Valve device

Abstract

To further improve the cooling performance of a valve body in a valve device.SOLUTION: A valve device is equipped with a valve box 2 provided in a fluid supply path 10, a valve body 20 that elevates / lowers in the valve box 2 to open / close the fluid supply path 10, a refrigerant passage 32 that is provided in the valve body 20 and in which a refrigerant supplied from the outside of the valve box 2 circulates, a hood 5 that stores the valve body 20 in an opening-valve state, a valve seat 45 that is provided in the valve box 2 and on which a peripheral edge portion of the valve body 20 in a closing-valve state abuts, a valve box inner annular passage 43 that is provided in a circumferential direction along the valve seat 45, and a cooling gas supply portion 40 that supplies cooling gas supplied from the outside of the valve box 2 into the valve box 2 through an ejection passage 44 drawn out from the valve box inner annular passage 43. The valve seat 45 is shaped in an arc on a vertical cross-section passing through an axis of the fluid supply path 10.SELECTED DRAWING: Figure 1

Description

Technical Field

[0001] This invention relates to a valve device provided in a high-temperature fluid supply passage.

Background Art

[0002] As a valve device provided in a high-temperature fluid supply passage, for example, there is one described in Patent Document 1. This valve device is a partition valve having a cooling structure, and a valve body for opening and closing a flow path is attached to be vertically movable inside a housing composed of a valve box and a bonnet (described as a cap portion in Patent Document 1) provided on the upper part thereof. The bonnet serves as a housing space for the valve body in the valve opening position.

[0003] The valve body is formed by connecting two disc-shaped valve plates made of steel plates with a pair of spiral plates that form a cooling water flow path from the center to the outer peripheral edge. An annular sheet ring is attached to the outer peripheral edge of the connected valve plates by welding.

[0004] Water supply ports and drain ports for cooling water supplied to the cooling water flow path are provided on the peripheral wall of the sheet ring, and a pair of valve rods having a hollow structure are connected in parallel to the water supply port and the drain port. An inlet and an outlet for cooling water are respectively provided at the upper part of the valve rod. The cooling water is supplied from the inlet, passes through the inside of the valve rod, enters the spiral cooling water flow path inside the sheet ring from the water supply port, passes through the center part of the valve body, passes through the inside of the valve rod from the drain port, and is discharged from the outlet. Thereby, the entire valve body is uniformly cooled.

[0005] Also, the valve device described in Patent Document 2 is also known. This valve device opens and closes a hot air pipeline leading to a blast furnace, includes a vertically movable valve plate inside a housing composed of a valve box and a bonnet, and is provided with an annular air cooling passage adjacent to a sealing valve seat where the valve plate comes into contact with and separates from. The air cooling passage is connected to a cooling air source. Cooling air supplied from the cooling air source is supplied to the internal space of the housing through the air cooling passage and a cooling gap opening to the sealing surface of the sealing valve seat.

[0006] In the closed valve state, the cooling gap of the sealing valve seat is closed by the valve plate. Therefore, the inflow of cooling air into the internal space of the housing is interrupted, and it is said that the sealing valve seat can be cooled (see the first to eighth lines from the bottom left on page 2 of Patent Document 2). Note that in the closed valve state, since the valve body shields the hot fluid, the necessity of cooling the sealing valve seat is considered to be relatively low. On the other hand, in the open valve state, since the valve plate is pulled up by the bonnet provided at the upper part of the valve box, cooling air flows into the internal space of the housing from the cooling gap. Thereby, not only the sealing valve seat but also the internal space of the housing is said to be cooled (see the 15th line from the upper right to the first line from the bottom left on page 2 of Patent Document 2).

Prior Art Documents

Patent Documents

[0007]

Patent Document 1

Patent Document 2

Summary of the Invention

Problems to be Solved by the Invention

[0008] In the valve device of Patent Document 2, in the open valve state, since the valve body (valve plate) is separated from the sealing valve seat, the cooling gap is opened and cooling air flows into the housing. At this time, since the valve body is pulled up inside the bonnet (cover) provided at the upper part of the valve box, the cooling air ejected from the cooling gap is not directly applied to the valve plate.

[0009] However, depending on the type of fluid handled in the hot air pipeline and the specifications of the facility, there is a demand to further enhance the cooling effect on the valve plate. For this reason, in each of the closed valve state and the open valve state, it is required to cool the valve plate more efficiently.

[0010] Therefore, an object of the present invention is to further improve the cooling performance of a valve body in a valve device provided in a high-temperature fluid supply passage.

Means for Solving the Problems

[0011] To solve the above problems, the present invention provides a valve box provided in a fluid supply passage, a valve body that moves forward and backward in the valve box to open and close the fluid supply passage, a refrigerant passage provided in the valve body through which refrigerant supplied from outside the valve box flows, a bonnet that houses the valve body in an open valve state, a valve seat provided on the valve box against which the peripheral edge of the valve body in a closed valve state abuts, an annular passage in the valve box provided along the circumferential direction of the valve seat, and a cooling gas supply unit that supplies cooling gas supplied from outside the valve box into the valve box through an ejection passage drawn from the annular passage in the valve box. The valve seat adopts a valve device that is arcuate in a longitudinal section passing through the axis of the fluid supply passage.

[0012] Further, to solve the above problems, the present invention provides a valve box provided in a fluid supply passage, a valve body that moves forward and backward in the valve box to open and close the fluid supply passage, a refrigerant passage provided in the valve body through which refrigerant supplied from outside the valve box flows, a bonnet that houses the valve body in an open valve state, a valve seat provided on the valve box against which the peripheral edge of the valve body in a closed valve state abuts, an annular passage in the valve box provided along the circumferential direction of the valve seat, and a cooling gas supply unit that supplies cooling gas supplied from outside the valve box into the valve box through an ejection passage drawn from the annular passage in the valve box. The opening of the ejection passage into the valve box adopts a valve device that is tapered such that the cross-section gradually expands or gradually contracts as it goes into the valve box.

[0013] Here, a configuration can be adopted in which the cooling gas supplied from outside the valve box is introduced into the annular passage in the valve box through an annular introduction passage provided in the valve box along the outer periphery of the fluid supply passage.

[0014] Also, in order to solve the above problems, the present invention includes a valve box provided in a fluid supply passage, a valve body that moves forward and backward within the valve box to open and close the fluid supply passage, a refrigerant passage provided within the valve body through which refrigerant supplied from outside the valve box flows, a bonnet that houses the valve body in an open valve state, a valve seat provided in the valve box against which the peripheral edge of the valve body in a closed valve state abuts, an annular passage within the valve box provided along the circumferential direction of the valve seat, and a cooling gas supply unit that supplies cooling gas supplied from outside the valve box into the valve box through an ejection passage drawn from the annular passage within the valve box, and employs a valve device including a guide ring provided opposite to the valve seat and abutting against the valve body in a closed valve state.

[0015] Here, the ejection passage can adopt a configuration that opens to the valve seat.

[0016] Also, the center of the opening edge of the ejection passage into the valve box can adopt a configuration that is located on the fluid supply passage side rather than the center in the thickness direction of the end face on the valve body side of the guide ring.

[0017] In each of these aspects, the inner wall of the fluid supply passage can be made of a refractory, and the ejection passage can be composed of a hole that penetrates the refractory from the annular passage side within the valve box toward the fluid supply passage side.

[0018] Also, the opening of the ejection passage into the valve box can be composed of holes arranged side by side along the circumferential direction of the valve seat.

[0019] Furthermore, the cooling gas supplied from outside the valve box is introduced into the annular passage within the valve box through an annular introduction passage provided along the outer periphery of the fluid supply passage, and a flow rate adjustment valve or a pressure adjustment damper can be provided in a connection passage connecting the annular introduction passage and the annular passage within the valve box.

Advantages of the Invention

[0020] In the valve device provided in the high-temperature fluid supply path, the cooling performance of the valve plate can be further enhanced.

Brief Description of the Drawings

[0021]

Figure 1

Figure 2

Figure 3

Figure 4A

Figure 4B

Figure 4C

Figure 4D

Figure 4E

Figure 5

Figure 6A

Figure 6B

Figure 7

Figure 8

Figure 9

Figure 10

Figure 11

Figure 12

Modes for Carrying Out the Invention

[0022] Embodiments of the present invention will be described with reference to the drawings. In this embodiment, the configuration of the present invention will be described by taking as an example a valve device 1 provided in a pipeline 10 for supplying a heat fluid leading to a blast furnace (hereinafter referred to as the fluid supply path 10).

[0023] Figures 1 to 9 show the first embodiment and its modified examples. As shown in FIG. 1, the valve device 1 is of a partition valve type in which a valve box 2 is provided in the middle of the fluid supply passage 10, and a valve body 20 that can move up and down is provided in the valve box 2. The fluid supply passage 10 is opened and closed by the forward and backward movement of the valve body 20 in the valve box 2. In FIG. 1, the left side in the figure is the upstream side and the right side is the downstream side. A valve box valve seat 45 that contacts and separates from the valve body valve seat portion 34 provided at the peripheral edge of the valve body 20 is provided on the upstream side of the valve body 20 in the valve box 2. The valve body valve seat portion 34 on the upstream side of the valve body 20 and the valve box valve seat 45 on the valve box side (hereinafter simply referred to as the valve seat 45) are each provided in an annular shape and contact each other over the entire circumference in the closed valve state. An annular guide ring 7 is provided on the downstream side of the valve body 20 in the valve box 2. The guide ring 7 is arranged to face the upstream valve box valve seat 45 and also faces the valve body valve seat portion 34 on the downstream side of the valve body 20 in the closed valve state. Hereinafter, the direction parallel to the axis of the linear fluid supply passage 10 is referred to as the axial direction, and the direction orthogonal to the axis is referred to as the radial direction.

[0024] The peripheral edge of the valve body 20 is pressed against the valve seat 45 by receiving the force from the relatively high-pressure downstream side in the closed valve state. For this reason, in the embodiment, a single-sided valve seat with the valve seat 45 provided only on the upstream side is adopted. Depending on the use of the valve device 1, valve seats 45 may be provided on both the upstream side and the downstream side of the valve body 20. In this case, the downstream guide ring 7 can be omitted.

[0025] The inner surface of the fluid supply passage 10 in the valve box 2 is covered with refractory materials 13 and 14 made of a material that can withstand high heat and has heat insulation performance, except for the space where the valve body 20 enters. The refractory material 13 is arranged on the inner surface of the upstream flow path 11 with respect to the valve body 20, and the refractory material 14 is arranged on the inner surface of the downstream flow path 12. A recess 8 into which the valve body 20 enters is provided between the upstream flow path 11 and the downstream flow path 12. The inner surface of the recess 8 is also covered with a similar refractory material 15. The reference numeral 9 shown in FIGS. 1 to 3 is a drain, and the reference numeral 9a shown in FIG. 2 is a drain valve.

[0026] The valve box 2 is provided, at its upper part, with a hollow mounting portion 3 that protrudes outward from the outer surface of the cylindrical body forming the fluid supply passage 10. Further, a lid member 4 is attached to the upper part of the mounting portion 3 via flanges 3a and 4a. The valve box 2 (including the mounting portion 3) and the lid member 4 constitute a housing H. Also, the interior of the mounting portion 3 and the lid member 4 functions as a bonnet 5 that houses the valve body 20 in the open valve state. The inner surfaces of the mounting portion 3 and the lid member 4 are also covered with a refractory 16 similar to that in the fluid supply passage 10. Hereinafter, the valve box 2 and the lid member 4 together are referred to as the housing H.

[0027] A valve rod 6 is attached to the valve body 20. The valve rod 6 extends upward within the bonnet 5 and is drawn out outside the housing H. The valve rod 6 is driven by a driving device to move forward and backward in the axial direction of the valve rod 6, and the valve body 20 moves forward and backward in the same direction together with the valve rod 6. That is, the valve body 20 closes when the valve rod 6 moves (descends) to one side along the axial direction of the valve rod 6, and opens when the valve rod 6 moves (ascends) to the other side along the axial direction of the valve rod 6.

[0028] A refrigerant passage 32 through which refrigerant supplied from outside the housing H flows is provided within the valve body 20. As shown in FIG. 1, the valve body 20 includes two front and back metal (steel) valve plates 24 and 25 that sandwich the refrigerant passage 32 disposed at the central portion in the thickness direction. Also, the outside of the upstream valve plate 24 is covered with a refractory 21, and the outside of the downstream valve plate 24 is covered with a refractory 22. An annular sheet ring is attached to the outer peripheral edge of the valve body 20 to form a valve body valve seat portion 34.

[0029] As shown in Fig. 3, the refrigerant passage 32 is formed by the partition wall 33. In this embodiment, a pair of spiral plates 33a and 33b are adopted as the partition wall 33. A pair of refrigerant passages 31 provided in the two valve rods 6 are respectively connected to the supply port 32a and the discharge port 32b provided on the outer peripheral edge of the valve body 20. The pair of refrigerant passages 31 communicate with a refrigerant supply source (not shown). The refrigerant supplied from the refrigerant supply source enters the refrigerant passage 32 from the supply port 32a through the refrigerant passage 31 inside one of the valve rods 6, passes through the central portion of the valve body 20, and then returns to the refrigerant supply source through the refrigerant passage 31 inside the other valve rod 6 from the discharge port 32b, constituting a refrigerant supply unit 30. The valve body 20 is cooled by this refrigerant supply unit 30. In this embodiment, air is adopted as the refrigerant handled by the refrigerant supply unit 30, but it may also be a refrigerant composed of other gases other than air or a refrigerant composed of a liquid.

[0030] In addition, the valve device 1 includes a cooling gas supply unit 40 that supplies the cooling gas supplied from a gas supply source 54 provided outside the valve box 2 and the bonnet 5, that is, outside the housing H, into the valve box 2 through an ejection passage 44 (hereinafter referred to as an opening 44 in the embodiment), which is a cooling gap provided in the valve seat 45. As shown in Figs. 1 and 2, the cooling gas supply unit 40 is connected to the gas supply source 54 via a communication passage 55 and is introduced into an annular passage (first annular passage) 46 provided along the outer periphery of the fluid supply passage 10 and then into an annular passage (second annular passage) 43 provided in the valve box 2. The opening 44 is drawn out from the annular passage 43 in the valve box. The annular introduction passage 46 is located radially outside the annular passage 43 in the valve box, and the two are connected by a connecting passage 47 extending in the radial direction. In this embodiment, the annular introduction passage 46 is provided integrally with the valve box 2, but it may be provided separately from the valve box 2. In this embodiment, air is adopted as the cooling gas, but it may also be other gases other than air.

[0031] The cooling gas supplied from the gas supply source 54 is introduced from the gas inlet 49 to which the communication passage 55 is connected into the annular introduction passage 46. As shown in the schematic diagram of FIG. 5, since a plurality of gas inlets 49 are provided around the axis of the fluid supply path 10, the supply of gas to the annular introduction passage 46 is smooth. Since the connection portion between the annular introduction passage 46 and the gas inlet 49 is provided with a pressure adjustment damper 48, the pressure inside the annular introduction passage 46 is maintained at a certain level or higher. Further, since the plurality of connection passages 47 connecting the annular introduction passage 46 and the annular passage 43 in the valve box are provided around the axis of the fluid supply path 10 (equally spaced around the axis in the embodiment), the supply of gas from the annular introduction passage 46 to the annular passage 43 in the valve box is also smooth. With these configurations, the supply of the cooling gas to the annular passage 43 in the valve box is stabilized. Note that, as the pressure adjustment damper 48, for example, it includes blades or an opening / closing plate that is opened to the downstream side (the annular introduction passage 46 side) when the pressure on the upstream side (the gas inlet 49 side) becomes a certain level or higher.

[0032] The cooling gas is supplied into the valve box 2 through the opening 44 provided in the valve seat 45, and exhibits a cooling function for each part of the valve body 20 and the valve box 2. Here, if the cooling gas is introduced into a simple circulation type cooling device without the opening 44, the temperature of the cooling gas will immediately rise, and there may occur a problem that the cooling performance cannot be maintained. This is because the temperature of the gaseous refrigerant rises more easily than that of the liquid refrigerant. On the other hand, in this embodiment, since the cooling gas is discharged through the opening 44, the cooling gas is continuously supplied from the gas supply source 54 into the annular passage 43 in the valve box so as to replenish it. Thereby, while using the gas as the refrigerant, the cooling performance for the valve seat 45 can be enhanced. Further, if the direction of the opening 44 is directed toward the axis side of the fluid supply path 10, that is, the center side of the valve body 20, a low temperature region is formed by the refrigerant, and thus it is possible to reduce the amount of heat transfer from the high temperature fluid in the fluid supply path 10 to the valve seat 45.

[0033] Also, both the annular introduction passage 46 and the annular passage 43 in the valve box are located on the upstream side of the valve box 2, and the hot air is blocked by the valve seat 45 in this upstream position in the closed valve state. Therefore, when the downstream side is relatively hotter than the upstream side, the heat influence from the hot downstream side is reduced. In particular, when the valve device 1 is a burner shut-off valve or the like provided in the fluid supply path 10 connecting between a hot blast stove that supplies hot air to a blast furnace and a burner that is its heat source, the downstream side can be hotter than the upstream side in the closed valve state as in this embodiment.

[0034] Also, in this first embodiment, as shown in FIG. 1, since the guide ring 7 and the opening 44 face each other, the cooling performance to the guide ring 7 is enhanced. Here, in the first embodiment, the line connecting the center of the opening edge on the valve box 2 side of the opening 44 and the center in the thickness direction of the end face on the valve body 20 side of the guide ring 7 is parallel to the axial direction. That is, the center line of the hole of the opening 44 and the center line in the thickness direction of the guide ring 7 are in a straight line. By disposing the guide ring 7 instead of the valve seat on the downstream side with respect to the valve body 20, the refrigerant discharged from the opening 44 can keep the valve box valve seat surface temperature (the temperature of the valve seat 45) low and reduce the heat transfer to the bottom of the valve body 20 when the valve body 20 is fully open. Also, it is possible to improve the sealing performance by discharging the refrigerant from the opening 44 when the valve body 20 is fully closed.

[0035] In contrast, for example, as shown in FIG. 7, the center of the opening edge of the opening 44 into the valve box 2 may be positioned on the inner diameter side, i.e., on the fluid supply passage 10 side, rather than the center in the thickness direction of the end face on the valve body 20 side of the guide ring 7 (or the center in the thickness direction of the downstream valve seat 45 when the guide ring 7 is not provided). As a result, the cooling gas supplied from the opening 44 is injected at a position closer to the fluid supply passage 10. The cooling gas injected at a position closer to the fluid supply passage 10 forms a flow in the same direction as the flow direction of the hot fluid in the fluid supply passage 10 and in a generally parallel direction, forming an air layer (air curtain) that separates the space in the fluid supply passage 10 and the space in the bonnet 5. This is presumably because the cooling gas is pulled by the flow of the hot fluid in the fluid supply passage 10, forming an air layer with a lower temperature than the hot fluid between the space in the fluid supply passage 10 and the space in the bonnet 5. By forming such an air layer, the cooling performance (including reduction of the thermal influence from the hot fluid) on the guide ring 7 (or the downstream valve seat 45) is enhanced.

[0036] Here, the center of the opening edge of the opening 44 is the center of the annular opening edge at the location where the opening 44 opens into the bonnet 5. In this embodiment, since the cross-section of the opening 44 is a perfect circle, the center of the perfect circle is the center of the opening edge. In FIG. 7, the center line of the hole of the opening 44 is indicated by the reference symbol c1. Also, the radial space width in the valve box inner annular passage 43 is the same throughout the entire circumference. It is desirable that the center of the opening edge of the opening 44 is on the fluid supply passage 10 side of the center of the radial space width in the valve box inner annular passage 43, i.e., the radial center of the valve box inner annular passage 43. In FIG. 7, the center line in the thickness direction of the end face on the valve body 20 side of the guide ring 7 is indicated by a chain line with the reference symbol c2.

[0037] Note that, for example, as shown in FIG. 6A, the opening 44 may be configured such that a plurality of holes 44a having a circular cross-section or the like are arranged at predetermined intervals along the circumferential direction of the valve seat 45. Alternatively, as shown in FIG. 6B, the opening 44 may be a slit 44b that is continuously provided annularly along the circumferential direction of the valve seat 45. By forming the opening 44 as a plurality of holes 44a, these holes 44a can function as nozzles to enhance the momentum of the injection of the cooling gas. Further, by forming the opening 44 as a circumferential slit 44b, the guide ring 7 (or the downstream valve seat 45 when the guide ring 7 is not provided) can be effectively cooled over the entire circumference. Note that the slit 44b can be continuously provided over the entire circumference, but it may also be intermittently arranged in the circumferential direction.

[0038] A further modification example is shown in FIG. 8. In the example of FIG. 8, the opening 44 is composed of holes that penetrate from the side of the annular passage 43 in the valve box toward the fluid supply passage 10 side. That is, the direction of the center line c1 of the hole of the opening 44 is inclined with respect to the axial direction of the fluid supply passage 10, and the inclination direction is such that as it goes into the valve box 2 (as it moves away from the side of the annular passage 43 in the valve box), it gradually approaches the axis of the fluid supply passage 10. As a result, the injection position of the cooling gas approaches the axis side of the fluid supply passage 10, so that the thermal influence received by the guide ring 7 from the high-temperature fluid in the fluid supply passage 10 can be further reduced. Further, in the example of FIG. 8, since the opening 44 is tapered such that the cross-section gradually expands as it goes into the valve box 2, the diffusion range of the cooling gas can be made wider. In FIG. 8, the range where the cross-section is tapered is the entire length in the longitudinal direction of the opening 44, but the above effect can be expected by making at least the opening portion into the valve box 2 tapered.

[0039] In the above-described embodiment, the opening 44 is formed in the valve seat 45. However, an embodiment in which the opening 44 is formed in a position other than the valve seat 45 may also be adopted. In the example of FIG. 9, the opening 44 is constituted by a hole that penetrates the refractory 13, which is the inner wall of the fluid supply passage 10, from the side of the annular passage 43 in the valve box toward the side of the fluid supply passage 10. That is, the opening 44 penetrates the wall of the hollow member that constitutes the annular passage 43 in the valve box at a portion closer to the outer diameter of the housing H, and penetrates the refractory 13 at a portion closer to the inner diameter. In this way, when the opening 44 is configured to penetrate the refractory 13, the penetrating direction of the opening 44 may be inclined with respect to the tube axis of the fluid supply passage 10 as shown in FIG. 9, or may be perpendicular to the tube axis of the fluid supply passage 10. By supplying the cooling gas through the opening 44, the upstream surface of the valve element 20 in the closed valve state can be cooled.

[0040] Here, also in FIG. 9, the center of the opening edge of the opening 44 is on the side of the fluid supply passage 10 rather than the center in the thickness direction of the end face on the valve element 20 side of the guide ring 7. Since the opening 44 opens directly into the fluid supply passage 10 instead of on the valve seat 45 side, the center c1 of the opening edge of the opening 44 is further closer to the fluid supply passage 10 side, so that the thermal influence on the guide ring 7 (the downstream valve seat 45 when the guide ring 7 is not provided) can be suppressed.

[0041] Modified examples of the cooling gas supply unit 40 are shown in FIGS. 4A to 4E. FIG. 4A shows a case where the shape of the valve seat 45 is a rounded shape, that is, an arcuate cross section, in a longitudinal section passing through the axis of the fluid supply passage 10. The opening 44 is formed at the tip protruding in an arc shape of the valve seat 45. By making the cross section of the valve seat 45 arc-shaped, the tip protruding in an arc shape of the valve seat 45 contacts the valve element valve seat portion 34 with a limited and narrow area. Thereby, the opening 44 can be closed more airtightly by the valve element 20. Further, by making the cross section of the valve seat 45 arc-shaped, the thermal stress on the valve seat surface of the valve seat 45 can be made closer to uniform, so that stress concentration in the valve seat 45 can be suppressed.

[0042] FIG. 4B is tapered such that the cross-section gradually decreases as it goes toward the space inside the valve box 2, that is, toward the valve seat 45 side. This can enhance the momentum of the injection of the cooling gas, allow the cooling gas to reach a longer distance, that is, a farther part, and improve its cooling efficiency. FIG. 4C is tapered such that the cross-section of the opening 44 gradually increases as it goes toward the space inside the valve box 2, that is, toward the valve seat 45 side. This can improve the cooling efficiency by making the diffusion range of the cooling gas wider. FIG. 4D is shaped such that the cross-section of the internal space of the annular passage 43 in the valve box gradually increases as it goes toward the valve seat 45 side. This can ensure a large volume inside the annular passage 43 in the valve box. FIG. 4E, conversely, is shaped such that the cross-section of the internal space of the annular passage 43 in the valve box gradually decreases as it goes toward the valve seat 45 side. It is also possible to adopt such a cross-sectional shape.

[0043] The variations such as the cross-sectional shape and position of the opening 44 illustrated above can be applied to the opening 44 in all embodiments.

[0044] The second embodiment of the present invention is shown in FIGS. 10 to 12. Since the basic configuration of the valve device 1 is the same as that of the previous embodiment, the following description will focus on the differences.

[0045] The gas supply section 40 for cooling provided in the valve device 1 of the second embodiment is connected to a gas supply source 54 via a communication passage 55 and is provided along the outer periphery of the fluid supply passage 10. The annular introduction passage 41 (in the second embodiment, since the annular introduction passage 41 is provided outside the valve box 2, hereinafter it will be referred to as the annular passage 41 outside the valve box), an annular passage (air-cooling circulation annular pipe) 43 provided circumferentially along the valve seat 45 inside the valve box 2, and a plurality of connecting passages 42 extending radially that connect the annular passage 41 outside the valve box and the annular passage 43 inside the valve box. The valve seat 45 is formed of a hollow annular member, and the fact that its interior is the annular passage 43 inside the valve box, which is a passage for the cooling gas, is the same as in the above-described embodiment. Also, both the annular passage 41 outside the valve box and the annular passage 43 inside the valve box are located on the upstream side of the valve box 2, and the fact that the hot air is blocked by the valve seat 45 in the closed valve state at this upstream position is also the same as in the above-described embodiment.

[0046] A flow rate adjustment valve 42a is provided in the connecting passage 42. By providing the flow rate adjustment valve 42a in the connecting passage 42, the amount and pressure of the cooling gas supplied to the annular passage 43 inside the valve box can be adjusted, and the supply can be stabilized. As a result, the pressure inside the annular passage 43 inside the valve box can be made closer to being uniform. In this way, by making the pressure of the refrigerant closer to being uniform, the discharge rate of the refrigerant approaches uniformly over the entire area of the valve seat 45, so that temperature unevenness of the valve seat 45 can be suppressed.

[0047] Note that the cross-sectional areas of the plurality of connecting passages 42 may all be the same, but the cross-sectional areas of the connecting passages 42 may also be made different from each other according to the locations where the connecting passages 42 are installed. For example, the cross-sectional area of the connecting passage 42 close to a portion where the pressure is likely to drop in the annular passage 43 inside the valve box can be set relatively larger than the cross-sectional areas of the connecting passages 42 at other locations. Thereby, the pressure inside the annular passage 43 inside the valve box can also be made closer to being uniform. Also, as another means, for example, the cross-sectional areas of the plurality of connecting passages 42 can be made variable, and the cross-sectional area of the connecting passage 42 close to a portion where the pressure is low in the annular passage 43 inside the valve box can be adjusted to be relatively larger than the cross-sectional areas of the connecting passages 42 at other locations. A portion where the pressure is likely to drop in the annular passage 43 inside the valve box is, for example, a location far from the gas inlet 49. Each configuration regarding these connecting passages 42 can also be applied to the connecting passage 47 of the first embodiment.

[0048] In the second embodiment, a valve body ring 27 that comes into contact with and separates from the guide ring 7 is provided at the peripheral edge of the valve body 20. The valve body ring 27 is a member that forms an annular shape similar to the guide ring 7. Also, the guide ring 7 and the valve body ring 27 are each made of metal, similar to the valve body valve seat portion 34 and the valve seat 45. When the valve body 20 opens and closes, on the downstream side surface of the valve body 20 where the valve seat is not provided, the guide ring 7 and the valve body ring 27 rub against each other, so that the refractory materials 14 and 22 described later do not interfere with the operation of the valve body 20. Instead of this valve body ring 27, a valve body valve seat portion 34 similar to that of the first embodiment may be provided.

[0049] A heat pipe 23 having a function of transferring the heat absorbed in the high-temperature portion to a low-temperature portion having a lower temperature than the high-temperature portion is provided inside the valve body 20. The heat pipe 23 is disposed outside the downstream valve plate 25 and inside the refractory 22.

[0050] Generally, a heat pipe seals a working fluid in a closed container and has a capillary structure within the container. When a part of the container is heated to generate a high-temperature part, the working fluid absorbs heat and evaporates at the high-temperature part. The vapor moves toward the low-temperature part within the same container, where the vapor condenses and heat is released. The condensed working fluid returns to the high-temperature part by capillary action. Through this repetition, heat transfer from the high-temperature part to the low-temperature part is carried out.

[0051] In the closed valve state, the part of the valve body 20 that enters the fluid supply passage 10 corresponds to the high-temperature part of the heat pipe 23. In contrast, the upper part of the valve body 20, that is, the part that enters the mounting part 3, corresponds to the low-temperature part of the heat pipe 23, which has a relatively lower temperature than the high-temperature part because it is less affected by the heat from the hot fluid. For this reason, the heat pipe 23 performs heat transfer from the high-temperature part (lower part 23a) in the fluid supply passage 10 toward the low-temperature part (upper part 23b) on the bonnet 5 side. Thereby, the valve body 20 is cooled. Here, means for ejecting the cooling gas supplied from outside the housing H toward the low-temperature part (upper part 23b) of the heat pipe 23 of the valve body 20 in the closed valve state may be provided.

[0052] Also, in the open valve state, the heat pipe 23 within the valve body 20 is in a state where its entirety is housed within the bonnet 5 outside the fluid supply passage 10. Also in this case, the lower part 23a, which is the side of the valve body 20 closer to the fluid supply passage 10, corresponds to the high-temperature part. In contrast, the upper part 23b of the valve body 20 corresponds to the low-temperature part, which has a relatively lower temperature than the high-temperature part because it is far from the hot fluid in the fluid supply passage 10. For this reason, the heat pipe 23 performs heat transfer from the lower part 23a to the upper part 23b of the valve body 20. Here, means for ejecting the cooling gas supplied from outside the housing H toward the low-temperature part (upper part 23b) of the heat pipe 23 of the valve body 20 in the open valve state may also be provided.

[0053] Note that since the installation of the heat pipe 23 is optional, when the cooling function of the valve body 20 by either the refrigerant supply unit 30 or the cooling gas supply unit 40, or a combination thereof, is sufficient, the installation of the heat pipe 23 can be omitted.

[0054] The valve device 1 of the present invention can be applied to various fluid supply paths 10 that handle high-temperature heat fluids. For example, in addition to the aforementioned burner shut-off valve, the valve device 1 of the present invention can also be applied to a hot air valve provided in a fluid supply path 10 connecting between a hot blast stove and a blast furnace. Further, in the above-described embodiment, the configuration of the valve device 1 was described by taking the situation where the downstream side is the high-temperature side and the upstream side is the low-temperature side as an example. However, the present invention can also be applied to an environment where the upstream side is the high-temperature side and the downstream side is the low-temperature side. In addition, the configuration in which the valve seat 45 is arc-shaped in a longitudinal section passing through the axis of the fluid supply path 10 (Configuration 1), the configuration in which the opening of the ejection passage 44 into the valve box 2 is tapered such that the cross-section gradually expands as it goes into the valve box 2, or the cross-section gradually shrinks as it goes into the valve box 2 (Configuration 2), and the configuration including a guide ring 7 provided opposite to the valve seat 45 and contacting the valve body 20 in the closed valve state (Configuration 3) can each be used alone, or a part or all of these Configurations 1 to 3 can be combined and used.

Explanation of Reference Numerals

[0055] 1 Valve device 2 Valve box 5 Bonnet 7 Guide ring 10 Fluid supply path (hot air pipeline) 13 Refractory 20 Valve body 40 Cooling gas supply section 41, 46 Annular introduction passage (outer annular passage of valve box) 42, 47 Connecting passage 42a Flow control valve 43 Inner annular passage of valve box 44 Ejection passage (opening) 45 Valve seat of valve box (valve seat) 48 Pressure regulating damper

Claims

1. A valve box (2) provided in a fluid supply passage (10); A valve body (20) that moves forward and backward within the valve box (2) to open and close the fluid supply passage (10); A refrigerant passage (32) provided within the valve body (20) through which refrigerant supplied from outside the valve box (2) flows; A bonnet (5) that houses the valve body (20) in an open valve state; A valve seat (45) provided on the valve box (2) against which the peripheral edge of the valve body (20) in a closed valve state abuts; An annular passage (43) within the valve box provided along the circumferential direction of the valve seat (45); A cooling gas supply unit (40) that supplies cooling gas supplied from outside the valve box (2) into the valve box (2) through an ejection passage (44) drawn from the annular passage (43) within the valve box; and One side of the valve box (2) is connected to the downstream fluid supply passage (10) with relatively high pressure across the valve body (20) in the closed valve state, and the other side is connected to the upstream fluid supply passage (10) with relatively low pressure, The valve seat (45) is a valve device provided only on the upstream side of the valve body (20).

2. The valve device according to claim 1, wherein the cooling gas supplied from outside the valve box (2) is introduced into the annular passage (43) within the valve box through an annular introduction passage (46) provided within the valve box (2) along the outer periphery of the fluid supply passage (10).

3. A valve box (2) provided in a fluid supply passage (10); A valve body (20) that moves forward and backward within the valve box (2) to open and close the fluid supply passage (10); A refrigerant passage (32) provided within the valve body (20) through which refrigerant supplied from outside the valve box (2) flows; A bonnet (5) that houses the valve body (20) in an open valve state; A valve seat (45) provided on the valve box (2) against which the peripheral edge of the valve body (20) in a closed valve state abuts; An annular passage (43) within the valve box provided along the circumferential direction of the valve seat (45); A cooling gas supply unit (40) that supplies cooling gas supplied from outside the valve box (2) into the valve box (2) through an ejection passage (44) drawn from the annular passage (43) within the valve box; and A valve device comprising a guide ring (7) provided so that at least a part thereof faces the valve seat (45) in an open valve state and abuts against the valve body (20) in a closed valve state.

4. The valve device according to any one of claims 1 to 3, wherein the ejection passage (44) opens to the valve seat (45).

5. The center of the opening edge of the ejection passage (44) into the valve box (2) is located on the fluid supply passage (10) side with respect to the thickness direction center of the end face on the valve body (20) side of the guide ring (7), according to the valve device of claim 3 or 4.

6. The inner wall of the fluid supply passage (10) is composed of a refractory (13), and the ejection passage (44) is composed of a hole penetrating the refractory (13) from the valve box inner annular passage (43) side toward the fluid supply passage (10) side, according to the valve device of any one of claims 1 to 3.

7. The opening of the ejection passage (44) into the valve box (2) is a hole provided side by side in the circumferential direction along the valve seat (45), according to the valve device of any one of claims 1 to 3.

8. The cooling gas supplied from outside the valve box (2) is introduced into the valve box inner annular passage (43) through an annular introduction passage (41, 46) provided along the outer periphery of the fluid supply passage (10), and a flow rate adjustment valve (42a) or a pressure adjustment damper (48) is provided in a connection passage (42, 47) connecting the annular introduction passage (41, 46) and the valve box inner annular passage (43), according to the valve device of any one of claims 1 to 7.

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