JP2002180908A - Gas pressure reducing valve - Google Patents

Abstract

(57) Abstract: A stable sliding resistance against self-excited vibration of a coil spring is imparted to a diaphragm to prevent a decrease in responsiveness irrespective of the size and temperature change of the diaphragm. I do. A leaf spring (132) for providing sliding resistance to a diaphragm by frictionally contacting an inner surface of a cylindrical portion that is a part of a valve housing, a retainer and a coil spring mounted on a center portion of the diaphragm on a spring chamber side. A closed-end cylindrical cup portion 132a having a closed end interposed therebetween is integrally connected to an open end of the cup portion 132a so as to resiliently contact a plurality of portions at equal intervals in the circumferential direction of the cylindrical portion. And a plurality of leaf portions 132b.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gas pressure reducing valve, and more particularly, to a valve housing in which a peripheral portion of a diaphragm for applying gas pressure in a pressure reducing chamber to a whole surface is sandwiched by a valve housing, and a valve hole communicating with the pressure reducing chamber is formed in a central portion. A valve body that can be seated on a valve seat that is opened at the center is connected to a central portion of the diaphragm, and a spring chamber that faces the other surface of the diaphragm is formed in a cylindrical portion that forms a part of the valve housing, The present invention relates to an improvement in a gas pressure reducing valve in which a coil spring for urging a diaphragm in a direction to separate a body from a valve seat is housed in a spring chamber.

[0002]

2. Description of the Related Art Conventionally, such a pressure reducing valve for gas has been already known, for example, from Japanese Patent Application Laid-Open No. 11-270718. In this device, a sliding resistance against self-excited vibration of a coil spring is applied to a diaphragm. For this purpose, a piston slidably fitted to a cylindrical portion that is a part of the valve housing is connected to the center of the diaphragm on the spring chamber side, and a pair of Os mounted on the outer surface of the piston is provided. Grease is filled between the rings.

[0003]

By the way, if the diameter of the diaphragm is set small in accordance with the demand for downsizing of the gas pressure reducing valve, the diameter of the piston and the O-ring mounted on the piston also become small, and the diameter of the O-ring is reduced. As the sliding resistance increases, the response of the gas pressure reducing valve decreases.
The grease filled between the two O-rings hardens in a low temperature range and increases the sliding resistance, and decreases in a high temperature range.

The present invention has been made in view of the above circumstances, and is intended to provide a stable sliding resistance against self-excited vibration of a coil spring to a diaphragm irrespective of the size of the diaphragm and a change in temperature. Accordingly, an object of the present invention is to provide a gas pressure reducing valve in which a decrease in responsiveness is prevented.

[0005]

SUMMARY OF THE INVENTION In order to achieve the above object, the present invention is directed to a pressure-reducing chamber in which a peripheral portion of a diaphragm for applying gas pressure to the entire surface is sandwiched by a valve housing, and a valve hole communicating with the pressure-reducing chamber is provided. A valve body that can be seated on a valve seat that is opened at the center is connected to the center of the diaphragm, and a spring chamber facing the other surface of the diaphragm is formed in a cylindrical portion that constitutes a part of the valve housing, In a gas pressure reducing valve in which a coil spring for urging a diaphragm in a direction to separate the valve body from a valve seat is housed in a spring chamber, frictional contact is made on the inner surface of the cylindrical portion to reduce sliding resistance on the diaphragm. A leaf spring to be applied, the leaf spring being a bottomed cylindrical cup portion having a closed end sandwiched between a coil spring and a retainer mounted on a center portion of the diaphragm on the spring chamber side. And a plurality of leaf portions integrally connected to the opening end of the cup portion so as to resiliently slidably contact a plurality of portions at equal intervals in the circumferential direction of the cylindrical portion. .

According to such a configuration, the leaf spring is
A plurality of leaf portions of the leaf spring are elastically slidably brought into contact with the inner surface of a cylindrical portion which is a part of the valve housing, so that a diaphragm is provided with sliding resistance against self-excited vibration of the coil spring. Therefore, even if the diameter of the cylindrical portion becomes smaller as the diameter of the diaphragm becomes smaller, the contact area of the leaf spring with the cylindrical portion does not change, and the sliding resistance reduces the size of the gas pressure reducing valve. It does not increase along with the temperature, and even if the temperature changes, the sliding resistance due to resilient sliding contact with the cylindrical portion of the leaf spring does not change, so regardless of the size reduction of the diaphragm and the temperature change In addition, a stable sliding resistance against the self-excited vibration of the coil spring can be given to the diaphragm, and the response of the gas pressure reducing valve can be prevented from being lowered. Moreover, since a plurality of leaf portions are supported by the cup portion having relatively high rigidity, the leaf portions are prevented from being broken when the leaf spring is assembled into the valve housing, so that the assembling efficiency is improved. Can be improved.

[0007]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described based on embodiments of the present invention shown in the accompanying drawings.

1 to 22 show a first embodiment of the present invention. FIG. 1 schematically shows the structure of a fuel gas supply device, and FIG. 2 shows a fuel gas supply device mounted on a vehicle. FIG. 3 is a side view of the regulator, FIG. 4 is a plan view of the regulator as viewed from the direction of arrow 4 in FIG. 3, FIG. 5 is a bottom view of the regulator as viewed from the direction of arrow 5 of FIG. FIG.
7 is a sectional view taken along line 6-6 of FIG. 4, FIG. 7 is a sectional view taken along line 7-7 of FIG. 3, FIG. 8 is an enlarged longitudinal sectional view of the electromagnetic shut-off valve, FIG. Is a plan view of a leaf spring provided in the primary pressure reducing valve, FIG. 11 is a sectional view taken along line 11-11 of FIG.
12 is a side view of the secondary pressure reducing valve, as viewed in the direction of the arrow 12 in FIG. 13, FIG. 13 as viewed in the direction of the arrow 13 in FIG. 12, and FIG.
FIG. 15 is a sectional view taken along line 15-15 of FIG. 14, FIG.
6 is a sectional view taken along line 16-16 of FIG. 13, FIG. 17 is an enlarged view of a main part of FIG. 16, FIG. 18 is a plan view of a partition member provided in the secondary pressure reducing valve, and FIG. 19 is a sectional view taken along line 19-19 of FIG. FIG. 20 is an enlarged vertical sectional view of a diaphragm provided in the secondary pressure reducing valve, and FIG.
Is a plan view of a leaf spring provided in the secondary pressure reducing valve, and FIG. 22 is a sectional view taken along line 22-22 of FIG.

First, in FIG. 1, compressed natural gas (Compressed Natural Gas: CNG) as fuel gas is stored in one or a plurality of CNG tanks 20 at a high pressure of, for example, 25 to 1 MPa. CN
The container shut-off valves 21 provided in each of the G tanks 20 are:
A pressure sensor 26 is connected to the filling port 22 in common via a check valve 23 and commonly connected to a manual shutoff valve 24. And a temperature sensor 27.

When the container shutoff valves 21 and the manual shutoff valves 24 are opened, the CNG from the CNG tanks 20
The G tanks 20 are guided to a regulator RA via a high-pressure line 28 provided with an oil filter 29 for removing oil that may be mixed when the compressor fills CNG with the compressor RA.
CNG decompressed to 0.7 MPa is supplied to the low-pressure filter 3.
The CNG guided to the secondary pressure reducing valve 31 as a gas pressure reducing valve through the pressure control valve 0 and reduced to, for example, 0.2 to 0.3 MPa by the secondary pressure reducing valve 31 passes through the pipe 33 to the injector 32 of the engine E. The temperature sensor 3
4 and a pressure sensor 35 are provided.

In FIG. 2, a plurality of injectors 32 provided in a multi-cylinder engine E are commonly connected to a fuel gas pipe 36 in an engine room of a vehicle V.
The secondary pressure reducing valve 31 arranged near the engine E is connected to the line 3
3 is connected to the fuel gas line 36. Further, a low-pressure filter 30 connected to the secondary pressure reducing valve 31 is also disposed near the engine E, and is mounted on a rear portion of the vehicle V.
In order to minimize the length of the high pressure line 28 for guiding CNG from the G tanks 20.
It is located at the rear of the engine room at a distance from the engine compartment.

The regulator RA has a high-pressure filter 3 mounted on a common regulator body 38A having a hot water passage 37.
9. An electromagnetic shut-off valve 40 and a primary pressure reducing valve 41 as a gas pressure reducing valve are provided.
2 is attached to the regulator RA.

The high-pressure filter 39 removes impurities contained in CNG which is guided from the manual shut-off valve 24 via the high-pressure line 28. The primary pressure reducing valve 41 operates to reduce the pressure of the high-pressure CNG of 25 to 1 MPa from which impurities have been removed by the high-pressure filter 39 to, for example, 0.6 to 0.7 MPa. It is interposed between the high-pressure filter 39 and the primary pressure-reducing valve 41 to shut off when the operation is stopped or when a signal is output from the pressure switch 42. Further, the pressure switch 42 changes the switching mode in response to the pressure of CNG reduced by the primary pressure reducing valve 41 becoming, for example, a preset set pressure, for example, 1.65 MPa or more, and a signal for shutting off the electromagnetic shut-off valve 40. Is output.

The hot water passage 37 of the regulator body 38A
In order to prevent the temperature of the regulator body 38A from excessively lowering due to the pressure reducing operation of the primary pressure reducing valve 41, the engine cooling water is introduced from the engine E. The disposed thermostat 43 closes when the engine cooling water flowing through the hot water passage 37 exceeds, for example, 70 ° C., so that the temperature of the regulator body 38A does not rise too much.

Referring also to FIGS. 3 to 7, regulator body 38A is formed to have a substantially square cross-sectional shape, and slightly outside the outer surface of regulator body 38A. The high-pressure filter 39 is mounted on the regulator body 38A from the side of the first side 44 formed to expand, and the second side 4 opposite to the first side 44 is mounted.
On the fifth side, an electromagnetic shutoff valve 40 is mounted on the regulator body 38A. Further, a third side surface 46 connecting the first and second side surfaces 44 and 45 among the outer side surfaces of the regulator body 38A.
Is provided with a concave portion serving as a hot water passage 37, and the cover plate 4 fastened to the third side surface 46 so as to close the concave portion.
A pair of connecting pipes 48 and 49 for supplying and discharging the engine cooling water to and from the hot water passage 37 are attached to 7.

The regulator body 38A is provided with
It has a first end face 50 orthogonal to the third side faces 44 to 46, and a second end face 51 opposite to the first end face 50. The primary pressure reducing valve 41 is provided to the regulator body 38A on the first end face 50 side.
Is mounted, and the pressure switch 42 is mounted on a projection 51a provided on the regulator body 38A so as to protrude from the second end face 51.

Hereinafter, the configurations of the high-pressure filter 39, the electromagnetic shut-off valve 40, and the primary pressure reducing valve 41 constituting the regulator RA will be sequentially described.

[High-Pressure Filter 39] With particular attention to FIG. 7, a concave portion 53 is provided on the first side surface 44 of the regulator body 38A, and a pipe joint 54 is provided at an outer end opening of the concave portion 53. A high-pressure pipe 28 for guiding CNG from the manual shut-off valve 24 is connected to the outer end of the pipe joint 54. The high-pressure pipe 28 is screwed between the inner end and the regulator body 38A so as to sandwich the annular seal member 55 therebetween. In the concave portion 53,
A high-pressure filter 39 is fitted so as to be spaced from the inner end of the pipe joint 54, and the high-pressure filter 39 is closed between the high-pressure filter 39 and the pipe joint 54 by closing the inner end of the recess 53. A spring 56 that exerts a resilient force to press against the portion is provided.

Between the outer periphery of the high-pressure filter 39 fitted in the recess 53 and the regulator body 38A, the pipe joint 5 is provided.
An annular unpurified chamber 57 communicating with the inside of the high-pressure filter 39 is formed in the regulator body 38 </ b> A. Thus, the CNG guided through the high-pressure pipe 28 passes through the high-pressure filter 39 from the unpurified chamber 57 and flows into the purification chamber 58, and the CNG from which impurities have been removed is guided to the passage 59. .

[Electromagnetic shut-off valve];
An electromagnetic shut-off valve 40 is mounted on the second side surface 45 of the regulator body 38A at a position corresponding to the high-pressure filter 39.

The electromagnetic shut-off valve 40 includes a coil assembly 60
And a guide cylinder 61 made of a non-magnetic material having one end inserted into the coil assembly 60 and the other end fixed to the regulator body 38A, and fixed to the guide cylinder 61 so as to close one end of the guide cylinder 61. Fixed core 62,
A plunger 63 slidably fitted in the guide cylinder 61 so as to face the fixed core 62, a return spring 64 provided between the fixed core 62 and the plunger 63, and a fixed core covering the coil assembly 60. 62, a magnetic metal solenoid housing 65 fastened to
Support frame 66 screwed to the regulator body 38A so as to be sandwiched between the
And a valve member 67 held by the plunger 63 on the side opposite to the fixed core 62.

The coil assembly 60 has a bobbin 68 made of synthetic resin and a coil 69 wound around the bobbin 68 covered by a coating portion 70 made of synthetic resin.
In the portion of the covering portion 70 on the regulator body 38A side,
A coupler 70a facing a pair of connection terminals 71 connected to the coil 69 is integrally provided so as to protrude outward, and a conductor (not shown) is connected to the coupler 70a.

Second side 45 of regulator body 38A
A small-diameter hole 73 having an inner end closed and a large-diameter hole 74 having a diameter larger than that of the small-diameter hole 73 and coaxially connected to an outer end of the small-diameter hole 73 are connected to an annular step 75 facing outward. It is formed and provided between them. Guide tube 6 for inserting one end side into bobbin 59
A flange 61a for making the outer peripheral surface close to and facing the inner surface of the large-diameter hole 74 is provided integrally with the outer surface on the other end side of the large diameter hole 74 so as to project radially outward. The other end of the guide cylinder 61 is inserted into the large-diameter hole 74 so as to sandwich the annular seal member 76 between the parts 75.

The magnetic support frame 66 is mounted on the regulator body 38A by being screwed into the large-diameter hole 74. In addition, the seal member 76 and the flange 61a are sandwiched between the step 75 and the magnetic support frame 66, so that the guide cylinder 61 is also fixed to the regulator body 38A.

A screw shaft portion 62a penetrating the center of the closed end of the solenoid housing 65 having a bottomed cylindrical shape is integrally connected to the fixed core 62, and the screw shaft portion 62a protrudes from the solenoid housing 65. A cap nut 78 is screwed into the part with a washer 77 interposed between the solenoid housing 65 and the cap nut 78. The closed end center of the solenoid housing 65 is fastened to the fixed core 62 by tightening the cap nut 78. Will be.

The other end of the guide cylinder 61 is fixed to the regulator body 38A while being inserted into the large-diameter hole 74, and the plunger 63 is slidably fitted to the guide cylinder 61, so that the regulator body 38A is provided. Small diameter hole 7
A main valve chamber 79 is formed between the inner end of the cylinder 3 and the other ends of the guide cylinder 61 and the plunger 63. Further, a passage 59 communicating with the purification chamber 58 of the high-pressure filter 39 is communicated with the main valve chamber 79, and CNG from which impurities have been removed by the high-pressure filter 39 is introduced into the main valve chamber 79.

A passage 80 is formed in regulator body 38A so as to open at the center of the inner end of small diameter hole 73.
An annular valve seat 81 slightly protruding toward the main valve chamber 79 so as to surround an open end of the passage 80 to the main valve chamber 79 is provided with a regulator body 38A.
Is provided.

The valve member 67 has a disc-shaped pilot valve portion 67 a having a tapered surface having a smaller diameter toward the plunger 63 on one end surface, and faces the inner end of the small-diameter hole 73. And the other main valve portion 6 formed in a disk shape
7b are integrally connected to each other via a connecting cylinder 67c which forms a step between the two valve portions 67a, 67b. The diameter of the pilot valve portion 67a is larger than the diameter of the main valve portion 67b. Set smaller. In the center of the valve member 67, a first passage 82 which is always in communication with the passage 80, and a second passage 83 which communicates with the first passage 82 and opens at the center of one end surface of the pilot valve portion 67a are provided coaxially. And the second passage 8
3 has a smaller diameter than the first passage 82.

At the end of the plunger 63 facing the main valve chamber 79, a concave portion 84 into which the pilot valve portion 67a is inserted is provided. The pilot valve portion 67a is a C-shaped fixed to the other end of the plunger 63. Pilot valve chamber 86 is loosely inserted into recess 84 so that retaining ring 85 prevents removal from recess 84, and pilot valve chamber 86 communicates with main valve chamber 79 between pilot valve portion 67 a and plunger 63.
Is formed. A rubber seal 87 for closing the opening of the second passage 83 to the pilot valve chamber 86 when the central portion of the one end surface of the pilot valve portion 67a is seated is embedded in the central portion of the closed end of the concave portion 84. Thus, the retaining ring 85
The pilot valve portion 67a is fixed to the plunger 63 at a position where the pilot valve portion 67a can move relative to the plunger 63 in the axial direction between the closed end of the concave portion 84 and the retaining ring 85.

In the main valve portion 67b, a small-diameter hole 73 is provided.
An annular rubber seal 88 that sits on the valve seat 81 and shuts off the space between the main valve chamber 79 and the passage 80 is embedded in the surface facing the closed end.

In such an electromagnetic shut-off valve 40, the coil 6
0, the plunger 63 is moved in a direction away from the fixed core 62 by the spring force of the return spring 64, and the rubber seal 88 of the main valve portion 67b is seated on the valve seat 81, and the main valve chamber 79 and the passage are removed. At the same time, the pilot valve portion 67a is seated on the rubber seal 87 and the pilot valve chamber 86 and the passage 80 are also shut off, and the supply of high-pressure CNG to the passage 80 is stopped.

On the other hand, when power is supplied to the coil 60,
First, the plunger 63 moves toward the fixed core 62 only by separating the pilot valve portion 67a from the rubber seal 87, and the second passage 8 communicating with the passage 80 via the first passage 82.
3 will communicate with the pilot valve chamber 86. As a result, CNG gradually flows from the main valve chamber 79 to the passage 80 via the pilot valve chamber 86, the second passage 83, and the first passage 82, whereby the main valve chamber 79 and the passage 80 The difference in pressure acting from the side is reduced. Thus, when the electromagnetic force by the coil 60 overcomes the differential pressure acting on the main valve portion 67b, the plunger 63 moves further to the fixed core 62 side, and the rubber seal 88 of the main valve portion 67b moves the valve seat 81. And CNG flows from the main valve chamber 79 to the passage 80.

[Primary pressure reducing valve 41] Referring to FIG. 9, the valve housing 90 of the primary pressure reducing valve 41 includes a portion on the first end face 50 side of the regulator body 38A and a first end face of the regulator body 38A. A plurality of bolts 92 at 50 ...
The first end face 50 of the regulator body 38A and the cylindrical portion 91
The peripheral edge of the diaphragm 93 is sandwiched between the cover 93 and the cover 91 having a.

The first end face 50 is provided with a recess 95 for forming a decompression chamber 94 between the first end face 50 and the diaphragm 93.
The regulator body 38 </ b> A has a mounting hole 9 having one end opened at the center of the decompression chamber 94 and extending toward the second end face 51.
7 are provided. The mounting hole 97 has a first hole 97a having one end opened at the center of the closed end of the concave portion 95, and a first hole 97a having a diameter smaller than that of the first hole 97a and having one end coaxially connected to the other end of the first hole 97a. A second hole 97b, a third hole 97c having a smaller diameter than the second hole 97b and having one end coaxially connected to the other end of the second hole 97b, and a third hole having a smaller diameter than the third hole 97c. Fourth hole 97 having one end coaxially connected to the other end of portion 97c
and a passage 80 for guiding CNG from the electromagnetic shut-off valve 40 is opened in the inner surface of the second hole 97b.

In the first hole 97a of the mounting hole 97, a cylindrical valve seat member 98 is provided with an annular seal member 99 between the step portion between the first and second holes 97a and 97b.
Are screwed together. That is, a female screw 100 is cut into the inner surface of one end of the first hole portion 97 a in the mounting hole 97, and the valve seat member 98 is screwed into the female screw 100.

On the end face of the valve seat member 98 on the side of the decompression chamber 94,
A plurality of, for example, four projections 102 are formed in a plane orthogonal to the axis of the mounting hole 97 to form a plurality of, for example, four grooves 101 extending in the radial direction of the valve seat member 98 therebetween. The grooves 101 are arranged in a cross shape.
When the valve seat member 98 is screwed into the female screw 100, a tool (not shown) can be engaged with the grooves 101 arranged in a cross shape to rotate the valve seat member 98. The member 98 can be easily attached to the regulator body 38A.

A valve chamber 103 communicating with the passage 80 is formed between the valve seat member 98 and the stepped portion between the second and third holes 97b and 97c in the mounting hole 97. Further, the valve seat member 98 integrally includes an inward flange 98a that protrudes radially inward at an end portion on the decompression chamber 94 side, and a valve that communicates with the decompression chamber 94 on the inner periphery of the inward flange 98a. A hole 104 is formed, and the inner surface of the inward flange 98a is provided with the valve hole 104.
Is opened at the center, and a tapered valve seat 105 facing the valve chamber 103 is formed.

In the valve chamber 103, a synthetic resin valve 106 which can be seated on the valve seat 105 is accommodated.
Is fixed to a valve shaft 107 arranged coaxially with the valve hole 104.

The valve body 106 has a tapered valve seat 105.
One end face facing the valve seat 105 is formed in a cylindrical shape with a tapered shape so as to be seated on the valve shaft 105.
Fixed to Moreover, the valve body 10 is provided on the outer surface of the valve shaft 107.
An O-ring 108 is mounted on the inner surface of the O-ring 6 so as to resiliently contact it.

One end of the valve shaft 107 is supported by the regulator body 38A so as to be movable in the axial direction by an O-ring 109 interposed between the mounting hole 97 and the inner surface of the third hole 97c. The outer surface of the valve body 106
The inner surface of the valve seat member 98 is slidably contacted at a plurality of locations spaced at equal intervals in the circumferential direction.
Flow passages 110 extending along the axial direction of the valve shaft 107 are formed between the valve seat 6 and the valve seat member 98.

The holding plate 111 for holding the O-ring 109 between the mounting hole 97 and the step between the third and fourth holes 97c and 97d is provided in the second and third holes 9.
7b and 97c, the holding plate 1
A spring 112 that exerts a spring force in a direction in which the valve body 106 is seated on the valve seat 105 is provided between the valve body 11 and the valve body 106.

A spring chamber 115 is formed between the cover 91 and the diaphragm 93, and a coil spring 116 for urging the diaphragm 93 toward the pressure reducing chamber 94 is formed in the spring chamber 115.
Is stored.

The valve hole 1 is provided in the cylindrical portion 91a of the cover 91.
A storage hole 117 extending coaxially with the hole 04 is provided so as to open the outer end. The storage hole 117 has a screw hole portion 117a on the outer side in the axial direction and a larger diameter than the screw hole portion 117a. A sliding hole 117b on the axially inward side coaxially connected to the screw hole 117a.

A first diaphragm retainer 118 integrally having a cylindrical portion 118a penetrating the center of the diaphragm 93 and protruding toward the spring chamber 115 is brought into contact with the surface of the diaphragm 93 facing the decompression chamber 94 at the center. On the surface facing the spring chamber 115 side at the center of the diaphragm 93, the inner periphery is engaged with an annular step 119 provided on the outer surface of the cylindrical portion 118a, so that the center of the diaphragm 93 is brought into contact with the first diaphragm 118. The second diaphragm retainer 120 interposed therebetween is brought into contact.

The other end of the valve shaft 107, that is, the end on the side of the diaphragm 93, is coaxially fastened to a diaphragm rod 121, and the diaphragm rod 121 is connected to the first rod.
It is inserted into the central part of the diaphragm retainer 118 from the decompression chamber 94 side. An annular step 122 facing the decompression chamber 94 is provided on the inner surface of the cylindrical section 118 a of the first diaphragm retainer 118, and the diaphragm rod 121 is engaged with the annular step 122. Further, the second diaphragm retainer 120 is sandwiched between the diaphragm 93 and the auxiliary retainer 123, and a screw shaft portion 1 provided on the diaphragm rod 121 at a portion protruding from the cylindrical portion 118a.
21a, a washer 1 between the auxiliary retainer 123 and the auxiliary retainer 123.
24 are screwed together. By tightening the nut 125, the center of the diaphragm 93 is sandwiched between the two diaphragm retainers 118 and 120, and the valve shaft 107 is fixed to the center of the diaphragm 93. Will be. Moreover, the decompression chamber 94 and the spring chamber 11
In order to seal the gap between the five, the O-ring 126 mounted on the outer periphery of the diaphragm rod 121 resiliently contacts the inner surface of the cylindrical portion 118a.

Incidentally, the diaphragm 93 is connected to the valve shaft 10.
The thickness of the connecting portion, ie, the central portion, and the portion sandwiched between the regulator body 38A and the cover 91, ie, the thickness of the peripheral portion, are relatively large, and the portion connecting the central portion and the peripheral portion is large. The diaphragm 93 is formed in a relatively thin curved shape.
According to this, the pressure resistance of the diaphragm 93 can be improved, and the response at low temperatures can be improved.

The second diaphragm retainer 120 is integrally provided on the outer peripheral side with a bending restricting portion 120a for restricting the bending of the diaphragm 93 toward the spring chamber 115. The flexure restricting portion 120 a is formed in a curved shape bulging toward the spring chamber 115, and the outer peripheral edge of the flexure restricting portion 120 a approaches and faces the inner surface of the cover 91. In addition, the thickness of the diaphragm 93 is formed to be larger than the gap at a portion corresponding to the gap between the outer edge of the deflection regulating portion 120a and the inner peripheral surface of the cover 91.

Such a second diaphragm retainer 12
The shape of 0 allows the diaphragm 93 to smoothly bend from the second diaphragm retainer 120 to the inner surface of the cover 91 even when a pressure higher than the specified pressure acts on the decompression chamber 94, and the second diaphragm retainer 120
Prevents the diaphragm 93 from bending toward the spring chamber 115 at the outer edge of the diaphragm 93.
The adjusting screw 127 is screwed into the opening at the outer end of the storage hole 117, that is, the screw hole 117 a, which can prevent the life of the adjusting screw 127 from increasing and improve the durability of the diaphragm 93. In the protrusion from 91,
A lock nut 128 for adjusting the advance / retreat position of the adjustment screw 127 is screwed. The adjusting screw 127 is provided with an opening 129 for opening the spring chamber 115 to the atmosphere.

The coil spring 116 is provided with the adjusting screw 126.
And a leaf spring 132 abutting against an auxiliary retainer 123 mounted on the diaphragm 93 on the spring chamber 115 side. Therefore, the spring load of the coil spring 116 can be adjusted by adjusting the advance / retreat position of the adjustment screw 126.

Referring to FIGS. 10 and 11, the leaf spring 132 is brought into frictional contact with the inner surface of the cylindrical portion 91a which is a part of the valve housing 90, so that the diaphragm 93 is
To provide sliding resistance to the spring chamber 115.
The bottomed cylindrical cup portion 132a having a closed end sandwiched between the auxiliary retainer 123 and the coil spring 116 mounted on the central portion of the diaphragm 93 on the side thereof, and a circumferential direction of the inner surface of the sliding hole 117b in the cylindrical portion 91a. A plurality of leaf portions 132b, 132b,... Are integrally connected to the opening end of the cup portion 132a so as to resiliently slide at a plurality of portions at equal intervals, for example, eight portions.

The regulator body 38A has a decompression chamber 9
A plurality of, for example, two outlet passages 13 through one end
3,133 are drilled in parallel with the mounting hole 97,
A connection hole 134 for commonly opening the other ends of the outlet passages 133 and 133 is provided in the second body of the regulator body 38A.
The protrusion 51a is provided on the end surface 51 side.

In such a primary pressure reducing valve 41, when high-pressure CNG does not flow into the valve chamber 103, the diaphragm 93 is bent toward the pressure reducing chamber 94 by the spring force of the coil spring 116, and the valve body 106 The valve hole 104 is opened away from the valve seat 105. Thus, the valve chamber 103
When the high-pressure CNG flows into the pressure reducing chamber 94 through the valve hole 104 and the pressure in the pressure reducing chamber 94 increases to the extent that the diaphragm 93 is bent toward the spring chamber 115 against the spring force of the coil spring 116, The valve body 106 is seated on the valve seat 105 and the valve hole 104 is closed. By repeatedly opening and closing the valve hole 104, the valve chamber 103 is kept at a high pressure of, for example, 25 to 1 MPa. Inflowing CN
G is decompressed to, for example, 0.6 to 0.7 MPa and flows from the decompression chamber 94 to the outlet passages 133 and 133.

Paying particular attention to FIG. 6, the protrusion 51a of the regulator body 38A is provided with a bottomed mounting hole 135 for screwing and mounting the pressure switch 42, and a closed end of the mounting hole 135. A detection hole 136 that opens in the side inner surface is provided in the regulator body 38A coaxially with the mounting hole 97. Regulator body 38A
Is provided with a communication hole 137 that connects between the connection hole 134 and the detection hole 136. The pressure switch 42 reduces the pressure of the CNG that is reduced in pressure by the primary pressure reducing valve 41 and flows from the outlet passages 133 and 133 to the connection hole 134. , For example, 1.65M
The switching mode will be changed in accordance with Pa or more.

The secondary pressure reducing valve 31 is connected to the connection hole 134 of the regulator RA. The structure of the secondary pressure reducing valve 31 will be described below.

[Secondary pressure reducing valve 31]; the valve housing 140 of the secondary pressure reducing valve 31 is also referred to with reference to FIGS.
Are a body 141, a partition member 142, and a cover 143.
Is the partition member 1 between the body 141 and the cover 143.
42 are sandwiched by a plurality of bolts 144, 144..., And both ends of a plurality of knock pins 145.
And the cover 143, respectively,
The relative positions of the body 141, the partition member 142, and the cover 143 are fixed.

The periphery of partition member 142 is sandwiched between body 141 and cover 143, and the periphery of diaphragm 146 is sandwiched between partition member 142 and cover 143. Thus, a decompression chamber 147 is formed between the body 141 and the partition member 142, and a pressure action chamber 148 communicating with the decompression chamber 147 is formed between the partition member 142 and one surface of the diaphragm 146, and the other surface of the diaphragm 146 and A spring chamber 149 is formed between the covers 143.

Referring to FIG. 17 as well, a concave portion 150 opened toward the partition member 142 is provided in the body 141 so as to form the decompression chamber 147 between the body 141 and the partition member 142. A bottomed mounting hole 151 having one end opened at the center of the closed end of the recess 150 and the other end closed. Further, a protruding portion 152 protruding toward the decompression chamber 147 is provided at the other end closing portion of the mounting hole 151.

A female screw 153 is formed in the inner surface of the mounting hole 151 on the decompression chamber 147 side. A cylindrical valve seat member 154 is screwed to the female screw 153, and a mounting hole is formed in the outer surface of the valve seat member 154. An O-ring 155 that elastically contacts the inner surface of the 151 is mounted.

Moreover, a plurality of, for example, four grooves 156 extending in the radial direction of the valve seat member 154 in a plane perpendicular to the axis of the mounting hole 151 are formed between the end surfaces of the valve seat member 154 on the decompression chamber 147 side. A plurality of, for example, four projections 1
57 are protruded, and the grooves 156 are arranged in a cross shape. When the valve seat member 154 is screwed into the female screw 153, a tool (not shown) can be engaged with a groove 156 arranged in a cross shape to rotate the valve seat member 154. The member 154 can be easily attached to the body 141.

A valve chamber 158 is formed between the valve seat member 154 and the other end closing portion of the mounting hole 151.
Is connected to an input port 159 provided on the body 141 so as to open to the side surface of the body 141.
Thus, CNG from the primary pressure reducing valve 41 is introduced into the input port 159, that is, the valve chamber 158.

The body 141 has the input port 1
An output port 160 that opens on a side surface different from the side surface on which the 59 is provided and a passage 161 that connects the output port 160 to the decompression chamber 147 are provided. CNG from the decompression chamber 147 passes through the passage 161 and the output port 160. Through the fuel gas pipe 36.

The valve seat member 154 is integrally provided with an inward flange 154a projecting inward in the radial direction at the end on the decompression chamber 147 side, and the inner periphery of the inward flange 154a is connected to the decompression chamber 147. The communicating valve hole 162 is formed, and the inward flange 154 is formed.
On the inner peripheral portion of a, an annular valve seat 163 facing the valve chamber 158 with the valve hole 162 opened at the center is formed so as to protrude toward the valve chamber 158 side.

The raised portion 152 is provided with a bottomed sliding hole 164 that is open to the valve hole 162 side and is coaxial with the valve hole 162, and the valve body 165 is slidably fitted in the sliding hole 164. Are combined. Further, an annular rubber seal 166 that can be seated on the valve seat 163 is fixed to the valve body 165.

The valve body 165 has at least a decompression chamber 147.
A through hole 167 having a female screw 167a at the side portion is provided between both ends in the axial direction. One end of a valve shaft 168 coaxial with the valve hole 162 is screwed to the female screw 167a. That is, the valve body 165 is fixed to one end of the valve shaft 168.

A back pressure chamber 169 is formed between the valve body 165 and the closed end of the sliding hole 164, and the outer surface of the valve body 165 resiliently comes into sliding contact with the inner surface of the sliding hole 164. The O-ring 170 is mounted.

18 and 19, the partition member 142 has a circular recess 171 facing the diaphragm 146 so as to form a pressure action chamber 148 between the diaphragm member 146 and the diaphragm member 146. The annular groove 172 for fitting the ring-shaped outer peripheral seal portion 146a provided on the peripheral edge of the diaphragm 146 is formed in the concave portion 171.
Is provided on the partition member 142 so as to surround the partition wall 142.

The partition member 142 is provided with a through hole 173 through which the valve shaft 168 is axially movably inserted at the center of the partition member 142, and a pressure action chamber 148 is provided.
A plurality of, for example, four restricting projections 174,1 for restricting the stroke limit of the diaphragm 146 to the side of reducing the volume of
74 are arranged so as to surround the through hole 173 and protrude from the diaphragm 146 side.

The partition member 142 includes the pressure action chamber 14.
A communication hole 175 is formed to allow the passage 8 to communicate with the decompression chamber 147.

In FIG. 20, the diaphragm 146 is
The partition member 1 is fitted into the annular groove 172 of the partition member 142.
A ring-shaped outer peripheral seal portion 146 a sandwiched between the valve shaft 42 and the cover 143, a cylindrical valve shaft connecting portion 146 b disposed at the center for connecting the valve shaft 168, and a spring chamber 1.
The outer peripheral seal portion 14 having a cross-sectional shape swelling to the 49 side.
The diaphragm 1 is formed integrally with a bending portion 146c disposed on the inner side of the diaphragm 6a.
In a natural state where no external force acts on the bending portion 146,
The diaphragm 146 is arranged such that the inner peripheral portion of the diaphragm c is offset toward the decompression chamber 147 from the outer peripheral portion by the set offset amount e.
Is formed.

The bending portion 146c and the valve shaft connecting portion 14
The first diaphragm retainer 176 is in contact with the surface of the diaphragm 146 facing the pressure action chamber 148 between the 6b and 6b.
The diaphragm 146 is located on the inner side of the bending portion 146c.
A second diaphragm retainer 178 having an insertion hole 177 at the center thereof is in contact with the surface facing the spring chamber 149 so as to sandwich the diaphragm 146 between the second diaphragm retainer 178 and the first diaphragm 176.

A valve shaft 168 having a valve body 165 fixed to one end.
The valve hole 162 of the valve seat member 154, the through hole 173 of the partition member 142, the valve shaft connecting portion 146 of the diaphragm 146
b, and first and second diaphragm retainers 17
6, 178 extending coaxially through the center of the first diaphragm retainer 176 and the annular step 179 engaging the inner peripheral edge of the first diaphragm retainer 176, and the valve shaft connecting portion 146b to the second diaphragm retainer. An annular step 180 sandwiched between the valve shaft 178 and the valve shaft 168 is provided on the valve shaft 168.
8 is attached to the outer periphery.

The valve shaft connecting portion 146b of the diaphragm 146
And the insertion hole 177 of the second diaphragm retainer 178
A screw shaft 168a is provided at the other end of the valve shaft 168 that projects through the spring chamber 149, and a washer 181 is interposed between the valve shaft 168 and the second diaphragm retainer 178, and a nut 182 is attached to the screw shaft 168a. Is screwed. By tightening the nut 182, the diaphragm 146
Of the first and second diaphragm retainers 17
6, 178, and the valve shaft 168 is connected to the center of the diaphragm 146. Moreover, the valve shaft 1
68, the decompression chamber 1 through the through hole 167 of the valve body 165.
A communication path 183 that connects the back pressure chamber 49 to the back pressure chamber 169 is provided.

At the center, the two diaphragm retainers 1 are provided.
76, 178, a valve shaft 168 connected to the central portion of the diaphragm 146, and a valve body 165 fixed to the valve shaft 168, the valve housing 1
When the diaphragm 146 is in a natural state in which the action of external force is avoided at the time of assembling to the valve 40, the rubber seal 166 of the valve body 165 is assembled so as to be at a position away from the valve seat 163.

The cover 143 has a cylindrical portion 143 having an end wall 143b at the end opposite to the diaphragm 146.
a at the center of the end wall 143b.
A support cylinder portion 184 coaxially arranged in 43a and having both ends opened is integrally connected.

The support cylindrical portion 184 is provided coaxially with a small-diameter hole 185 on the inner side in the axial direction and a large-diameter hole 186 on the outer side in the axial direction in which a female screw 187 is formed at least partially. An adjustment screw 188 is screwed into the support cylinder 184 so that the advance / retreat position can be adjusted. The adjusting screw 188 is fitted into the small-diameter hole 185 and has a small-diameter shaft portion 188 a on the outer surface of which an annular seal member 189 is resiliently brought into contact with the inner surface of the small-diameter hole 185, and a male screw screwed into the female screw 187. The large-diameter shaft portion 18 having an outer periphery 190 and an outer end face provided with an engagement recess 191 capable of engaging a rotary operation tool.
8b are integrally and coaxially connected,
The position of the adjusting screw 188 in the axial direction is such that the inner end of the small-diameter shaft portion 188a protrudes into the spring chamber 149 and the large-diameter shaft portion 188b
Is set so that the outer end is located more inward than the outer surface of the end wall 143b.

By setting the position of the adjusting screw 188 in the axial direction, a concave portion 192 having the closed end at the outer end of the large-diameter shaft portion 188b is formed at the outer end of the large-diameter hole 186. Is filled with a filler 193 which can be solidified. Moreover, a seal 194 is attached to the outer surface of the end wall 143b so as to cover the recess 192.

The female screw 187 into which the adjusting screw 188 is screwed is formed in the large-diameter hole 186 such that a part thereof faces the concave portion 192.

In the spring chamber 149, a retainer 195 is in contact with and supported by the inner end of the adjusting screw 188. The retainer 195 and the diaphragm 14 are disposed on the spring chamber 149 side.
6, a second diaphragm retainer 17 mounted at the center of
8 between the leaf spring 197 and the leaf spring 197
A coil spring 196 for urging the diaphragm 146 in a direction in which the diaphragm 146 separates from the valve seat 163 is contracted. Therefore, the spring load of the coil spring 196 can be adjusted by adjusting the advance / retreat position of the adjustment screw 180.

Referring to FIGS. 21 and 22 together, leaf spring 197 frictionally contacts the inner surface of cylindrical portion 143a, which is a part of valve housing 140, to provide sliding resistance to diaphragm 146. A second diaphragm retainer 178 and a coil spring 196 mounted on the center of the diaphragm 146 on the spring chamber 149 side.
A bottomed cylindrical cup portion 197a having a closed end interposed therebetween.
And a plurality of leaf portions integrally connected to an open end of the cup portion 197a so as to resiliently slide at a plurality of locations, for example, five locations at equal intervals in the circumferential direction of the inner surface of the cylindrical portion 143a. 197b, 197b...

Further, a connection pipe 198 is connected to the cover 143, and the intake air of the engine E is stored in the spring chamber 149 via the connection pipe 198 and a pipe (not shown) connected to the connection pipe. Pressure is introduced.

In such a secondary pressure reducing valve 31, when CNG does not flow into the valve chamber 158, the diaphragm 146 is moved by the spring force of the coil spring 196.
The valve body 165 is separated from the valve seat 163 to open the valve hole 162. Thus, the CNG flowing into the valve chamber 158 flows from the valve hole 162 through the pressure reducing chamber 147 into the pressure action chamber 148, and the differential pressure between the pressure action chamber 158 and the spring chamber 149 resists the spring force of the coil spring 196. When the diaphragm 146 is increased to the extent that the diaphragm 146 is bent toward the spring chamber 149, the rubber seal 166 of the valve body 165 is
The valve hole 162 is closed by sitting on the valve 63, and the opening and closing of the valve hole 162 is repeated, so that CNG flowing into the valve chamber 158 at 0.6 to 0.7 MPa, for example, For example, the pressure is reduced to 0.2 to 0.3 MPa.
3 to the injectors 32 of the engine E.

Next, the operation of the first embodiment will be described. A high-pressure filter 39, an electromagnetic shut-off valve 40, a primary pressure reducing valve 41, and a pressure switch 42 interposed between the CNG tanks 20 and the injectors 32 of the engine E are described. And the secondary pressure reducing valve 31, the high pressure filter 39, the electromagnetic shutoff valve 4
0, a passage 59 connecting the primary pressure reducing valve 41 to the high pressure filter 39 and the electromagnetic shutoff valve 40, a passage 80 connecting the electromagnetic shutoff valve 40 and the primary pressure reducing valve 41, and an outlet passage 133 having one end connected to the primary pressure reducing valve 41. Are arranged on a common regulator body 38A having a pressure regulator 42, and a pressure switch 42 is attached to the regulator RA.

The high pressure filter 3 on the high pressure side
9. By forming the regulator RA by integrating the electromagnetic shut-off valve 40 and the primary pressure reducing valve 41 in the regulator body 38A, the regulator body 38A has a larger size than the one in which all the high-pressure parts and low-pressure parts are integrated. The structure of the passage is simplified, and accordingly, the processing to be performed on the regulator body 38A is also facilitated. In addition, the regulator RA can be made more compact, and the restrictions on layout with other components that occur when the regulator RA is mounted on the vehicle V can be reduced.

Since the valve housing 140 of the secondary pressure reducing valve 31 on the low pressure side is formed separately from the regulator body 38A, the valve housing 140 of the secondary pressure reducing valve 31 is made of a material having relatively low strength. Thus, cost reduction can be achieved.

The primary pressure reducing valve 41 is provided with a leaf spring 132 for applying a sliding resistance to the diaphragm 93 by making frictional contact with a sliding hole 117b in a cylindrical portion 91a which is a part of the valve housing 90. , The secondary pressure reducing valve 31,
The diaphragm 146 is provided with a leaf spring 197 for providing sliding resistance to the diaphragm 146 by frictionally contacting the inner surface of the cylindrical portion 143a which is a part of the valve housing 140.

The leaf springs 132 and 197 are closed-bottomed cylinders whose closed ends are sandwiched between retainers 123 and 178 and coil springs 116 and 196 mounted at the center of the diaphragms 93 and 146 on the spring chambers 115 and 149 side. Cup portions 132a, 197a and the cylindrical portions 91a, 1
A plurality of leaf portions 132b, 1 integrally connected to the open ends of the cup portions 132a, 197a so as to resiliently slidably contact a plurality of portions at equal intervals in the circumferential direction of the inner surface of the 43a.
32b ...; 197b, 197b ...

That is, the leaf springs 132, 197 are composed of a plurality of leaf portions 132b, 132b.
b are resiliently slidably brought into contact with the inner surfaces of the cylindrical portions 91a and 143a, thereby imparting sliding resistance against self-excited vibration of the coil springs 116 and 196 to the diaphragms 93 and 146. Even if the diameters of the cylindrical portions 91a and 143a decrease as the diameters of the 93 and 146 decrease, the cylindrical portions 91 of the leaf springs 132 and 197 also decrease.
a, 143a does not change, so that the sliding resistance exerted by the leaf springs 132, 197 does not increase with the downsizing of the primary pressure reducing valve 41 and the secondary pressure reducing valve 31, and Even if the temperature changes, the sliding resistance due to the resilient sliding contact of the leaf springs 132, 197 with the cylindrical portions 91a, 143a does not change, so that the diaphragms 93, 146 are not downsized and the temperature does not change. ,
A stable sliding resistance against self-excited vibrations of the coil springs 116 and 196 can be provided to the diaphragms 93 and 146 to prevent the responsiveness of the primary pressure reducing valve 41 and the secondary pressure reducing valve 31 from being lowered. Can be.

Further, the cup portion 132 having relatively high rigidity
a, a plurality of leaf portions 132b, 132b at 197a
, 197b, 197b... Are supported, so that the valve housings 90, 1 of the leaf springs 132, 197 are supported.
At the time of assembling into the inside 40, the leaf portions 132b, 132b ...;
197b, 197b ... can be prevented from being broken, and assemblability can be improved.

In the secondary pressure reducing valve 31, the diaphragm 1
46 is sandwiched between the cover 143 and the partition member 142 sandwiched between the cover 143 and the body 141, and the decompression chamber 147 is formed between the partition member 142 and the body 14.
A pressure action chamber 148 communicating with the decompression chamber 147 is formed between one surface of the diaphragm 146 and the partition member 142. For this reason, the structure of the part of the body 141 facing the decompression chamber 147 is simplified,
Of the partition member 142 can be easily performed in a state separated from the body 141.

The diameter of the pressure action chamber 148 changes in accordance with the change in the diameter of the diaphragm 146.
The pressure reducing chamber 14 having the pressure action chamber 42 interposed between the pressure action chamber 148
7 can be determined independently of the change in the diameter of the diaphragm 146. Even if the diameter of the diaphragm 146 is set small based on the demand for downsizing the secondary pressure reducing valve 31, the diameter of the pressure reducing chamber 147 can be determined. It is not necessary to set the diameter to be small, and it is possible to avoid a change in the flow rate characteristic such that the gas pressure in the decompression chamber 147 greatly decreases from the target control pressure.

Further, since the gas pressure in the pressure reducing chamber 147 does not directly act on one surface of the diaphragm 146, when the gas pressure in the pressure reducing chamber 147 changes greatly,
The diaphragm 146 can be protected by preventing an excessive load from acting on the diaphragm 6.

Further, since the body 141 is provided with the sliding hole 164 for slidably fitting the valve body 165, the axial movement of the valve body 165 and the valve shaft 168 causes the body 141 to move.
Of the sliding hole 164 and the inner surface of the through hole 173 provided in the partition member 142, thereby preventing the valve body 165 and the valve shaft 168 from falling down, and 165 can be reliably opened and closed.

When the diaphragm 146, the valve shaft 168, and the valve body 165 of the secondary pressure reducing valve 31 are assembled in the valve housing 140, when the diaphragm 146 is in a natural state in which the action of external force is avoided, the valve body The valve seal 165 is assembled such that the rubber seal 166 is located at a position away from the valve seat 162, and the valve body 165 is acted upon by the gas pressure in the pressure action chamber 148 communicating with the pressure reducing chamber 147.
When the diaphragm 146 is flexed so as to be seated on the valve seat 163, the diaphragm 146
Is deflected toward the spring chamber 149 so as to exhibit a resilient force in the same direction as the spring force of the pressure reducing chamber 147, that is, in the direction opposite to the force in the valve closing direction due to the gas pressure of the decompression chamber 147. Therefore, when the valve body 165 is further separated from the valve seat 163 to increase the gas flow rate, the elastic force exerted by the diaphragm 146 against the force in the valve closing direction due to the gas pressure of the decompression chamber 147 becomes smaller, The resilience exerted by the diaphragm 146 can be minimized from adversely affecting the responsiveness, and the pressure in the decompression chamber 147 is not controlled to a lower value even when the gas flow rate increases.

Further, the diaphragm 146 has a ring-shaped outer peripheral seal portion 146a sandwiched by the valve housing 140.
And a valve shaft connecting portion 146b to which the valve shaft 168 is connected, and a bending portion 146c having a transverse cross-sectional shape swelling toward the spring chamber 149 and disposed inward of the outer peripheral sealing portion 146a. In a natural state, the inner peripheral portion of the bending portion 146c is formed to be offset from the outer peripheral portion toward the decompression chamber 147 by the set offset amount e. For this reason, the diaphragm 146 is naturally moved to the valve housing 14.
0, the flexible portion 14 of the diaphragm 146
The inner peripheral portion of 6c, that is, the center portion where the valve body 165 is connected via the valve shaft 168 is offset to the decompression chamber 147 side from the outer peripheral portion of the bending portion 146c, and the diaphragm 146 is naturally opened. A state in which the valve body 165 is separated from the valve seat 163 when assembled to the housing 140 can be easily made to appear, and the diaphragm 146
Is easy to assemble.

Further, in the secondary pressure reducing valve 31, an end wall 143b is provided at an end of the cylindrical portion 143a constituting a part of the valve housing 140, opposite to the diaphragm 146, and is integrally formed with the end wall 143b. Cylindrical part 143 connected continuously
An adjusting screw 188 capable of adjusting the spring load of the coil spring 196 in accordance with the axially advanced / retracted position is screwed to the support cylinder portion 184 coaxially arranged in a. Accordingly, the spring load of the coil spring 196 can be adjusted only by adjusting the advance / retreat position by screwing the adjustment screw 188 into the support cylinder portion 184, and the number of components necessary for adjusting the spring load of the coil spring 196 is reduced. It is possible to reduce the number of assembling steps while reducing the number of assembling steps.

Further, the support cylinder portion 184 is provided with an inner small-diameter hole 185 and an outer large-diameter hole 186 coaxially, and the adjusting screw 188 is fitted into the small-diameter hole 185. An annular seal member 189 that resiliently contacts the inner surface of the small-diameter hole 185 has a small-diameter shaft portion 188a mounted on the outer surface at the distal end side. When the adjustment screw 188 is inserted into the support cylinder portion 184, a large diameter is used. The internal thread 187 provided on the inner surface of the diameter hole 186 can prevent the seal member 189 from being damaged as much as possible.

The adjusting screw 188 has an outer end formed at the end wall 1.
43b to a position inside the outer surface of the support tube 43b.
Therefore, the adjusting screw 188 does not protrude from the outer surface of the end wall 143b, which can contribute to downsizing of the secondary pressure reducing valve 31.

Further, the large-diameter shaft portion 1 provided with the adjusting screw 188
A concave portion 192 is formed at the outer end of the large-diameter hole 886 with the outer end of 88b as a closed end, and the filler 193 is filled in the concave portion 192. Thus, the filler 193 is solidified, so that a lock nut or a cap is not required. In addition, it is possible to prevent the adjustment screw 188 from rotating and prevent erroneous operation.
The locking of the adjusting screw 188 can be further ensured by inserting the 93 into the engaging recess 191 at the outer end of the adjusting screw.

Further, the female screw 187 for screwing the adjusting screw 188 is formed in the large-diameter hole 186 so that a part thereof faces the concave portion 192, and the filler 193 filled in the concave portion 192 is filled with the female screw 187. By entering the thread groove, the filler 193 can be reliably held in the concave portion 192, and the filler 193 is efficiently inserted into the threaded portion between the male screw 190 of the adjusting screw 188 and the female screw 187 of the large-diameter hole 186. Adjustment screw 1 that can penetrate well and is more sure
88 detents can be achieved.

FIGS. 23 and 24 show a second embodiment of the present invention, in which parts corresponding to those of the first embodiment are denoted by the same reference numerals.

The high-pressure filter 39, the electromagnetic shut-off valve 40, and the primary pressure-reducing valve 41 are provided in a common regulator body 38B, thereby forming a regulator RB.

The mounting surface 2 has a flat end surface of the regulator body 38B on the side opposite to the side on which the primary pressure reducing valve 41 is provided.
01, and on this mounting surface 201,
One end is connected to the pressure reducing chamber 94 of the primary pressure reducing valve 41, and the other end of the outlet passage 133 'provided in the regulator body 38B is opened.

A body 202A shown in FIG. 23 and a body 202B shown in FIG.
It is alternatively and removably attached, and each body 202A, 202B has
Low pressure passages 203, 203 communicating with the outlet passage 133 'when the A, 202 are mounted on the mounting surface 201 are provided, respectively.

In one body 202A shown in FIG.
A relief valve 204 is mounted on the valve housing 2. The relief valve 204 has a valve hole 205 at the tip end communicating with the low-pressure passage 203 and is fixed to the body 202 </ b> A.
06, a rubber seal 207 capable of closing the valve hole 205
And a spring 209 for urging the valve body 208 in a direction to close the valve hole 205 with the rubber seal 207 are housed. The valve housing 206 and the valve body 208 When open, low pressure passage 203
Is formed to be able to open CNG from the outside.

That is, the relief valve 204 is connected to the low pressure passage 2
03, that is, the output pressure of the primary pressure reducing valve 41
The valve is opened to release CNG to the atmosphere when the pressure becomes equal to or higher than the set pressure determined by 9, for example, 1.65 MPa.

In the other body 202B shown in FIG.
A pressure switch 42 is mounted, and the pressure switch 42 controls the pressure in the low pressure passage 203, that is, the primary pressure reducing valve 41.
The switching mode is changed in accordance with the output pressure of, for example, being equal to or higher than a preset pressure, for example, 1.65 MPa, and a signal for shutting off the electromagnetic shut-off valve 40 is output.

According to the second embodiment, the secondary pressure reducing valve 31
In order to prevent a high pressure higher than the set pressure from acting on (see the first embodiment), C output from the primary pressure reducing valve 41 as the output pressure of the primary pressure reducing valve 41 becomes higher than the set pressure.
It is arbitrarily selected whether to use the relief valve 204 for releasing a part of NG or to use the pressure switch 42 for shutting off the electromagnetic shut-off valve 40 when the output pressure of the primary pressure reducing valve 41 becomes equal to or higher than the set pressure. And the regulator RB is selected by selecting one of the relief valve 204 and the pressure switch 42.
And the versatility of the gas fuel supply device when mounted on a vehicle can be increased.

Although the embodiments of the present invention have been described above, the present invention is not limited to the above embodiments, and various design changes can be made without departing from the present invention described in the appended claims. It is possible.

[0109]

As described above, according to the present invention, the sliding resistance does not increase with downsizing of the gas pressure reducing valve.
Even if the temperature changes, the sliding resistance does not change due to the resilient sliding contact of the leaf spring with the cylindrical part, so the self-excited vibration of the coil spring is not affected by the size reduction of the diaphragm and the temperature change. An opposing stable sliding resistance can be imparted to the diaphragm, and the response of the gas pressure reducing valve can be prevented from lowering. Moreover, at the time of assembling the leaf spring into the valve housing, the leaf portion is prevented from being broken, so that the assemblability can be improved.

[Brief description of the drawings]

FIG. 1 is a diagram schematically showing a configuration of a fuel gas supply device of a first embodiment.

FIG. 2 is a plan view showing a state in which the fuel gas supply device is mounted on a vehicle.

FIG. 3 is a side view of the regulator.

FIG. 4 is a plan view of the regulator as viewed from the direction of arrow 4 in FIG. 3;

FIG. 5 is a bottom view of the regulator as viewed from the direction of arrow 5 in FIG. 3;

FIG. 6 is a sectional view taken along line 6-6 of FIG. 4;

FIG. 7 is a sectional view taken along line 7-7 of FIG. 3;

FIG. 8 is an enlarged vertical sectional view of an electromagnetic shut-off valve.

FIG. 9 is an enlarged vertical sectional view of a primary pressure reducing valve.

FIG. 10 is a plan view of a leaf spring provided in the primary pressure reducing valve.

FIG. 11 is a sectional view taken along line 11-11 of FIG. 10;

12 is a side view of the secondary pressure reducing valve, and is a view as viewed from an arrow 12 in FIG.

FIG. 13 is a view taken in the direction of arrow 13 in FIG. 12;

FIG. 14 is a view taken in the direction of arrow 14 in FIG.

FIG. 15 is a sectional view taken along line 15-15 of FIG. 14;

FIG. 16 is a sectional view taken along line 16-16 of FIG. 13;

FIG. 17 is an enlarged view of a main part of FIG. 16;

FIG. 18 is a plan view of a partition member provided in the secondary pressure reducing valve.

FIG. 19 is a sectional view taken along line 19-19 of FIG. 18;

FIG. 20 is an enlarged vertical sectional view of a diaphragm provided in the secondary pressure reducing valve.

FIG. 21 is a plan view of a leaf spring provided in the secondary pressure reducing valve.

FIG. 22 is a sectional view taken along line 22-22 of FIG. 21;

FIG. 23 is a sectional view corresponding to FIG. 6 of the second embodiment.

24 is a cross-sectional view corresponding to FIG. 23 in a state where a body is replaced.

[Explanation of symbols]

 31: Secondary pressure reducing valve as gas pressure reducing valve 41: Primary pressure reducing valve as gas pressure reducing valve 90, 140 ... Valve housing 91a, 143a ... Cylindrical part 93, 146 ... Diaphragm 94, 147 ... decompression chamber 104, 162 ... valve hole 105, 163 ... valve seat 106, 165 ... valve element 115, 149 ... spring chamber 116, 196 ... coil spring 123, 176: retainers 132, 197: leaf springs 132a, 197a: cup portions 132b, 197b: leaf portions

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[Procedure amendment]

[Submission date] December 7, 2001 (2001.12.
7)

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] 0045

[Correction method] Change

[Correction contents]

A diaphragm rod 121 is coaxially fastened to the other end of the valve shaft 107, that is, an end on the diaphragm 93 side.
It is inserted into the central part of the diaphragm retainer 118 from the decompression chamber 94 side. An annular step 122 facing the decompression chamber 94 is provided on the inner surface of the cylindrical section 118 a of the first diaphragm retainer 118, and the diaphragm rod 121 is engaged with the annular step 122. Further, the second diaphragm retainer 120 is sandwiched between the diaphragm 93 and the auxiliary retainer 123, and a screw shaft portion 1 provided on the diaphragm rod 121 at a portion protruding from the cylindrical portion 118a.
21a, a washer 1 between the auxiliary retainer 123 and the auxiliary retainer 123.
24 are screwed together. By tightening the nut 125, the center of the diaphragm 93 is sandwiched between the two diaphragm retainers 118 and 120, and the valve shaft 107 is fixed to the center of the diaphragm 93. Will be. Moreover, the decompression chamber 94 and the spring chamber 11
In order to seal the gap between the five, the O-ring 126 mounted on the outer periphery of the diaphragm rod 121 resiliently contacts the inner surface of the cylindrical portion 118a.

[Procedure amendment 2]

[Document name to be amended] Statement

[Correction target item name] 0048

[Correction method] Change

[Correction contents]

Such a second diaphragm retainer 12
The shape of 0 allows the diaphragm 93 to smoothly bend from the second diaphragm retainer 120 to the inner surface of the cover 91 even when a pressure higher than the specified pressure acts on the decompression chamber 94, and the second diaphragm retainer 120
Prevents the diaphragm 93 from bending toward the spring chamber 115 at the outer edge of the diaphragm 93.
, And the durability of the diaphragm 93 can be improved . An adjustment screw 127 is screwed into the opening at the outer end of the storage hole 117, that is, the screw hole 117 a so as to be able to advance and retreat, and the protrusion of the adjustment screw 127 from the cover 91 is used to adjust the advance and retreat position of the adjustment screw 127. Lock nut 128 is screwed. In addition, adjustment screw 127
An opening 129 for opening the spring chamber 115 to the atmosphere is provided.

[Procedure amendment 3]

[Document name to be amended] Statement

[Correction target item name] 0070

[Correction method] Change

[Correction contents]

The bending portion 146c and the valve shaft connecting portion 14
The first diaphragm retainer 176 is in contact with the surface of the diaphragm 146 facing the pressure action chamber 148 between the 6b and 6b.
The diaphragm 146 is located on the inner side of the bending portion 146c.
A second diaphragm retainer 178 having an insertion hole 177 at the center thereof is in contact with the surface facing the spring chamber 149 so as to sandwich the diaphragm 146 between the second diaphragm retainer 176 and the first diaphragm retainer 176.

[Procedure amendment 4]

[Document name to be amended] Statement

[Correction target item name] 0101

[Correction method] Change

[Correction contents]

[0102] high-pressure filter 39, the electromagnetic cut-off valve 40, by the primary pressure reducing valve 41 is disposed in a common regulator body 38B, the regulator RB is Ru configured.

Claims (1)

[Claims] 1. A peripheral portion of a diaphragm (93, 146) for applying a gas pressure of a decompression chamber (94, 147) to one side is sandwiched between valve housings (90, 140), and is connected to the decompression chamber (94, 147). A valve element (106, 165) which can be seated on a valve seat (105, 163) having a valve hole (104, 162) opening at the center thereof communicates with the diaphragm (93, 14).
6) and connected to the center of the diaphragm (93, 1).
46) The spring chamber (115, 149) facing the other surface is
The valve body (1) is formed in a cylindrical portion (91a, 143a) constituting a part of the valve housing (90, 140).
The coil springs (116, 196) for urging the diaphragms (93, 146) in a direction to separate the valve seats (106, 165) from the valve seats (105, 163) are formed in spring chambers (115, 149).
In the gas pressure reducing valve housed in the cylinder, the cylindrical portion (91
a, 143a) are provided with leaf springs (132, 197) for providing sliding resistance to the diaphragms (93, 146) by frictional contact with the inner surfaces of the diaphragms (93, 146).
2, 197) includes a retainer (123, 176) and a coil spring (11) mounted on the center of the diaphragm (93, 146) on the side of the spring chamber (115, 149).
6, 196) and a closed-end cylindrical cup portion (132a, 197a) between which the closed end is sandwiched, and the cylindrical portion (132a, 197a).
197a) so that the cup portions (132a, 197a) are resiliently slidably contacted at a plurality of locations at equal intervals in the circumferential direction.
a) a plurality of leaf portions (13) integrally connected to the open end;
2b, 197b).