JP7709875B2 - Valve mechanism - Google Patents

Description

This invention relates to a valve device installed in a high-temperature fluid supply passage.

For example, Patent Document 1 describes a valve device that is installed in a high-temperature fluid supply passage. This valve device is a gate valve with a cooling structure, and a valve element that opens and closes the flow passage is attached inside a housing consisting of a valve box and a bonnet (referred to as a cap section in Patent Document 1) installed on top of the valve box, so that the valve element can be raised and lowered freely. The bonnet serves as a storage space for the valve element when in the open position.

The valve body is made of two circular steel valve plates connected by a pair of spiral plates that form a cooling water flow path from the center to the outer periphery. An annular seat ring is attached by welding to the outer periphery of the connected valve plates.

The peripheral wall of the seat ring is provided with a water inlet and a water outlet for cooling water to be supplied to the cooling water flow path, and a pair of hollow valve stems are connected in parallel to the water inlet and the water outlet. A cooling water inlet and outlet are provided at the top of the valve stem. Cooling water is supplied from the inlet, passes through the inside of the valve stem, enters the spiral cooling water flow path inside the seat ring from the water inlet, passes through the center of the valve body, passes through the inside of the valve stem from the water outlet, and is discharged from the outlet. This allows the entire valve body to be cooled uniformly.

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, and is provided with a valve plate that can be raised and lowered inside a housing consisting of a valve box and a bonnet, and an annular air cooling passage adjacent to the sealed valve seat with which the valve plate moves. The air cooling passage is connected to a cooling air source. Cooling air supplied from the cooling air source is supplied to the housing interior space through the air cooling passage and a cooling gap that opens into the sealed surface of the sealed valve seat.

In the closed valve state, the cooling gap of the sealed valve seat is closed by the valve plate. This stops the inflow of cooling air into the housing internal space, allowing the sealed valve seat to be cooled (see Patent Document 2, page 2, lines 1 to 8, bottom left). In the closed valve state, the valve body blocks the thermal fluid, so the need to cool the sealed valve seat is considered to be relatively low. On the other hand, in the open valve state, the valve plate is pulled up to the bonnet provided on the top of the valve box, allowing cooling air to flow from the cooling gap into the housing internal space. This cools not only the sealed valve seat but also the housing internal space (see Patent Document 2, page 2, lines 15 to 1, bottom left).

JP 2003-262286 A Japanese Patent Application Laid-Open No. 60-132191

In the valve device of Patent Document 2, when the valve is open, the valve body (valve plate) is separated from the sealed valve seat, opening the cooling gap and allowing cooling air to flow into the housing. At this time, the valve body is pulled up inside the bonnet (cover) provided on the top of the valve box, so the cooling air ejected from the cooling gap does not hit the valve plate directly.

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 improve the cooling effect on the valve plate. For this reason, there is a need to cool the valve plate more efficiently in both the closed and open valve states.

The objective of this invention is to further improve the cooling performance of the valve body in a valve device installed in a high-temperature fluid supply passage.

In order to solve the above problems, the present invention employs a valve device that includes a valve box that is provided in a fluid supply passage, a valve element that opens and closes the fluid supply passage by moving back and forth within the valve box, a refrigerant passage that is provided within the valve element and through which a refrigerant supplied from outside the valve box flows, a bonnet that accommodates the valve element in an open valve state, a valve seat that is provided in the valve box and against which the peripheral edge of the valve element in a closed valve state abuts, an annular passage in the valve box that is provided in the circumferential direction along the valve seat, and a cooling gas supply unit that supplies cooling gas supplied from outside the valve box through a jet passage drawn from the annular passage in the valve box into the valve box, and the valve seat is arc-shaped in a vertical cross section that passes through the axis of the fluid supply passage.

In order to solve the above problems, the present invention employs a valve device that includes a valve box that is provided in a fluid supply passage, a valve element that opens and closes the fluid supply passage by moving back and forth within the valve box, a refrigerant passage that is provided within the valve element and through which a refrigerant supplied from outside the valve box flows, a bonnet that accommodates the valve element in an open valve state, a valve seat that is provided in the valve box and against which the peripheral portion of the valve element in a closed valve state abuts, an annular passage in the valve box that is provided in the circumferential direction along the valve seat, and a cooling gas supply unit that supplies cooling gas supplied from outside the valve box to the valve box through a blow-out passage drawn from the annular passage in the valve box, and the opening of the blow-out passage into the valve box is tapered so that the cross section gradually expands as it approaches the valve box, or is tapered so that the cross section gradually decreases as it approaches the valve box.

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

In order to solve the above problems, the present invention employs a valve device that includes a valve box that is provided in a fluid supply path, a valve element that opens and closes the fluid supply path by moving back and forth within the valve box, a refrigerant passage that is provided within the valve element and through which a refrigerant supplied from outside the valve box flows, a bonnet that accommodates the valve element in an open valve state, a valve seat that is provided in the valve box and against which the peripheral edge of the valve element in a closed valve state abuts, an annular passage in the valve box that is provided in the circumferential direction along the valve seat, and a cooling gas supply section that supplies cooling gas supplied from outside the valve box to the inside of the valve box through a blow-out passage drawn from the annular passage in the valve box, and a guide ring that is provided opposite the valve seat and abuts the valve element in a closed valve state.

Here, the ejection passage may be configured to open into the valve seat.

In addition, a configuration can be adopted in which the center of the opening edge of the ejection passage into the valve box is located closer to the fluid supply passage than the center of the thickness direction of the end face of the guide ring on the valve body side.

In each of these embodiments, the inner wall of the fluid supply passage is made of a refractory material, and the ejection passage can be made of a hole that penetrates the refractory material from the annular passage side inside the valve box toward the fluid supply passage side.

The opening of the ejection passage into the valve box can be configured as holes arranged in a circumferential direction along the valve seat.

Furthermore, the cooling gas supplied from outside the valve box is introduced into the annular passage inside the valve box through an annular inlet passage provided along the outer periphery of the fluid supply path, and a configuration can be adopted in which a flow control valve or a pressure control damper is provided in the connecting passage connecting the annular inlet passage and the annular passage inside the valve box.

This invention can further improve the cooling performance of the valve plate in a valve device installed in a high-temperature fluid supply passage.

FIG. 1 is an enlarged longitudinal sectional view showing a main part of a first embodiment of the present invention; FIG. Cross-sectional view showing the flow path of the refrigerant supply part in the valve body FIG. 13 is an enlarged cross-sectional view showing a modified example of a main part. FIG. 13 is an enlarged cross-sectional view showing a modified example of a main part. FIG. 13 is an enlarged cross-sectional view showing a modified example of a main part. FIG. 13 is an enlarged cross-sectional view showing a modified example of a main part. FIG. 13 is an enlarged cross-sectional view showing a modified example of a main part. Schematic diagram showing the flow path of a cooling gas supply unit FIG. 13 is an enlarged perspective view of a main portion showing an example of an opening. FIG. 13 is an enlarged perspective view of a main portion showing an example of an opening. Enlarged view of the main part showing a modified example Enlarged view of the main part showing a modified example Enlarged view of the main part showing a modified example FIG. 11 is an enlarged longitudinal sectional view showing a main part of a second embodiment of the present invention. Front view of FIG. FIG. 11 is an enlarged vertical cross-sectional view of a main part showing the open state of the valve of FIG.

An embodiment of the present invention will be described with reference to the drawings. In this embodiment, the configuration of the present invention will be described using as an example a valve device 1 provided in a pipeline 10 for supplying a hot fluid (hereinafter referred to as a fluid supply line 10) leading to a blast furnace.

Figures 1 to 9 show the first embodiment and its modified examples. As shown in Figure 1, the valve device 1 is configured as a gate valve type in which a valve box 2 is provided in the middle of a fluid supply line 10 and a valve body 20 that can be raised and lowered is provided in the valve box 2. The fluid supply line 10 is opened and closed by the valve body 20 moving forward and backward in the valve box 2. In Figure 1, the left side of the figure is the upstream side and the right side is the downstream side. A valve box valve seat 45 that comes into contact with and separates from a valve body valve seat portion 34 provided on the peripheral portion 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 abut against each other over the entire circumference in the closed valve state. In addition, 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 disposed opposite the valve body valve seat 45 on the upstream side, 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 path 10 is referred to as the axial direction, and the direction perpendicular to the axis is referred to as the radial direction.

When the valve is closed, the peripheral portion of the valve body 20 is pressed against the valve seat 45 by the force from the downstream side where the pressure is relatively high. For this reason, in this embodiment, a one-sided valve seat is used in which the valve seat 45 is provided only on the upstream side. Note that, depending on the application of the valve device 1, the valve seats 45 may be provided on both the upstream and downstream sides of the valve body 20. In this case, the guide ring 7 on the downstream side can be omitted.

The inner surface of the fluid supply passage 10 in the valve box 2, except for the space into which the valve body 20 enters, is covered with refractories 13, 14 made of a material that can withstand high heat and has heat retention properties. Refractory material 13 is arranged on the inner surface of the flow passage 11 on the upstream side of the valve body 20, and refractory material 14 is arranged on the inner surface of the flow passage 12 on the downstream side. A recess 8 into which the valve body 20 enters is provided between the upstream flow passage 11 and the downstream flow passage 12. The inner surface of the recess 8 is also covered with a similar refractory material 15. Reference numeral 9 in Figures 1 to 3 denotes a drain, and reference numeral 9a in Figure 2 denotes a drain valve.

The valve box 2 is provided at its top with a hollow mounting portion 3 that protrudes outward beyond the outer surface of the cylindrical body that constitutes the fluid supply passage 10. Furthermore, a lid member 4 is attached to the top of the mounting portion 3 via flanges 3a, 4a. The valve box 2 (including the mounting portion 3) and the lid member 4 constitute a housing H. The interior of the mounting portion 3 and the lid member 4 also function as a bonnet 5 that houses the valve body 20 in the open state. The inner surfaces of the mounting portion 3 and the lid member 4 are also covered with a refractory material 16 similar to that of the inside of the fluid supply passage 10. Hereinafter, the valve box 2 and the lid member 4 will be collectively referred to as the housing H.

A valve stem 6 is attached to the valve element 20. The valve stem 6 extends upward inside the bonnet 5 and is pulled out of the housing H. The valve stem 6 is driven by a drive device to move back and forth in the axial direction of the valve stem 6, and the valve element 20 moves back and forth together with the valve stem 6 in the same direction. That is, the valve element 20 closes when the valve stem 6 moves to one side along the axial direction of the valve stem 6 (downward), and opens when the valve stem 6 moves to the other side along the axial direction of the valve stem 6 (upward).

A refrigerant passage 32 is provided within the valve body 20, through which the refrigerant supplied from outside the housing H flows. As shown in FIG. 1, the valve body 20 has two metal (steel) valve plates 24, 25 on the front and back that sandwich the refrigerant passage 32 located in the center in the thickness direction. The outside of the upstream valve plate 24 is covered with refractory material 21, and the outside of the downstream valve plate 24 is covered with refractory material 22. An annular seat ring is attached to the outer periphery of the valve body 20 to form the valve body valve seat portion 34.

As shown in FIG. 3, the refrigerant passage 32 is formed by a partition wall 33. In this embodiment, a pair of spiral plates 33a, 33b are used as the partition wall 33. A pair of refrigerant passages 31 provided in each of the two valve rods 6 are connected to the supply port 32a and the discharge port 32b provided on the outer periphery of the valve body 20. The pair of refrigerant passages 31 are connected to 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 center 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, forming a refrigerant supply section 30. The valve body 20 is cooled by this refrigerant supply section 30. In this embodiment, air is used as the refrigerant handled by the refrigerant supply section 30, but it may be a refrigerant made of a gas other than air, or a refrigerant made of a liquid.

The valve device 1 also includes a cooling gas supply unit 40 that supplies cooling gas supplied from a gas supply source 54 provided outside the valve box 2 and the bonnet 5, i.e., outside the housing H, into the valve box 2 through a jet 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 through a communication passage 55 and is introduced into the valve box inner annular passage (second annular passage) 43 provided in the valve box 2 through an annular introduction passage (first annular passage) 46 provided along the outer periphery of the fluid supply path 10. The opening 44 is drawn out from the valve box inner annular passage 43. The annular introduction passage 46 is located radially outward relative to the valve box inner annular passage 43, and the two are connected by a connecting passage 47 extending radially. In this embodiment, the annular introduction passage 46 is provided integrally with the valve box 2, but it may be separate from the valve box 2. In this embodiment, air is used as the cooling gas, but gases other than air may also be used.

The cooling gas supplied from the gas supply source 54 is introduced into the annular introduction passage 46 from the gas inlet 49 connected to the communication passage 55. As shown in the schematic diagram of FIG. 5, the gas inlet 49 is provided in multiple locations around the axis of the fluid supply passage 10, so that the gas is smoothly supplied to the annular introduction passage 46. The connection between the annular introduction passage 46 and the gas inlet 49 is provided with a pressure adjustment damper 48, so that the pressure inside the annular introduction passage 46 is kept at a constant level or higher. In addition, the connecting passage 47 connecting the annular introduction passage 46 and the annular passage 43 in the valve box is provided in multiple locations around the axis of the fluid supply passage 10 (in the embodiment, in equal directions around the axis), so that the gas is smoothly supplied from the annular introduction passage 46 to the annular passage 43 in the valve box. These configurations ensure a stable supply of cooling gas to the annular passage 43 in the valve box. The pressure adjustment damper 48 is equipped with, for example, a blade or an opening and closing plate that opens to the downstream side (the annular inlet passage 46 side) when the pressure on the upstream side (the gas inlet port 49 side) exceeds a certain level.

The cooling gas is supplied into the valve box 2 through the opening 44 provided in the valve seat 45, and exerts a cooling function for the valve body 20 and each part of the valve box 2. Here, if the cooling gas is introduced into a simple circulation type cooling device that does not have the opening 44, the temperature of the cooling gas will rise quickly, and a problem may occur in which the cooling performance cannot be maintained. This is because the temperature of a gas refrigerant is easier to rise than that of a liquid refrigerant. In contrast, in this embodiment, the cooling gas is discharged through the opening 44, and the cooling gas is continuously supplied from the gas supply source 54 to the annular passage 43 in the valve box to replenish it. This makes it possible to improve the cooling performance for the valve seat 45 while using gas as the refrigerant. In addition, if the opening 44 is oriented toward the axial center side of the fluid supply path 10, that is, toward the center side of the valve body 20, a low-temperature area is formed by the refrigerant, and the amount of heat transferred from the high-temperature fluid in the fluid supply path 10 to the valve seat 45 can be reduced.

The annular introduction passage 46 and the annular passage 43 inside the valve box are both located upstream of the valve box 2, and this upstream position is blocked from hot air by the valve seat 45 when the valve is closed. Therefore, when the downstream side is relatively hotter than the upstream side, the thermal effect from the hot downstream side is reduced. In particular, when the valve device 1 is a burner shutoff valve or the like provided in the fluid supply path 10 connecting the hot air stove that supplies hot air to the blast furnace and the burner that is its heat source, as in this embodiment, the downstream side can become hotter than the upstream side when the valve is closed.

In addition, in this first embodiment, as shown in FIG. 1, the guide ring 7 and the opening 44 face each other, thereby improving the cooling performance of the guide ring 7. Here, in the first embodiment, the line connecting the center of the opening edge of the opening 44 on the valve box 2 side and the center in the thickness direction of the end face of the guide ring 7 on the valve body 20 side 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 located in a straight line. By arranging the guide ring 7 instead of the valve seat downstream of 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, while reducing heat transfer to the bottom of the valve body 20 when the valve body 20 is fully open. It is also possible to improve the sealing performance by discharging the refrigerant from the opening 44 when the valve body 20 is fully closed.

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 path 10 side, from the center of the thickness direction of the end face of the guide ring 7 on the valve body 20 side (the center of the thickness direction of the downstream valve seat 45 if the guide ring 7 is not provided). As a result, the cooling gas supplied from the opening 44 is injected to a position closer to the fluid supply path 10. The cooling gas injected at a position closer to the fluid supply path 10 forms a flow in the same direction as the flow direction of the thermal fluid in the fluid supply path 10 and in a direction roughly parallel to it, forming an air layer (air curtain) that separates the space in the fluid supply path 10 from the space in the bonnet 5. This is thought to be due to the cooling gas being pulled by the flow of the thermal fluid in the fluid supply path 10, forming an air layer with a lower temperature than the thermal fluid between the space in the fluid supply path 10 and the space in the bonnet 5. The formation of this air layer improves the cooling performance (including reducing the thermal effects from the thermal fluid) for the guide ring 7 (or the downstream valve seat 45).

The opening edge center of the opening 44 is the center of the annular opening edge at the point where the opening 44 opens into the bonnet 5. In this embodiment, the cross section of the opening 44 is a perfect circle, so the center of the perfect circle is the opening edge center. In FIG. 7, the center line of the hole of the opening 44 is indicated by the symbol c1. In addition, the radial space width in the annular passage 43 inside the valve box is the same over the entire circumference. It is desirable that the opening edge center of the opening 44 is the center of the radial space width in the annular passage 43 inside the valve box, that is, closer to the fluid supply passage 10 than the radial center of the annular passage 43 inside the valve box. In FIG. 7, the thickness direction center line of the end face of the guide ring 7 on the valve body 20 side is indicated by the chain line indicated by the symbol c2.

The opening 44 may be, for example, as shown in FIG. 6A, a plurality of holes 44a, each having a circular cross section, arranged at a predetermined interval along the circumferential direction of the valve seat 45, or as shown in FIG. 6B, the opening 44 may be a slit 44b arranged continuously in a ring shape along the circumferential direction of the valve seat 45. By forming the opening 44 into a plurality of holes 44a, the holes 44a can function as nozzles to increase the force of the injection of the cooling gas. Furthermore, by forming the opening 44 into a circumferential slit 44b, the guide ring 7 (or the downstream valve seat 45 if no guide ring 7 is provided) can be effectively cooled all around. The slits 44b can be arranged continuously all around, but may also be arranged intermittently in the circumferential direction.

A further modified example is shown in FIG. 8. In the example of FIG. 8, the opening 44 is configured as a hole penetrating from the valve box inner annular passage 43 side toward the fluid supply passage 10 side. That is, the direction of the center line c1 of the opening 44 is inclined with respect to the axial direction of the fluid supply passage 10, and the inclination direction is a direction gradually approaching the axis of the fluid supply passage 10 as it approaches the inside of the valve box 2 (as it moves away from the valve box inner annular passage 43 side). As a result, the injection position of the cooling gas approaches the axis of the fluid supply passage 10, so that the thermal influence that the guide ring 7 receives from the high-temperature fluid in the fluid supply passage 10 can be further reduced. In the example of FIG. 8, the opening 44 is tapered in such a way that the cross section gradually expands toward the inside of the valve box 2, so that the diffusion range of the cooling gas can be made wider. The range of the tapered cross section is the entire length of the opening 44 in FIG. 8, but the above effect can be expected by tapering at least the opening into the valve box 2.

In the above embodiment, the opening 44 is open to the valve seat 45, but the opening 44 may be open to a location other than the valve seat 45. In the example of FIG. 9, the opening 44 is configured as a hole penetrating the refractory 13, which is the inner wall of the fluid supply passage 10, from the valve box inner annular passage 43 side to the fluid supply passage 10 side. That is, the opening 44 is configured to penetrate the wall of the hollow member constituting the valve box inner annular passage 43 in the portion closer to the outer diameter of the housing H, and to penetrate the refractory 13 in the portion closer to the inner diameter. In this way, when the opening 44 is configured to penetrate the refractory 13, the penetration direction of the opening 44 may be a direction inclined with respect to the tube axis of the fluid supply passage 10 as shown in FIG. 9, or may be a direction perpendicular to the tube axis of the fluid supply passage 10. By supplying cooling gas through this opening 44, the upstream surface of the valve body 20 in the closed state can be cooled.

Here, also in FIG. 9, the center of the opening edge of the opening 44 is closer to the fluid supply path 10 than the center of the thickness direction of the end face of the guide ring 7 on the valve body 20 side. By opening the opening 44 directly into the fluid supply path 10 instead of the valve seat 45 side, the opening edge center c1 of the opening 44 is closer to the fluid supply path 10 side, so that the thermal effect on the guide ring 7 (or the downstream valve seat 45 if no guide ring 7 is provided) can be suppressed.

Modified examples of the cooling gas supply unit 40 are shown in Figs. 4A to 4E. In Fig. 4A, the shape of the valve seat 45 is a radius shape, i.e., an arc-shaped cross section, in a vertical cross section passing through the axis of the fluid supply path 10. The opening 44 opens at the tip of the valve seat 45 that protrudes in an arc shape. By making the cross section of the valve seat 45 arc-shaped, the tip of the valve seat 45 that protrudes in an arc shape abuts the valve body valve seat portion 34 with a limited, narrow area. This allows the valve body 20 to close the opening 44 more airtightly. In addition, 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 stress concentration on the valve seat 45 can be suppressed.

In FIG. 4B, the opening 44 is tapered so that the cross section gradually decreases toward the space inside the valve box 2, i.e., toward the valve seat 45 side. This increases the force of the cooling gas injection, and allows the cooling gas to reach a longer distance, i.e., a more distant part, thereby improving the cooling efficiency. In FIG. 4C, the opening 44 is tapered so that the cross section gradually increases toward the space inside the valve box 2, i.e., toward the valve seat 45 side. This increases the diffusion range of the cooling gas, thereby improving the cooling efficiency. In FIG. 4D, the cross section of the internal space of the annular passage 43 inside the valve box is gradually enlarged toward the valve seat 45 side. This allows the volume inside the annular passage 43 inside the valve box to be large. In FIG. 4E, the cross section of the internal space of the annular passage 43 inside the valve box is gradually reduced toward the valve seat 45 side. Such a cross-sectional shape can also be adopted.

The variations in cross-sectional shape and position of the opening 44 exemplified above can be applied to the opening 44 in all embodiments.

The second embodiment of the invention is shown in Figures 10 to 12. The basic configuration of the valve device 1 is similar to that of the previously described embodiment, so the following explanation will focus on the differences.

The cooling gas supply unit 40 of the valve device 1 of the second embodiment is provided with an annular introduction passage 41 (in the second embodiment, the annular introduction passage 41 is provided outside the valve box 2, so hereinafter, it will be referred to as the valve box outer annular passage 41) connected to the gas supply source 54 via a communication passage 55 and provided along the outer periphery of the fluid supply path 10, an inner annular passage (air-cooled circulation annular pipe) 43 provided in the valve box 2 in the circumferential direction along the valve seat 45, and a plurality of connecting passages 42 extending radially connecting the valve box outer annular passage 41 and the valve box inner annular passage 43. The valve seat 45 is made of a hollow annular member, and its inside is the valve box inner annular passage 43, which is a passage for cooling gas, as in the previous embodiment. In addition, both the valve box outer annular passage 41 and the valve box inner annular passage 43 are located upstream of the valve box 2, and the upstream position is blocked from hot air by the valve seat 45 in the closed valve state, as in the previous embodiment.

The connecting passage 42 is provided with a flow rate adjustment valve 42a. By providing the connecting passage 42 with the flow rate adjustment valve 42a, the amount and pressure of the cooling gas supplied to the annular passage 43 inside the valve box can be adjusted, stabilizing the supply. This makes it possible to make the pressure inside the annular passage 43 inside the valve box more uniform. In this way, by making the pressure of the refrigerant more uniform, the amount of refrigerant discharged becomes more uniform across the entire area of the valve seat 45, thereby suppressing temperature unevenness at the valve seat 45.

The cross-sectional areas of the multiple connecting passages 42 may all be the same, but the cross-sectional areas of the connecting passages 42 may differ from each other depending on the location where the connecting passages 42 are installed. For example, the cross-sectional area of the connecting passage 42 close to the part 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 area of the connecting passage 42 at other locations. This also makes it possible to make the pressure in the annular passage 43 inside the valve box more uniform. As another method, for example, the cross-sectional areas of the multiple connecting passages 42 may be made variable so that the cross-sectional area of the connecting passage 42 close to the part where the pressure is low in the annular passage 43 inside the valve box is adjusted to be relatively larger than the cross-sectional area of the connecting passage 42 at other locations. The part where the pressure is likely to drop in the annular passage 43 inside the valve box is, for example, a place far from the gas inlet 49. Each configuration related to these connecting passages 42 can also be applied to the connecting passage 47 of the first embodiment.

In the second embodiment, a valve ring 27 that comes into contact with and separates from the guide ring 7 is provided on the periphery of the valve body 20. The valve ring 27 is an annular member similar to the guide ring 7. The guide ring 7 and the valve ring 27 are made of metal similar to the valve seat portion 34 and the valve seat 45, respectively. When the valve body 20 opens and closes, the guide ring 7 and the valve ring 27 rub against each other on the downstream surface of the valve body 20 where the valve seat is not provided, so that the refractories 14 and 22 described below do not interfere with the operation of the valve body 20. Instead of this valve ring 27, a valve seat portion 34 similar to that of the first embodiment may be provided.

The valve body 20 is provided with a heat pipe 23 that has the function of transferring heat absorbed in the high temperature portion to the low temperature portion, which is at a lower temperature than the high temperature portion. The heat pipe 23 is disposed outside the downstream valve plate 25 and inside the refractory material 22.

In general, a heat pipe is a container that contains a working fluid sealed inside and has a capillary structure inside it. When part of the container is heated and a high-temperature area is generated, the working fluid in that high-temperature area absorbs the heat and evaporates. The vapor moves toward the low-temperature area inside the same container, where it condenses and releases heat. The condensed working fluid returns to the high-temperature area due to capillary action. This process is repeated to transfer heat from the high-temperature area to the low-temperature area.

In the closed valve state, the part of the valve body 20 that is inserted into 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, i.e., the part that is inserted into the mounting part 3, corresponds to the low temperature part of the heat pipe 23 that is relatively lower in temperature than the high temperature part because it is less affected by heat from the thermal fluid. Therefore, the heat pipe 23 transfers heat from the high temperature part (lower part 23a) in the fluid supply passage 10 to the low temperature part (upper part 23b) on the bonnet 5 side. This cools the valve body 20. Here, a means may be provided for ejecting 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.

In addition, in the open valve state, the heat pipe 23 in the valve body 20 is entirely housed in the bonnet 5 outside the fluid supply path 10. In this case, the lower part 23a of the valve body 20, which is closer to the fluid supply path 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 is relatively lower in temperature than the high temperature part, because it is farther from the thermal fluid of the fluid supply path 10. Therefore, the heat pipe 23 transfers heat from the lower part 23a to the upper part 23b of the valve body 20. Here, a means may be provided for ejecting cooling gas, which is also 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.

The installation of the heat pipe 23 is optional, so if the cooling function of the valve body 20 provided by either the refrigerant supply unit 30 or the cooling gas supply unit 40, or a combination of the two, is sufficient, the installation of the heat pipe 23 can be omitted.

The valve device 1 of the present invention can be applied to various fluid supply passages 10 that handle high-temperature thermal fluids. For example, in addition to the burner shutoff valve described above, the valve device 1 of the present invention can also be applied to a hot air valve installed in a fluid supply passage 10 connecting a hot air stove and a blast furnace. In the above embodiment, the configuration of the valve device 1 was described using an example of a situation in which the downstream side is the high temperature side and the upstream side is the low temperature side. However, the present invention can also be applied in an environment in which 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 vertical section passing through the axis of the fluid supply passage 10 (configuration 1), the configuration in which the opening of the ejection passage 44 into the valve box 2 is tapered so that the cross section gradually expands as it approaches the valve box 2, or the configuration in which the cross section gradually decreases as it approaches the valve box 2 (configuration 2), and the configuration in which a guide ring 7 is provided opposite the valve seat 45 and abuts against the valve body 20 in the closed valve state (configuration 3) can each be used alone, or some or all of these configurations 1 to 3 can be used in combination.

1 Valve device 2 Valve box 5 Bonnet 7 Guide ring 10 Fluid supply path (hot air pipe)
13 Refractory material 20 Valve body 40 Cooling gas supply section 41, 46 Annular introduction passage (valve box outer annular passage)
42, 47 Connection passage 42a Flow rate control valve 43 Valve box inner annular passage 44 Jet passage (opening)
45 Valve box seat (valve seat)
48 Pressure adjustment damper

Claims (8)

A valve body (2) provided in a fluid supply passage (10);
a valve body (20) that opens and closes the fluid supply path (10) by moving back and forth within the valve box (2);
a refrigerant passage (32) provided in the valve body (20) through which a refrigerant supplied from outside the valve box (2) flows;
a bonnet (5) that houses the valve body (20) in an open state;
a valve seat (45) provided in the valve box (2) against which a peripheral portion of the valve body (20) in a closed state abuts;
a valve body inner annular passage (43) provided in a circumferential direction along 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 a jet passage (44) drawn out from the valve box inner annular passage (43),
One side of the valve body (2) in a closed state is connected to the downstream fluid supply path (10) where the pressure is relatively high, and the other side is connected to the upstream fluid supply path (10) where the pressure is relatively low,
The valve device, wherein the valve seat (45) is 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 valve box inner annular passage (43) via an annular introduction passage (46) provided in the valve box (2) along an outer periphery of the fluid supply path ( 10 ). A valve body (2) provided in a fluid supply passage (10);
a valve body (20) that opens and closes the fluid supply path (10) by moving back and forth within the valve box (2);
a refrigerant passage (32) provided in the valve body (20) through which a refrigerant supplied from outside the valve box (2) flows;
a bonnet (5) that houses the valve body (20) in an open state;
a valve seat (45) provided in the valve box (2) against which a peripheral portion of the valve body (20) in a closed state abuts;
a valve body inner annular passage (43) provided in a circumferential direction along 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 a jet passage (44) drawn out from the valve box inner annular passage (43),
a guide ring (7) arranged so that at least a portion of the guide ring faces the valve seat (45) in an open state and abuts against the valve body (20) in a closed state. 4. The valve device according to claim 1 , wherein the ejection passage (44) opens into the valve seat (45). 5. A valve device as described in claim 3 or 4, wherein the center of the opening edge of the ejection passage (44) into the valve box (2) is located on the fluid supply path (10) side relative to the thickness direction center of the end face of the guide ring ( 7 ) on the valve body (20) side. 4. The valve device according to claim 1, wherein an inner wall of the fluid supply passage (10) is made of a refractory material (13), and the ejection passage (44) is made of a hole penetrating the refractory material (13) from the valve box inner annular passage ( 43 ) side toward the fluid supply passage (10) side. 4. The valve device according to claim 1 , wherein the opening of the ejection passage (44) into the valve box (2) is a pair of holes arranged in a circumferential direction along the valve seat (45). 8. 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) inside the valve box via an annular introduction passage (41, 46) provided along the outer periphery of the fluid supply path (10), and a flow control valve (42a) or a pressure control damper (48) is provided in a connecting passage (42, 47) connecting the annular introduction passage (41, 46 ) and the annular passage (43) inside the valve box.