JP2017025957A - Rotary valve and quick exhaust valve for railway vehicle using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotary valve, suitable for, in particular, a quick exhaust valve for an automatic door opening/closing device of a railway vehicle, capable of preventing fluid leakage by increasing a primary-side seal face pressure when pressure fluctuation occurs in valve closing, surely preventing fluid leakage by increasing the seal face pressure by applying the primary-side pressure to the whole face of a seal member in valve closing, switching a flow channel while improving operability by securing high sealability and low torque property in opening/closing a valve element, and quickly exhausting pressure air in a short exhaust time from an exhaust hole of a large diameter while entirely miniaturized and reducing the number of components.SOLUTION: Inflow/outflow ports 10, 11, and an exhaust port are formed on a valve element accommodation portion 16 having a spherical portion 15 formed on a part of an inner periphery of a body 2, through-openings 30-32 communicated with the inflow/outflow ports or the exhaust port, and a mounting groove 33 are formed on the valve element 3 having a spherical part 28 rotatably mounted on the valve element accommodation portion 16, one of the inflow/outflow ports and the exhaust port is sealed and closed by the seal member 5 mounted on the mounting groove, and a seal face pressure is improved by utilizing a back pressure applied to a back face side 5b.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a rotary valve that reduces operating torque during valve body operation while ensuring sealing performance, and a rapid exhaust valve for a railway vehicle using the rotary valve.

  Conventionally, for example, in an automatic door opening and closing device using the air pressure of a railway vehicle, if an emergency occurs, the railway vehicle can be quickly evacuated to the outside of the railway vehicle, or when repair or maintenance is required, the railway vehicle can be quickly In order to enter the door, the door can be manually opened from inside or outside the railway vehicle. In order to make this possible, the air flow path of the door opening and closing device is usually provided with a cock valve as a quick exhaust valve for emergency railway vehicles. By closing the cock valve, the air tank is moved to the door cylinder. At the same time as stopping the supply of pressurized air to the flow path, the flow path can be switched so that the pressure air accumulated in the door cylinder is released to the atmosphere, and the door opening and closing device can be opened by opening the door. It is like that. In this case, it is necessary to ensure sealing performance when the flow path is switched, and to reduce the operating torque when operating the valve body to facilitate manual operation.

  As such a rotary valve, for example, a ball cock valve for a railway vehicle of Patent Document 1 is disclosed. This type of two-way ball cock valve is mounted in a railcar side wall or in a pipe outside the vehicle, and a substantially spherical ball valve body is provided in the body of the valve. The body has a primary side and a secondary side. Exhaust holes are provided between the ball sheets. The ball valve body is provided with a communication hole that communicates the primary side hole and the secondary side hole, and an exhaust port hole that communicates the secondary side hole and the exhaust hole. The secondary side hole and the exhaust hole are communicated with each other by the exhaust port hole in a state in which the secondary side is shut off, and the door can be manually opened and closed by exhausting the air pressure in the pipe from the secondary side through the exhaust hole It has become.

  The ball cock of Patent Document 2 is a ball cock that allows the compressed air to be exhausted from the branch hole by switching the flow path. In this ball cock, a strainer member is provided between the valve seat and the primary side pipe mounting hole. Is provided. In this case, the strainer member removes foreign matter on the side of the primary side pipe mounting hole, and the ball due to the intrusion of foreign matter such as rust into the pipe when the exhaust port of the body communicates with the exhaust hole of the valve body or when it is not exhausted It tries to prevent biting into the seat and scratching of the ball seat.

  Since automatic door opening and closing devices for railway vehicles are operated with high-pressure air due to door opening and closing operations, etc., fluid pressure fluctuations in piping often occur due to door opening and closing, and leakage from the above valves does not occur. Therefore, it is necessary to ensure the sealing performance by the ball seat on the primary side when the valve is closed and when the valve is open, and to prevent leakage.

  On the other hand, for example, a ball valve disclosed in Patent Document 3 is disclosed as a rotary valve for flowing a liquid. This ball valve is used for, for example, a food-related pipeline, and includes a case having a hemispherical hollow space, a plug, and a seal member. The plug is formed integrally with a hemispherical valve body and a valve shaft, is fitted in the hollow / hemispheric space of the case, and is rotatable about the valve shaft. A concave portion is formed in the hemispherical valve body of the plug, and a seal member is fitted into the concave portion. In FIG. 6 of the same document 3, a hemispherical valve body is provided with a T-shaped flow path and a seal member for closing the flow path, and the plug is rotated to block the communication hole with the seal member. A valve provided so that the three flow paths can be switched is disclosed.

  In railway vehicles using these quick exhaust valves, a plurality of automatic door opening / closing devices are usually provided for each vehicle, and a plurality of exhaust valves are provided for each automatic door opening / closing device.

Japanese Utility Model Publication No. 6-23802 JP-A-11-304020 JP-A-9-79391

  However, since the valves of Patent Documents 1 to 3 press the seal surface pressure by the seal member with a certain size such as a spring load, these are used for the pipeline for the automatic door opening and closing device of the railway vehicle. In this case, it is difficult to prevent leakage to the secondary side due to a limit in sealing by the seal member due to wear or the like in the pressure sealing on the primary side.

  Further, as in Patent Document 1 and Patent Document 2, when the exhaust hole is processed into a body and the exhaust port hole of the valve body is formed at a position where it does not interfere with the communication hole, the exhaust port hole may be formed large. difficult. For this reason, these valves require a long exhaust time, and may take a long time of, for example, 5 seconds or longer. Furthermore, if the diameter of the exhaust port hole is reduced in order to make the valve compact, it is more difficult to shorten the exhaust time. For these reasons, with the structures of Patent Document 1 and Patent Document 2, it is difficult to shorten the exhaust time while making the whole compact for a railway vehicle.

  As a countermeasure, it is conceivable to use a full-bore ball valve with a large port hole and a large flow rate as a quick exhaust valve. In this case, due to the structure of the ball valve, A two-piece structure is essential. As a result, it is necessary to take sealing measures to prevent leakage of high-pressure air at the joints of the body and to prevent loosening of the screw fittings of the body of the body during piping construction. This leads to an increase in points.

  The ball valve of Patent Document 3 has a spherical arc-shaped surface where the surface of the seal member is continuous with the outer surface of the hemispherical valve body, and has a structure that cannot be tightened without having a cavity in the case. There is also a possibility that the seal surface pressure of the member may be insufficient, and in particular, the sealing performance on the primary side which is the inlet side may be impaired and fluid leakage may occur. In this ball valve, when the hemispherical valve body rotates, the entire surface of the spherical arc-shaped surface of the sealing member slides while always in contact with the inner peripheral surface of the case, so that the sliding resistance increases and the operating torque increases. The seal member is also heavily worn, making it difficult to ensure sealing performance. In addition, when there is a hemispherical valve body at a position where the sealing member seals the outflow inlet, the portion where the sealing member is pressed against the hemispherical sealing surface of the case and the portion exposed to the outflow inlet are elastic. It is conceivable that a step due to deformation occurs and the seal member is cut and damaged when the valve body is rotated. For these reasons, it is difficult for this rotary valve to reliably prevent leakage of pressurized air, and it is not suitable for use in a rapid exhaust valve for a railway vehicle.

  The present invention has been developed in order to solve the above-described problems, and the object of the present invention is to provide a primary side pressure by the primary pressure even when a pressure fluctuation occurs during sealing of the primary side pressure when the valve is closed. Increases the seal surface pressure to prevent fluid leakage reliably.When the valve is open, the primary pressure is applied to the entire seal member to increase the seal surface pressure to prevent fluid leakage. A rotary valve that can switch the flow path while ensuring operability and improving operability, and shortens exhaust time through a large-diameter exhaust hole while reducing the overall size and the number of parts. It is an object of the present invention to provide a rotary valve suitable for a rapid exhaust valve for an automatic door opening / closing device of a railway vehicle.

  In order to achieve the above-mentioned object, the invention according to claim 1 is characterized in that an outflow inlet and an exhaust port are formed in a valve body storage portion having a spherical portion formed in a part of an inner periphery in a body, A valve body having a spherical surface portion is rotatably mounted, and the valve body has a plurality of through-holes communicating with the outflow inlet or the exhaust port, and a mounting groove facing the outflow inlet in a direction intersecting the through-holes. A disk-shaped sealing member that closes the outflow inlet or the exhaust port is formed in the mounting groove, and any one outflow inlet or the exhaust port is hermetically closed by the seal member, The rotary valve improves the seal surface pressure of the seal member by utilizing the back pressure applied to the back surface side of the seal member when the exhaust port is hermetically closed.

  The invention according to claim 2 is the rotary valve in which the back side pressure receiving area of the back side of the seal member is larger than the body side pressure receiving area of the surface of the seal member.

  In the invention according to claim 3, the seal member is provided with a through hole penetrating the surface and the back surface of the seal member, and a side surface of the seal member is provided with a seal ring for sealing between the cavity of the body and penetrating. This is a rotary valve that uses a primary fluid pressure on the back surface as a back pressure through a hole.

  According to a fourth aspect of the present invention, a groove portion that communicates the side surface and the back surface is provided on the side surface of the seal member, and pressure in the body cavity is introduced to the back surface through the groove portion, or the seal member is provided on the valve body. A communication part is provided to connect the back surface and the secondary side flow path, and the pressure of the secondary side flow path is introduced to the back surface through this communication part, or the pressure is applied to the back surface by both the groove part and the communication part. The rotary valve introduced in

  According to the fifth aspect of the present invention, the valve body is inserted from the opening opened from the valve body storage section, and the opening is covered with a lid member via a spring member between the valve body and the sealing member. A rotary valve with increased stop surface pressure.

  The invention according to claim 6 is a rapid exhaust valve for a railway vehicle in which the rotary valve is used as an exhaust valve provided in piping for an automatic door opening / closing device of the railway vehicle.

  According to the first aspect of the present invention, the valve body having the spherical surface portion is provided in the body having the spherical surface portion, and the outflow inlet or the exhaust port is hermetically closed by the disc-shaped sealing member attached to the valve body. Therefore, when the valve body is opened and closed, the flow path can be switched while ensuring high sealing performance and torque performance and exhibiting excellent operability. In addition, the pressure air can be quickly exhausted in a short exhaust time through the large-diameter exhaust hole while reducing the overall size and the number of parts. When sealing with a seal member, the back pressure applied to the back side is used to improve the seal surface pressure, so even if pressure fluctuations occur, the primary seal surface pressure is increased to ensure fluid leakage. Can be prevented. These are particularly suitable for use as a quick exhaust valve for an automatic door opening / closing device of a railway vehicle.

  According to the second aspect of the present invention, the back pressure applied to the back side of the seal member can be made larger than the pressure applied from the primary side according to the pressure fluctuation, and the self-seal function by the back pressure is surely generated in the seal member. Thus, the primary side sealing surface pressure of the seal member can be increased by this surface pressure and the surface pressure generated when the valve is assembled, thereby preventing fluid leakage.

  According to the invention of claim 3, the primary side pressure is applied to the back side of the seal member through the through hole, and the primary side pressure is reduced by preventing the pressure from leaking to the cavity side by the seal ring. The sealing performance of the sealing member due to the back pressure can be enhanced by effectively using the pressure.

  According to the fourth aspect of the present invention, the pressure in the cavity is introduced to the back surface through the groove portion, the pressure of the secondary flow path is introduced to the back surface through the communication portion, or both of these pressures are applied. By introducing it on the back surface, a floating check operation is applied to the seal member, thereby improving the sealing performance when the valve is opened and reliably preventing fluid leakage.

  According to the invention which concerns on Claim 5, the pressing force of the valve body to a body can be set via a spring member by adjusting tightening of a cover member, and the operation torque at the time of valve body operation can be set by adjusting this pressing force. The valve body can be mounted in a state in which the sealing surface pressure of the seal member is increased to prevent fluid leakage while enabling smooth operation. Accordingly, even when the seal member is worn or changes in size due to a temperature change, the sealing surface pressure and low operating torque by the optimum seal member can be restored by tightening the lid member.

  According to the invention which concerns on Claim 6, the pressure air in the automatic door opening / closing apparatus of a railway vehicle can be exhausted rapidly, and an automatic door can be manually operated rapidly also at the time of an emergency or security. Since the body can have a one-piece structure, there is little loosening of parts during piping work, the number of parts is reduced, the whole is downsized, and installation in a narrow space inside or outside the railway vehicle is also possible.

It is a perspective view which shows 1st Embodiment of the rotary valve of this invention. It is a longitudinal cross-sectional view of FIG. It is a partially notched front view which shows 2nd Embodiment of the rotary valve of this invention. It is a perspective view which shows the sealing member of FIG. It is sectional drawing which shows 3rd Embodiment of the rotary valve of this invention.

  Hereinafter, embodiments of a rotary valve and a rapid exhaust valve for a railway vehicle using the rotary valve according to the present invention will be described in detail with reference to the drawings. In FIG. 1, the perspective view of 1st Embodiment of the rotary valve of this invention is shown, and in FIG. 2, the longitudinal cross-sectional view of FIG. 1 is shown. The rotary valve of the present invention (hereinafter referred to as a valve body 1) is used as, for example, an exhaust valve provided in a piping for an automatic door opening / closing device of a railway vehicle. By opening and closing the valve body 1, an automatic door of a railway vehicle is used. Can be automatically opened and closed with pressurized air, or manually opened and closed. The valve body 1 includes a body 2, a valve body 3, a lid member 4, a seal member 5, a spring member 6, and a manual operation handle 7.

  In FIG. 2, the body 2 of the valve body 1 is formed in a one-piece structure with a material such as bronze, brass, stainless steel, and the like, and has an outflow inlet 10, 11 and an exhaust port 12 intersecting with the outflow inlet 10, 11. In this example, exhaust ports 12 are formed at intervals of 90 ° between the two outflow ports 10 and 11 connected in series. The valve body 1 can be piped in such a state that the direction of the two outlets 10 and 11 can be reversed and the direction of the exhaust port 12 can be reversed by 180 ° due to the overall shape of the body 2.

  A valve body storage portion 16 having a spherical surface portion 15 is formed on a part of the inner periphery of the body 2, and a shaft mounting portion 17 is provided on the upper side of the valve body storage portion 16. An insertion hole 18 is provided therein. As shown in FIG. 1, four mounting holes 20 are formed at an upper portion of the shaft mounting portion 17 as shown in FIG. 1. A locking pin 21 is press-fitted or screwed into one of the mounting holes 20, for example. It is installed by. In FIG. 2, an opening 22 is formed on the lower side of the valve body storage portion 16, and a female screw 23 is provided in the opening 22. The spherical portion 15 is provided in a substantially hemispherical concave shape by a substantially hemispherical counterbore process.

  The exhaust port 12 is provided with substantially the same diameter as the outflow inlets 10 and 11, and is formed in communication with the valve body storage portion 16 together with the outflow ports 10 and 11. On the other hand, a screwing portion 25 which is a female screw portion is formed on the inner peripheral side of the outflow inlets 10 and 11, and external piping such as a pipe (not shown) can be connected to the outflow inlets 10 and 11 through the screwing portion 25. Is provided.

  The valve body 3 is provided in a shape that can be inserted into the spherical surface portion 15, and is inserted rotatably into the valve body storage portion 16 through the opening 22 of the body 2 and is rotatably mounted while being positioned in the vertical direction. The valve body 3 is provided with a spherical surface portion 28 in part, and in this embodiment, the spherical surface portion 28 is provided in a hemispherical shape.

  A plurality of through-holes 30, 31, 32 that can communicate with the outflow inlets 10, 11 or the exhaust port 12 of the body 2 are formed in the valve body 3 in three directions, and the transverse direction intersects with these through-holes 30-32. A mounting groove 33 that can be opposed to the outflow inlets 10 and 11 or the exhaust port 12 is formed. The mounting groove 33 is detachably mounted with the seal member 5 capable of closing the outflow inlets 10 and 11 or the exhaust port 12. In the present embodiment, the mounting groove 33 is a circular concave groove, and the seal member 5 is formed in a disk shape that can be fitted into the circular concave groove 33. Although not shown, the through hole, the outflow inlet, and the exhaust port may be provided in four or more directions. In this case, the interval between the through hole, the outflow inlet, and the exhaust port is 90 ° or less. Become.

  The through holes 30 to 32 are formed in a full bore shape having substantially the same diameter as the outflow inlets 10 and 11 or the exhaust port 12, and pressure loss when communicating with the outflow ports 10 and 11 or the exhaust port 12 is suppressed. Yes. In addition to the full bore type, the through-holes 30 to 32 have a narrowed diameter called a standard bore type (reduced diameter) with a passage diameter smaller than that of the full bore type, or a reduced bore type with two stages. Also good. The full bore type has an advantage that the flow rate characteristic is improved because the pressure loss can be further suppressed as compared with other types.

  In FIG. 2, an upper stem 35 to which the handle 7 can be attached is provided integrally or separately on the upper part of the valve body 3, and a fitting projection 36 is formed at the handle 7 mounting position of the upper stem 35. . A lower stem 37 is integrally provided on the side opposite to the upper stem 35. The upper stem 35 and the lower stem 37 are provided with substantially the same shaft diameter, and an equal pressure is applied to the valve body 3 by the air pressure in the pipe. It is like that.

  The valve body 3 is a portion corresponding to the spherical surface portion 28 as long as the through-holes 30 to 32 and the seal member 5 can be switched so that the flow path can be switched by rotating so as to face the outflow ports 10 and 11 or the exhaust port 12. May have a shape other than a hemispherical surface. A gap G is provided between the spherical surface portion 28 and the spherical surface portion 15, and the amount of the gap G is adjusted by the rotation of the lid member 4, whereby the tightening amount when the valve body 3 is tightened can be regulated.

  The seal member 5 attached to the valve body 3 is formed of an elastic material such as a polymer material such as PTFE (polytetrafluoroethylene) or PTFE containing carbon fiber. When the valve body 3 is rotated, the seal member 5 is rotated integrally with the valve body 3 so that any one of the outflow inlets 10 and 11 or the exhaust port 12 can be hermetically closed. , 11 or the exhaust port 12, the fluid is allowed to flow through the outflow ports 10, 11 and the exhaust port 12, or the outflow ports 10, 12 communicate with each other through the through ports 30, 31, 32. it can. An annular seal surface 38 is provided on the surface side of the seal member 5, and the annular seal surface 38 abuts and seals on the peripheral portions of the outflow inlets 10 and 11 or the exhaust port 12.

  In the valve body 1, when the inlet / outlet ports 10, 11 or the exhaust port 12 are closed by the seal member 5, the pressure (back pressure) applied to the back surface 5 b side of the seal member 5 is used to seal the seal member 5. The contact pressure is improved.

  In this case, the relationship between the back side pressure receiving area S1 of the back side 5b of the seal member 5 and the body side pressure receiving area S2 of the surface of the seal member is such that the body side pressure receiving area S2 is formed inside the annular seal surface 38 of the seal member 5. Therefore, the back side pressure receiving area S1 is larger than the body side pressure receiving area S2.

  The seal member 5 is provided with at least one through hole 39 penetrating the front surface 5a and the back surface 5b of the seal member 5. In this embodiment, the through hole 39 is formed in the center of the seal member 5. . The primary side of the valve body 1 and the back surface 5 b side of the seal member 5 are communicated with each other through the through hole 39.

  An annular mounting groove 5c is formed on the side surface of the seal member 5, and a seal ring 34 made of an O-ring is attached to the mounting groove 5c. The seal ring 34 seals between the back surface 5 b side of the seal member 5 and the cavity C formed in the body 2.

  When the primary fluid pressure is applied from the surface 5a side of the seal member 5, the primary fluid pressure is introduced into the back surface 5b of the seal member 5 through the through hole 39, and the applied back pressure is used to seal the seal member. 5 can exhibit the sealing surface pressure in the primary side direction. At this time, the primary-side fluid pressure that has entered the back surface 5 b side is prevented from entering the cavity C side by the seal ring 34.

  The lid member 4 is provided in a shape capable of covering the opening 22, and a columnar portion 40 is formed on the outer periphery of the lid member 4. The cylindrical portion 40 is provided with an outer diameter that can be fitted into the opening 22 of the body 2, and an O-ring 42 is attached to the outer periphery thereof. A male screw 43 that can be screwed into the female screw 23 of the body 2 is provided on the outer periphery of the lower portion of the cylindrical portion 40, and the opening 22 is covered with the lid member 4 by screwing the male screw 43 and the female screw 23.

Between the cover member 4 and the lower stem 37 of the valve body 3, four spring members 6 made of disc springs are provided via upper and lower plain washers 48, 48, and these spring members 6 are stacked. The sealing member 5 is provided by the lid member 4 so as to be tightened with an arbitrary tightening force. The plain washer 48 and the spring member 6 may be handled as a set. An insertion hole 45 is provided at the center position of the lid member 4 on the valve body 3 side, and the space between the insertion hole 45 and the cylindrical part 40 is thinned to reduce the weight of the entire lid member 4. ing. A thrust bearing 51 is provided between the upper surface of the lid member 4 and the valve body 3, and the inner and outer peripheral cylindrical surfaces of the thrust bearing 51 are radial bearings of a disc fitting outer peripheral surface 3a and a body cylindrical inner peripheral surface 2a. The valve body 3 is provided so as to be able to rotate smoothly.
The height of the lid member 4 in FIG. 2 is kept low, whereby the overall height of the valve body 1 is also suppressed.

  In the valve body 3 described above, the upper stem 35 is mounted in the insertion hole 18 of the body 2 via the seal material 47 made of an O-ring, and the lower stem 37 is installed in the insertion hole portion 45 of the lid member 4. The trunnion structure is pivotally supported between the body 2 and the lid member 4. A gap dimension 46 is provided between the upper stem 35 and the body 2.

  In this case, the spring member 6 is mounted between the insertion hole 45 of the lid member 4 and the lower stem 37 of the valve body 3, and the opening 22 is covered with the lid member 4 via the spring member 6. When the valve body 3 is pressed against the spherical surface portion 15 by the lid member 4, the sealing surface pressure of the seal member 5 is increased.

  When the lid member 4 is tightened, when the lid member 4 is strongly tightened against the body 2, the amount of compression of the spring member 6 increases, and the valve body 3 is pushed in the insertion direction by the spring force, and the seal member 5 As a result, the adhesion between the spherical portion 15 and the spherical portion 15 is increased, and sealing performance by primary back pressure (biflow) can be secured. At this time, by absorbing the dimensional error of the body 2 and the valve body 3 by the spring member 6, the valve body 3 can be mounted at a predetermined position of the valve body storage portion 16. In addition, by increasing the tightening of the lid member 4, the compression amount of the seal member 5 is increased by the screw feed amount while preventing the compression amount of the spring member 6 from exceeding the maximum set value by the thrust bearing 51. Therefore, consumption due to wear of the seal member 5 or the like can be offset.

  The handle 7 shown in FIG. 1 is provided with a substantially cross-shaped fitting hole that can be fitted to a fitting protrusion (not shown), and the upper portion of the upper stem 35 is arbitrarily oriented at an interval of 90 ° through the fitting hole. It is provided so that it can be mounted. In this case, as long as the handle 7 can be attached to the upper stem 35 at 90 ° intervals, the fitting hole and the fitting protrusion may have a shape other than a substantially cross shape. The handle 7 is formed with a notch-shaped stopper portion 50, and this stopper portion 50 abuts and locks on the locking pin 21 attached to any one of the four mounting holes 20, thereby the handle 7. While the direction and the operation direction are set, the handle 7 is rotated 90 degrees in an arbitrary operation direction to open and close the valve body 3, thereby switching the flow path. In FIG. 2, the handle 7 is attached to the upper stem 35 with a fixing nut 56 via a washer member 55.

In the present embodiment, the through hole 39 is provided at one place in the center of the seal member 5, but the number, shape, and drilling position of the through hole 39 can be arbitrarily set.
Further, although the spring member 6 is a disc spring, various springs can be used.

  Further, the valve body 1 is provided in a so-called bottom entry structure in which the valve body 3 is inserted from below the body 2, but is provided in a so-called top entry structure in which the valve body 3 is inserted from above the body 2. May be. In any case, three or more outlets are provided in the body 2 of the valve body 1, one exhaust port is provided between these outlets, and at least one of the outlets communicates with the exhaust port. You may make it make it.

  When assembling the above-described valve body 1, the sealing member 5 and the sealing materials 47 and 47 are attached to the valve body 3, and the valve body 3 is inserted into the valve body housing portion 16 of the spherical surface portion 15 from the opening portion 22 below the body 2. Then, the upper stem 35 is inserted into the insertion hole 18. At this time, the seal member 5 comes into contact with the body 2 in a state where no pressing force is applied.

  Subsequently, the spring member 6 is mounted in the insertion hole 45 of the lid member 4, and the male screw 45 and the female screw 23 are screwed together while the lower stem 37 is inserted into the insertion hole 45, so that the lid member 4 is mounted on the body. 2 Integrate from the bottom, and press the valve body 3 from below through the thrust bearing 51 by the lid member 4. At that time, the lid member 4 is tightened and disassembled with a general-purpose tool such as a socket wrench (not shown), the tightening force is adjusted, and the pressing force of the seal member 5 by the spring member 6 is adjusted while the lid member 4 is attached to the body 2. Installing. At this time, since the valve body 1 has a bottom entry structure, the position of the valve body 3 with respect to the body 2 is adjusted by the lid member 4, and the dimensional error of the body 2 and the valve body 3 is absorbed, while the valve body storage portion 16 The valve body 3 can be easily mounted at a predetermined position.

  Further, the locking pin 21 is attached to a desired location of the mounting hole 20, the fitting hole of the handle 7 is fitted to the fitting protrusion 36 of the upper stem 35, and the fixing nut 56 is inserted through the washer member 55. The handle 7 is attached to the upper stem 35 while the direction and the opening / closing operation direction are arbitrarily set.

  In this case, the direction of the two outlets 10 and 11 connected in series can be changed so that the direction of the exhaust port 12 can be reversed by 180 °, and the handle 7 is connected via the fitting hole and the fitting projection 36 of the handle 7. It is possible to change the direction in the open state to a direction parallel to or intersecting with the outflow inlets 10, 11, and when the handle 7 is opened or closed by attaching a locking pin 21 to any mounting hole 20 of the body 2. It is possible to change the operation direction. By combining these three elements, various types of valves can be configured.

  That is, there are two ways of the right and left sides of the outlets 10 and 11 in which the pipes of the exhaust port 12 for exhausting in the closed position are in series, and the open position of the handle 7 is a so-called parallel open type or right angle open type 2 Since there are two operation directions of the handle 7 so-called right hand or left hand, it is possible to provide 2 × 2 × 2 = 8 quick exhaust valves by combining them. As a result, a desired configuration can be obtained according to the mounting position of the valve body 1 to the air piping of the railway vehicle (not shown) and the direction of the exhaust port 12. For example, by changing the direction when the valve body 1 is mounted, The operability can be improved, or the discharge of pressurized air to the person who operates by changing the direction of the exhaust port 12 can be avoided.

  After the valve body 1 is assembled, it can be rotated by the handle 7 while providing a gap G between the valve body storage portion 16 and the spherical surface portion 28, and an accident caused by an erroneous operation can be prevented via the handle 7. The valve body 3 can be rotated every 90 °. Thereby, any one or all of the outflow ports 10, 11, and 12 are communicated with each other through the through-holes 30 to 32 and the seal member 5, and the flow path can be switched. At the closed position of the valve body 3, any of the outflow ports 10, 11, and 12 can be hermetically sealed by the seal member 5.

Next, the operation of the rotary valve of the present invention and the rapid exhaust valve for a railway vehicle using the rotary valve according to the above embodiment will be described.
In the valve body 1 of the present invention, a valve body 3 having a spherical surface portion 28 to which a seal member 5 is attached is rotatably mounted in a body 2 having a spherical portion 15, and the outflow inlets 10, 11 or 11 The exhaust port 12 is hermetically closed, and a gap G is provided between the spherical surface portion 28 and the spherical portion 15, so that only the annular sealing surface 38 of the seal member 5 slides on the spherical portion 15 and slides. Resistance decreases. Thereby, at the time of operation, the operation torque is reduced and the operability is improved, and the operation can be performed while suppressing the wear of the seal member 5 and suppressing the deterioration of the seal performance.

  When the outflow inlets 10 and 11 or the exhaust port 12 are hermetically closed by the seal member 5, the primary fluid pressure is introduced to the back surface through the through hole 39 while sealing the space between the cavity C with the seal ring 34. The seal surface pressure of the seal member 5 can be improved by using the back pressure applied to 5b. As a result, the sealing surface pressure by the annular sealing surface 38 and the sealing surface pressure by the pressing force of the spring member 6 are synergistically exhibited as the sealing force of the annular sealing surface 38, and the pressure fluctuation on the primary side of the body 2 Even in the case of the occurrence of this, the seal surface pressure having a magnitude corresponding to this change in pressure can be exhibited, and fluid leakage to the secondary side can be reliably prevented.

  Moreover, by making the back surface side pressure receiving area S1 of the back surface 5b of the seal member 5 larger than the body side pressure receiving area S2 of the seal member surface 5a, (back side pressure receiving area S1-body side pressure receiving area S2) × fluid The surface pressure of the pressure acts on the sealing member back surface 5b as a fluid sealing surface pressure together with the surface pressure due to the elastic force of the disc spring 6, and the fluid member pressure surely presses the sealing member 5 to the primary side to perform the self-sealing function. Demonstrate.

  The seal member 5 is elastically or plastically deformed when the seal is closed to exhibit a high sealing performance, and reliably prevent foreign matters and fluid from leaking. For this reason, for example, even if high temperature air is supplied and the sealing member 5 tries to expand, the pressure sealing structure by the spring member 6 increases, and the sealing force increases, and leakage due to biting, creep, stress relaxation, etc. Can be prevented. On the other hand, when the seal member 5 is about to contract at a low temperature, the sealing performance can be secured by obtaining the necessary sealing pressing force of the fluid by the spring member 6. From these things, it becomes possible to exhibit high sealing performance against pressure air while maintaining compactness.

  Since the fluid pressure of the self-sealing function is applied to the seal member 5 when the seal is closed, and only the pressure of the disc spring is applied when the seal is fully opened, the wear is further minimized by using a lubricant such as grease. The deformation and movement of the seal member 5 due to the fluid pressure can also be prevented. Thereby, durability of the sealing member 5 is ensured and high sealing performance can be maintained. Therefore, it is excellent in economic efficiency, and the cost can be reduced even when a large number of pipes are installed for one pipe in a railway vehicle.

  The seal member 5 is provided so that it can be tightened with an arbitrary tightening force by the lid member 4 by screwing the male screw 43 and the female screw 23 via the spring member 6. The cover member 4 is further tightened in the piping state of the valve body 1, and the amount of tightening at this time is adjusted to recover the seal surface pressure by the annular seal surface 38 and prevent seal leakage. Furthermore, since the valve body 3 can be easily attached / detached by removing the lid member 4, it can be replaced when the seal member 5 is consumed heavily.

On the other hand, at the communication position of the outflow inlets 10 and 11, a large amount of pressurized air is secured, and particularly when the exhaust port 12 and the outflow ports 10 and 11 are communicated, the full bore diameter effectively functions. The residual air on the secondary side can be exhausted in a short time.
Due to these functionalities, the valve body 1 is particularly suitable for use as a rapid exhaust valve for railway vehicles. When the valve body 1 is provided in an automatic door opening / closing device of a railway vehicle, an emergency situation may occur. When repair and maintenance are required, the automatic door can be exhausted to a state where it can be manually operated in a short time.

  Furthermore, by providing a trunnion structure in which the upper stem 35 is mounted in the insertion hole 18 of the body 2 and the lower stem 37 is mounted in the insertion hole 45 of the lid member 4, the valve body 3 is secondary by pressure. Since the seal member 5 is attached to the valve body 3, the flow path is switched by one seal member 5 without the need for a plurality of seal members as in a general ball valve. it can. This eliminates the need to form the spherical surface portion 15 of the body 2, the spherical surface portion 28 of the valve body 3, and the seal member 5 with high processing accuracy, and simplifies the whole and reduces the size and weight while reducing the number of parts. You can also

  Unlike the floating type ball valve, there is no possibility of abnormal pressure increase because a sealed space is not formed. If the processing accuracy of the spherical surface portion 15 of the valve body storage portion 16, more specifically the peripheral portion that becomes the valve seat surface of the outflow inlets 10, 11, is secured, the valve body 3 is inserted into the body 2 and covered with the lid member 4. By simply covering, it can be easily assembled into a predetermined state while ensuring sealing performance. If the mounting position of the seal member 5 is changed, a variety of flow paths can be switched.

  Since the valve body 3 has a structure in which the valve body 3 is pivotally supported between the body 2 and the lid member 4, the torque performance is improved. When the handle 7 is operated, the load is lightened and the opening / closing operation of the valve body 3 is smooth. In addition, since the upper stem 35 and the lower stem 37 are provided with substantially the same diameter to apply the equal pressure, the pressure receiving pressure of the seal member 5 is made uniform, the operation torque is kept low, and the valve body has stable operability. 3 can be operated. Accordingly, even when the valve body 1 is installed in a narrow space in the railway vehicle, it can be easily operated with one hand without applying a large force.

When the valve body 1 is assembled, the valve body 3 on which the seal member 5 is mounted in advance is inserted from the opening 22 of the body 2, and the cover member 4 can be screwed on while mounting the spring member 6. When exchanging the seal member 5 or other consumable parts, it is possible to minimize the number of work steps without removing the body 2 from the piping. Since the valve element 3 is pressed into the body 2 by the spring member 6 by the bottom entry structure, the valve element 3 is safe without jumping out.
For these reasons, when the valve body 1 is used as a rapid exhaust valve for a railway vehicle, connection to the piping of the railway vehicle and maintenance are facilitated, and leakage and the like are performed safely. it can.

  Next, a second embodiment of the rotary valve in the present invention will be described. In the following embodiments, the same parts as those in the above embodiments are denoted by the same reference numerals, and the description thereof is omitted. 3 is a partially cutaway front view of a second embodiment of the rotary valve of the present invention, and FIG. 4 shows the seal member in FIG.

  In the valve main body 60 of this embodiment, a plurality of groove portions 62 that connect the side surface and the back surface 61b are provided on the side surface of the seal member 61 having the front surface 61a and the back surface 61b. Alternatively, when the exhaust port 12 is hermetically closed, the pressure in the cavity C of the body 2 can be introduced into the back surface 61b through the groove 62, and this is used as a back pressure to improve the seal surface pressure. . In this case, the back surface 61b of the seal member 61 is applied with a surface pressure of the back surface side pressure receiving area S3 × fluid pressure together with the surface pressure due to the elastic force of the disc spring 6, and the seal member 61 is sealed by performing a floating check operation. Performance can be improved. Further, the primary fluid seal is capable of an optimum sealing surface pressure and friction amount offset by the sheet compression surface pressure by the lid member 4 and the pressurizing load by the disc spring 6.

  The groove portion 62 is formed up to a position where it does not reach the annular seal surface 38, and fluid pressure does not escape from the groove portion 62 to the primary side and the sealing performance of the annular seal surface 38 does not deteriorate. The groove portions 62 are preferably provided at a plurality of locations on the seal member 61 at equal intervals. In this case, the fluid pressure flows evenly from the side surface of the seal member 61 and the seal member 61 is less likely to be inclined, The sealing surface 38 can be uniformly pressed and sealed to the peripheral portion of the outflow inlets 10 and 11 or the exhaust port 12.

In FIG. 5, 3rd Embodiment of the rotary valve of this invention is shown.
In the valve main body 70 of this embodiment, a communication portion 71 that connects the mounting groove 33 of the valve body 3 and the through holes 30 to 32 is formed, and a surface 72a that is mounted to the mounting groove 33 via the communication portion 71, The back surface 72b of the sealing member 72 having the back surface 72b is communicated with the secondary side flow path (outlet inlet 11 side). In this case, the pressure in the secondary channel is introduced to the back surface 72b side of the seal member 72 via the communication portion 71, and the seal surface pressure can be improved using this back pressure.

  As in the second embodiment, the pressure in the cavity C is introduced into the back surface 61b of the seal member 61 via the groove 62 on the side surface of the seal member 61, or the valve body 3 is applied to the valve body 3 as in the third embodiment. The seal surface pressure can be improved by introducing the pressure of the secondary flow path to the back surface 72b of the seal member 72 through the provided communication portion 71, and further, the pressure is introduced into the back surface by combining both of these to provide a sealing property. Can also be increased.

In the above-described embodiment, the example in which the rotary valve of the present invention is used as a rapid exhaust valve for a railway vehicle has been described. However, the rotary valve of the present invention is limited to an application as a rapid exhaust valve for a railway vehicle. In various technical fields, it can be used as a two-way, three-way, four-way or more multi-way rotary valve.
For example, the rotary valve of the present invention is a flow-regulating rotary valve used for switching a flow path in a heat exchanger (cold / hot water) control piping system of a heat exchanger, for adjusting a flow rate or opening / closing in a bypass piping such as steam. Rotary valves used as high-pressure valves, multi-way valves used for branching in high-pressure water / oil / gas / air piping systems, etc., easy to disassemble / assemble, easy to sterilize / flush, etc. Various multi-way valves for sanitary use, anti-freezing plugs in water supply pipes, various manual or automatic multi-way valves used for opening / closing, draining, testing, switching channels, etc. in fire prevention sprinkler equipment Etc., and can be used for various purposes other than these examples.

DESCRIPTION OF SYMBOLS 1 Valve body 2 Body 3 Valve body 4 Lid member 5 Seal member 5a Surface 5b Back surface 6 Spring member 10,11 Outflow inlet 12 Exhaust port 15 Spherical surface part 16 Valve body accommodating part 22 Opening part 28 Spherical surface part 30, 31, 32 Through Port 33 Mounting groove 34 Seal ring 39 Through hole 62 Groove 71 Communication portion C Cavity S1 Back side pressure receiving area S2 Body side pressure receiving area

Claims (6)

  An outflow inlet and an exhaust port are formed in a valve body housing portion having a spherical portion formed on a part of an inner periphery in the body, and a valve body having a spherical surface portion is rotatably mounted on the valve body housing portion, The valve body is formed with a plurality of through-holes communicating with the outflow inlet or the exhaust port, and a mounting groove facing the outflow inlet in a direction intersecting with the through-holes. A disc-shaped sealing member that closes the exhaust port is mounted, and any one of the outflow inlet or the exhaust port is hermetically closed with the seal member, and when the outflow inlet or the exhaust port is sealed by the seal member, A rotary valve characterized in that a seal surface pressure of the seal member is improved by using a back pressure applied to the back side of the seal member.   The rotary valve according to claim 1, wherein a pressure receiving area on the back side of the back surface of the sealing member is larger than a pressure receiving area on the body side of the surface of the sealing member.   The seal member is provided with a through hole penetrating the front and back surfaces of the seal member, and a seal ring for sealing between the cavity of the body is attached to the side surface of the seal member, and the through hole is inserted through the through hole. The rotary valve according to claim 1 or 2, wherein a primary fluid pressure is introduced into the back surface to obtain a back pressure.   A groove portion that communicates the side surface and the back surface is provided on the side surface of the seal member, and pressure in the cavity of the body is introduced to the back surface through the groove portion, or the back surface of the seal member is connected to the valve body. A communication part that communicates with the secondary flow path is provided, and the pressure of the secondary flow path is introduced to the back surface through this communication part, or the pressure is applied by both the groove and the communication part. The rotary valve according to claim 1 or 2, introduced into the back surface.   The valve body is inserted from an opening portion opened from the valve body housing portion, and the opening portion is covered with a lid member via a spring member between the valve body and the sealing surface pressure of the seal member. The rotary valve according to claim 1, wherein the rotary valve is enhanced.   A rapid exhaust valve for a railway vehicle, wherein the rotary valve according to any one of claims 1 to 5 is used as an exhaust valve provided in a piping for an automatic door opening / closing device of the railway vehicle.

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