JP5570937B2 - Heat treatment equipment - Google Patents

Description

  The present invention relates to a heat treatment facility. More specifically, the present invention relates to a heat treatment facility provided with an externally heated horizontal rotary heat treatment furnace in which an object to be treated in the inner cylinder is heat-treated by a heat medium flowing in a heating chamber between the inner cylinder and the outer cylinder.

  In a heat treatment furnace provided in this type of heat treatment equipment, a heating chamber between an inner cylinder and an outer cylinder is closed by a pair of side walls, and a heat medium is circulated in the heating chamber. However, since the inner cylinder forming the heating chamber rotates but the outer cylinder does not rotate, the pair of side walls usually extends from the outer cylinder and extends to the outer peripheral surface of the inner cylinder, but is not connected to the inner cylinder. State. Therefore, the heat medium in the heating chamber may flow out or the outside air may flow into the heating chamber through the gap between the side wall and the outer peripheral surface of the inner cylinder. The outflow of the heat medium causes a problem that the energy efficiency is lowered, and the inflow of outside air causes a problem that it is difficult to reuse the heat medium flowing out from the heating chamber. This is because when the outside air flows in, the oxygen concentration, temperature, and the like of the heat medium flowing out of the heating chamber fluctuate, and the combustion becomes unstable when the heat medium is burned with the combustion air to obtain the heat medium.

  Therefore, various seal structures have been proposed at present in order to prevent the heat medium from flowing out and the outside air from flowing in (see, for example, Patent Documents 1 and 2). However, the addition of a seal structure leads to an increase in equipment cost. Moreover, since the member which comprises the seal structure which contact | connects the rotating inner cylinder wears out, it will be necessary to replace | exchange the said member and it leads to the increase in running cost.

Japanese Patent Laid-Open No. 10-141624 JP 2008-256288 A

  The main problem to be solved by the present invention is a horizontal rotary heat treatment that can prevent the heat medium from flowing out of the heating chamber and the outside air from flowing into the heating chamber, and can suppress an increase in equipment cost and running cost. It is to provide a heat treatment facility equipped with a furnace.

The present invention that has solved this problem is as follows.
[Invention of Claim 1]
An inner cylinder that rotates around an axis, and an outer cylinder that is concentrically arranged at a predetermined interval from the inner cylinder, and a space between the inner cylinder and the outer cylinder is a heating chamber, and both ends of the heating chamber are The workpiece to be processed is supplied to the inner cylinder by a heat medium that extends from the outer cylinder and is closed by a pair of side walls extending to the outer peripheral surface of the inner cylinder and is supplied to the inner cylinder. Heat treatment equipment equipped with a horizontal rotary heat treatment furnace,
The internal pressure at both ends of the heating chamber is the same as the external pressure outside the heating chamber,
Heat treatment equipment characterized by that.

(Main effects)
If the internal pressure at both ends of the heating chamber is the same as the external pressure outside the heating chamber, the force (pressure) at which the heat medium flows out from the heating chamber and the force (pressure) at which the outside air flows into the heating chamber are balanced. Therefore, the problem that the heat medium flows out from the heating chamber through the gap between the side wall and the outer peripheral surface of the inner cylinder and the problem that the outside air flows into the heating chamber are solved. In addition, since a complicated seal structure is not added, an increase in equipment cost and running cost can be suppressed.

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[Invention of Claim 2]
Two inlets for the heat medium and one outlet for the heat medium are formed in the outer cylinder,
The pressure loss of the heat medium from the inflow port to the outflow port is adjusted by at least one of the following configurations (A) to (C), and the heat medium that has flowed in from one of the inflow ports and reached the outflow port The pressure and the pressure of the heat medium flowing in from the other inlet and reaching the outlet are the same,
The heat treatment facility according to claim 1.
(A) Of the flow path from the one inflow port to the outflow port and the flow path from the other inflow port to the outflow port, the length of the flow path having a relatively larger heat medium flow rate A configuration that adjusts the pressure loss of the heat medium by increasing the length.
(B) A rectifying plate that spirally circulates the heat medium in the heating chamber between the one inlet and the outlet and the heating chamber between the other inlet and the outlet. And a configuration in which the pressure loss of the heat medium is adjusted by shortening the pitch of the rectifying plates into which a relatively large amount of the heat medium flows from the inlet.
(C) The pressure loss of the heat medium is adjusted by narrowing the predetermined interval between the one inlet and the outlet and between the other inlet and the outlet. Constitution.

(Main effects)
By adjusting the pressure loss of the heat medium from the inflow port to the outflow port according to the configuration of (A) to (C) above, the pressure of the heat medium that has flowed in from one inflow port and reached the outflow port, and the other flow The pressure of the heat medium that flows in from the inlet and reaches the outlet can be made the same. If this pressure is not the same, the flow of the heat medium toward the one side or the other side in the axial direction will occur, so the flow of the heat medium may be disturbed and the internal pressure at the end of the heating chamber may be affected. .

[Invention of Claim 3]
The heating chamber extends from one of the inner cylinder and the outer cylinder and is divided into a plurality by partition walls extending to the other, and at least the heating chambers at both ends form an inlet and an outlet for the heat medium in the outer cylinder. Has been
A heat medium circulation path is constituted by an outflow path connected to each of the outflow ports, a combined flow path formed by joining the outflow paths, and an inflow path branched from the combined flow path and connected to the inflow ports.
The pressure loss of the heat medium flowing in from the inlet is adjusted by at least one of the following configurations (A) to (D), and the pressure of the heat medium flowing in from the one inlet and reaching the combined flow path; The pressure of the heat medium flowing in from the other inlet and reaching the combined flow path is the same,
The heat treatment facility according to claim 1.
(A) Heating medium by increasing the distance from the one inlet to one outlet and the distance from the other inlet to the other outlet that has a larger heat medium flow rate Configuration to adjust the pressure loss of the.
(B) A heating medium is spirally circulated in the heating chamber between the one inlet and the one outlet and the heating chamber between the other inlet and the other outlet. A configuration in which a current plate is provided, and a pressure loss of the heat medium is adjusted by shortening a pitch of the current plate through which a relatively large amount of the heat medium flows from the inlet.
(C) The predetermined one having a relatively small flow rate of the heat medium between the one inlet and the one outlet and between the other inlet and the other outlet. A configuration that adjusts the pressure loss of the heat medium by narrowing the interval.
(D) A configuration in which resistance adjusting means is provided in one of the outflow paths, and the pressure loss of one heat medium is increased by the resistance adjusting means to adjust the pressure loss of the heat medium.

(Main effects)
By adjusting the pressure loss of the heat medium flowing in from the inflow port according to the configuration of (A) to (D) above, the pressure of the heat medium flowing in from one inflow port and reaching the combined flow path, and from the other inflow port The pressure of the heat medium that has flowed in and reaches the combined flow path can be made the same. If this pressure is not the same, the flow of the heat medium from the high pressure outflow path to the low pressure outflow path will occur, so the flow of the heat medium will be disturbed and the internal pressure at both ends of the heating chamber will be affected. there is a possibility.

[Reference invention]
An inlet and an outlet for the heat medium are formed in the outer cylinder,
Pressure loss is applied to the heat medium from the inlet to the end of the heating chamber by at least one of the following configurations (A) to (C), and the internal pressure at the end of the heating chamber is the same as the external pressure outside the heating chamber. Being
The heat treatment facility according to claim 1.
(A) A configuration in which the distance from the inlet to the end of the heating chamber is increased to increase the pressure loss of the heat medium.
(B) A configuration in which a current plate that circulates the heat medium in a spiral shape is provided in the heating chamber between the inlet and the end of the heating chamber, and the pressure loss of the heat medium is increased by shortening the pitch of the current plate.
(C) A configuration in which the predetermined gap between the inlet and the heating chamber end is narrowed to increase the pressure loss of the heat medium.

(Main effects)
By applying pressure loss to the heat medium from the inlet to the end of the heating chamber with the above-described configurations (A) to (C), the internal pressure at both ends of the heating chamber can be made the same as the external pressure outside the heating chamber. it can.

  According to the present invention, there is no fear that the heat medium flows out of the heating chamber or the outside air flows into the heating chamber, and the heat treatment equipment includes a horizontal rotary heat treatment furnace that can suppress an increase in equipment cost and running cost. Become.

It is an equipment flow diagram of heat treatment equipment provided with a horizontal rotary heat treatment furnace. It is a schematic cross section of the heating chamber edge part of the form which lengthened the distance from an inflow port to a heating chamber edge part. It is a schematic cross section of the end part of the heating chamber of the form provided with the baffle plate in the heating chamber. It is a schematic cross section of the heating chamber end in a form in which a predetermined interval from the inner cylinder of the outer cylinder is narrowed. It is a modification of a horizontal rotary heat treatment furnace.

Next, an embodiment of the present invention will be described.
FIG. 1 shows a heat treatment facility equipped with a horizontal rotary heat treatment furnace 1 for heat treatment of an object C1 such as petrochemical products, sludge, and industrial waste, and a heat medium circulation mechanism. The horizontal rotary heat treatment furnace 1 includes a cylindrical inner cylinder 10 that rotates around an axis, and a cylinder that is installed concentrically at a predetermined interval from the inner cylinder 10 and that does not rotate as the inner cylinder 10 rotates. The outer cylinder 20 is mainly formed.

  Openings are formed in both end faces of the inner cylinder 10. For example, a supply mechanism for the workpiece C1 is provided in one opening, and a product C2 obtained by heat-treating the workpiece C1 is provided in the other opening. Each mechanism is inserted. The axial center of the inner cylinder 10 is slightly inclined with respect to the horizontal plane so that the discharge mechanism side becomes lower, and the workpiece C1 supplied into the inner cylinder 10 as the inner cylinder 10 rotates is supplied to the supply side (one end). Side) to the discharge side (the other end side). In the course of this transfer, the workpiece C1 is subjected to heat treatment such as drying, carbonization, thermal decomposition, and combustion while being stirred by the inner peripheral surface of the inner cylinder 10. The stirring efficiency of the workpiece C1 can be improved by attaching a stirring blade (not shown) to the inner peripheral surface of the inner cylinder 10. The workpiece C1 staying at the bottom of the inner cylinder 10 is scraped up by the stirring blade, and the contact efficiency between the workpiece C1 and the inner peripheral surface of the inner cylinder 10 which is the heat transfer surface is improved. As this stirring blade, the thing extended in the axial direction of the inner cylinder 10, the thing extended in the diagonal direction, etc. can be used.

  The workpiece C1 transferred to the discharge side in the inner cylinder 10 is discharged out of the apparatus as a product C2 which is the workpiece C1 after the heat treatment. Although not shown in particular, an inert gas can be supplied into the inner cylinder 10 from the discharge side. The inert gas supplied into the inner cylinder 10 is discharged from the supply side as an internal gas together with the dry distillation gas generated in association with the heat treatment of the workpiece C1. The flow direction of the inert gas may be a countercurrent type opposite to the transfer direction of the workpiece C1, or a parallel flow type in the same direction as the transfer direction of the workpiece C1. The inert gas is for preventing ignition of the object to be processed C1 or promoting discharge of dry distillation gas or the like, and for example, nitrogen, carbon dioxide, water vapor or the like can be used. Of course, when the contents of the heat treatment include combustion or the like, the supply of the inert gas can be omitted, or the supply can be changed to the supply of an oxygen-containing gas or the like.

  The outer cylinder 20 is disposed concentrically at a predetermined interval from the inner cylinder 10, and is provided in heating chambers R <b> 1 and R <b> 2 formed between the inner peripheral surface of the outer cylinder 20 and the outer surface of the inner cylinder 10. Heat media H1 and H2 are circulated. The heat mediums H1 and H2 include, for example, a hot gas such as hot air, a hot liquid such as hot water, a mixture thereof, and the like, and the heat of the heat mediums H1 and H2 is indirectly processed through the inner cylinder 10. C1 is transmitted, and the workpiece C1 is heat-treated. Both end portions of the heating chambers R1 and R2 are closed by a pair of side walls 21 and 22 extending from the outer cylinder 20 and extending to the outer peripheral surface of the inner cylinder 10. However, since the inner cylinder 10 rotates but the outer cylinder 20 does not rotate, the pair of side walls 21 and 22 are not connected to the inner cylinder 20. Therefore, the heat medium H1 and H2 in the heating chambers R1 and R2 may flow out through the gap between the side walls 21 and 22 and the outer peripheral surface of the inner cylinder 10, or the outside air may flow into the heating chambers R1 and R2. . However, in this embodiment, the internal pressures at both end portions (both side wall side end portions) of the heating chambers R1 and R2 are the same as the external pressure outside the heating chambers R1 and R2. Therefore, the force (pressure) at which the heat medium flows out of the heating chambers R1 and R2 and the force (pressure) at which the outside air flows into the heating chambers R1 and R2 are balanced, and the outflow of the heat medium and the inflow of outside air are prevented. The In addition, in the conventional form, in order to prevent the outflow of the heat medium and the outside air, a seal mechanism is provided. However, this form is adopted instead of or together with this seal mechanism. be able to.

  The heating chambers R1 and R2 are divided into a heating chamber R1 and a heating chamber R2 by a partition wall 10X extending from the outer cylinder 20 and extending to the inner cylinder 10. In each heating chamber R1, R2, heat medium H1, H2 is circulated separately, and the amount of heat of the heat medium H1, H2 can be different for each heating chamber. By making the heat amounts of the heat media H1 and H2 different, a heating zone in which heat treatment is performed by the heat medium H1 flowing in the heating chamber R1, and heating in which heat treatment is performed by the heat medium H2 flowing in the heating chamber R2 It can be divided into zones. In this case, the content of the heat treatment performed in each heating zone is not particularly limited, but the heat treatment furnace 1 of the present embodiment discharges the drying treatment of the workpiece C1 in the heating zone on the supply side (left side of the paper). This is suitable when carbonizing the workpiece C2 in the heating zone on the side (right side of the drawing). By these heat treatments, the workpiece C1 can be converted into fuel. In addition, although not particularly illustrated, the heating zone (heating chamber) may be a plurality of three or more. Furthermore, since the inner cylinder 10 rotates but the outer cylinder 20 does not rotate, the partition wall 10 </ b> X extending from the outer cylinder 20 is not connected to the inner cylinder 10. However, the distal end portion of the partition wall 10X and the outer peripheral surface of the inner cylinder 10 do not need to be separated from each other, and may contact each other if allowed from the viewpoint of member wear. Further, the partition wall 10 </ b> X may extend from the inner cylinder 10 and extend to the outer cylinder 20.

  Here, in this specification, the both ends of a heating chamber mean the both ends of the whole heating chamber, and do not mean the both ends of each heating chamber. Therefore, in the example of illustration, only the side wall 21 and 22 side edge part of each heating chamber R1 and R2 is meant, and the edge part by the side of the partition wall 10X is not meant.

Next, a mechanism for circulating the heat mediums H1 and H2 through the heating chambers R1 and R2 will be described.
In the heat treatment furnace 1 of the present embodiment, the heat medium H1 enters the heating chamber R1 from the inlet 11 formed at the supply-side end of the outer cylinder 10, and the inlet 12 formed at the discharge-side end of the outer cylinder 10. The heating medium H2 flows into the heating chamber R2 individually. The inflow ports 11 and 12 are preferably formed so that the inflow directions of the heat mediums H1 and H2 are tangential to the heating chambers R1 and R2. Moreover, although the formation position regarding the axial direction and circumferential direction of each inflow port 11 and 12 and the number to form are not specifically limited, the inflow port 11 of heating chamber R1 is a supply side edge part, and a heating chamber. It is preferable that the heat medium H1 flowing into R1 is formed so as to heat the bottom surface of the inner cylinder 10 first. According to this embodiment, first, the object to be processed C1 deposited on the supply side bottom is effectively heated in the inner cylinder 10. In the illustrated example, the number of the inlets 11 and 12 is one for each of the heating chambers R1 and R2. However, the number of the inlets 11 and 12 may be two or more.

The heat medium H1 that has flowed into the heating chamber R1 flows to the partition wall 10X side (discharge side) and flows out of the heating chamber R1 from the outlet 13 formed in the vicinity of the partition wall 10X of the outer cylinder 20. The heat medium H2 that has flowed into the heating chamber R2 flows to the partition wall 10X side (supply side), and flows out of the heating chamber R2 from the outlet 14 formed in the vicinity of the partition wall 10X of the outer cylinder 20. The The outlets 13 and 14 are preferably formed so that the outflow direction of the heat mediums H1 and H2 is tangential to the heating chambers R1 and R2. Moreover, although the formation position regarding the axial direction and circumferential direction of each outflow port 13 and 14 and the number to form are not specifically limited , like the example of illustration, the corresponding inflow port 11 in each heating chamber R1 and R2. , 12 is preferably formed at the end opposite to the axial direction. When the inlets 11 and 12 and the outlets 13 and 14 are formed at opposite ends in the axial direction in each of the heating chambers R1 and R2, uniform heat treatment is performed over the entire length in each heating zone. I Ru Unina. In the illustrated example, the number of outlets 13 and 14 is one for each of the heating chambers R1 and R2. However, the number of outlets 13 and 14 may be two or more.

  The heat mediums H1 and H2 whose temperature has flowed out from the outlets 13 and 14 are circulated through the outlets 81 and 82 connected to the outlets 13 and 14, respectively. The outflow channels 81 and 82 merge at the junction M1, and the heat mediums H1 and H2 are mixed at the junction M1 and are circulated in the junction 83 as the heat medium H3 having a lowered temperature. The joint channel 83 is provided with heating means 90 such as a combustion furnace, an electric heater, a heat exchanger or the like. In the heating means 90, the heat medium H3 is heated while an oxygen-containing gas A such as air is separately supplied. The heat medium H whose temperature after heating has risen continues to flow through the combined flow path 83. This joint channel 83 branches into an inflow channel 84 connected to the inflow port 11 and an inflow channel 85 connected to the inflow port 12 at the branch point M2, and the heated heat medium H is circulated in the inflow channel 84. The heat medium H1 and the heat medium H2 flowing through the inflow path 85 are divided. These heat media H1 and H2 flow into the heating chambers R1 and R2 from the inlets 11 and 12, respectively, thereby realizing the circulation of the heat medium. The combined flow path 83 is provided with a heat medium circulating means P such as a blower.

  In this heat medium circulation mechanism, the temperature of the heat medium H1 and H2 flowing out from the outlets 13 and 14 may fluctuate, so the temperature of the heat medium H that has passed through the heating means 90 may also fluctuate. There is. Therefore, in the present embodiment, flow rate adjusting means 17 and 18 for the heat mediums H1 and H2 including valves and dampers are provided in the inflow paths 84 and 85, respectively. The flow rate adjusting means 17 and 18 are for controlling the amount of heat supplied to the heat treatment furnace 1. For example, the outlet exhaust gas temperature of the heat treatment furnace 1 (inner cylinder 10), the gas temperature inside the heat treatment furnace 1 (inner cylinder 10), The supply amount can be controlled based on the detection result of the product temperature of the heat-treated product, the surface temperature of the inner cylinder 10, and the like. For measuring each temperature, a known temperature measuring means such as a thermocouple can be used. By adjusting the flow rate of the heat mediums H1 and H2 flowing into the heating chambers R1 and R2 by the flow rate adjusting means 17 and 18, the necessary heat quantity can be stably supplied to the heating chambers R1 and R2.

  However, the internal pressure at both ends of the heating chamber may also vary with the flow rate adjustment of the heat mediums H1 and H2. Therefore, in the present embodiment, the resistance adjusting means 15 including a valve, a damper or the like is provided in the outflow passage 82 on the discharge side (right side of the paper), and the internal pressure detection means 15X detects the internal pressure in the vicinity of the end of the heating chamber on the discharge side wall 22. Is provided. Based on the internal pressure (detected internal pressure) detected by the internal pressure detecting means 15X, the resistance adjusting means 15 adjusts the resistance of the heat medium H2 flowing through the outflow passage 82, thereby heating the internal pressure at the end of the discharge-side heating chamber. It can be kept the same as the outdoor pressure outside. Specifically, when the detected internal pressure is higher than the external pressure, the resistance applied to the heat medium H2 is decreased by increasing the degree of valve opening, the opening degree of the damper, and the like. On the other hand, when the detected internal pressure is lower than the external pressure, the opening degree of the valve, the opening degree of the damper, etc. are reduced to increase the resistance applied to the heat medium H2.

  In addition, in this embodiment, the circulation flow rate control means 16 is provided in the combined flow path 83 upstream of the heating means 90, and the internal pressure detection means 16X for detecting the internal pressure at the end of the heating chamber is provided on the supply side wall 21. Yes. On the basis of the internal pressure (detected internal pressure) detected by the internal pressure detection means 16X, the flow rate of the heat medium H3 reaching the heating means 90 is reduced by the circulation flow rate control means 16 to thereby reduce the internal pressure at the end of the heating chamber on the supply side outside the heating chamber. It can be kept the same as the external pressure. Specifically, when the detected internal pressure is higher than the external pressure, the decrease amount of the heat medium H3 is increased, and when the detected internal pressure is lower than the external pressure, the decrease amount of the heat medium H3 is decreased. The circulation flow rate control means 16 can be constituted by, for example, a branch path 16A that branches from the combined path 83 and a flow rate control means 16B that includes valves, dampers, and the like provided in the branch path 16A. By increasing the flow rate of the heat medium H3 flowing through the branch passage 16A by the flow rate adjusting means 16B, the amount of decrease of the heat medium H3 reaching the heating means 90 is increased. On the other hand, by reducing the flow rate of the heat medium H3 flowing through the branch passage 16A by the flow rate adjusting means 16B, the amount of decrease in the heat medium H3 reaching the heating means 90 is reduced. In this embodiment, both the outflow paths 81 and 82 can be provided with resistance adjusting means. However, the internal pressure at the end of the heating chamber on the supply side by the resistance adjustment means on the supply side, and the internal pressure at the end of the heating chamber on the discharge side by the resistance adjustment means on the discharge side are all made equal to the external pressure outside the heating chamber. This is not recommended. Although both the outflow paths 81 and 82 provided with the resistance adjusting means merge downstream, a pressure loss occurs in the heat medium in the resistance adjusting means. Therefore, according to this form, it is impossible to achieve pressure balance when the heat medium is merged.

  As shown in FIG. 1, when the inlets 11 and 12 are provided in the vicinity of the side walls 21 and 22, the inlets 11 and 12 are included in the vicinity of the end portion of the heating chamber. Therefore, the internal pressure detecting means 15X and 16X can be provided at the inflow ports 11 and 12.

Next, a method for making the internal pressure at both ends of the heating chamber (ends on the side of the side walls 21 and 22) the same as the external pressure outside the heating chamber will be described.
Since the heat medium H1 and H2 flowing in from the inlets 11 and 12 cause pressure loss in the process of reaching the both ends of the heating chamber, in order to make the internal pressure at the end of the heating chamber the same as the external pressure, the inlets 11 and 12 It is necessary that the pressure of the heat medium H1 and H2 flowing from the outside exceeds the external pressure. Then, by appropriately applying pressure loss to the heat mediums H1, H2 having a pressure exceeding the external pressure, the internal pressure at the end of the heating chamber is made the same as the external pressure. As a form of applying pressure loss to the heat medium, it is preferable to apply the following configuration.

  In the example shown in FIG. 1, the inlets 11 and 12 are provided at both ends (near the side walls 21 and 22) of the outer cylinder 20. However, as shown in FIG. It is possible to increase the pressure loss of the heat medium H1 by increasing the distance L1 in the axial direction from the side wall 21 to the side wall 21. This distance L1 is designed so that the internal pressure at the end of the heating chamber is the same as the external pressure with reference to the design pressure of the heat medium H1 flowing from the inlet 11.

  Further, as shown in FIG. 3 by taking the case of the supply side as an example, first, a rectifying plate 61 that circulates the heat medium H1 spirally in the heating chamber R1 between the inlet 11 and the side wall 21 (heating chamber end) is provided. Provide. The rectifying plate 61 has a function of preventing a short path of the heat medium H1 and has an effect of improving thermal efficiency, like the rectifying plate disclosed in Japanese Patent Application Laid-Open No. 2005-164094. However, in this embodiment, the pitch L2 of the rectifying plate 61 is shortened from the viewpoint of increasing the pressure loss of the heat medium H1. The pitch L2 is designed so that the internal pressure at the end of the heating chamber is the same as the external pressure with reference to the design pressure of the heat medium H1 flowing from the inlet 11.

  Further, as shown in FIG. 4 taking the supply side as an example, the predetermined distance L3 between the inlet 11 and the side wall 21 (heating chamber end) is narrowed to increase the pressure loss of the heat medium H1. The predetermined interval L3 is also designed so that the internal pressure at the end of the heating chamber is the same as the external pressure with reference to the design pressure of the heat medium H1 flowing from the inlet 11.

  By the way, the example in which the heating chamber is divided into two (or a plurality of three or more) by the partition wall 10X has been described above. This is because it is preferable to control the heat mediums H1 and H2 separately so that the internal pressure at both ends of the heating chamber is the same as the external pressure outside the heating chamber. However, the heating chamber may not be divided as long as the internal pressure at both ends of the heating chamber can be made equal to the external pressure. And when a heating chamber is not divided | segmented, as shown to (a)-(c) of FIG. 5, for example, the inflow ports (11, 12) are 2 places (or more than 3 places). In addition, the outlet (71) can be provided at one location. However, in this embodiment, the pressure of the heat medium H1 that has flowed in from the inlet 11 on the supply side (left side of the paper) and reaches the outlet 71 (hereinafter also referred to as “supply side pressure”), and the discharge side (right side of the paper). If the pressure of the heat medium H2 flowing in from the inlet 12 and reaching the outlet 71 (hereinafter also referred to as “discharge side pressure”) is not the same, the supply side (one axial direction) or the discharge side (axial direction) The heat medium flows to the other side. As a result, the flow of the heat medium in the heating chamber R is disturbed, and the internal pressure at both ends of the heating chamber may be affected. Therefore, the pressure loss of the heat mediums H1 and H2 from the inlets 11 and 12 to the outlet 71 is adjusted to make the supply side pressure and the discharge side pressure the same. As a mode of adjusting the pressure loss of the heat medium, it is preferable to apply the following configuration.

  In the example shown in FIG. 5A, the distance L4 from the inlet 11 to the outlet 71 is the same as the distance L5 from the inlet 12 to the outlet 71, but the supply side pressure is the discharge side pressure. If it is higher than this, the distance L4 from the inlet 11 to the outlet 71 is lengthened to increase the pressure loss of the heat medium H1. In this embodiment, since there is only one outlet, in this case, the distance L5 from the inlet 12 to the outlet 71 is reduced, and the pressure loss of the heat medium H2 is reduced. On the other hand, when the discharge side pressure becomes higher than the supply side pressure, the distance L5 from the inlet 12 to the outlet 71 is increased to increase the pressure loss of the heat medium H2. In this case, the distance L4 from the inlet 11 to the outlet 71 is reduced, and the pressure loss of the heat medium H1 is reduced. In this way, the pressure loss of the heat mediums H1 and H2 is adjusted. The distances L4 and L5 are designed so that the supply-side pressure and the discharge-side pressure are the same based on the design pressure of the heat mediums H1 and H2 flowing from the inlets 11 and 12.

  Further, as shown in FIG. 5B, heat is generated in the heating chamber R between the inlet 11 and the outlet 71 and in the heating chamber R between the inlet 12 and the outlet 71, respectively. A configuration in which rectifying plates 63 and 64 for circulating the media H1 and H2 in a spiral shape are also suitable. The rectifying plates 63 and 64 may be the same as the rectifying plate 61 (see FIG. 3) provided between the inlet 11 and the end of the heating chamber. The rectifying plates 63 and 64 also have a function of preventing a short path of the heat mediums H1 and H2 and have an effect of improving thermal efficiency. However, in this embodiment, in addition to this function and effect, the supply side pressure and the discharge side pressure are made the same by using the rectifying plates 63 and 64. Specifically, when the supply-side pressure is higher than the discharge-side pressure, the pitch L6 of the supply-side rectifying plate 63 is made shorter than the pitch L7 of the discharge-side rectifying plate 64 to reduce the pressure loss of the heat medium H1. Increase On the other hand, when the discharge-side pressure is higher than the supply-side pressure, the pitch L7 of the discharge-side rectifying plate 64 is made shorter than the pitch L6 of the supply-side rectifying plate 63 to increase the pressure loss of the heat medium H2. . In this way, the pressure loss of the heat mediums H1 and H2 is adjusted. The pitches L6 and L7 of the rectifying plates 63 and 64 are designed such that the supply side pressure and the discharge side pressure are the same based on the design pressure of the heat mediums H1 and H2 flowing from the inlets 11 and 12.

  Further, as shown in FIG. 5C, the predetermined intervals L8 and L9 between the inlet 11 and the outlet 71 and between the inlet 12 and the outlet 71 are narrowed. A configuration for adjusting the pressure loss of the heat mediums H1 and H2 is also suitable. Specifically, when the supply side pressure is higher than the discharge side pressure, although not shown, the supply side predetermined interval L8 is made narrower than the discharge side predetermined interval L9 to reduce the pressure loss of the heat medium H1. Enlarge. On the other hand, when the discharge-side pressure is higher than the supply-side pressure, as shown in the figure, the discharge-side predetermined interval L9 is made narrower than the supply-side predetermined interval L8 to increase the pressure loss of the heat medium H2. In this way, the pressure loss of the heat mediums H1 and H2 is adjusted. The predetermined intervals L8 and L9 are designed such that the supply side pressure and the discharge side pressure are the same based on the design pressure of the heat mediums H1 and H2 flowing in from the inlets 11 and 12.

The configuration for making the supply side pressure and the discharge side pressure the same has been described above. However, a problem similar to this also exists in the configuration in which the inlets (11, 12) and the outlets (13, 14) described above with reference to FIG.
That is, in the form in which the heat mediums H1 and H2 that have flowed out from the outlets 13 and 14 merge, the pressure (hereinafter “ ) And the pressure of the heat medium H2 that has flowed in from the other inlet 12 and reached the merging channel 83 (merging point M1) (hereinafter also referred to as “discharge-side merging pressure”). Must be identical. If the pressures are not the same, the flow of the heat medium (H1, H2) from the high pressure outflow passages (81, 82) to the low pressure outflow passages (81, 82) occurs. May disturb the internal pressure at both ends of the heating chamber. Therefore, in the process from the inlets 11 and 12 to the junction M1, the pressure loss of the heat mediums H1 and H2 is adjusted so that the supply side junction pressure and the discharge side junction pressure are the same. As a mode of adjusting the pressure loss of the heat medium, it is preferable to apply the configuration described based on the above-described FIG. 5 (a) to (c). In this embodiment, the “outlet 71” is the “outlet 13” or the “outlet 14”.

  Further, in this embodiment in which the point where the pressure is the same is the confluence point M1, the resistance adjusting means 15 is provided in the discharge side outflow passage 82, and the pressure loss of the heat medium H2 is increased by the resistance adjusting means 15 and supplied. It is also preferable that the side merging pressure and the discharge side merging pressure are the same. Specifically, when the supply-side merging pressure is higher than the discharge-side merging pressure, although not shown, resistance adjusting means is provided in the supply-side outflow passage 81, and the pressure loss of the heat medium H1 is caused by this resistance adjusting means. Increase On the other hand, when the discharge-side merging pressure is higher than the supply-side merging pressure, resistance adjusting means 15 is provided in the discharge-side outflow passage 82 as shown in the figure, and the resistance adjusting means 15 reduces the pressure loss of the heat medium H2. Enlarge. In this way, the pressure loss of the heat mediums H1 and H2 is adjusted. Which outflow passages 82 and 83 are provided with the resistance adjusting means and how much resistance (pressure loss) is set are supplied based on the design pressure of the heat mediums H1 and H2 flowing from the inlets 11 and 12. The side merging pressure and the discharge side merging pressure are designed to be the same. Further, the resistance adjusting means can be provided in both outflow passages 81 and 82, and if provided in both outflow passages 81 and 82, it is necessary to reverse the strength of the supply side merging pressure and the discharge side merging pressure. Even in cases, it can be handled without changing the device configuration. Note that, as described above, the resistance adjusting means 15 of the present embodiment is also used to maintain the internal pressure at the end of the heating chamber on the discharge side equal to the external pressure during the operation of the heat treatment furnace 1.

  In the above, the configuration for making the internal pressure at both ends of the heating chamber the same as the external pressure, the configuration for making the supply side pressure and the discharge side pressure, or the supply side merging pressure and the discharge side merging pressure the same have been described separately. . However, these configurations do not have to be applied separately, and a desired effect can be realized by a combination of a plurality of configurations. Further, although not shown, the heat medium inlet and outlet may be a plurality of three or more, and even in this case, a desired effect can be realized by utilizing the technical idea of the present invention. it can. Furthermore, the heat medium that has flowed out from the plurality of outlets can be heated by different heating means without being joined (mixed), and can flow again into the heating chamber from the inlet. However, providing a plurality of heating means for the heat medium increases the equipment cost.

  INDUSTRIAL APPLICABILITY The present invention can be applied as a heat treatment facility provided with an externally heated horizontal rotary heat treatment furnace in which an object to be treated in an inner cylinder is heat-treated by a heat medium flowing in a heating chamber between the inner cylinder and the outer cylinder.

  DESCRIPTION OF SYMBOLS 1 ... Horizontal rotary heat treatment furnace, 10 ... Inner cylinder, 10X ... Partition wall, 11, 12 ... Inlet, 13, 14, 71 ... Outlet, 15 ... Resistance adjustment means, 15X, 16X ... Internal pressure detection means, 16 ... Circulating flow rate control means, 16A ... branch path, 16B ... flow rate adjusting means, 17, 18 ... flow rate adjusting means, 19 ... temperature detecting means, 20 ... outer cylinder, 21,22 ... side wall, 61,63,64 ... rectifying plate, 81, 82 ... Outflow channel, 83 ... Combined channel, 84, 85 ... Inflow channel, 90 ... Heating means, A ... Oxygen-containing gas, C1 ... Object to be treated, C2 ... Product, H, H1, H2, H3 ... Heat medium , M1 ... Junction point, M2 ... Branch point, P ... Circulation pump, R, R1, R2 ... Heating chamber.

Claims (3)

An inner cylinder that rotates around an axis, and an outer cylinder that is concentrically arranged at a predetermined interval from the inner cylinder, and a space between the inner cylinder and the outer cylinder is a heating chamber, and both ends of the heating chamber are The workpiece to be processed is supplied to the inner cylinder by a heat medium that extends from the outer cylinder and is closed by a pair of side walls extending to the outer peripheral surface of the inner cylinder and is supplied to the inner cylinder. Heat treatment equipment equipped with a horizontal rotary heat treatment furnace,
The internal pressure at both ends of the heating chamber is the same as the external pressure outside the heating chamber,
Heat treatment equipment characterized by that. Two inlets for the heat medium and one outlet for the heat medium are formed in the outer cylinder,
The pressure loss of the heat medium from the inflow port to the outflow port is adjusted by at least one of the following configurations (A) to (C), and the heat medium that has flowed in from one of the inflow ports and reached the outflow port The pressure and the pressure of the heat medium flowing in from the other inlet and reaching the outlet are the same,
The heat treatment facility according to claim 1.
(A) Of the flow path from the one inflow port to the outflow port and the flow path from the other inflow port to the outflow port, the length of the flow path having a relatively larger heat medium flow rate A configuration that adjusts the pressure loss of the heat medium by increasing the length.
(B) A rectifying plate that spirally circulates the heat medium in the heating chamber between the one inlet and the outlet and the heating chamber between the other inlet and the outlet. And a configuration in which the pressure loss of the heat medium is adjusted by shortening the pitch of the rectifying plates through which a relatively large amount of the heat medium flows from the inlet.
(C) The pressure loss of the heat medium is adjusted by narrowing the predetermined interval between the one inlet and the outlet and between the other inlet and the outlet. Constitution. The heating chamber extends from one of the inner cylinder and the outer cylinder and is divided into a plurality by partition walls extending to the other, and at least the heating chambers at both ends form an inlet and an outlet for the heat medium in the outer cylinder. Has been
A heat medium circulation path is constituted by an outflow path connected to each of the outflow ports, a combined flow path formed by joining the outflow paths, and an inflow path branched from the combined flow path and connected to the inflow ports.
The pressure loss of the heat medium flowing in from the inlet is adjusted by at least one of the following configurations (A) to (D), and the pressure of the heat medium flowing in from the one inlet and reaching the combined flow path; The pressure of the heat medium flowing in from the other inlet and reaching the combined flow path is the same,
The heat treatment facility according to claim 1 .
(A) Heating medium by increasing the distance from the one inlet to one outlet and the distance from the other inlet to the other outlet that has a larger heat medium flow rate Configuration to adjust the pressure loss of the.
(B) A heating medium is spirally circulated in the heating chamber between the one inlet and the one outlet and the heating chamber between the other inlet and the other outlet. A configuration in which a current plate is provided, and a pressure loss of the heat medium is adjusted by shortening a pitch of the current plate through which a relatively large amount of the heat medium flows from the inlet.
(C) The predetermined one having a relatively small flow rate of the heat medium between the one inlet and the one outlet and between the other inlet and the other outlet. A configuration that adjusts the pressure loss of the heat medium by narrowing the interval.
(D) A configuration in which resistance adjusting means is provided in one of the outflow paths, and the pressure loss of one heat medium is increased by the resistance adjusting means to adjust the pressure loss of the heat medium.

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