JP5702261B2 - Vulcanization can - Google Patents

Description

  The present invention relates to a vulcanizing can suitably used for vulcanization molding of a tire, and more particularly to a vulcanizing can capable of making the internal temperature distribution uniform.

As a process of manufacturing a tire called a retread tire, a base tire that is the foundation of the tire and a tread rubber that is stuck in the circumferential direction of the base tire are accommodated in an envelope, and the pressure in the envelope is reduced. In this state, there is a vulcanization process in which the cushion rubber as an adhesive layer interposed between the base tire and the tread rubber is vulcanized and the both are firmly integrated. Are known.
The vulcanization can used in the vulcanization process is a cylindrical pressure vessel capable of storing a plurality of sets of tires (base tires and tread rubber) accommodated in an envelope, and one side portion in the extending direction of the cylindrical pressure vessel. A heat source that heats the air in the pressure vessel, a fan that is arranged in the vicinity of the heat source and circulates the air heated by the heat source, and that can be opened and closed on the other side in the extension direction of the pressure vessel. With an airtight door.
In addition, a duct extending along the extending direction of the pressure vessel is disposed on the inner wall surface of the pressure vessel, and the air heated by the heat source is supplied into the duct by the fan, and the air passing through the duct is connected to the fan. Is discharged at the airtight door provided on the opposite side.
Then, the air exhausted on the airtight door side collides with the wall surface of the airtight door and flows out in the pressure vessel toward the fan side, and reaches the heat source while heating a plurality of tires stored in the pressure vessel. Then, it is discharged again from the airtight door side by the fan and the duct.
In other words, the vulcanizing can is configured to heat a plurality of sets of tires stored therein by circulating air heated in the pressure vessel in the extending direction. In addition, the pressure in the pressure vessel is pressurized to, for example, about 6 to 8 atmospheres, and the pedestal tire and the tread rubber stored therein are heated and pressurized in the envelope and vulcanization proceeds. .

JP 2006-88049 A Special table 2008-500898

However, as is apparent from the airflow distribution shown in FIG. 13 (a), in the conventional vulcanizing can, the air discharged to the airtight door side tends to be an upward airflow in the process of flowing into the fan side, and the pressure vessel Although air actively flows in the upper part, air stays easily in the lower part of the pressure vessel. For example, as one method for suppressing the generation of ascending air current, a method of increasing the flow rate when the air discharged to the airtight door side flows in the pressure vessel to the fan side can be considered. Therefore, in order to increase the flow velocity in the pressure vessel, a centrifugal fan that enables a large flow rate to be sent to the fan is applied, and the flow velocity of the air flowing from the airtight door side to the fan side is increased so that the air in the pressure vessel is increased. Experiments on flow and temperature distribution were conducted. As a result, as shown in FIG. 13B, the airflow that collided with the hermetic door advances so as to crawl the lower part of the pressure vessel, thereby suppressing the retention of air in the lower part of the pressure vessel and the variation in temperature in the pressure vessel. Although some improvement was observed, sufficient effects were not obtained.
In addition, as another method for suppressing the generation of ascending airflow, a method of changing the flow of air (airflow) in the pressure vessel instead of simply increasing the flow velocity of air flowing from the airtight door side to the fan side is also conceivable. . For example, the air is discharged from the discharge port of the duct along the inner wall surface of the pressure vessel in the same circumferential direction to generate a swirling flow in the pressure vessel. According to this method, it can be expected that the entire air in the pressure vessel is moved from the airtight door side to the fan side by the swirling flow to reduce the temperature variation, but simply from the duct toward the same circumferential direction. Since only the air is discharged, the swirling flow cannot be controlled sufficiently, so that a sufficient effect as expected cannot be obtained.
Further, in Patent Document 1, as a facility for equalizing the temperature distribution, the furnace for storing the molded product has a double structure, a plurality of auxiliary heat sources are provided in the furnace, and the position of the auxiliary heat source is supported. As described above, a structure for agitating and mixing the gas in the furnace and providing a uniform temperature difference in the furnace by providing a stirring fan that rotates in the furnace is disclosed. There is a problem that the energy loss becomes extremely large because it is large compared with the vulcanized can of this type and requires a plurality of power sources.
Patent Document 2 discloses that a plurality of duct valves for opening and closing a duct are provided, and turbulent flow is generated in the furnace by opening and closing the duct valve. However, a driving source for opening and closing the duct valve is disclosed. And a control system are separately required, and problems such as an increase in equipment size and an increase in energy loss cannot be avoided.

  The present invention has been made to solve the above problems, and provides a vulcanizing can that can avoid the increase in scale and increase in energy loss, and can efficiently uniformize the temperature distribution in the pressure vessel.

As a configuration related to the vulcanizing can for solving the above problems, a heat source and a fan installed on one end side inside the cylindrical pressure vessel, and an inner wall surface extending in the extending direction of the pressure vessel is provided with a duct for discharging air blown by the fan at the other end of the pressure vessel, and the outlet of the duct, with respect to the circumferential direction of the inner wall surface, the air in the same circumferential direction at different angles from each other A plurality of plates to be discharged are provided along the circumferential direction of the pressure vessel, and the plurality of plates are twisted in the proximity of the inner wall surface at different angles from one end side to the other end side of the pressure vessel, and one end in the circumferential direction of the duct It was set as the structure arrange | positioned so that the angle to twist may become large gradually as it goes to the other end side from the side .
According to this configuration, the air heated by the heat source and flowing into the open / close end side of the pressure vessel by the fan and the plurality of ducts is directed in the circumferential direction of the pressure vessel by the plurality of plates provided at the discharge port of the duct. Because the air is discharged, the air flowing from one end side to the other end side turns into a swirl flow swirling along the circumferential direction of the pressure vessel, causing forced convection in the entire pressure vessel, and stopping in the pressure vessel. Can be eliminated. In addition, since forced convection is generated in the entire pressure vessel, air heated by the heat source is distributed in the pressure vessel, so that the temperature distribution in the pressure vessel can be made uniform. Furthermore, by controlling the direction of the plurality of plates discharged at different angles with respect to the circumferential direction, it is possible to control the spread and direction of the air discharged from the duct outlet, so that the strength of the swirling flow The size can be controlled. And the forced convection generated in the whole pressure vessel is optimized by the swirling flow whose strength and size are controlled, and the air heated by the heat source is distributed in the pressure vessel by eliminating the retention in the pressure vessel. And the temperature distribution in the pressure vessel can be made uniform. Therefore, the tire vulcanized with the vulcanizing can of the present invention can be uniformly vulcanized regardless of the position inside the pressure vessel. The size of the swirling flow is the width of the flow that flows spirally in the pressure vessel.
Further, according to this configuration, in addition to the effects of the above configuration, the plurality of plates are twisted in the inner wall proximity direction from the closed end side to the open end side in the duct, and the circumferential direction from one end side to the other end side of the duct By gradually increasing the twisting angle toward the air, the air discharged from the duct outlet toward the circumferential direction of the pressure vessel is discharged in the circumferential direction while being drawn toward the inner wall surface direction, Since the flow velocity of the air discharged from the discharge port can be increased, a strong swirling flow can be generated in the pressure vessel. In other words, since it is possible to cause forced convection in the entire pressure vessel by the strong swirl flow, there is no retention in the pressure vessel, and the temperature distribution in the pressure vessel can be made uniform.

Moreover, as another structure which concerns on the vulcanization can for solving the said subject, a some plate curves with a different curvature radius toward the other end side from the one end side of a pressure vessel, and the circumferential direction one end side in a duct The radius of curvature of curvature of the plate gradually increases from the other end toward the other end.
According to this configuration, in addition to the effects of the above configuration, the plurality of plates bend in one direction from one end side to the other end side in the duct, and extend from one end side to the other end side along the circumferential direction of the duct. As the angle of bending gradually increases, the air discharged from the duct outlet toward the circumferential direction of the pressure vessel can be discharged so as to be wider than the size of the duct, and is generated in the pressure vessel. Since the size of the swirl flow can be increased, the large swirl flow efficiently generates forced convection in the entire pressure vessel, eliminating the retention in the pressure vessel and making the temperature distribution in the pressure vessel uniform. It becomes possible to do.

Further, as another configuration related to the vulcanizing can for solving the above-described problem, the duct is disposed opposite to each other at horizontal positions on the inner wall surface circumference of the pressure vessel, and is symmetrical with respect to the center of the pressure vessel. The plate having the same shape is provided at each position in each duct.
According to this configuration, in addition to the above effects, the ducts are disposed opposite to each other at horizontal positions on the circumference of the inner wall surface of the pressure vessel, and have the same shape at symmetrical positions across the central axis of the pressure vessel. By providing the plates in the same circumferential direction, it is possible to more efficiently generate a swirling flow that is a strong forced convection along the same circumferential direction from the two ducts in the entire pressure vessel. As a result, there is no stationary region in the pressure vessel, and the temperature distribution in the pressure vessel can be made uniform.

Moreover, as another structure which concerns on the vulcanization can for solving the said subject, the length along the circumferential direction of the pressure vessel of a duct is set to 15%-20% of the inner peripheral length of a pressure vessel It was.
According to this configuration, in addition to the effects of the above configuration, the length of the duct along the circumferential direction of the pressure vessel is set to 15% to 20% of the inner circumferential length of the pressure vessel, so that Since the exhausted air and the air exhausted from the other duct do not interfere with each other so as to prevent the flow, strong forced convection can be efficiently generated in the entire pressure vessel. The stationary region in the pressure vessel is eliminated, and the temperature distribution in the pressure vessel can be made uniform.

Moreover, as another structure which concerns on the vulcanization can for solving the said subject, the plate was set as the structure provided in a duct with the space | interval of 10-30 cm.
According to this structure, in addition to the effect by the said structure, a plate can provide a swirl flow more efficiently in a pressure vessel by being provided in a duct by the space | interval of 10-30 cm.

Moreover, as another structure which concerns on the vulcanization can for solving the said subject, the plate was set as the structure set to the length of 10 cm-30 cm from the obstruction | occlusion end side to the opening end side.
According to this configuration, since the plate is set to a length of 10 cm to 30 cm from the closed end side to the open end side, the air can be discharged without impairing the flow velocity of the air sent from the fan. Can be obtained.

It is the schematic which shows the internal structure of the vulcanization can which concerns on this invention. It is a front view of a vulcanization can. It is an expansion perspective view which shows the discharge port vicinity of a duct. It is the front view and side view of a discharge plate. It is a figure which shows the direction of the air discharged | emitted from the partial duct formed in the duct. It is a figure which shows the flow after the air discharged | emitted from the duct collided with the cover body. It is a figure which shows typically the swirl | flow which generate | occur | produces in a pressure vessel. It is a graph which shows the temperature change inside the conventional vulcanization can and the vulcanization can of this invention. It is the front view and side view of another form of a discharge plate (embodiment 2). It is a figure which shows the direction of the air discharged | emitted by the partial duct from a duct (embodiment 2). It is the front view and side view of another form of a discharge plate (embodiment 3). It is a figure which shows the direction of the air discharged | emitted by the partial duct from a duct (Embodiment 3). It is a schematic diagram which shows the air flow distribution and temperature distribution inside the conventional vulcanization can. It is a disassembled perspective view and width direction sectional drawing which show a tire.

  Hereinafter, the present invention will be described in detail through embodiments of the invention. However, the following embodiments do not limit the invention according to the claims, and all combinations of features described in the embodiments are included in the invention. It is not necessarily essential to the solution, but includes a configuration that is selectively adopted.

Embodiment 1
FIG. 1 is a schematic view showing the internal structure of a vulcanizing can 1 according to the present invention.
In the figure, a vulcanizing can 1 is formed in a cylindrical shape with one end closed, and a pressure vessel 2 capable of storing a plurality of tires 10 therein, and an airtight door 3 provided at the other end of the pressure vessel 2 so as to be freely opened and closed. With.
The peripheral wall portion of the pressure vessel 2 is lined with a heat insulating material (not shown) arranged in the circumferential direction without any gap, and a vulcanization capable of storing and vulcanizing a plurality of tires 10 inside. Region R1 is formed.

  The hermetic door 3 is a door that can be freely opened and closed at the open end of the pressure vessel 2, and is formed concentrically with the cylindrical pressure vessel 2. The hermetic door 3 closes the opening of the pressure vessel 2 through a seal material (not shown) disposed around the airtight door 3, and prevents the air supplied into the pressure vessel 2 from leaking to the outside. That is, the pressure vessel 2 with one end closed is maintained as a sealed space by closing the other end with the airtight door 3. The back side of the hermetic door 3 that forms a sealed space together with the pressure vessel 2 is formed in a spherical shape on the opposite side to the pressure vessel 2 so that the central axis of the pressure vessel 2 and the center of the spherical surface are concentric. .

  A floor plate 4 extending along the extending direction of the pressure vessel 2 is laid in the lower half of the pressure vessel 2. When carrying into the pressure vessel 2, a plurality of tires 10 are carried from the open / close end side where the airtight door 3 is provided to the closed end side using a cart or the like that can travel on the floor plate 4. The plurality of tires 10 are stored side by side along the extending direction of the pressure vessel 2 by being suspended in order by hooks (not shown) provided in the case.

  Here, the tire 10 stored in the vulcanizing can 1 according to the present embodiment will be outlined. FIG. 14 is an exploded perspective view and a cross-sectional view in the width direction showing an unvulcanized retread tire as an example of the tire 10 vulcanized by the vulcanizing can 1. As shown in the figure, the tire 10 includes a base tire 11 as a base, a cushion rubber 12 attached to a circumferential surface of the base tire 11, and a circumference of the base tire 11 via the cushion rubber 12. The tread rubber 13 is wound around the directional surface.

  The base tire 11 includes a pair of bead portions 11A made of a member such as an annular steel cord, and a side portion 11B and a crown portion 11C that extend in a toroidal shape so as to straddle the pair of bead portions 11A. A plurality of belts are stacked in the radial direction inside the crown portion 11C. The base tire 11 can be obtained, for example, by cutting (buffing) a tread portion of a used tire or by vulcanizing with a mold that does not have irregularities corresponding to the tread pattern on the surface. Moreover, the vulcanization degree of the base tire 11 may be a semi-vulcanized state equal to or lower than the vulcanization degree required for the product tire.

  The cushion rubber 12 is an unvulcanized rubber having substantially the same composition as the base tire 11 and the tread rubber 13, and is vulcanized by the vulcanizing can 1 so that the base tire 11 and the tread rubber 13 are integrated. Functions as an adhesive layer. The tread rubber 13 is a belt having a length corresponding to the circumferential length of the base tire 11, and is vulcanized in a state of being wound on the crown part 11C of the base tire 11, so that the tread part of the product tire It is a member. The belt-like tread rubber 13 can be obtained, for example, by vulcanizing with a press-type vulcanizing device in which unevenness corresponding to a desired tread pattern is formed on one mold.

Further, the belt-shaped tread rubber 13 obtained by the press-type vulcanizer is wound along the circumferential surface of the base tire 11 on which the cushion rubber 12 is adhered, and the ends are joined together. Preliminarily integrated with the base tire 11.
In addition, the molding apparatus of the tread rubber 13 is not limited to the press die, and for example, the tread rubber 13 may be vulcanized by a dedicated mold capable of molding the annular tread rubber 13. In order to wind the annular tread rubber 13 formed by the dedicated mold around the base tire 11, the tread rubber 13 is expanded on the outer peripheral side of the base tire 11 while the diameter of the tread rubber 13 is expanded by a non-illustrated diameter expanding device. And then reducing the diameter to the original outer diameter again. Further, the degree of vulcanization of the tread rubber 13 may be in a semi-vulcanized state equal to or less than the degree of vulcanization required for the product tire, similarly to the base tire 11.

The tire 10 having the above-described configuration is accommodated in a non-illustrated bag called an envelope and is suspended in the pressure vessel 2. The pressure in the envelope is reduced to atmospheric pressure or less, and the inner surface of the envelope is in close contact with the outer surface of the tread rubber 13. That is, when the tire 10 is accommodated in the envelope, the tread rubber 13 is maintained in a state of being pressed against the circumferential surface of the base tire 11.
In addition, although the retread tire provided with the vulcanized base tire 11 and the vulcanized tread rubber 13 was demonstrated as an example of the tire 10 stored in the pressure vessel 2 of the vulcanization can 1, vulcanization | cure is demonstrated. The tire 10 stored in the can 1 is not limited to the above configuration, and any tire may be used as long as the molding process includes a vulcanization process.

Returning to FIG. 1, the structure of the pressure vessel 2 will be described again.
An air supply region R <b> 2 is formed on the closed end side in the pressure vessel 2. The air supply region R2 is a region formed by the partition wall 7 that partitions the vulcanization region R1, and a heat source 5 and a fan 6 that circulate while heating the air in the vulcanization region R1 are installed in the region. The

The heat source 5 is disposed at the center in the partition wall 7. The heat source 5 is a heater that is electrically heated, for example, and generates heat to a predetermined temperature by controlling the power supplied to the heater.
The fan 6 is disposed on the closed end side with respect to the heat source 5, and includes a motor 6A and a rotary blade 6B that rotates by driving of the motor 6A. The fan 6 is driven by the motor 6A so that the rotor blades 6B rotate and heat the heat source 5 while taking the air in the vulcanization region R1 into the air supply region R2, and compress the air in the air supply region R2. And air is sent out to the discharge port 9B of the below-mentioned duct 8 opened by the airtight door 3 side.
In other words, when the fan 6 is driven, the air flowing from the vulcanization region R1 side to the air supply region R2 side is heated by the heat source 5 and the air pressure in the air supply region R2 is increased, thereby providing the air supply region R2. In addition, air is caused to flow into the intake ports 9A of the plurality of ducts 8 and the heated air is discharged from the discharge ports 9B of the ducts 8 opened on the airtight door 3 side.

As shown in FIG. 1, the duct 8 is a pipe that extends from the air supply region R <b> 2 to the airtight door 3 side through the vulcanization region R <b> 1 along the extending direction of the inner peripheral wall surface 2 </ b> A of the pressure vessel 2. As shown in the front view of the vulcanizing can 1 in FIG. 2, the duct 8 in this embodiment is disposed at two locations on the inner peripheral wall surface 2A of the pressure vessel 2 (hereinafter referred to as ducts 8A and 8B). . The ducts 8A and 8B have the same dimensions.
One duct 8 </ b> A and the other duct 8 </ b> B are disposed at horizontal positions at equal intervals so as to face each other in the circumferential direction of the inner peripheral wall surface 2 </ b> A of the pressure vessel 2. Specifically, a horizontal plane passing through the vulcanization can center O is disposed so as to pass through the centers of the duct 8A and the duct 8B.
The ducts 8A and 8B are tubular bodies having a rectangular cross section extending along the extending direction of the pressure vessel 2, and a discharge port 9B for discharging the air heated by the heat source 5 opens on the airtight door 3 side.
That is, the air heated and sent by the heat source 5 and the fan 6 positioned on the closed end side of the pressure vessel 2 is discharged toward the airtight door 3 positioned on the open / close end side through the ducts 8A and 8B.

FIG. 3 is an enlarged perspective view showing the vicinity of the discharge port 9 </ b> B of the duct 8 </ b>A; 8 </ b> B that discharges air toward the hermetic door 3. Hereinafter, a description will be given with reference to FIGS.
As shown in FIG. 3, the ducts 8 </ b>A; 8 </ b> B are connected to the pair of plate pieces 21; 21 and the pair of plate pieces 21; 21 rising from the inner peripheral wall surface 2 </ b> A of the pressure vessel 2. A tubular body is formed by the inner peripheral wall surface 2A and the air guide plate 22 facing the inner wall surface 2A.
The plate pieces 21; 21 are provided at a predetermined distance from each other and extend from the inner peripheral wall surface 2 A of the pressure vessel 2 toward the vulcanization can center O with the same length. The separation distance N of the plate pieces 21; 21 is set so as to be separated by at least a distance smaller than 25% of the circumferential length M of the inner peripheral wall surface 2A. Preferably, the separation distance N of the plate pieces 21; 21 may be provided so as to be separated in a range of 15 to 20% of the circumferential length M of the inner peripheral wall surface 2A.
The plate pieces 21; 21 extend in the vulcanization can center O direction, but may be provided so as to extend in the horizontal direction from the inner peripheral wall surface 2A.

  For example, the air guide plate 22 is curved along the inner peripheral wall surface 2A of the pressure vessel 2 and is connected to the plate pieces 21; 21. Note that when the diameter of the tire 10 to be vulcanized by the vulcanizing can 1 is substantially the same size, the air guide plate 22 may be formed so as to correspond to the curvature of the outer peripheral surface of the tire 10. However, if the distance between the air guide plate 22 and the outer peripheral surface of the tire is equal to or less than a predetermined distance, the air exhausted to the open / close end side is obstructed to flow to the closed end side, and the tire may not be uniformly vulcanized. It is preferable to adjust the lengths of the plate pieces 21 and 21 so that the distance S between the air guide plate 22 and the tire outer peripheral surface does not become a predetermined distance or less.

  A plurality of discharge plates are respectively provided along the circumferential direction of the inner peripheral wall surface 2A at the discharge port 9B of the duct 8A; 8B. In the present embodiment, the description will be made assuming that five discharge plates 31 to 35 are provided in each of the ducts 8A and 8B. In addition, what is necessary is just to set the quantity of the discharge | emission plate not only with the said number of sheets but appropriate.

4A is a front view of the discharge plates 31 to 35, and FIG. 4B is a side view of the discharge plates 31 to 35.
The discharge plates 31 to 35 are plate bodies formed in a predetermined shape, and are formed so as to have different shapes. Specifically, as shown in FIGS. 4A and 4B, the discharge plates 31 to 35 are formed to be curved in one direction with different curvatures along the extending direction. For example, the curvature of the discharge plate 31 is the smallest, the curvature of the discharge plate 32 is the second smallest, the curvature of the discharge plate 33 is the third smallest, and the curvature of the discharge plate 34 is the fourth. Next, the curvature of the discharge plate 35 is the fifth smallest. In other words, the curvature of curvature of the discharge plate 31, the discharge plate 32, the discharge plate 32, the discharge plate 33, the discharge plate 34, and the discharge plate 35 is set so as to increase. The lengths of the discharge plates 31 to 35 are set so that the linear length L from the rear end portions 31B to 35B to the front end portions 31A to 35A is 10 cm to 30 cm (see FIG. 4). A necessary and sufficient effect can be obtained by setting the lengths of the discharge plates 31 to 35 to 10 cm to 30 cm. That is, when the length of the discharge plates 31 to 35 is shorter than 10 cm, the air discharged from the discharge port 9B cannot be sufficiently directed. Even if the length of the discharge plates 31 to 35 is longer than 30 cm, no change is observed in the orientation of the air discharged from the discharge port 9B. Furthermore, since the space problem when attaching discharge plate 31 thru | or 35 in duct 8A, 8B and the effort concerning attachment will also increase, it is preferable to set length to 10 cm-30 cm.
Note that the curves of the discharge plates 31 to 35 may be formed with a uniform radius of curvature from the rear end portions 31B to 35B to the front end portions 31A to 35A, and from the rear end portions 31B to 35B to the front end portions 31A to 35A. You may form so that it may curve locally in the middle of.

2 and 3, the discharge plates 31 to 35 will be described.
In each duct 8A, 8B, the discharge plates 31 to 35 are fixed between the inner peripheral wall surface 2A of the pressure vessel 2 and the air guide plate 22 of the duct 8 through fastening means (not shown) or by welding, The tip portions 31A to 35A terminate at substantially the same position as the discharge port 9B.
The discharge plates 31 to 35 are arranged at predetermined intervals along the circumferential direction in each of the ducts 8A and 8B. For example, the discharge plates 31 to 35 are evenly distributed along the circumferential direction so that the rear end portions 31B to 35B of the discharge plates 31 to 35 coincide with virtual radiation extending radially from the vulcanization can center O. Arranged at intervals.
In each of the ducts 8A and 8B, the discharge plates 31 to 35 have a curved curvature that increases in the direction in which the discharge plates 31 to 35 are curved in the same circumferential direction and from one end side to the other end side in the circumferential direction in each duct 8A and 8B. It is provided to become.

  Specifically, in one duct 8A, the discharge plates 31 to 35 are provided such that the direction of curve is downward, the discharge plate 31 having the smallest curvature is disposed at the top, and the discharge plate is disposed below the discharge plate 31. 32, the discharge plate 33, the discharge plate 34, the discharge plate 35, and the discharge plate 35 are arranged in this order so that the curvature gradually increases from top to bottom. In the other duct 8B, the discharge plates 31 to 35 are provided so that the curved direction is upward, the discharge plate 31 having the smallest curvature is disposed at the bottom, and the discharge plate 32, the discharge plate 33, The discharge plate 34, the discharge plate 35, and the discharge plate 35 are arranged in this order so that the curvature gradually increases from the bottom to the top.

  Therefore, the discharge plates 31 to 35 disposed in the ducts 8A and 8B have the same shape at positions facing each other across the vulcanization can center O with the curving direction facing the same circumferential direction. Provided. In other words, the discharge plates 31 to 35 provided in the duct 8A are rotated by 180 ° around the vulcanization can center O to be provided in the duct 8B.

Since the discharge plates 31 to 35 are provided in the ducts 8A and 8B, partial ducts A to F partitioned by the discharge plates 31 to 35 are formed in the discharge port 9B.
In the duct 8A, the partial duct A is formed by the discharge plate 31, the inner peripheral wall surface 2A, the plate piece 21, and the air guide plate 22, and the partial duct B is guided by the discharge plate 31, the discharge plate 32, and the inner peripheral wall surface 2A. The partial duct C is formed by the discharge plate 32, the discharge plate 33, the inner peripheral wall surface 2A, and the air guide plate 22, and the partial duct D is formed by the discharge plate 33, the discharge plate 34, and the inner periphery. The wall surface 2A and the air guide plate 22 are formed. The partial duct E is formed by the discharge plate 34, the discharge plate 35, the inner peripheral wall surface 2A and the air guide plate 22. The partial duct F is formed by the discharge plate 35 and the plate piece. 21, the inner peripheral wall surface 2 </ b> A, and the air guide plate 22.

  In the duct 8B, the partial duct A is formed by the discharge plate 31, the inner peripheral wall surface 2A, the plate piece 21, and the air guide plate 22, and the partial duct B is formed by the discharge plate 31, the discharge plate 32, and the inner peripheral wall surface 2A. The partial duct C is formed by the discharge plate 32, the discharge plate 33, the inner peripheral wall surface 2A, and the wind guide plate 22. The partial duct D is formed by the discharge plate 33, the discharge plate 34, and the discharge plate 34. The inner peripheral wall surface 2A and the air guide plate 22 are formed. The partial duct E is formed by the discharge plate 34, the discharge plate 35, the inner peripheral wall surface 2A and the air guide plate 22. The partial duct F is formed by the exhaust plate 35 and the air guide plate 22. The plate piece 21, the inner peripheral wall surface 2 </ b> A, and the air guide plate 22 are formed.

FIG. 5A is a diagram showing the direction of air discharged by the partial ducts A to F formed in the duct 8A, and FIG. 5B is discharged by the partial ducts A to F formed in the duct 8B. It is a figure which shows the direction of the air.
As shown in FIG. 5A, the air discharged from the partial duct A of the duct 8A is discharged along the inner peripheral wall surface 2A slightly downward with respect to the extending direction of the duct 8A and discharged from the partial duct B. The air is discharged along the inner peripheral wall surface 2A downward from the air discharged from the partial duct A, and the air discharged from the partial duct C is directed downward to the inner peripheral wall surface 2A than the air discharged from the partial duct B. The air discharged from the partial duct D is discharged along the inner peripheral wall surface 2A downward from the air discharged from the partial duct C, and the air discharged from the partial duct E is discharged from the partial duct D. The air discharged from the partial duct F is discharged downward along the inner peripheral wall surface 2A downward from the air discharged from the partial duct E. . That is, the air that has passed through the duct 8A is discharged by the partial ducts A to F in the same circumferential direction along the inner peripheral wall surface 2A at different angles in a direction different from the extending direction of the duct 8A.

Further, as shown in FIG. 5 (b), the air discharged from the partial duct A of the duct 8B is discharged along the inner peripheral wall surface 2A slightly upward with respect to the extending direction of the duct 8A and from the partial duct B. The discharged air is discharged along the inner peripheral wall surface 2A upward from the air discharged from the partial duct A, and the air discharged from the partial duct C is higher than the air discharged from the partial duct B. The air discharged along the inner peripheral wall surface 2A and discharged from the partial duct D is discharged along the inner peripheral wall surface 2A upward from the air discharged from the partial duct C, and discharged from the partial duct E. Is exhausted along the inner peripheral wall surface 2A upward from the air exhausted from the partial duct D, and the air exhausted from the partial duct F is upward from the air exhausted from the partial duct E. It is discharged along. That is, the air that has passed through the duct 8B is discharged by the partial ducts A to F in the same circumferential direction along the inner peripheral wall surface 2A at different angles in a direction different from the extending direction of the duct 8B.
Therefore, the flow of air discharged from the partial ducts A to F formed in the duct 8A and the duct 8B is a unidirectional flow around the vulcanization can center O.

FIG. 6 is a diagram illustrating a flow when the air discharged from the duct 8 </ b> A and the duct 8 </ b> B collides with the back surface 3 </ b> A of the airtight door 3. In the same figure, the arrow shown as a continuous line shows the flow of the air discharged | emitted from the duct 8A, and the arrow shown with a broken line shows the flow of the air discharged | emitted from the duct 8B.
As shown in FIG. 6, the air discharged by being directed in different directions by the discharge plates 31 to 35 of the ducts 8A and 8B collides with the back surface 3A of the hermetic door 3, and crosses the back surface 3A. Flowing. Specifically, the air discharged from the partial duct A of the duct 8A flows so as to cross slightly below the center of the hermetic door 3 on the back surface 3A of the hermetic door 3, and the air discharged from the partial duct B is backside. 3A flows below the flow of air discharged from the partial duct A, and the air discharged from the partial duct C flows below the flow of air discharged from the partial duct B on the back surface 3A. The air discharged from D flows below the flow of air discharged from the partial duct C on the back surface 3A, and the air discharged from the partial duct E flows from the flow of air discharged from the partial duct D on the back surface 3A. Also, the air discharged from the partial duct F flows below the flow of the air discharged from the partial duct E on the back surface 3A.

The air discharged from the duct 8B flows on the back surface 3A of the hermetic door 3 slightly above the center of the hermetic door 3 so as to cross the air discharged from the duct 8A in the opposite direction, and is discharged from the partial duct A. The air that has been discharged flows so as to cross slightly above the center of the back surface 3A, the air discharged from the partial duct B flows above the air flow discharged from the partial duct A on the back surface 3A, and from the partial duct C. The discharged air flows above the flow of air discharged from the partial duct B on the back surface 3A, and the air discharged from the partial duct D flows above the flow of air discharged from the partial duct C on the back surface 3A. The air discharged from the partial duct E flows above the flow of the air discharged from the partial duct D on the back surface 3A and is discharged from the partial duct F. Air flows through the upper side of the flow of air discharged from the partial duct E on the back surface 3A.
That is, the air discharged from the duct 8A is discharged in the opposite direction to the air discharged from the duct 8A, so that the air discharged from the duct 8A and the duct 8B is the same on the inner peripheral surface of the pressure vessel 2. It will flow in the circumferential direction. Therefore, the air discharged from the duct 8A and the duct 8B collides with the back surface 3A of the hermetic door 3 and flows across the back surface 3A, and then turns into the swirl flows F1 and F2 in the pressure vessel 2 and opens and closes. To the closed end side (see FIG. 7).

  As described above, the ducts 8A and 8B are disposed opposite to each other at horizontal positions on the inner wall surface circumference of the pressure vessel, and the discharge plates 31 to 35 are curved at different angles to the ducts 8A and 8B. In the ducts 8A and 8B, the curvatures of the discharge plates 31 to 35 are gradually increased in one direction, so that the ducts 8A and 8B have the same circumferential direction. The flow of the air blown out from each discharge port 9B of 8B flows as shown in FIGS. 5 and 6, and the swirl flows F1 and F2 can be generated over the entire pressure vessel 2. Further, by setting the length X along the circumferential direction of the duct 8A; 8B to 25% or less of the circumferential length L of the inner peripheral wall surface 2A, as shown in FIG. 6, the air discharged from the duct 8A and the duct The air discharged from 8B is prevented from interfering with each other, and a swirling flow can be efficiently generated.

FIG. 7 is a diagram schematically showing a swirling flow generated in the pressure vessel 2. In the figure, the solid line indicates the flow of air from the duct 8A, and the broken line indicates the flow of air from the duct 8B.
As shown in the figure, air that passes through the discharge plates 31 to 35 of the ducts 8A and 8B and is discharged from the partial ducts A to F at different angles is airtight along the circumferential direction of the inner peripheral wall surface 2A. It collides with the door 3 and flows so as to cross along the back surface 3A of the hermetic door 3. The air flowing through the back surface 3A of the hermetic door 3 flows at a different angle with respect to the inner peripheral wall surface 2A, thereby generating a rotating flow along the circumferential direction of the inner peripheral wall surface 2A. Let Furthermore, the rotating air flows spirally from the hermetic door 3 side to the closed end side so as to draw a circle along the inner peripheral wall surface 2A, becomes a swirling flow in the pressure vessel 2, and is provided in the partition wall 7. It passes through the heat source 5 and is taken into the air supply region R2.

Specifically, the air discharged in a state directed by the discharge plates 31 to 35 of the duct 8A flows downward at different angles along the inner peripheral wall surface 2A to become one swirl flow F1 shown in FIG. The air discharged from the discharge plate 20 of the duct 8B flows upward along the inner peripheral wall surface 2A and becomes the other swirl flow F2 shown in FIG. In addition, since the ducts 8A and 8B are equally provided so as to face each other, the swirling flows F1 and F2 are flows that are shifted from each other by a half cycle.
One swirl flow F1, as shown in the figure, is a flow F1A discharged from the partial duct A of the duct 8A, a flow F1B discharged from the partial duct B, a flow F1C discharged from the partial duct C, and a partial duct D. Formed by the flow F1D discharged from the flow, the flow F1E discharged from the partial duct E, and the flow F1F discharged from the partial duct F. The other swirl flow F2 is a flow F2A discharged from the partial duct A of the duct 8B, a flow F2B discharged from the partial duct B, a flow F2C discharged from the partial duct C, and a flow discharged from the partial duct D. F2D, the flow F2E discharged from the partial duct E, and the flow F2F discharged from the partial duct F are formed. That is, by changing the curvature of curvature of the discharge plates 31 to 35 constituting the partial ducts A to F, the width W of the swirl flow F1 from the flow F1A to the flow F1F and the swirl flow from the flow F2A to the flow F2F. The width W of F2 can be controlled. Therefore, by changing the curvature of curvature of the discharge plates 31 to 35 so that the distance between the flow F1F of the swirl flow F1 and the flow F2A of the swirl flow F2 approaches, the swirl flow F1, over the entire vulcanization region R1. F2 can be generated.

  FIG. 8A shows a graph showing the temperature change inside the conventional vulcanizing can, and FIG. 8B shows a graph showing the temperature change of the vulcanizing can 1 of the present invention. FIG. 8 (a) shows the time change of the temperature on the airtight door 3 side and the temperature on the air supply region R2 side in the lower part in the vulcanization region of the conventional vulcanizing can (position corresponding to P1; Q1 in FIG. 7). It is a graph. FIG. 8B shows the temperature change at the same position P1; Q1 at which the temperature was measured in FIG. 8A and the temperature change at the upper position P2; Q2 facing the position P1; Q1. (See FIG. 7).

In the conventional vulcanizing can, as shown in FIG. 8 (a), the temperature at the position P1 at the lower part on the airtight door 3 side rapidly rises compared with the temperature at the position Q1 at the lower part on the air supply region side. Is heated in a state in which a temperature difference of about 20 ° C. has occurred until the temperature becomes constant. Then, a difference of about 20 minutes occurs between the temperature at the position P1 and the temperature at the position Q1 reaching the maximum temperature.
On the other hand, in the vulcanizing can 1 according to the present embodiment, as shown in FIG. 8 (b), the temperature P1 on the airtight door 3 side and the lower position P1; the temperature of P2; After the temperature of Q2 rises to approximately 60 ° C. with substantially the same temperature gradient, the temperature between the position P1 on the hermetic door 3 side; the temperature at position P2 and the position Q1 on the air supply region R2 side; However, the temperature rises again with substantially the same temperature gradient.

As is clear from the figure, the temperature difference between the position P1; P2 on the airtight door 3 side and the position Q1; Q2 on the air supply region R2 side is about 3 ° C. It is very small compared to the temperature difference generated in the can. That is, in the vulcanizing can 1 of the present invention, the discharge plates 31 to 35 that are curved at a plurality of different angles are provided in the ducts 8A and 8B so that the curvature of curvature gradually increases, and the swirl flow over the entire vulcanization region R1. By generating F1 and F2 and circulating the air heated by the fan 6, the temperature in the pressure vessel 2 can be raised substantially uniformly.
That is, in the vulcanizing can 1 of the present invention, the temperature in the pressure vessel 2 rises almost uniformly in the extension direction, and therefore, in vulcanizing a plurality of tires 10 stored side by side along the extension direction of the pressure vessel 2. The tire 10 can be vulcanized by a uniform temperature rise regardless of the position where the tire 10 is stored. Furthermore, since the temperature rises uniformly at the upper and lower parts of the pressure vessel 2, the individual tires can be heated uniformly by the uniform temperature rise from the circumferential direction, and the entire tire can be uniformly vulcanized. be able to.

Embodiment 2
In the first embodiment, the plurality of discharge plates 31 to 35 are formed to bend with different curvatures. However, in the second embodiment, the discharge plates 31 to 35 are unidirectionally directed from the rear end portions 31B to 35B toward the front end portions 31A to 35A. It differs from the first embodiment in that it is formed to be twisted at a different angle.

9A is a front view of the discharge plates 31 to 35 according to the second embodiment, and FIG. 9B is a side view of the discharge plates 31 to 35 according to the second embodiment.
Hereinafter, this embodiment will be described with reference to FIG. In addition, about the same structure as Embodiment 1, the same code | symbol is attached | subjected and description is abbreviate | omitted. In addition, the structure of each duct 8A; 8B and the space | interval in which each discharge plate 31 thru | or 35 is provided are demonstrated as the same thing as Embodiment 1. FIG.

  The discharge plates 31 to 35 according to the second embodiment are twisted toward the inner peripheral wall surface at different angles from the rear end portions 31B to 35B toward the front end portions 31A to 35A. In the present embodiment, when the discharge plates 31 to 35 are viewed from the front in a state where the discharge plates 31 to 35 are disposed in the duct A, the tip portions 31A to 35A have the air guide plate 22 side within the tip portions 31A to 35A. It demonstrates as what is twisted so that it may rotate in the clockwise direction with respect to the surrounding wall surface 2 side, and it may approach 2 A of inner wall surfaces (FIG. 9). In the discharge plates 31 to 35, the twist angle of the discharge plate 31 is the smallest, the twist angle of the discharge plate 32 is the second smallest, and the twist angle of the discharge plate 33 is the third smallest. The twist angle of the discharge plate 34 is the fourth smallest, and the twist angle of the discharge plate 35 is the fifth smallest. In other words, the angle of twisting in the order of the discharge plate 31, the discharge plate 32, the discharge plate 32, the discharge plate 33, the discharge plate 34, and the discharge plate 35 is set to increase. Further, the discharge plates 31 to 35 are arranged so that the twisting angle gradually increases from one end side to the other end side in the circumferential direction of the ducts 8A and 8B. The lengths of the discharge plates 31 to 35 are set so that the linear length L from the rear end portions 31B to 35B to the front end portions 31A to 35A is 10 cm to 30 cm.

Specifically, in one duct 8A, the discharge plate 31 with the smallest twisting angle is at the top, and below that is the discharge plate 32, the discharge plate 33, the discharge plate 34, and the discharge plate 35 in this order from top to bottom. The twisting angle is gradually increased.
Further, in the other duct 8B, the discharge plates 31 to 35 are provided so that the leading end portions 31A to 35A on the leading wind plate 22 side are clockwise and close to the inner peripheral wall surface 2A, and the discharge plate having the smallest twisting angle is provided. 31 is arranged at the bottom, and the discharge plate 32, the discharge plate 33, the discharge plate 34, and the discharge plate 35 are arranged so that the twisting angle from the bottom to the top gradually increases.
Therefore, the partial ducts A to F partitioned by the discharge plates 31 to 35 are formed at the discharge ports of the ducts 8A and 8B.

  FIG. 10 is a diagram showing the direction of air discharged by the partial ducts A to F formed in the duct 8A. As shown in the figure, the air discharged from the partial duct A of the duct 8A is slightly downward along the inner peripheral wall surface 2A so as to be pressed against the inner peripheral wall surface 2A by the twist of the tip 31A of the discharge plate 31. Discharged. Further, the air discharged from the partial duct B is pressed more strongly against the inner peripheral wall surface 2A than the air discharged from the partial duct A due to twisting of the distal end portion 31A of the discharge plate 31 and the distal end portion 32A of the discharge plate 32. Then, it is discharged downward along the inner peripheral wall surface 2A. Further, the air discharged from the partial duct C is pressed more strongly against the inner peripheral wall surface 2A than the air discharged from the partial duct B due to the twist of the distal end portion 32A of the discharge plate 32 and the distal end portion 33A of the discharge plate 33. Then, it is discharged downward along the inner peripheral wall surface 2A. Further, the air discharged from the partial duct D is pressed against the inner peripheral wall surface 2A more strongly than the air discharged from the partial duct C due to twisting of the distal end portion 33A of the discharge plate 33 and the distal end portion 34A of the discharge plate 34. Then, it is discharged downward along the inner peripheral wall surface 2A. Further, the air discharged from the partial duct E is pressed against the inner peripheral wall surface 2A more strongly than the air discharged from the partial duct D due to twisting of the distal end portion 34A of the discharge plate 34 and the distal end portion 35A of the discharge plate 35. Then, it is discharged downward along the inner peripheral wall surface 2A. Further, the air discharged from the partial duct F is along the inner peripheral wall surface 2A so that the air is pressed against the inner peripheral wall surface 2A more strongly than the air discharged from the partial duct E due to the twist of the tip portion 35A of the discharge plate 35. It is discharged downward.

  Further, the air discharged from the partial duct A of the duct 8B is discharged slightly upward along the inner peripheral wall surface 2A so as to be pressed against the inner peripheral wall surface 2A due to the twist of the distal end portion 31A of the discharge plate 31. Further, the air discharged from the partial duct B is pressed more strongly against the inner peripheral wall surface 2A than the air discharged from the partial duct A due to twisting of the distal end portion 31A of the discharge plate 31 and the distal end portion 32A of the discharge plate 32. Then, it is discharged upward along the inner peripheral wall surface 2A. Further, the air discharged from the partial duct C is pressed more strongly against the inner peripheral wall surface 2A than the air discharged from the partial duct B due to the twist of the distal end portion 32A of the discharge plate 32 and the distal end portion 33A of the discharge plate 33. Then, it is discharged upward along the inner peripheral wall surface 2A. Further, the air discharged from the partial duct D is pressed against the inner peripheral wall surface 2A more strongly than the air discharged from the partial duct C due to twisting of the distal end portion 33A of the discharge plate 33 and the distal end portion 34A of the discharge plate 34. Then, it is discharged upward along the inner peripheral wall surface 2A. Further, the air discharged from the partial duct E is pressed against the inner peripheral wall surface 2A more strongly than the air discharged from the partial duct D due to twisting of the distal end portion 34A of the discharge plate 34 and the distal end portion 35A of the discharge plate 35. Then, it is discharged upward along the inner peripheral wall surface 2A. Further, the air discharged from the partial duct F is along the inner peripheral wall surface 2A so that the air is pressed against the inner peripheral wall surface 2A more strongly than the air discharged from the partial duct E due to the twist of the tip portion 35A of the discharge plate 35. It is discharged upward.

  That is, the air that has passed through the duct 8B is discharged in a direction different from the circumferential direction by the plurality of partial ducts A to F formed by the plurality of discharge plates 31 to 35 of the discharge port 9B, and is formed in the duct 8A. The flow of air discharged from the partial ducts A to F and the flow of air discharged from the partial ducts A to F formed in the duct 8B are point-symmetrical flows around the vulcanization can center O.

Even if the discharge plates 31 to 35 are configured as in the present embodiment, the swirl flows F1 and F2 can be generated over the entire pressure vessel 2.
That is, the discharge plates 31 to 35 are twisted from the rear end portions 31B to 35B toward the front end portions 31A to 35A at different angles in the inner peripheral surface proximity direction, and twisted along the circumferential direction of the ducts 8A and 8B. By arranging so that the angle gradually increases, the air discharged from the partial ducts A to F formed in each of the ducts 8A and 8B is circumferentially along the inner peripheral wall surface 2A as shown in FIG. The flow flows at different angles and different strengths, and flows across the back surface 3A of the hermetic door 3 as shown in FIG. 6, so that swirl flows F1 and F2 over the entire pressure vessel 2 as shown in FIG. Can be generated.
Therefore, the temperature in the pressure vessel 2 can be raised substantially uniformly in the extending direction, so that the tire 10 is stored in the vulcanization of the plurality of tires 10 stored side by side along the extending direction of the pressure vessel 2. Regardless of the position, vulcanization can be achieved by a uniform temperature rise. Furthermore, since the temperature rises uniformly at the upper and lower parts of the pressure vessel 2, the individual tires can be heated uniformly by the uniform temperature rise from the circumferential direction, and the entire tire can be uniformly vulcanized. be able to.

Embodiment 3
In the first embodiment, the plurality of discharge plates 31 to 35 are formed to be curved along the extension direction with different curvatures, and in the second embodiment, the discharge plates 31 to 35 are changed from the rear end portions 31B to 35B to the front end portions 31A to 35A. In this embodiment, the plurality of discharge plates 31 to 35 are formed to be curved along the extension direction with different curvatures, and the rear end in the extension direction is formed. It differs from the first and second embodiments in that it is formed so as to be twisted at different angles in one direction from the portions 31B to 35B toward the tip portions 31A to 35A.

  FIG. 11A is a front view of the discharge plates 31 to 35 according to the third embodiment, and FIG. 11B is a side view of the discharge plates 31 to 35 according to the third embodiment. Hereinafter, this embodiment will be described with reference to FIG. In addition, about the same structure as Embodiment 1, the same code | symbol is attached | subjected and description is abbreviate | omitted. In addition, the structure of each duct 8A; 8B and the space | interval which each discharge plate 31 thru | or 35 space | separate are demonstrated as the same thing as Embodiment 1. FIG.

The discharge plates 31 to 35 in the third embodiment are curved in one direction with different curvatures along the extending direction, and the inner peripheral wall surface at different angles in one direction from the rear end portions 31B to 35B toward the front end portions 31A to 35A. Twist in the close direction. As for the direction in which the discharge plates 31 to 35 are twisted, when the discharge plates 31 to 35 are viewed from the front in a state where the discharge plates 31 to 35 are disposed in the duct A, the air guide plates of the tip portions 31A to 35A. Description will be made assuming that the 22 side rotates clockwise with respect to the inner peripheral wall surface 2 side of the tip portions 31A to 35A and is twisted so as to approach the inner peripheral wall surface 2A (FIG. 11).
For example, in the discharge plates 31 to 35, the curvature and twist angle of the discharge plate 31 are the smallest, the curvature and twist angle of the discharge plate 32 are the second smallest, and the curvature and the twist of the discharge plate 33 are next. The twisting angle is the third smallest, the curvature of the discharge plate 34 and the twisting angle are the fourth smallest, and the curvature and the twisting angle of the discharge plate 35 are the fifth smallest. In other words, the curvature and the twisting angle of the discharge plate 31, the discharge plate 32, the discharge plate 32, the discharge plate 33, the discharge plate 34, and the discharge plate 35 are set so as to increase. The discharge plates 31 to 35 are set so that the linear length from the rear end portions 31B to 35B to the front end portions 31A to 35A is 10 cm to 30 cm.

Specifically, in one duct 8A, the discharge plates 31 to 35 are provided with a curved curvature downward, and the discharge plate 31 having the smallest curvature and twisting angle is disposed at the top, and below that. The discharge plate 32, the discharge plate 33, the discharge plate 34, and the discharge plate 35 are arranged so that the curvature and the twisting angle are gradually increased from the top to the bottom.
Further, in the other duct 8B, the discharge plates 31 to 35 are provided with the curved direction facing upward, the discharge plate 31 having the smallest curvature and twisting angle is disposed at the bottom, and the discharge plate is disposed thereon. 32, the discharge plate 33, the discharge plate 34, and the discharge plate 35 are arranged so that the curvature of curvature and the twisting angle gradually increase from the bottom to the top.
Therefore, the partial ducts A to F partitioned by the discharge plates 31 to 35 are formed at the discharge ports of the ducts 8A and 8B.

FIG. 12 is a diagram showing the direction of air discharged by the partial ducts A to F formed in the duct 8A. As shown in the figure, the air discharged from the partial duct A of the duct 8A is slightly downward with respect to the extending direction of the duct 8A due to the twist of the tip 31A in addition to the curvature of the discharge plate 31, and the inner periphery. It is discharged so as to be pressed against the wall surface 2A. In addition to the curvature of the discharge plates 31 and 32, the air discharged from the partial duct B faces downward from the air discharged from the partial duct A due to the twisting of the tip portions 31 </ b> A and 32 </ b> A and to the inner peripheral wall surface 2 </ b> A. It is discharged so as to be pressed. In addition to the curvature of the discharge plates 32 and 33, the air discharged from the partial duct C faces downward from the air discharged from the partial duct B due to the twisting of the tip portions 32A and 33A, and on the inner peripheral wall surface 2A. It is discharged so as to be pressed. In addition to the curvature of the discharge plates 33 and 34, the air discharged from the partial duct D faces downward from the air discharged from the partial duct C due to the twisting of the tip portions 33A and 34A, and is directed to the inner peripheral wall surface 2A. It is discharged so as to be pressed. In addition to the curvature of the discharge plates 34 and 35, the air discharged from the partial duct E faces downward to the air discharged from the partial duct D due to the torsion of the end portions 34 A and 35 A and is directed to the inner peripheral wall surface 2 A. It is discharged so as to be pressed. In addition to the curvature of the discharge plate 35, the air discharged from the partial duct F is pressed downward to the air discharged from the partial duct E and pressed against the inner peripheral wall surface 2 </ b> A due to the twist of the tip 35 </ b> A. Discharged.
That is, the air that has passed through the duct 8A is discharged in a direction different from the circumferential direction by the plurality of partial ducts A to G formed by the plurality of discharge plates 31 to 35 of the discharge port 9B.

In addition to the curvature of the discharge plate 31, the air discharged from the partial duct A of the duct 8B is pressed slightly upward with respect to the extending direction of the duct 8A and pressed against the inner peripheral wall surface 2A by the twist of the tip 31A. So that it is discharged. In addition to the curvature of the discharge plates 31 and 32, the air discharged from the partial duct B faces upward from the air discharged from the partial duct A due to the twist of the tip portions 31A and 32A, and on the inner peripheral wall surface 2A. It is discharged so as to be pressed. In addition to the curvature of the discharge plates 32 and 33, the air discharged from the partial duct C faces upward from the air discharged from the partial duct B due to the twist of the tip portions 32A and 33A, and is directed to the inner peripheral wall surface 2A. It is discharged so as to be pressed. In addition to the curvature of the discharge plates 33 and 34, the air discharged from the partial duct D is upward from the air discharged from the partial duct C due to the twisting of the tip portions 33A and 34A, and is directed to the inner peripheral wall surface 2A. It is discharged so as to be pressed. In addition to the curvature of the discharge plates 34 and 35, the air discharged from the partial duct E is upward from the air discharged from the partial duct D due to the twisting of the end portions 34A and 35A, and on the inner peripheral wall surface 2A. It is discharged so as to be pressed. In addition to the curvature of the discharge plate 35, the air discharged from the partial duct F is upwardly pressed from the air discharged from the partial duct E and pressed against the inner peripheral wall surface 2 </ b> A due to the twist of the tip 35 </ b> A. Discharged.
That is, the air that has passed through the duct 8B is discharged in a direction different from the circumferential direction by the plurality of partial ducts A to F formed by the plurality of discharge plates 31 to 35 of the discharge port 9B, and is formed in the duct 8A. The flow of air discharged from the partial ducts A to F and the flow of point symmetry around the vulcanization can center O, in other words, a large flow in one direction is formed.

Even if the discharge plates 31 to 35 are configured as in the present embodiment, the swirl flows F1 and F2 can be generated over the entire pressure vessel 2.
That is, the discharge plates 31 to 35 are curved in one direction with different curvatures along the extending direction, and approach the inner peripheral wall surface at different angles in one direction from the rear end portions 31B to 35B toward the front end portions 31A to 35A. In each of the ducts 8A and 8B, the direction of bending along the circumferential direction and the direction of twisting are set to the same direction, and further, the angle of bending along the circumferential direction of the discharge plates 31 to 35. In addition, by arranging the twisting angle to be gradually increased, the air discharged from the partial ducts A to F formed in the ducts 8A and 8B is circular along the inner peripheral wall surface 2A as shown in FIG. The swirl flow over the entire inside of the pressure vessel 2 as shown in FIG. 7 by flowing at different angles and different strengths with respect to the circumferential direction and flowing across the back surface 3A of the hermetic door 3 as shown in FIG. 1, F2 can be generated.
Therefore, the temperature in the pressure vessel 2 can be raised substantially uniformly in the extending direction, so that the tire 10 is stored in the vulcanization of the plurality of tires 10 stored side by side along the extending direction of the pressure vessel 2. Regardless of the position, vulcanization can be achieved by a uniform temperature rise. Furthermore, since the temperature rises uniformly at the upper and lower parts of the pressure vessel 2, the individual tires can be heated uniformly by the uniform temperature rise from the circumferential direction, and the entire tire can be uniformly vulcanized. be able to.

  As described above in the first to third embodiments, the pair of ducts 8A; 8B are arranged at the horizontal position of the vulcanizing can, and air is discharged at different angles in the same circumferential direction in each duct 8A; 8B. Thus, by providing a plurality of discharge plates in the ducts 8A and 8B, respectively, it becomes possible to generate a swirling flow over the entire pressure vessel, and the temperature rise in the pressure vessel can be made substantially uniform. Therefore, uniform vulcanization can be performed regardless of the position of the tire 10 stored in the pressure vessel.

Although the discharge plates 31 to 35 are described as being curved, the discharge plates 31 to 35 may be formed so as to be bent at different angles and provided in the ducts 8A and 8B.
Moreover, the structure of the vulcanizing can 1 demonstrated in the said Embodiment 1 thru | or Embodiment 3 is an example, Comprising: The structure different from the said structure may be sufficient.

  As mentioned above, although this invention was demonstrated using embodiment, the technical scope of this invention is not limited to the said embodiment. It will be apparent to those skilled in the art that various changes and modifications can be made to the above-described embodiment, and it is obvious that such changes and modifications can be included in the technical scope of the present invention. It is clear from the description.

1 vulcanized can, 2 pressure vessel, 2A inner peripheral wall, 3 airtight door, 4 floor plate, 5 heat source,
6 fan, 6A motor, 6B rotor blade, 7 partition, 8; 8A; 8B duct,
9A intake port, 9B discharge port, 10 tires, 21 plate pieces, 22 air guide plate,
31 to 35 discharge plate,
F1; F2 swirl flow, R1 vulcanization region, R2 air supply region.

Claims (6)

A heat source and a fan installed on one end side inside the cylindrical pressure vessel;
A duct that extends in an extending direction of the pressure vessel and is arranged on an inner wall surface circumference, and that discharges air blown by the fan on the other end side of the pressure vessel;
With
A plurality of plates for discharging the air in the same circumferential direction at different angles with respect to the circumferential direction of the inner wall surface are provided along the circumferential direction of the pressure vessel at the discharge port of the duct ,
The plurality of plates are twisted toward the inner wall surface at different angles from one end side to the other end side of the pressure vessel, and the angle at which the plurality of plates are twisted gradually from one end side in the circumferential direction toward the other end side is gradually increased. A vulcanizing can arranged to be . The plurality of plates are curved with different radii of curvature from one end side to the other end side of the pressure vessel,
The vulcanization can according to claim 1, wherein the duct is arranged so that a curvature radius of curvature of the plate gradually increases from one circumferential side to the other side in the duct . The ducts are disposed opposite to each other at horizontal positions on the inner wall surface circumference of the pressure vessel, and plates of the same shape are provided in each duct at symmetrical positions across the center of the pressure vessel. The vulcanization can according to claim 1 or claim 2 . The vulcanization can according to any one of claims 1 to 3 , wherein the duct has a length of 15% to 20% of an inner circumferential length of the pressure vessel along a circumferential direction of the pressure vessel. The plate vulcanizer according to any one of claims 1 to 4 is provided in the duct at intervals of 10 to 30 cm. The vulcanization can according to any one of claims 1 to 5 , wherein the plate has a length of 10 cm to 30 cm from one end side to the other end side of the pressure vessel.

Images