JP4084644B2 - High pressure solenoid valve - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a high pressure solenoid valve for controlling a high pressure fluid.
[0002]
[Prior art]
In recent years, development of a natural gas vehicle replacing a gasoline vehicle has been promoted from the viewpoint of environmental problems, particularly energy problems. A natural gas vehicle is basically the same as a gasoline vehicle, but the high-pressure (for example, 20 MPa) compressed natural gas stored in a fuel tank is used as engine fuel. Have different specific fuel supply devices.
[0003]
FIG. 14 is a conceptual diagram showing an example of a fuel supply device for a natural gas vehicle.
In the fuel supply device, an overflow prevention valve 102 is connected to the fuel tank 101, and check valves 103 and 104 are connected in parallel to the overflow prevention valve 102. The check valve 104 is disposed on the downstream side of the main check valve 105, and the check valve 103 is connected to a bypass circuit L that connects the filling port 106 and the fuel tank 101. Here, the check valves 103 and 104 are disposed so as to relatively control the flow of the compressed natural gas. That is, the check valve 103 is installed so that the compressed natural gas flows only from the filling port 106 to the fuel tank 101 during fuel filling. On the other hand, the check valve 104 is installed so as to flow only from the upstream side connected to the fuel tank 101 to the downstream side connected to the regulator 107 and the engine 108 when compressed natural gas is supplied to the engine 108 side.
[0004]
In such a fuel supply apparatus, when filling the fuel, if the filling port 106 is connected to a compressed natural gas supply source, the compressed natural gas is supplied from the filling port 106 via the check valve 103 and the overflow prevention valve 102 to the fuel tank. 101. At this time, the check valve 104 stops the flow to the main stop valve 105, and the main stop valve 105 is closed.
Further, when the main stop valve 105 is opened when fuel is supplied to the engine 108, the compressed natural gas flows from the fuel tank 101 through the overflow prevention valve 102, the main stop valve 105, the check valve 104, and the regulator 107. Are introduced into the engine 108. Thus, since the check valve 104 prevents the backflow of the compressed natural gas, the compressed natural gas always flows through the main stop valve 105 in a certain direction. When the flow rate of the compressed natural gas supplied from the fuel tank 101 becomes excessive, the overflow prevention valve 102 automatically closes to adjust the flow rate (see, for example, Patent Document 1).
[0005]
A high pressure solenoid valve 100 as shown in FIG. 15 is used as the main stop valve 105 for controlling the high pressure compressed natural gas. FIG. 15 is a cross-sectional view showing an example of a conventional high-pressure electromagnetic valve 100.
The high-pressure solenoid valve 100 of FIG. 15 is of a pilot type, and includes a drive unit 111 on the drive side and a valve unit 112 on the flow rate adjustment side. In the drive unit 111, a fixed core 115 and a pipe 118 are disposed in a cylindrical coil bobbin 114 around which a coil 113 is wound, and a plunger 116 is slidably inserted in the pipe 118. A spring 117 is disposed between the fixed core 115 and the plunger 116, and always urges the plunger 116 toward the valve portion 112 (the lower side in the figure).
[0006]
On the other hand, the valve part 112 is formed with an input port 121 and an output port 122 in the body 120, a valve hole 123 communicating therewith, and a valve seat 124 at the input side opening of the valve hole 123, and a primary chamber on the input port 121 side. 125 and a secondary chamber 126 on the output port 122 side are provided. A filter 127 for removing dust mixed in the compressed natural gas is loaded on the input port 121 side.
[0007]
A pilot valve body 131 is held via a holding metal fitting 139 on the lower end surface of the plunger 116 extending from the drive portion 111 into the primary chamber 125 of the valve portion 112. A main valve element 132 is engaged with the plunger 116 so as to surround the lower end portion of the plunger 116, and a pilot chamber 137 is formed between the main valve element 132 and the pilot valve element 131. The main valve body 132 is attached to the plunger 116 so as to be movable in the axial direction by loosely fitting a pin 133 that is loosely inserted into the pin hole 116 a of the plunger 116. A pilot port 135 penetrating in the axial direction is formed in the shaft core portion of the main valve body 132, and a pilot valve seat 136 that contacts the pilot valve body 131 is formed at the upper end opening portion of the pilot port 135 in the figure. . A communication hole (not shown) for communicating the primary chamber 125 and the pilot chamber 137 is formed in the outer peripheral surface of the main valve body 132.
[0008]
When the electric signal is not supplied to the drive unit 111, the high-pressure solenoid valve 100 presses the plunger 116 downward by the spring 117 to bring the pilot valve body 131 into contact with the pilot valve seat 136, and further causes the main valve body 132 to move. It abuts on the valve seat 124. Since the primary chamber 125 communicates with the pilot chamber 137 through a communication hole (not shown) formed in the main valve body 132 and becomes the same pressure, the main valve body 132 is strongly pressed against the valve seat 124 by the pressure of the compressed natural gas. To be sealed. Therefore, the compressed natural gas does not flow from the input port 121 to the output port 122.
[0009]
Then, when an electric signal is supplied to the drive unit 111, the plunger 116 rises against the urging force of the spring 117 and separates the pilot valve body 131 from the pilot valve seat 136, so that the compressed natural gas in the pilot chamber 137 It flows out from the pilot port 135 to the secondary chamber 126. When the pressure in the secondary chamber 126 rises and the pressure difference from the primary chamber 125 becomes smaller, the plunger 116 further rises against the urging force of the spring 117, and pulls up the main valve element 132 via the pin 133 to lift the valve seat Separated from 124. Thereby, the compressed natural gas flows from the input port 121 to the output port 122 (for example, refer to Patent Document 2).
[0010]
[Patent Document 1]
Japanese Patent Laid-Open No. 10-281909 (paragraphs 0007 to 0012, FIG. 1).
[Patent Document 2]
Japanese Patent Laid-Open No. 10-160024 (paragraphs 0010 to 0013, FIG. 1)
[0011]
[Problems to be solved by the invention]
However, in order to reduce the cost by reducing the number of parts, the fuel supply apparatus omits the portion surrounded by the dotted line in FIG. 14, that is, the bypass circuit L and the check valves 103 and 104, and fills the fuel tank 101. It has been proposed that the flow path connecting the port 106 and the engine 108 be a single system. Therefore, the high pressure solenoid valve 100 used as the main stop valve 105 is required to have a backflow function.
[0012]
Therefore, when the compressed natural gas was caused to flow backward through the conventional high-pressure solenoid valve 100, there was a problem that the portion where the pilot valve body 131 abuts on the pilot valve seat 136 was damaged. The following points can be considered as the reason.
In the high pressure solenoid valve 100, as shown in the explanatory diagram of FIG. 16, the compressed natural gas supplied to the output port 122 flows through the valve hole 123 because the valve hole 123 is smaller than the flow passage cross-sectional area of the secondary chamber 126. The flow velocity Vi when passing through the valve seat 124 becomes faster than the flow velocity Vo when supplying the output port 122, and the main valve element 132 is directly hit with the momentum. Therefore, when the valve is opened, the main valve body 132 rises vigorously while pressing the pilot valve seat 136 against the pilot valve body 131 as shown in the operation explanatory diagram of FIG.
[0013]
In such a reverse flow, the plunger 116 is pushed up by the main valve body 132 and collides with the fixed core 115, and the upward movement is restricted. However, the main valve body 132 will be pushed up by the compressed natural gas and will continue to rise. And Therefore, the pilot valve seat 136 of the main valve body 132 is pushed into the pilot valve body 131 as shown in the operation explanatory diagram of FIG. As a result, the pilot valve body 131 is strongly pressed upward in the figure. On the other hand, the compressed natural gas is supplied to the pilot valve seat 136 via the pilot port 135 of the main valve body 132 at an accelerated flow rate Vi (see FIG. 16) at the start of the backflow, and strikes the pilot valve body 131 directly.
[0014]
Therefore, the pilot valve body 131 has a hole in the portion that comes into contact with the pilot valve seat 136 as shown in the operation explanatory diagram of FIG. 17C due to the pushing of the pilot valve seat 136 and the pressure of the compressed natural gas. It was damaged. Such breakage occurred even when the compressed natural gas was backflowed once because of the high pressure of the compressed natural gas of 20 MPa.
[0015]
Accordingly, the present invention has been made to solve the above-described problems, and an object thereof is to provide a high-pressure electromagnetic valve capable of improving the durability of the pilot valve body against the backflow of the high-pressure fluid.
[0016]
[Means for Solving the Problems]
The high pressure solenoid valve according to the present invention has the following configuration.
(1) A valve seat is an opening of the valve hole with respect to a body that is excited by energization of a coil and uses a solenoid that attracts a plunger as a drive source and a valve hole is formed in a communication portion between an input port and an output port. A pilot valve that is provided around the part and is movably engaged with the plunger so as to be movable in the axial direction with respect to the plunger and that communicates between the input port side and the output port side While the seat is formed, a pilot valve body that contacts or separates from the pilot valve seat is held by the plunger, When a fuel tank that stores fuel for an automobile and a filling port that supplies fuel to the fuel tank are connected to a pipe, and when the engine of the automobile is operating, when fuel flows from the input port to the engine side through the output port, When the solenoid is energized, the pilot valve body is separated from the pilot valve seat so that the input port side communicates with the output port side, and the differential pressure between the input port side and the output port side is reduced. After that, the main valve body is separated from the valve seat, and the input port and the output port are communicated with each other. On the other hand, when the fuel is supplied from the filling port to the fuel tank, the pilot valve body is separated from the pilot valve seat by energizing the solenoid, so that the main valve body is separated from the valve seat, and the output port and the Input port In a high-pressure solenoid valve that communicates, a throttle is provided between the valve hole and the output port. When the fuel is supplied from the filling port to the fuel tank, the throttle causes a pressure loss in the fuel, and the fuel flow rate is decelerated from the flow rate when the output port flows in. A high-pressure solenoid valve characterized by that.
[0017]
According to the invention having the above-described configuration, the high-pressure fluid supplied to the output port is subjected to volume expansion after being squeezed by the restrictor and then discharged from the valve hole. Is decelerated from the flow rate when the output port is supplied. At this time, the force by which the high pressure fluid pushes up the main valve body and presses the pilot valve seat against the pilot valve body, and the force by which the high pressure fluid supplied to the pilot valve seat of the main valve body directly hits the main valve body is reduced. The stress applied to the pilot valve body is reduced.
[0018]
Therefore, in the high pressure solenoid valve of the present invention, the flow velocity when the high pressure fluid supplied to the output port is discharged from the valve seat to the input port side is decelerated from the time of supply to the output port, and the stress of the pilot valve body is reduced. Therefore, the durability of the pilot valve body against the backflow of the high-pressure fluid can be improved.
[0019]
(2) In the invention described in (1), the throttle is a throttle channel having a smaller channel cross-sectional area than the valve hole and communicating the output port with the valve hole.
According to the invention having the above configuration, the flow rate of the high-pressure fluid discharged from the valve seat can be decelerated from the time of supply to the output port without changing the diameter of the valve hole or the like. It is possible to ensure the same operating characteristics as.
[0020]
(3) In the invention described in (1) or (2), the throttle is an orifice plate in which a throttle hole having a channel cross-sectional area smaller than that of the valve hole is formed and disposed in the output port. .
According to the invention having the above-described configuration, when an orifice plate is attached to the output port of the conventional high-pressure solenoid valve, the high-pressure fluid supplied to the output port undergoes volume expansion after passing through the throttle hole of the orifice plate, thereby causing a pressure loss. And the flow rate when passing through the valve hole is decelerated from the flow rate when the output port is supplied, so that the same operating characteristics as those of the conventional high-pressure solenoid valve can be ensured.
[0021]
(4) In the invention according to any one of (1) to (3), the flow passage cross-sectional area of the throttle is 90% or less of the flow passage cross-sectional area of the valve hole.
According to the high pressure solenoid valve having the above configuration, the flow rate of the compressed natural gas supplied to the output port can be reduced.
[0022]
(5) In the invention according to any one of (1) to (4), the body has a throttle provided in a direction intersecting the valve hole, and the throttle is in communication with the valve hole; A turbulent flow chamber that opens only to the valve hole is formed at an opposing position. According to the invention having the above-described configuration, the high-pressure fluid that has passed through the throttle is disturbed in the turbulent flow chamber to generate turbulent flow, and then flows out into the valve hole to cause volume expansion to cause pressure loss. The flow rate of the high pressure fluid can be reduced more effectively. Further, since the high-pressure fluid supplied to the input port flows to the output port on the side opposite to the turbulent flow chamber, the operating characteristics are not affected.
[0023]
(6) The invention according to any one of (1) to (5), characterized in that it has a movement restricting means for restricting movement of the main valve element.
According to the invention having the above configuration, the movement of the plunger is restricted by restricting the movement of the main valve body by the movement restricting means. Therefore, at the time of backflow, the pilot valve seat exceeds the predetermined load with respect to the pilot valve body. There is no pressing.
[0024]
(7) In the invention according to any one of (1) to (6), a refraction flow path having an elbow shape or a cross shape is formed, and the refraction flow path and the pilot valve are loaded by being loaded on the main valve body. It has the flow-path block which connects a seat.
According to the invention having the above-described configuration, after the high-pressure fluid flowing through the valve seat toward the input port enters the refracting channel of the channel block and causes pressure loss at the elbow portion or the cross portion of the refracting channel. Since it is supplied to the pilot valve seat, the stress applied to the pilot valve body can be further reduced by decelerating the flow velocity when the pilot valve seat passes than when passing the valve seat.
[0025]
(8) In the invention according to any one of (1) to (7), a filter is disposed in the output port.
According to the invention having the above configuration, the filter removes dust contained in the high-pressure fluid supplied from the output port, so that the opening of the pilot valve seat and the like are prevented from being clogged, and the pressure loss is the same as that of the throttle. Can be obtained, and the stress on the pilot valve body can be reduced.
[0026]
DETAILED DESCRIPTION OF THE INVENTION
(First embodiment)
Next, a first embodiment of a high pressure solenoid valve according to the present invention will be described with reference to the drawings. FIG. 1 is a cross-sectional view of the high-pressure solenoid valve 1A.
The high pressure solenoid valve 1A controls the flow rate of a compressed gas obtained by compressing a gas such as natural gas, nitrogen, argon, etc. to 10 MPa or more. Similarly to the conventional high pressure solenoid valve 100 (see FIG. 15), the input port A pilot system that can reliably open even when the differential pressure between the 31 side and the output port 32 is large is employed, and is used, for example, as the main stop valve 105 of the fuel supply device shown in FIG. As shown in FIG. 1, the high-pressure solenoid valve 1A is roughly composed of a drive unit 2 on the drive side and a valve unit 3 on the flow rate adjustment side.
[0027]
The drive unit 2 includes a cylindrical coil bobbin 21 around which the coil 20 is wound. A fixed core 22 is disposed in the cylinder of the coil bobbin 21, and a cylindrical plunger 23 is fitted on the same axis as the fixed core 22 from below in the figure. Between the coil bobbin 21, the fixed core 22 and the plunger 23, a pipe 24 made of a non-magnetic material is disposed as a plunger guide from the drive unit 2 to the valve unit 3 in order to ensure pressure resistance against compressed gas. 23 is slidably inserted into the pipe 24. On the other hand, the fixed core 22 is fixed to the pipe 25 by welding or the like, and the magnetic frame 25 is fixed by screwing a nut 26 into the threaded portion of the protruding fixed core 22. A spring 27 is disposed between the fixed core 22 and the plunger 23, and always urges the plunger 23 toward the valve portion 3 side (the lower side in the figure). The wiring 28 connected to the coil 20 is sent out from the bush 29 and connected to a control device (not shown). Then, after assembling each member, a filler made of resin is injected into the bush 29 and the magnetic frame (magnetic frame) 25 to constitute a solenoid.
[0028]
On the other hand, the valve unit 3 has an input port 31 and an output port 32 formed in the body 30A in the horizontal direction, and a valve hole 33 communicating therewith is formed in the vertical direction. A secondary chamber (corresponding to “throttle” and “throttle channel”) 35A on the output port 32 side is formed. Further, a turbulent flow chamber 36 is provided in the body 30A. The secondary chamber 35A and the turbulent flow chamber 36 are characteristic of this embodiment and will be described later. A valve seat 38 with an annular seal ring 37 is provided around the opening of the valve hole 33.
[0029]
As shown in FIG. 1, such a body 30 </ b> A has a mounting port 39 that is female-threaded coaxially with the valve hole 33, and a male screw is cut on the outer peripheral surface of the mounting port 39. The lower fixed core 40 is screwed and connected, and a high pressure fluid is prevented from leaking by a packing member such as an O-ring disposed between the attachment port 39 and the lower fixed core 40. A magnetic plate 41 is disposed between the drive unit 2 and the valve unit 3 to form a magnetic circuit.
[0030]
A pilot valve body 42 is held on a lower end surface of the plunger 23 extending from the drive unit 2 into the primary chamber 34 of the valve unit 3 via a holding metal fitting 43 for preventing the drop, while the pilot valve body 42 A main valve body 44 having a pressure receiving surface larger than 42 is engaged with a reduced diameter portion of the plunger 23. The main valve body 44 has a cylindrical shape that is substantially the same diameter as the inner diameter of the pipe 24, has a lower end portion that is larger in diameter than the pipe 24, and is provided with an overhanging portion (corresponding to “movement restricting means”) 4. It has been. A recess for fitting the reduced diameter portion of the plunger 23 is formed on the upper end surface of the main valve body 44, and is loosely fitted to a pin 46 that is loosely inserted into the pin hole 45 of the plunger 23. Therefore, the main valve body 44 is attached to the plunger 23 so as to be movable in the axial direction, and a pilot chamber 47 in which the pilot valve body 42 is accommodated is provided. The main valve body 44 is provided with a pilot port 48 extending through the shaft core in the vertical direction of the drawing, and a pilot valve seat 49 that contacts the pilot valve body 42 is formed at the upper end opening communicating with the pilot chamber 47. Yes. A communication hole 50 is provided in the outer peripheral surface of the main valve body 44 to allow the pilot chamber 47 and the primary chamber 34 to communicate with each other.
[0031]
Accordingly, the high pressure solenoid valve 1A is closed while the coil 20 is not energized, the plunger 23 is urged downward by the spring 27 and closes the valve seat 38 by bringing the main valve body 44 into close contact with the valve seat 38, The pilot port 48 is closed by bringing the pilot valve body 42 into close contact with the pilot valve seat 49 of the main valve body 44. At this time, since the communication hole 50 of the main valve body 44 communicates with the primary chamber 34, the compressed gas in the primary chamber 34 flows into the pilot chamber 47, and the primary chamber 34 and the pilot chamber 47 have the same pressure. The body 44 is pressed firmly against the valve seat 38 to ensure a seal.
[0032]
When the coil 20 is energized, only the pilot valve element 42 having a small pressure receiving area is pulled up by the plunger 23 and separated from the pilot valve seat 49 to open the pilot port 48. At this time, since the pilot chamber 47 and the primary chamber 34 communicate with each other via the communication path 50, the compressed gas on the output port 32 side flows to the input port 31 side, and the output port 32 side, the input port 31 side, The differential pressure of becomes smaller. Then, the plunger 23 pulls up the main valve body 44 and the pilot valve body 42 integrally and opens the valve seat 38.
[0033]
Next, the secondary chamber 35A and the turbulent flow chamber 36 that characterize the present embodiment will be described. First, the secondary chamber 35A will be described. FIG. 2 is an enlarged sectional view of the valve portion of the high pressure solenoid valve 1A.
The secondary chamber 35 </ b> A is formed coaxially with the output port 32, and communicates the valve hole 33 and the output port 32. In the secondary chamber 35 </ b> A, the flow passage cross-sectional area Dn is set smaller than the flow passage cross-sectional area Di of the valve hole 33.
[0034]
The reason why the flow passage cross-sectional area Dn of the secondary chamber 35A is set in this way is that the inventors have made the flow passage cross-sectional area Do of the output port 32 constant and the flow cut-off between the valve hole 33 and the secondary chamber 35A. When an experiment was performed to reversely flow air compressed to 20 MPa with respect to the high pressure solenoid valve with the ratio of the areas Di and Dn changed, the flow rate of the compressed air supplied to the output port 32 was changed between the output port 32 and the valve hole 33. This is because it has been found that the pilot valve element 42 can be prevented from being damaged by narrowing the gap between them. Specifically, it is as follows. FIG. 3 is a diagram conceptually showing the high pressure solenoid valve used in the experiment. FIG. 4 is an enlarged cross-sectional view of the valve portion of the high pressure electromagnetic valve 11A used in the experiment.
[0035]
If the flow passage cross-sectional area Dn of the secondary chamber 351A is larger than the flow passage cross-sectional area Di of the valve hole 331 as in the high-pressure electromagnetic valve 11A shown in FIG. A hole was formed in the portion where 42 is in contact with the pilot valve seat 49 and was damaged. This is considered because the compressed air supplied to the output port 32 is accelerated as it passes through the secondary chamber 351 </ b> A and the valve hole 331 and directly hits the main valve body 44.
[0036]
On the other hand, as shown in FIG. 3, when the flow cross-sectional area Dn of the secondary chamber 35A was gradually made smaller than the flow path cross-sectional area Di of the valve hole 33, a reverse flow experiment was performed. When the cross-sectional area Dn was 90% or less of the flow path cross-sectional area Di of the valve hole 33, the pilot valve body 42 was not damaged. This is because the compressed air input from the output port 32 is subjected to volume expansion in the valve hole 33 after the flow rate is throttled in the secondary chamber 35A to cause a pressure loss, so that the flow velocity when passing through the secondary chamber 35A is changed to the output port. 32 is decelerated from the flow velocity Vo at the time of supply, and then further collides with the body 30A to generate turbulent flow and flow to the valve seat 38, so that the flow velocity Vh when passing through the valve seat 38 is the same as that when passing through the secondary chamber 35A. This is considered to be further decelerated from the flow velocity Vn.
[0037]
Therefore, it is desirable to set the flow passage cross-sectional area Dn of the secondary chamber 35A to 90% or less of the flow passage cross-sectional area Di of the valve hole 33. In this case, since the flow passage cross-sectional area Dn of the secondary chamber 35A is related to the flow capacity of the high pressure solenoid valve 1A, it is determined according to the application of the high pressure solenoid valve 1A. For example, when the flow capacity of the high pressure solenoid valve 1A may be small, the flow passage cross-sectional area Dn of the secondary chamber 35A is 60%, 70%, 80%, etc. with respect to the flow passage cross-sectional area Di of the valve hole 33. It can also be considered. In the present embodiment, the flow passage cross-sectional area Dn of the secondary chamber 35A is 90% or less of the flow passage cross-sectional area Di of the valve hole 33, and as the main stop valve 105 of the fuel supply device shown in FIG. It is set so that the flow capacity can be obtained.
[0038]
Next, the turbulent flow chamber 36 will be described.
As shown in FIG. 2, the turbulent flow chamber 36 is provided at a position facing the portion where the secondary chamber 35 </ b> A communicates with the valve hole 33 so as to open only to the valve hole 33. The turbulent flow chamber 36 is formed by deeply drilling the secondary chamber 35 </ b> A beyond the valve hole 33. Therefore, the turbulent flow chamber 36, the secondary chamber 35A, and the output port 32 are formed on the same axis, and when the compressed gas supplied to the output port 32 passes through the secondary chamber 35A, it is turbulent through the valve hole 33. It is disturbed by being input to the flow chamber 36 and flows out to the valve hole 33 while generating a turbulent flow.
[0039]
In the high-pressure solenoid valve 1A having such a flow path configuration, the compressed gas supplied to the output port 32 is throttled when flowing into the secondary chamber 35A as shown in FIG. 3, and then the secondary chamber 35A. From the turbulent flow chamber 36 to the valve hole 33, the volume is expanded to cause a pressure loss. , And flows to the valve seat 38 while causing a pressure loss due to volume expansion. Therefore, the compressed gas has a much slower flow rate when passing through the valve seat 38 than when the output port is supplied.
[0040]
Therefore, the compressed gas pushes up the main valve body 44 and the force for pressing the pilot valve seat 49 against the pilot valve body 42 becomes weak, and the compressed gas that has entered the pilot port 48 of the main valve body 44 at the start of the backflow becomes the pilot valve body. The pressure when hitting 42 directly becomes smaller. Since the stress received from the compressed gas passing through the pilot valve seat 49 and the pilot port 48 during the backflow of the compressed gas is reduced, the pilot valve body 42 is damaged such as a hole in the portion that contacts the pilot valve seat 49. Hard to occur.
[0041]
Therefore, according to the high pressure electromagnetic valve 1A of the present embodiment, the secondary chamber 35A is provided between the output port 32 and the valve hole 33 so that the flow path cross-sectional area Dn is smaller than the flow path cross-sectional area Di of the valve hole 33. As a result (see FIG. 2), the flow rate when the compressed gas supplied to the output port 32 is discharged from the valve seat 38 to the input port 31 side is decelerated from the flow rate when the output port 32 is supplied, and the pilot valve element 42 Therefore, the durability of the pilot valve body 42 against the backflow of the compressed gas can be improved.
[0042]
In particular, in this case, since the flow rate is reduced in the portion other than the valve hole 33, that is, the secondary chamber 35A that communicates the output port 32 and the valve hole 33, the same operating characteristics as those of the conventional high-pressure electromagnetic valve are ensured. be able to. The advantage of not changing the operating characteristics is particularly beneficial in the fuel supply apparatus shown in FIG. That is, in the fuel supply device shown in FIG. 14, when the main stop valve 105 is connected to the overflow prevention valve 102 and the operation characteristic of the main stop valve 105 changes, the overflow prevention is performed in accordance with the operation characteristic. This is because the valve 102 must be replaced or the control system must be changed.
[0043]
The body 30A of the high pressure electromagnetic valve 1A is provided in a direction in which the secondary chamber 35A intersects the valve hole 33, and the secondary chamber 35A is opposed to a portion communicating with the valve hole 33. Since the turbulent flow chamber 36 that opens only to the valve hole 33 is formed, the flow rate of the compressed gas that has passed through the secondary chamber 35A can be more effectively reduced. Further, since the compressed gas supplied to the input port 31 flows to the output port 32 on the opposite side to the turbulent flow chamber 36, it does not easily enter the turbulent flow chamber 36 to generate turbulent flow and affects the operating characteristics. There is nothing.
[0044]
(Second Embodiment)
Then, 2nd Embodiment of the high voltage | pressure solenoid valve which concerns on this invention is described with reference to FIGS.
The high pressure solenoid valve 1B of the present embodiment is a high pressure solenoid valve 1A of the first embodiment in which the flow rate is reduced by the secondary chamber 35A in that the flow rate of the compressed gas is reduced by using the orifice plate 51A to reduce the flow rate. Here, the difference from the high pressure electromagnetic valve 1A of the first embodiment will be mainly described. In addition, about the structure same as 1 A of high pressure solenoid valves of 1st Embodiment, suppose that description is abbreviate | omitted using the same code | symbol.
[0045]
In the high-pressure solenoid valve 1B, as shown in the enlarged sectional view of the valve portion in FIG. 5, the body 30B is formed with a secondary chamber 35B. The secondary chamber 35B has the same flow path cross-sectional area as the valve hole 33. Or it is widely formed. An orifice plate 51A is disposed between the secondary chamber 35B and the output port 32.
[0046]
As shown in the plan view of FIG. 6, it is sufficient that the area of the throttle hole 52A of the orifice plate 51A is smaller than the flow path cross-sectional area of the valve hole 33. As shown in FIG. 7, a plurality of throttle holes 52B are formed. Orifice plate 51B may be used.
[0047]
In such a high pressure solenoid valve 1B, the flow rate of the compressed gas supplied to the output port 32 is reduced by the throttle hole 52A of the orifice plate 51A, and then volumetrically expanded in the secondary chamber 35B. It is decelerated from when the output port 32 is supplied. After that, it collides with the body 30 </ b> B to change the flow direction while generating turbulent flow, and is discharged from the valve hole 33. If the throttle hole 52A is smaller than the flow passage cross-sectional area of the valve hole 33, the flow rate of the compressed gas is a damper function of the secondary chamber 35B even if the flow passage cross-sectional area of the valve hole 33 is smaller than the secondary chamber 35B. Therefore, the rate of acceleration through the valve hole 33 is small, and the stress applied to the pilot valve body 42 is small.
[0048]
Therefore, according to the high pressure solenoid valve 1B of the present embodiment, the orifice plate 51A in which the throttle hole 52A smaller than the flow path cross-sectional area of the valve hole 33 is provided in the output port 32. In addition to improving the durability of the pilot valve body 42, it is possible to ensure the same operating characteristics as the conventional high-pressure solenoid valve.
[0049]
As shown in FIG. 8, if the orifice plates 51A and 51B are disposed in combination with the output port 32 of the body 30B, the flow rate of the compressed gas can be more effectively reduced to cause pressure loss.
[0050]
(Third embodiment)
Next, a third embodiment of the high pressure solenoid valve according to the present invention will be described with reference to FIGS.
The high-pressure solenoid valve 1C of the present embodiment is different from the high-pressure solenoid valve 1A of the first embodiment in that a buffer material 55 (corresponding to “movement restricting means”) is attached. The buffer material 55 is formed into an annular shape with a predetermined thickness using an elastic material such as rubber, and is fixed to the lower fixed core 40 and the lower end surfaces of the pipe 24. Here, the predetermined thickness is such that when the main valve body 44 is locked and when the plunger 23 comes into contact with the fixed core 22, the pilot valve seat 49 and the pilot valve body 42 are contacted over a predetermined load. Thickness necessary to prevent it from occurring.
[0051]
In such a high-pressure electromagnetic valve 1C, when the main valve body 44 rises while pressing the pilot valve seat 49 against the pilot valve body 42 during the backflow of the compressed gas, as shown in FIG. The upward movement is restricted by being locked to the pipe 24 and the lower fixed core 40 via the buffer material 55. The shock absorbing material 55 absorbs the impact force of the main valve body 44, thereby reducing the impact load acting on the main valve body 44 and the body 30A and suppressing the occurrence of collision noise.
[0052]
When the main valve body 44 is raised until it is locked, a gap S is formed between the fixed core 22 and the plunger 23 due to the thickness of the buffer material 55. Thereafter, since the compressed gas that has entered from the pilot port 48 pushes up the pilot valve body 42, the gap S between the fixed core 22 and the plunger 23 disappears as shown in FIG. A gap S ′ corresponding to the gap S is formed between the body 42 and the body 42. Therefore, even if the main valve 44 continues to be pressurized upward by the compressed gas flowing backward, the pilot valve seat 49 is not pushed into the pilot valve body 42.
[0053]
Therefore, according to the high pressure solenoid valve 1C, the pilot valve seat 49 is not pressed against the pilot valve body 42 beyond a predetermined load because the buffer member 55 that restricts the movement of the main valve body 44 is provided.
[0054]
(Fourth embodiment)
Next, a fourth embodiment of the high pressure solenoid valve according to the present invention will be described with reference to FIG.
The high pressure solenoid valve 1D is different from the second embodiment in that the flow rate of the compressed gas that strikes the pilot valve body 42 directly on the main valve body 44 side is reduced. Therefore, here, it demonstrates centering on the part which is different from 1 A of high pressure solenoid valves of 2nd Embodiment. In addition, the same code | symbol is attached | subjected to the same structural member as 1 A of high pressure solenoid valves of 2nd Embodiment.
[0055]
In the high pressure solenoid valve 1D, the flow passage cross-sectional area of the secondary chamber 35B is formed to be equal to or larger than the flow passage cross-sectional area of the valve hole 33 with respect to the body 30B. 38 is provided. The main valve body 56 that contacts or separates from the valve seat 38 is engaged with the plunger 23 so as to wrap the lower end portion of the plunger 23 that holds the pilot valve body 42.
[0056]
A pilot port 48 penetrating in the axial direction is formed in the shaft core portion of the main valve body 56, and a pilot valve seat 49 that abuts the pilot valve body 42 is formed in the upper end opening of the pilot port 48. A flow path block 57 is loaded on the lower end surface of the main valve body 56. In the flow path block 57, a single flow path communicating with the pilot port 48 of the main valve body 56 is formed from the upper end surface to the central portion, and a plurality of flow paths penetrating in the axial direction around the flow path. The refractive flow path 58 having an elbow shape or a cross shape is formed by communicating a plurality of flow paths with respect to one flow path.
[0057]
In such a high-pressure solenoid valve 1D, when the compressed gas supplied to the output port 32 flows to the valve seat 38 when the valve is closed, the compressed gas is input to the refraction flow path 58 of the flow path block 57 and the pilot port of the main valve body 44. It flows to 48. Since the compressed gas causes a pressure loss at the elbow portion or the cross portion of the refraction channel 58, when the compressed gas flows to the pilot port 48, it is decelerated from when passing through the valve seat 38, and the force hitting the pilot valve body 42 is weakened.
[0058]
Therefore, according to the high pressure solenoid valve 1D, the elbow-shaped or cross-shaped refracting flow path 58 is formed, and the refracting flow path 58 is connected to the pilot valve seat 49 via the pilot port 48 by being loaded into the main valve body 56. Since the flow path block 57 connected to is provided, the stress applied to the pilot valve body 42 can be further reduced.
[0059]
(Fifth embodiment)
Next, a fifth embodiment of the high pressure solenoid valve according to the present invention will be described.
As shown in FIG. 12, the high pressure solenoid valve 1E is obtained by loading a filter 60 into the output port 32 provided in the high pressure solenoid valve 1A of the first embodiment.
In such a high-pressure solenoid valve 1E, the filter 60 removes dust contained in the compressed gas supplied to the output port 32, and at the same time, a throttle such as the secondary chamber 35A (see FIG. 1) and the orifice plate 51A (see FIG. 5). Similarly, since it has an effect of generating pressure loss, it is possible to prevent the pilot port 48 of the main valve body 44 and the opening of the pilot valve seat 49 from being clogged, and to reduce the stress applied to the pilot valve body 42. it can.
In addition to the output port 32, a filter 60 may be mounted on the input port 31 side as shown in FIG. Further, if necessary, a fine filter may be attached.
[0060]
Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various applications are possible.
[0061]
(1) For example, in the above-described embodiment, a high-pressure electromagnetic valve used as a main stop valve in a fuel supply apparatus for a natural gas vehicle has been described. Anything that controls the above high-pressure fluid can be used.
[0062]
(2) For example, in the said embodiment, the output port 32 and the valve hole 33 are formed so that it may orthogonally cross. On the other hand, the output port 32 and the valve hole 33 may be formed coaxially, or the output port 32 may be formed to cross the valve hole 33 obliquely.
[0063]
(3) For example, in the above-described embodiment, the throttle channel 35A, the orifice 51A, and the channel block 57 each having a channel cross-sectional area smaller than the valve hole 33 are used alone. On the other hand, these may be combined to effectively cause pressure loss.
[0064]
【The invention's effect】
According to the high-pressure solenoid valve of the present invention, a solenoid that is excited by energization of a coil and attracts a plunger is used as a drive source, and a valve hole is formed in a communication portion between an input port and an output port. A seat is provided around the opening of the valve hole, and a main valve body that contacts or separates from the valve seat is movably disposed in the axial direction with respect to the plunger, and the input port side and the output port side A pilot valve seat that communicates with the pilot valve seat, while a pilot valve body that contacts or separates from the pilot valve seat is held by the plunger, When a fuel tank that stores fuel for an automobile and a filling port that supplies fuel to the fuel tank are connected to a pipe, and when the engine of the automobile is operating, when fuel flows from the input port to the engine side through the output port, When the pilot valve body is separated from the pilot valve seat by energization of the solenoid, the input port side and the output port side communicate with each other, and the differential pressure between the input port side and the output port side becomes small. Is separated from the valve seat to allow communication between the input port and the output port. On the other hand, when the fuel is supplied from the filling port to the fuel tank, the pilot valve body is separated from the pilot valve seat by energizing the solenoid, so that the main valve body is separated from the valve seat, and the output port and the input port Toga A high-pressure solenoid valve that communicates with a throttle between the valve hole and the output port. When the fuel is supplied from the filling port to the fuel tank, the throttle causes a pressure loss in the fuel, and the fuel flow rate is decelerated from the flow rate when the output port flows in Therefore, it is possible to improve the durability of the pilot valve body against the reverse flow of the high-pressure fluid.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a high-pressure solenoid valve according to a first embodiment of the present invention.
FIG. 2 is an enlarged cross-sectional view of the valve portion of the high-pressure solenoid valve, similarly.
FIG. 3 is a view conceptually showing a high-pressure electromagnetic valve used in the experiment.
FIG. 4 is an enlarged cross-sectional view of a valve portion of a high pressure solenoid valve used in the experiment.
FIG. 5 is an enlarged cross-sectional view of a valve portion of a high pressure solenoid valve according to a second embodiment of the present invention.
FIG. 6 is a plan view of the orifice plate.
FIG. 7 is a plan view of the orifice plate.
FIG. 8 is a view similarly showing a mounting structure of an orifice plate.
FIG. 9 is an enlarged cross-sectional view of a main part of a high pressure solenoid valve according to a third embodiment of the present invention.
FIG. 10 is an enlarged cross-sectional view of a main part of the high-pressure solenoid valve, similarly.
FIG. 11 is an enlarged cross-sectional view of a valve portion of a high pressure solenoid valve according to a fourth embodiment of the present invention.
FIG. 12 is a cross-sectional view of a high pressure solenoid valve according to a fifth embodiment of the present invention.
FIG. 13 is a diagram showing a modification of the high pressure solenoid valve according to the fifth embodiment.
FIG. 14 is a conceptual diagram showing an example of a fuel supply device for a natural gas vehicle.
FIG. 15 is a cross-sectional view showing an example of a conventional high-pressure solenoid valve.
FIG. 16 is an explanatory diagram of an operation at the time of back flow in a conventional high-pressure solenoid valve.
FIG. 17 is a diagram showing the operation of the pilot valve portion during reverse flow in a conventional high-pressure solenoid valve.
[Explanation of symbols]
1A, 1B, 1C, 1D, 1E High pressure solenoid valve
4 Overhang
20 coils
22 Fixed core
23 Plunger
30A, 30B body
31 Input port
32 output ports
33 Valve hole
35A secondary room
36 Turbulence chamber
38 Valve seat
42 Pilot valve body
44, 56 Main disc
49 Pilot valve seat
51A, 51B Orifice plate
52A, 52B Aperture hole
55 cushioning material
57 Channel block
58 Refraction channel
60 filters

Claims (8)

The valve seat is around the opening of the valve hole with respect to the body that is excited by energizing the coil and has a solenoid that sucks the plunger as a drive source and the valve hole is formed in the communication part between the input port and the output port. A main valve body that contacts or separates from the valve seat is movably attached in the axial direction with respect to the plunger, and a pilot valve seat that communicates the input port side and the output port side is formed On the other hand, a pilot valve body that contacts or separates from the pilot valve seat is held by the plunger,
When a fuel tank that stores fuel for an automobile and a filling port that supplies fuel to the fuel tank are connected to a pipe, and when the engine of the automobile is operating, when fuel flows from the input port to the engine side through the output port, When the solenoid is energized, the pilot valve body is separated from the pilot valve seat so that the input port side communicates with the output port side, and the differential pressure between the input port side and the output port side is reduced. After that, when the main valve body is separated from the valve seat to communicate the input port and the output port, when supplying fuel from the filling port to the fuel tank, the pilot valve is energized by energizing the solenoid. by the body moves away from the pilot valve seat, a high main valve body is separated from the valve seat, and the output port and the input port are communicated In the solenoid valve,
A throttle is provided between the valve hole and the output port ,
The aperture is
A high pressure solenoid valve characterized in that when the fuel is supplied from the filling port to a fuel tank, a pressure loss is caused in the fuel, and the flow rate of the fuel is decelerated from the flow rate when the output port flows in . In the high pressure solenoid valve according to claim 1,
The high-pressure solenoid valve according to claim 1, wherein the throttle is a throttle channel having a smaller channel cross-sectional area than the valve hole and communicating the output port with the valve hole. In the high pressure solenoid valve according to claim 1 or claim 2,
The high-pressure solenoid valve according to claim 1, wherein the throttle is an orifice plate having a throttle hole having a smaller channel cross-sectional area than the valve hole and disposed in the output port. The high pressure solenoid valve according to any one of claims 1 to 3,
The high-pressure solenoid valve according to claim 1, wherein a flow passage cross-sectional area of the throttle is 90% or less of a flow passage cross-sectional area of the valve hole. The high pressure solenoid valve according to any one of claims 1 to 4,
The body is
The throttle is provided in a direction intersecting the valve hole;
A high-pressure solenoid valve characterized in that a turbulent flow chamber that opens only to the valve hole is formed at a position facing the portion where the throttle communicates with the valve hole. The high pressure solenoid valve according to any one of claims 1 to 5,
A high-pressure solenoid valve comprising movement restriction means for restricting movement of the main valve body. The high pressure solenoid valve according to any one of claims 1 to 6,
A high-pressure solenoid valve comprising: a refraction channel having an elbow shape or a cross shape; and a flow channel block that connects the refraction channel to the pilot valve seat by being mounted on the main valve body. The high pressure solenoid valve according to any one of claims 1 to 7,
A high-pressure solenoid valve characterized in that a filter is disposed at the output port.

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