JP4943814B2 - Back-up roll bearing lubrication mechanism for outer ring rotation mounted on the rotating shaft - Google Patents

Description

  The present invention relates to a backup roll bearing lubrication mechanism for rotating an outer ring mounted on a rotation shaft suitable for a so-called intelligent plate shape correcting apparatus provided with a plurality of divided backup rolls so that an axial roll crown pattern can be adjusted.

As an intelligent plate shape correcting device, for example, there is one disclosed in Patent Document 1.
This is a split backup roll that can adjust the roll crown pattern in the axial direction. In order to simplify the disassembly and assembly work, the roll support shaft is rotatably supported by the reinforcing roll frame and the roll support is supported. In divided backup rolls that are provided with eccentric parts with different eccentric amounts at a plurality of locations on the shaft and divided reinforcing rolls are attached to the eccentric parts, the roll support shaft can be divided into a plurality of directions in a direction intersecting the axial direction. It is configured.

JP-A-2005-118822

  By the way, in the intelligent plate shape correcting apparatus as disclosed in Patent Document 1, in addition to high lubricity required in the bearing lubrication of the divided backup roll, leakage of lubricating oil to the outside is required. It is necessary to prevent the contamination of the steel plate surface as much as possible, and to prevent the mixing of cooling water from deteriorating the life of the backup roll.

  However, the conventional lubrication system that uses oil mist lubrication, grease lubrication, or rolling oil as the lubricating oil is not a system that satisfies the leakage of lubricating oil to the outside or high lubricity.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a backup roll bearing lubrication mechanism for rotating an outer ring mounted on a rotating shaft that can realize high lubricity without leaking lubricating oil to the outside.

  In order to achieve the above object, an outer ring rotating backup roll bearing lubrication mechanism mounted on a rotating shaft according to the present invention has an eccentric shaft coupled to one end face thereof for individually supporting a plurality of divided backup rolls rotatably. In the lubrication mechanism of the backup roll bearing provided with an eccentric mechanism that rotates eccentrically by swinging the arm, a lubrication path is provided over the external hose and piping, the arm, the eccentric shaft, and the divided backup roll. It is characterized by using oil-air lubrication.

  In addition, a steel cylindrical seal member with an O-ring is interposed at a connecting portion between the oil / air supply passage and discharge passage of the arm and the oil / air supply passage and discharge passage of the eccentric shaft, and is provided on the outer peripheral surface of the eccentric shaft. Is characterized in that O-rings are fitted at three predetermined axial positions.

  According to the backup roll bearing lubrication mechanism for rotating the outer ring mounted on the rotating shaft according to the present invention having the above-described configuration, by using oil-air lubrication effectively, the lubricating oil is not leaked to the outside and high lubricity is realized. The life of the split backup roll can be extended.

  Hereinafter, an outer ring rotating backup roll bearing lubrication mechanism mounted on a rotating shaft according to the present invention will be described in detail with reference to the drawings.

  1 is a side sectional view of a plate shape correcting apparatus showing an embodiment of the present invention, FIG. 2 is a side sectional view of the carriage, FIG. 3 is a side sectional view of a main part of a reduction mechanism in the carriage, and FIG. FIG. 5 is a diagram illustrating the action of the rolling device on the divided backup roll side during rolling (correcting), FIG. 5 is a diagram illustrating the operation of the same rolling device when the carriage is replaced, and FIG. FIG. 7 is a side sectional view of the reduction mechanism in the carriage, FIG. 8 is an enlarged view of the bearing portion, FIG. 9 is a sectional view taken along the line PP in FIG. 7, and FIG. 10 is a sectional view taken along the line Q-Q in FIG. FIG. 11 is an enlarged view of a portion R of FIG. 9, FIG. 12 is an explanatory diagram of a lubrication path from the shaft of the split backup roll to the roll, FIG. 13 is an explanatory diagram of a lubrication path from the outside of the split backup roll to the shaft, and FIG. FIG. 15 is a cross-sectional view taken along line S-S in FIG. It is a part enlarged view.

  A plate shape correcting device 10 shown in FIG. 1 is a so-called intelligent plate shape correcting device provided with a divided backup roll that can individually detect and control the load.

  More specifically, a pair of upper and lower work rolls 12a and 12b are rotatably supported via a pair of upper and lower work roll chocks 13a and 13b in a mill housing 11 that is a frame, and the pair of upper and lower work rolls 12a and 12b. The plate material is passed through the appropriate number of support rolls 14 from the entrance side (front side: left side in the figure) of the plate shape correction apparatus 10 to the exit side (rear side: right side in the figure) of the plate shape correction apparatus 10. It is possible to pass through.

  The lower work roll chock 13b that supports the lower work roll 12b is supported by the lower carriage 52, and is supported integrally with the lower carriage 52 on the mill housing 11. A pair of front and rear divided backup rolls 50 are rotatably supported on the lower carriage 52. On the other hand, the upper work roll chock 13a that supports the upper work roll 12a is supported from below by a pair of front and rear lift cylinders 54 built in the lower work roll chock 13b.

  A frame 18 is supported on the mill housing 11 by a pair of front and rear hydraulic fluid pressure type balance cylinders 19 so as to be movable up and down. The frame 18 is urged downward against the urging force of the balance cylinder 19 by a pair of left and right hydraulic pressure type pressure reduction cylinders 20 supported downward on the mill housing 11 to generate a predetermined reduction force. It can be applied to the upper work roll 12a and the lower work roll 12b.

  The frame 18 has a pair of front and rear legs 18b below the block-shaped main body 18a. The upper carriage 21 is supported between the front and rear legs 18b so as to be able to enter and exit from the work side of the rolling line. It is supported by a pair of front and rear hydraulic pressure type lift cylinders 22 so as to be movable up and down.

  The upper carriage 21 is positioned and fixed with respect to the frame 18 at this position by a clamp mechanism 23 provided at the center in the plate width direction on the front surface of the frame 18 and is shown by a balloon in FIG. As described above, the upper carriage 21 is pressed against the reference surface of the rear leg portion 18b of the frame 18 by a pair of left and right pressing cylinders 56 built in the frame 18, and thus the axes of the work roll and the backup roll are parallel to each other. It is possible to keep on.

  On the lower surface portion of the upper carriage 21, roll chock 27 is arranged in a plurality of three or more divisions in the plate width direction (axial direction) on the plate shape correction device entrance side and exit side. A roll 28 is rotatably supported.

  As shown in FIGS. 2 and 3, each roll chock 27 includes a bifurcated main body portion 27a in front view and a pair of left and right caps 27b coupled to the bifurcated portion of the main body portion 27a with bolts or the like. The main body 27a is supported so as to be slidable in the load direction by a rod 29 coupled to the main body 27a with respect to the upper carriage 21 and a spring 30 wound around the tip of the rod 29 (see FIG. 2). ). Further, a pair of left and right low friction guide mechanisms 60 such as linear guides are interposed between opposing surfaces along the load direction of the main body portion 27 a of each roll chock 27 and the upper carriage 21.

Both ends of the eccentric shaft 33 that supports the split backup roll 28 concentrically are rotatably supported by bearings (not shown) in a circular hole formed by the bifurcated portion of the main body 27a and the cap 27b. The In the figure, C ₁ is the rotation center of the eccentric shaft 33, C ₂ is the rotation center of the divided backup roll 28, and L is the eccentric distance.

  A load detection device 31 such as a load cell for detecting a load applied to each divided backup roll 28 is interposed between the upper surface of the main body 27 a of each roll chock 27 and the lower surface of the upper carriage 21. Two load detection devices 31 are arranged side by side in the plate width direction (axial direction).

  In addition, a reduction device 32 is provided between the frame 18 and the upper carriage 21 to individually apply a reduction force to each divided backup roll 28 (see FIG. 1).

  That is, the reduction device 32 is coupled to one end surface of the eccentric shaft 33 that rotatably supports each divided backup roll 28 in the upper carriage 21 by using a bolt 34 using a gap between the adjacent divided backup rolls 28. As shown in FIG. 1, an arm 35 and a lever 37 swingably supported by a hydraulic fluid pressure type reduction force adjusting cylinder (actuator) 36 mounted horizontally on the frame 18 in the frame 18. , And the upper end of each arm 35 and the lower end of each lever 37 are linked in a pinless structure. A key groove 61 is formed on one end surface of the eccentric shaft 33, and a key 62 formed on the lower side surface of the arm 35 is fitted into the key groove 61 to improve the assembling accuracy.

  In the illustrated example, as the pinless structure, a roller 39 supported by a pin 38 at the upper end of each arm 35 is formed in a U-shaped receiving port (crocodile port) 40 formed at the lower end of each lever 37 (see FIG. 1). Are inserted with a minute gap. The intermediate portion of each lever 37 is coupled by a pin 42 between a pair of left and right brackets attached to the main body portion 18a of the frame 18, and the piston rod tip of the above-described reduction force adjusting cylinder 36 is pinned to the upper end portion thereof. 43.

  The reduction device 32 is used for the divided backup roll 28 on the inlet side of the plate shape correcting device 10 and the divided backup roll 28 on the outlet side of the plate shape correcting device 10 in the frame 18 and the upper carriage 21 in the front-rear direction. In an inverted state, they are alternately arranged in the left-right direction.

  4 and 5 used for explanation of the action described later is a stopper for restricting the extension position in order to detect the origin position of each rolling force adjusting cylinder 36, and 45 in FIG. In order to provide a gap with the receiving port 40, it is a stopper that regulates the position where each arm 35 falls due to the moment due to the center of gravity when there is no load (when the carriage is replaced).

  As shown in FIG. 4, when the rolling reduction (correction) is performed, the reduction device 32 extends and contracts the reduction force adjusting cylinder 36, so that the lever 37 moves from the state of FIG. Swings in the direction (see FIG. 4C) or counterclockwise (see FIG. 4A), and thereby the eccentric shaft 33 (not shown in FIG. 4) is divided via the arm 35. The rolling force with respect to the upper work roll 12a is adjusted (increased or decreased) by rotating eccentrically in the counterclockwise direction (see FIG. 4C) or clockwise (see FIG. 4A) together with the backup roll 28. It has become. At this time, the roller 39 rolls up and down in the receptacle 40 and smoothly rotates the eccentric shaft 33 and the divided backup roll 28 eccentrically.

On the other hand, the upper carriage assembly Kawatoki, as shown in FIG. 5, only predetermined stroke rolling force adjusting cylinder 36 from the state of e.g., FIGS. 4 (a) to contract the rotational center C ₁ of the eccentric shaft 33 the arm 35 After swinging clockwise in the center (see FIG. 5A), the lift cylinder 22 is contracted to lower the upper carriage 21 relative to the frame 18 (see FIG. 5B). 39 is pulled out downward from the receiving port 40, and the upper carriage 21 is separated from the frame 18. After the roller 39 is pulled out, the arm 35 falls in the clockwise direction by its own weight, but eventually the position of the fall is restricted by the stopper 45, which hinders the operation when the upper carriage 21 is subsequently carried out to the work side of the rolling line. There is nothing.

  Further, the divided backup rolls 50 to be described later for applying a rolling force to the lower work roll 12b are arranged on the entry side and the exit side of the plate shape correcting device 10 and are arranged in the plate width direction in the same manner as the division backup roll 28. However, these are rotatably supported on an entry side and an exit side of the plate shape correcting device 10 on a single roll support shaft 51 via an eccentric bush described later having a predetermined eccentric amount. Thus, the structure is different from the above-described divided backup roll 28 that can individually adjust the rolling force. Such a divided backup roll 50 is already known from Patent Document 1 and the like.

  Both ends of the roll support shaft 51 are rotatably supported by the lower carriage 52, and are rotated to a required angle via a spindle or the like by a drive source (not shown) on the drive side of the rolling line. .

  The lower carriage 52 is supported so as to be able to enter and exit from the work side of the rolling line with respect to the mill housing 11 and is fixed to the mill housing 11 by a clamp mechanism 53 similar to the clamp mechanism 23 described above at a predetermined position in the plate width direction. It is designed to be positioned and fixed. The mill housing 11 positioned below the lower carriage 52 incorporates a pair of front and rear lift cylinders 55 for lifting the lower carriage 52 when the lower carriage 52 is assembled.

  In this embodiment, a plurality of outer ring rotating divided backup rolls 28 mounted on a plurality of single shafts composed of the eccentric shaft 33 and a single roll support shaft 51 spaced apart by a predetermined distance. The split backup roll 50 attached to the shaft is oil-air lubricated by a lubrication mechanism described later.

  First, in the divided backup roll 28 on the eccentric shaft 33, as shown in FIGS. 3 and 6, four systems (two systems are omitted in FIG. 6) for supplying oil and air on the upper carriage 21 are used. A pipe 70A and an oil / air discharge pipe 70B are provided, and the oil / air supplied from the oil / air supply source (not shown) from each oil / air supply pipe 70A is distributed to each arm 35 via the hose 71a. After supplying the corresponding divided backup rolls 28 to lubricate the inside (bearing portions), they are collected in the respective arms 35 and discharged (exhaust) from the oil / air discharge pipe 70B through the hose 71b. It has become.

  As shown in FIGS. 7 to 10, the oil air supplied to the supply passage 72a of the arm 35 is supplied to the inside (bearing portion) of the split backup roll 28 via the supply passage 73a of the eccentric shaft 33 and lubricated. The subsequent oil air is discharged to the discharge passage 72b of the arm 35 through the discharge passage 73b of the eccentric shaft 33. The outlet of the discharge passage 73b of the eccentric shaft 33 is provided at the lowermost portion, and the amount of oil in the divided backup roll 28 is minimized, thereby suppressing the increase in internal pressure due to stirring and improving the sealing performance by suppressing external force due to its own weight. It is preferable.

  As shown in FIG. 11, a steel cylindrical seal member 74 is interposed in a communication portion between the supply passage 72 a and the discharge passage 72 b of the arm 35 and the supply passage 73 a and the discharge passage 73 b of the eccentric shaft 33. The seal member 74 is fitted over both members between the opposing surfaces of the arm 35 and the eccentric shaft 33, and O-rings 75a and 75b are fitted on outer peripheral surfaces corresponding to the respective members.

  Further, on the outer peripheral surface of the eccentric shaft portion with which the divided backup roll 28 of the eccentric shaft 33 is fitted, there are three predetermined axial positions (in the illustrated example, positions corresponding to both ends of the divided backup roll 28 and the divided backup roll 28). O-rings 76a to 76c are fitted at three positions that do not correspond to the rollers built in 28.

  Next, in the divided backup roll 50 on the roll support shaft 51, as shown in FIGS. 12 to 15, an oil / air supply passage 80a and a discharge passage are provided in the roll support shaft 51 divided into a plurality of blocks. 80b is formed, and the oil / air formed in the supply passage 80a is divided into a plurality (four in the illustrated example) that are fitted on the roll support shaft 51 via the eccentric bush 82 via the distribution valves 81a to 81e. After being supplied to the backup roll 50 and lubricating its inside (bearing portion), it is again discharged (exhausted) through the discharge passage 80b of the roll support shaft 51. In FIG. 14, reference numeral 83 denotes a support for restricting the divided backup roll 50 in the axial direction.

  A key 84 is interposed between the roll support shaft 51 and the eccentric bush 82 so that the roll support shaft 51 and the eccentric bush 82 rotate integrally. The key 84 is formed with an oil supply port 85a and an oil discharge port 85b that are spaced apart from each other by a predetermined distance. (Communication to the bearing portion)), and the oil discharge port 85b and the supply passage 80b of the roll support shaft 51 and the discharge passage 87b of the eccentric bush 82 (communication to the inside (bearing portion) of the split backup roll 50). Is communicated.

  Rubber cylinder seal members 88a and 88b are fitted into the oil supply port 85a and the oil discharge port 85b, respectively, and a route for supplying and discharging oil air is secured.

  Further, on the outer periphery of the eccentric portion where the split backup roll 50 of the eccentric bush 82 is fitted, there are three predetermined axial positions (in the illustrated example, positions corresponding to both ends of the split backup roll 50 and the split backup roll 50. O-rings 89a to 89c are fitted at three positions that do not correspond to the built-in rollers.

  On the other hand, an oil supply side rotary joint 90a and an oil discharge side rotary joint 90b are fitted on the roll support shaft 51, and oil supply from an external oil air supply source (not shown) is roll supported by the oil supply side rotary joint 90a. The oil oil after lubrication supplied to the supply passage 80a of the shaft 51 and returned to the discharge passage 80a of the roll support shaft 51 by the rotary joint 90b on the oil discharge side is passed through the external hose and piping 91 (see FIG. 13). It is designed to be discharged (exhaust).

  As shown in FIGS. 13 to 15, the rotary joints 90 a and 90 b on the oil supply side and the oil discharge side are fitted in a fixed frame 92 fixed on the lower carriage 52 and rotatably mounted on the fixed frame 92. On the other hand, a ring-shaped cartridge 94 externally fitted to the roll support shaft 51 by a key 93 so as not to rotate, and a stepped cylindrical shape incorporated in the cartridge 94 so as to be movable in the radial direction by screw rotation of a small diameter screw portion 95. Supply of the roll support shaft 51 having a holder 96, a rubber cylindrical seal member 97 housed in the holder 96, and a flat surface on which the outer end of the seal member 97 is airtight and liquid-tightly seated And a plug 98 screwed into the opening end of the passage 80a or the discharge passage 80b.

  The cartridge 94 is divided into a main body member 94a and an end member 94b. The main body member 94a is fitted into the fixed frame 92 with the end member 94b removed, and the rear end member 94b is coupled to the fixed frame 92. Against the axial direction. Further, a pair of O-rings 99a and 99b are fitted on the outer peripheral surface of the main body member 94a with the holder 96 interposed therebetween.

  The supply passage 92 a or the discharge passage 92 b to which the external hose of the fixed frame 92 and the pipe 91 are connected communicates with an annular passage 92 c formed on the inner peripheral surface of the fixed frame 92, and this annular passage 92 c is always the internal passage of the holder 96. 96a. The internal passage 96a communicates with the supply passage 80a or the discharge passage 80b of the roll support shaft 51 in a gas-tight and liquid-tight manner via the seal member 97 and the plug 98. In FIG. 15, reference numeral 100 denotes an O-ring fitted on the outer peripheral surface of the large-diameter portion of the holder 96.

  Because of this configuration, during rolling (correction), the frame 18 is lowered from the state of FIG. 1 due to the contraction of the balance cylinder 19, and the plate material is placed between the upper and lower work rolls 12a and 12b in this state. Through.

  At this time, a predetermined reduction force is applied to the upper and lower work rolls 12 a and 12 b by the frame 18 being urged downward with respect to the mill housing 11 by a pair of left and right reduction cylinders 20. Further, the rolling force in the sheet width direction is adjusted by the divided backup roll 28 and the divided backup roll 50 arranged on the entry side and the exit side of the rolling mill 10.

  In the divided backup roll 28, the load is individually detected by the load detection device 31. Then, the individual reduction forces of the divided backup rolls 28 are adjusted by the control device (not shown) via the reduction device 32 so that the individual loads of the divided backup rolls 28 become the target loads.

  In the divided backup roll 50, the roll support shaft 51 is rotated to a required angle via a spindle or the like by a drive source (not shown) by a control device (not shown), and the reduction corresponding to the eccentric amount of each eccentric bush at this time is performed. Individually adjusted to power.

  Therefore, particularly in the divided backup roll 28, it is not necessary to detect and feed back the plate shape on the exit side of the rolling mill 10, and the plate shape can be directly controlled without time delay. Further, the divided backup roll 28 and the divided backup roll 50 divided into a plurality of parts can be finely adjusted in the plate width direction, and good plate quality, that is, good plate crown and flatness can be obtained.

  In this embodiment, during rolling (correction), the upper and lower divided backup rolls 28 and the divided backup rolls 50 (the bearing portions) are internally lubricated with oil and air, so that the upper and lower divided backup rolls 28 and divided backup rolls 28 are divided. Lubricating oil leakage from the roll 50 can be eliminated and high-viscosity lubricating oil can be supplied and discharged, and the life of the upper and lower divided backup rolls 28 and the divided backup rolls 50 can be extended. Further, compared with oil mist lubrication or the like, the supply passage 80a and the discharge passage 80b in the roll support shaft 51 for supporting each divided backup roll 50 may have a small diameter, so that the strength and rigidity of the roll support shaft 51 can be reduced.

  Specifically, in the lubrication path of each divided backup roll 28 on the eccentric shaft 33, the oil air from the oil / air supply source is the oil / air supply pipe 70A on the carriage 21 → the hose 71a → the supply path 72a of the arm 35. → After flowing through the supply passage 73a of the eccentric shaft 33 and supplied to each divided backup roll 28 and lubricating the inside (bearing portion), the discharge passage 73b of the eccentric shaft 33 → the discharge passage 72b of the arm 35 → the hose 71b → carriage 21 returns to the oil-air discharge pipe 70B on the pipe 21 and is discharged (exhaust) to the outside.

  At this time, the interior (bearing portion) of each divided backup roll 28 is controlled under negative pressure by increasing the exhaust efficiency of oil air, and the supply passage 72a and discharge passage 72b of the arm 35 and the supply passage 73a of the eccentric shaft 33 are controlled. A steel cylindrical seal member 74 with O-rings 75a and 75b is interposed at the connection portion with the discharge passage 73b, and the O-ring 76a is provided at three predetermined axial positions on the outer peripheral surface of the eccentric shaft 33. ˜76c is fitted to prevent oil air from leaking to the outside.

  On the other hand, in the lubrication path of each divided backup roll 50 on the roll support shaft 51, the external hose and pipe 91 → the supply path 92a of the fixed frame 92 and the annular path 92c → the internal path 96a of the holder 96 → the rubber cylindrical shape. The seal member 97 → the plug 98 → the supply passage 80a of the roll support shaft 51 and the distribution valves 81a to 81e → the oil supply port 85a of the key 84 → the supply passage 87a of the eccentric bush 82, and supplied to each divided backup roll 50, After lubricating the inside (bearing portion), the discharge passage 87b of the eccentric bush 82 → the oil discharge port 85b of the key 84 → the discharge passage 80b of the roll support shaft 51 and the distribution valves 81a to 81e → the plug 98 → the rubber cylindrical seal Member 97 → inner passage 96a of holder 96 → annular passage 92c and discharge passage 92b of fixed frame 92 → outer hose And return fine pipe 91, is discharged to the outside (exhaust).

  At this time, the inside (bearing portion) of each divided backup roll 50 is controlled under a negative pressure by increasing the exhaust efficiency of oil air, and the O-rings 99a and 99b, the rubber cylindrical seal member 97 and the plug 98 are connected. The provided rotary joints 90a and 90b are interposed in the connecting portion between the external hose and pipe 91 and the supply passage 80a and the discharge passage 80b of the roll support shaft 51, and the oil supply port 85a and the oil discharge port 85b of the key 84 are connected to each other. The rubber cylindrical seal members 88a and 88b are fitted, and the outer surfaces of the eccentric bush 82 are fitted with O-rings 89a to 89c at three predetermined axial positions so that the oil / air is externally provided. To prevent leaks.

  The rotary joints 90a and 90b use octagonal nuts (through holes) to secure the required cross section for oil and air. By pulling the holder 96 into the cartridge 94 with an octagonal spanner or the like, the rotary joints 90a and 90b are made of rubber. The cylindrical seal member 97 also moves integrally with the holder 96 and is separated from the plug 98. In this state, the rotary joints 90a and 90b can be detached from the roll support shaft 51. Conversely, after the rotary joints 90a and 90b are inserted into the roll support shaft 51 in the above state, the holder 96 is pushed out of the cartridge 94 with an octagonal spanner or the like, so that the rubber cylindrical seal member 97 also moves integrally with the holder 96. Then, the plug 98 is seated in an air-tight and liquid-tight state to be in the state shown in FIG.

  Further, when the surface of the upper and lower divided backup rolls 28 and 50 is cooled with a liquid, the inside of each divided backup roll 28 and each divided backup roll 50 (bearing portion) by reducing the oil-air exhaust efficiency or the like. May be controlled under a positive pressure to prevent internal penetration.

  In this embodiment, the divided backup roll 28 having a high inspection / replacement frequency is supported by the upper carriage 21, the upper carriage 21 is supported by the frame 18 having a low inspection / replacement frequency, and the reduction device 32 is connected to the frame 18. The upper carriage 21 is shared and supported.

  Accordingly, the weight of the frame 18 and the upper carriage 21 can be reduced and the upper carriage 21 can be made as small as possible, while the frame 18 and the upper carriage 21 can be separated and handled as necessary.

  As a result, even if the number of divisions of the divided backup rolls 28 is increased and the structure such as the frame 18 and the upper carriage 21 is large and heavy, the rearrangement of the divided backup rolls 28 and the reduction device 32 (single reduction mechanism). It is possible to improve the maintenance workability and reduce the weight and capacity of transportation equipment such as cranes and jigs.

  In the reduction device 32, the arm 35 and the lever 37 are linked in a pinless structure, so that the frame 18 and the upper carriage 21 can be easily separated. That is, only the upper carriage 21 can be easily extracted from the frame 18 to the outside when the divided backup roll 28 is rearranged.

  In addition, by positioning the upper carriage 21 with respect to the frame 18 at the center in the plate width direction by the clamp mechanism 23, the positional relationship between the frame 18 and the upper carriage 21 can be kept constant even when the rolling mill 10 is bent and deformed. In addition, the positional relationship in the line direction can be kept constant by pressing the upper carriage 21 against the reference surface of the rear leg portion 18b of the frame 18 with a pair of left and right pressing cylinders 56 built in the frame 18.

  Furthermore, according to the present embodiment, the eccentric shaft 33 that rotatably supports each divided backup roll 28 is divided for each divided backup roll, so that it is not restrained by the position of the adjacent divided backup roll 28, High-accuracy position control can be performed with good responsiveness. Further, since each of the divided backup rolls 28 is rotatably supported by the eccentric shaft 33, the maintainability can be improved by simplifying the eccentric mechanism.

  Note that the present invention is not limited to the above-described embodiments, and the rolling device 32 (single rolling mechanism) is applied to the divided backup roll 50 that is attached to the roll support shaft 51 formed of a single shaft without departing from the gist of the present invention. Needless to say, various modifications such as changing the structure of the reduction device 32 are possible. Alternatively, the frame 18 and the upper carriage 21 may be integrally formed, and the arm 35 may be directly swung by the reduction force adjusting cylinder 36.

It is a sectional side view of the plate shape correction apparatus which shows one Example of this invention. It is a sectional side view of the carriage. It is a principal part side sectional view of the reduction mechanism in the carriage. It is operation | movement explanatory drawing at the time of rolling (correction) of the reduction apparatus by the side of the division | segmentation backup roll on a single axis | shaft. It is operation | movement explanatory drawing at the time of carriage replacement of the same pressure reducing apparatus. It is explanatory drawing of the lubrication path | route in the carriage by the side of a division | segmentation backup roll. It is a sectional side view of the reduction mechanism in the carriage. It is an enlarged view of a bearing part. It is the PP sectional view taken on the line of FIG. It is the QQ sectional view taken on the line of FIG. It is the R section enlarged view of FIG. It is explanatory drawing of the lubrication path | route from the axis | shaft of a division | segmentation backup roll to a roll. It is explanatory drawing of the lubrication path | route from the exterior of a division | segmentation backup roll to an axis | shaft. It is the SS sectional view taken on the line of FIG. It is the T section enlarged view of FIG.

Explanation of symbols

  10 plate shape correction device, 11 mil housing, 12a upper work roll, 12b lower work roll, 13a upper work roll chock, 13b lower work roll chock, 14 support roll, 18 frames, 18a legs, 18b main body, 19 balance cylinder, 20 Reduction cylinder, 21 Upper carriage, 22 Lift cylinder, 23 Clamp mechanism, 27 Roll chock, 27a Main body, 27b Cap, 28 Split backup roll on a single axis, 29 Rod, 30 Spring, 31 Load detection device, 32 Reduction device, 33 Eccentric shaft, 35 arm, 36 Rolling force adjustment cylinder, 37 Lever, 38 pin, 39 Roller, 40 Receptor, 42 pin, 43 pin, 44 stopper, 45 stopper, 50 Split backup row on one axis 51, 51 roll support shaft, 52 lower carriage, 53 clamp mechanism, 54 lift cylinder, 55 lift cylinder, 56 pressing cylinder, 60 linear guide, 61 keyway, 62 key, 70A oil / air supply piping, 70B oil / air discharge piping, 71a hose, 71b hose, 72a supply passage, 72b discharge passage, 73a supply passage, 73b discharge passage, 74 steel cylindrical seal member, 75a, 75b O-ring, 76a-76c O-ring, 80a supply passage, 80b discharge passage 81a to 81e Distributing valve, 82 Eccentric bush, 83 Support, 84 key, 85a Oil supply port, 85b Oil discharge port, 87a Supply passage, 87b Discharge passage, 88a, 88b Rubber cylindrical seal member, 89a to 89c O-ring , 90a, 90b Rotary Joint, 91 External hose and piping, 92 fixed frame, 92a supply passage, 92b discharge passage, 92c annular passage, 93 key, 94 cartridge, 95 small diameter screw part, 96 holder, 96a internal passage, 97 rubber cylindrical seal member , 98 plug, 99a, 99b O-ring, 100 O-ring.

Claims (2)

  In a lubrication mechanism for a backup roll bearing having an eccentric mechanism for eccentrically rotating an eccentric shaft for individually supporting a plurality of divided backup rolls by swinging an arm coupled to one end face thereof, an external hose, a pipe and an arm In addition, a lubrication path is provided over the eccentric shaft and the split backup roll, and oil / air lubrication is performed using this lubrication path, and the backup roll bearing lubrication of the outer ring rotation mounted on the rotating shaft is characterized in that mechanism.   A connecting portion between the oil / air supply passage and discharge passage of the arm and the oil / air supply passage and discharge passage of the eccentric shaft is provided with a steel cylindrical seal member with an O-ring, and a shaft is provided on the outer peripheral surface of the eccentric shaft. 2. A backup roll bearing lubrication mechanism for rotating an outer ring mounted on a rotating shaft according to claim 1, wherein O-rings are fitted at three predetermined positions.

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