a flow rate adjusting valve that provides a large flow rate performance, and the second solenoid valve 38 is a flow rate adjusting valve that provides a small flow rate performance. The first internal passage 43a has a passage crossing area larger than that of the second internal passage 43b.

The first internal passage 43a is formed so that the flow rate of the fluid that can flow down is larger than that of the second internal passage 43b. With this configuration, the vibration associated with the opening / closing operation of the first valve body 42a can be larger than the vibration associated with the opening / closing operation of the second valve body 42b. The purge valve 3 has a configuration in which the first mounted portion 34 and the second mounted portion 35 are lined up with the first solenoid portion in between, as a configuration capable of suppressing this vibration.

For example, when the supply flow rate to the engine 2 requires a small flow rate, the first solenoid valve 37 is in the closed state, and the second solenoid valve 38 is energized and controlled by the control device to be in the valve open state. When a small flow rate is required, the control device controls the ratio of the on-time to the total time of energization on and off, that is, the duty ratio, to energize the coil portion 410 of the second solenoid valve 38. When a small flow rate is requested, the duty energization control allows the small flow rate of evaporated fuel flowing through the second internal passage 43b to be supplied into the intake pipe 21 from the outflow port 32a.

When a shift is made from the time when a small flow rate is requested to the time when a large flow rate is required, the second solenoid valve 38 is always open, and the first solenoid valve 37 is duty-energized controlled to be in an open state. When a large flow rate is requested, in addition to the small flow rate flowing through the second internal passage 43b in the fully open state, a large flow rate of evaporated fuel flowing through the first internal passage 43a is supplied into the intake pipe 21 from the outflow port 32a by duty energization control. Will be done. When a small flow rate is required, the valve opening rate of the second valve body 42b is increased and the supply flow rate is controlled to increase toward the time when a large flow rate is required. When a large flow rate is required, the supply flow rate when the second valve body 42b is always open is controlled so that the valve opening rate of the first valve body 42a increases and the supply flow rate increases. With such control, the flow rate increase rate when a large flow rate is requested becomes larger than the flow rate increase rate when a small flow rate is requested. The purge valve 3 is controlled so that the second solenoid valve 38, which provides the small flow rate performance, is opened first when the supply starts from the state where the supply flow rate to the engine 2 is zero.

The operation and effect brought about by the purge control valve device disclosed by the purge valve 3 of the first embodiment will be described. The purge control valve device includes a housing having an inflow port 31a and an outflow port 32a and having a housing internal passage connecting these ports. Inside the housing, a first solenoid unit that generates an electromagnetic force that displaces the first valve body 42a that can open and close the first internal passage 43a and a second valve body 42b that can open and close the second internal passage 43b are displaced. A second solenoid unit for generating an electromagnetic force is provided. The second internal passage 43b is formed to have a smaller passage crossing area than the first internal passage 43a. An inflow side chamber chamber 31b is provided inside the housing so that the evaporative fuel flowing out from the inflow passage 31a1 can flow in and the evaporative fuel can flow down into the first internal passage 43a and the second internal passage 43b. There is.

The housing internal passage has a large flow rate side passage in which the evaporated fuel flowing from the inflow passage 31a1 into the inflow side chamber chamber 31b flows down to the first internal passage 43a and a small flow rate side passage in which the evaporated fuel flows down to the second internal passage 43b. Includes. The small flow rate side passage includes a throttle passage 31e1 provided at a position where the evaporated fuel flowing down from the inflow side chamber chamber 31b to the first internal passage 43a does not pass. The throttle passage 31e1 is a passage whose crossing area is smaller than that of the passage on the upstream side.

According to this device, the throttle passage 31e1 is provided at a position included in the small flow rate side flow rate among the passages branched from the inflow side chamber chamber 31b into the large flow rate side flow rate and the small flow rate side flow rate. With the configuration related to the throttle passage 31e1, pulsation at the time of a small flow rate can be suppressed without affecting the flow rate on the large flow rate side. The purge control valve device can suppress a decrease in the flow rate of the flow rate on the large flow rate side and suppress pulsation at a small flow rate.

According to this purge control valve device, the pressure loss of the flow path leading to the second internal passage 43b, which has a small flow rate, can be further increased by the throttle passage 31e1. Therefore, the purge control valve device can further widen the flow rate range in the small flow rate range.

The small flow rate side flow path includes a small flow rate side communication passage that connects the second internal passage 43b and the inflow side chamber chamber 31b on the upstream side of the second internal passage 43b. The small flow rate side connecting passage is a passage having a passage crossing area smaller than that of the inflow side chamber chamber 31b. The throttle passage 31e1 is formed by a recess or a hole provided in the upstream side partition wall 31e that partitions the small flow rate side connecting passage and the inflow side chamber chamber 31b. The throttle passage 31e1 is a passage having a passage crossing area smaller than that of the inflow side chamber chamber 31b.

According to this configuration, the upstream side partition wall 31e for partitioning the small flow rate side connecting passage downstream from the inflow side chamber chamber 31b and the inflow side chamber chamber 31b is provided. Since the throttle passage 31e1 is provided on the upstream side partition wall 31e, the pulsation of the evaporated fuel can be reduced at the place where the inflow side chamber chamber 31b enters the small flow rate side connecting passage.

The inflow passage 31a1 and the inflow side chamber chamber 31b are provided so as to line up in the inflow direction in which the evaporated fuel flows down the inflow passage 31a1. The throttle passage 31e1 is located in a direction opposite to the inflow direction with respect to the inflow side chamber chamber 31b. According to this configuration, the evaporated fuel further flows down from the inflow side chamber chamber 31b to the small flow rate side flow path, and forms a flow path bent in the direction opposite to the inflow direction. The evaporated fuel suffers a pressure loss in the process of flowing down between the inflow side chamber chamber 31b and the small flow rate side connecting passage. Further, for example, the pulsating flow propagating to the upstream side in the valve closed state can be diffused in the small flow rate side connecting passage and then a pressure loss can be given by the throttle passage 31e1. With this flow path configuration, it is possible to provide an effect of further suppressing pulsation at a small flow rate.

The upstream side partition wall 31e is a wall that is erected from the wall portion that is the downstream end portion of the inflow passage 31a1 and forms the chamber chamber inflow portion 31a2 facing the inflow side chamber chamber 31b to the small flow rate side flow path. According to this, the throttle passage 31e1 can be set at the boundary portion with the inflow side chamber chamber 31b in the small flow rate side flow path by the configuration in which the upstream side partition wall 31e protrudes from the inner wall of the housing.

According to the purge valve 3, the upstream end portion of the first internal passage 43a is provided at a position separated from the chamber chamber inflow portion 31a2, which is the downstream end portion of the inflow passage 31a1, in the inflow direction. Further, the upstream end of the second internal passage 43b is provided on the side opposite to the side where the first internal passage 43a is located with respect to the chamber chamber inflow portion 31a2 in the inflow direction. The evaporated fuel that has flowed into the inflow side chamber chamber 31b from the inflow passage 31a1 flows into the first internal passage 43a without passing through a flow path that is bent in the direction opposite to the inflow direction. Further, in the process of flowing down from the inflow side chamber chamber 31b to the second internal passage 43b, the evaporated fuel flows down in the inflow direction and then forms a flow path bent in the opposite direction. With this flow path configuration, the pressure loss of the flow path leading to the first internal passage 43a having a large flow rate can be suppressed, and the pressure loss of the flow path leading to the second internal passage 43b having a small flow rate can be increased. This device further increases the flow rate in the large flow rate side flow path from the inflow side chamber chamber 31b to the first internal passage 43a, and realizes further reduction in the flow rate in the small flow rate side flow rate leading to the second internal passage 43b. The purge valve 3 can secure a large flow rate by utilizing the flow path leading to the first internal passage 43a. Further, the purge valve 3 can widen the flow rate range in the small flow rate range by utilizing the flow path leading to the second internal passage 43b.

A second connecting passage 316 that connects the second internal passage 43b and the inflow side chamber chamber 31b is provided on the upstream side of the second internal passage 43b. The second connecting passage 316 has a smaller passage crossing area than each of the first connecting passage 315 connecting the first internal passage 43a and the inflow side chamber chamber 31b and the inflow side chamber chamber 31b. According to this, the pressure loss of the flow path leading to the second internal passage 43b, which has a small flow rate, can be further increased. Therefore, the purge valve 3 can further widen the flow rate range in the small flow rate range.

The first internal passage 43a and the second internal passage 43b are located on one side in the housing in an orthogonal direction orthogonal to the inflow direction. The inflow passage 31a1 is located on the other side of the housing in the orthogonal direction.

According to this configuration, a large flow rate side flow path from the inflow passage 31a1 to the first internal passage 43a via the inflow side chamber chamber 31b can be extended in a direction orthogonal to the inflow direction. As a result, the chamber chamber inflow portion 31a2 and the first internal passage 43a can be arranged diagonally in the housing. Therefore, the large flow rate side flow path can be set long, and a flow path with further suppressed pressure loss can be provided.

Further, the outflow port 32a is located between the inflow port 31a and the first internal passage 43a and the second internal passage 43b in the orthogonal direction. According to this, it is possible to widely secure the outflow side chamber chamber 32b provided on the upstream side of the outflow port 32a and into which the evaporated fuel flowing down the first internal passage 43a and the second internal passage 43b flows in while suppressing the physique of the housing. ..

The inflow port 31a has a duct shape extending along the alignment direction of the first solenoid portion and the second solenoid portion. According to this, when the external pipe is connected to the inflow port 31a, the mounting space on the inflow port 31a side including the external pipe can be suppressed in the direction orthogonal to the arrangement direction.

The outflow port 32a has a duct shape extending along the inflow passage 31a1. According to this, when the external pipe is connected to the inflow port 31a and the outflow port 32a, the mounting space including the external pipe can be suppressed in the direction orthogonal to the arrangement direction.

The purge valve 3 includes a first tubular portion 331a having a first internal passage 43a inside, and a second tubular portion 331b having a second internal passage 43b inside. The first tubular portion 331a has a shape extending along the second tubular portion 331b, and forms an internal passage longer than the second tubular portion 331b. According to this, the first tubular portion 331a having a larger flow rate than the second tubular portion 331b is longer. This configuration is advantageous in securing the flow rate under the condition that the engine 2 side has a low negative pressure, and it is more efficient to lengthen the first tubular portion 331a. On the other hand, even if the second tubular portion 331b is made longer, the effect of securing the flow rate is low. Therefore, by shortening the second tubular portion 331b, the physique of the housing can be suppressed at the relevant portion, and the amount of the material forming the second tubular portion 331b can be suppressed.

(Second Embodiment)
The second embodiment will be described with reference to FIGS. 13 and 14. The second embodiment is different from the first embodiment in the configuration related to the throttle passage 31f1 formed in the inflow side housing 131. The configurations, actions, and effects that are not particularly described in the second embodiment are the same as those in the first embodiment, and only the differences will be described below.

As shown in FIGS. 13 and 14, the throttle passage 31f1 of the second embodiment is provided on the downstream side partition wall 31f. The downstream side partition wall 31f is a wall provided between the second internal passage 43b and the second connecting passage 316 on the upstream side of the second internal passage 43b. The downstream side partition wall 31f is provided so as to cover the second connecting passage 316 side or the inflow port 31a side in the second solenoid portion. The tip of the second solenoid section on the second valve body side is located at a lower position on the inflow port 31a side than the tip of the downstream partition wall 31f. The tip of the downstream partition wall 31f is located closer to the downstream end of the second internal passage 43b than the upstream end of the second valve seat 332b and the second internal passage 43b. The throttle passage 31f1 has a passage crossing area smaller than that of the second connecting passage 316, and is formed by a recess or a hole provided in the downstream side partition wall 31f. With this configuration, the evaporated fuel from the second connecting passage 316 to the second internal passage 43b flows so as to get over the downstream side partition wall 31f, and a part of the evaporated fuel passes through the narrow throttle passage 31f1.

The operation and effect brought about by the purge control valve device of the second embodiment will be described. The housing includes a downstream partition wall 31f provided between the second internal passage 43b and the small flow rate side connecting passage on the upstream side of the second internal passage 43b. The throttle passage 31f1 has a smaller passage crossing area than the small flow rate side connecting passage, and is formed by recesses or holes provided in the downstream side partition wall 31f. According to this, the pulsation of the evaporated fuel can be reduced at the place where the small flow rate side connecting passage enters the second internal passage 43b. Since this purge control valve device can reduce the pulsation at a position near the portion where the valve body opens and closes the second internal passage 43b, the distance for the pulsation to propagate can be shortened, which can contribute to the reduction of noise.

The inflow passage and the inflow side chamber chamber are arranged in the inflow direction in which the evaporated fuel flows down the inflow passage 31a1. The throttle passage 31f1 is located at the downstream end of the inflow passage 31a1 in a direction opposite to the inflow direction of the chamber chamber inflow portion 31a2 facing the inflow side chamber chamber 31b. The throttle passage 31f1 is located closer to the second solenoid portion than the inflow passage 31a1 in the orthogonal direction orthogonal to the inflow direction. According to this, the flow path from the inflow side chamber chamber 31b to the throttle passage 31f1 via the small flow rate side connecting passage can be formed so as to bend in the orthogonal direction. According to this bent flow path, it is possible to provide a purge control valve device capable of further increasing the pressure loss given to the evaporated fuel at a small flow rate.

The second tubular portion 331b provided coaxially with the second solenoid portion has a second internal passage 43b inside. The throttle passage 31f1 is located closer to the downstream end of the second inner passage 43b than the upstream end of the second inner passage 43b. According to this, the throttle passage 31f1 is located closer to the downstream end of the second inner passage 43b than the portion where the valve body opens and closes the second inner passage 43b. The evaporated fuel that has flowed back from the upstream end of the second internal passage 43b collides with the downstream partition wall 31f, then flows along the wall, and flows down the throttle passage 31f1. For example, it is possible to provide a purge control valve device in which the pressure loss of the evaporated fuel becomes larger and the pulsation can be reduced.

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

The purge control valve device that can achieve the object disclosed in the specification is not limited to the configuration described with reference to the drawings in the above-described embodiment. The purge valve in the above-described embodiment is shown so that the inflow port 31a is located below the outflow port 32a. The positional relationship between the inflow port 31a and the outflow port 32a is not limited to this form. The inflow port 31a may be configured to be located above the outflow port 32a, or the inflow port 31a and the outflow port 32a may be arranged side by side. Further, the positional relationship between the inflow port 31a and the first internal passage 43a and the second internal passage 43b may also be arranged in the vertical direction.

2 ... Engine, 13 ... Canister, 31 ... Inflow side housing (housing)
31a ... Inflow port, 31a1 ... Inflow passage, 31b ... Inflow side chamber chamber 31e1, 31f1 ... Squeezing passage, 32 ... Outflow side housing (housing)
32a ... Outflow port, 33 ... Seat valve member (housing)
37 ... 1st solenoid valve (1st solenoid part), 38 ... 2nd solenoid valve (2nd solenoid part)
42a ... 1st valve body, 42b ... 2nd valve body, 43a ... 1st internal passage 43b ... 2nd internal passage

Claims (7)

An inflow port (31a) having an inflow passage (31a1) into which the evaporated fuel spilled from the canister (13) flows in, and
An outflow port (32a) through which evaporative fuel flows toward the engine (2),
A housing (31, 32, 33) having the inflow port and the outflow port and having a housing internal passage connecting the inflow port and the outflow port.
A first solenoid unit (37) that is provided inside the housing and generates an electromagnetic force that displaces a first valve body (42a) that can open and close the first internal passage (43a).
An electromagnetic force is generated that displaces a second valve body (42b) that is provided inside the housing and can open and close the second internal passage (43b) that is formed to have a passage crossing area smaller than that of the first internal passage. The second solenoid part (38) and
An inflow side chamber chamber (31b) provided inside the housing so that the evaporated fuel flowing out from the inflow passage can flow into the first internal passage and the second internal passage separately and flow down.
With
The housing internal passage includes a large flow rate side flow path in which the evaporated fuel flowing from the inflow passage into the inflow side chamber chamber flows down to the first internal passage and a small flow rate side flow path in which the evaporated fuel flows down to the second internal passage. Including
The small flow rate side passage is provided at a position where the evaporated fuel flowing down from the inflow side chamber chamber to the first internal passage does not pass, and the passage crossing area is narrowed to be smaller than that of the upstream passage. A purge control valve device comprising (31e1; 31f1). The small flow rate side passage has a smaller passage crossing area than the inflow side chamber chamber, and is connected to the second internal passage and the inflow side chamber chamber on the upstream side of the second internal passage. Including passage (316)
The throttle passage has a passage crossing area smaller than that of the inflow side chamber chamber, and is provided by a recess or a hole provided in the upstream side partition wall (31e) that partitions the small flow rate side connecting passage and the inflow side chamber chamber. The purge control valve device according to claim 1, which is formed. The inflow passage and the inflow side chamber chamber are provided so as to line up in the inflow direction in which the evaporated fuel flows down the inflow passage.
The purge control valve device according to claim 2, wherein the throttle passage is located in a direction opposite to the inflow direction from the inflow side chamber chamber. The upstream side partition wall is erected in the small flow rate side flow path from the wall portion which is the downstream end of the inflow passage and forms the chamber chamber inflow portion (31a2) facing the inflow side chamber chamber. The purge control valve device according to claim 3, which is a wall. The small flow rate side passage has a smaller passage crossing area than the inflow side chamber chamber, and is connected to the second internal passage and the inflow side chamber chamber on the upstream side of the second internal passage. Including passage (316)
On the upstream side of the second internal passage, a downstream partition wall (31f) provided between the second internal passage and the small flow rate side connecting passage is provided.
The purge control valve device according to claim 1, wherein the throttle passage has a passage crossing area smaller than that of the small flow rate side connecting passage, and is formed by a recess or a hole provided in the downstream side partition wall. The inflow passage and the inflow side chamber chamber are provided so as to line up in the inflow direction in which the evaporated fuel flows down the inflow passage.
The throttle passage is located at the downstream end of the inflow passage and in a direction opposite to the inflow direction from the chamber chamber inflow portion (31a2) facing the inflow side chamber chamber, and is orthogonal to the inflow direction. The purge control valve device according to claim 5, which is located closer to the second solenoid portion than the inflow passage in the orthogonal direction. A second tubular portion (331b) provided coaxially with the second solenoid portion and having the second internal passage inside is provided.
The purge control valve device according to claim 6, wherein the throttle passage is located closer to the downstream end of the second internal passage than the upstream end of the second internal passage.

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