JP3991321B1 - Bearing device - Google Patents

Abstract

A bearing device capable of maintaining lubricating performance over a long period of time is provided.
Lubricating oil is stored in the housing to lubricate the self-aligning roller bearing, and an inner diameter φS of seal lips 13a and 13b is smaller than φP which is a PCD of the self-aligning roller bearing 12. Therefore, the lubricating oil stored in the housing leaks outward from between the seal lips 13a, 13b and the roller 4. Therefore, the position of the lubricating oil surface is always the same height, and the self-aligning roller bearing 12 can be lubricated in the same state. Furthermore, since the inside of the housing is pressurized by the gas supplied from the lubricating oil supply device, the inner pressure is higher than the outer pressure across the seal lips 13a and 13b, so that foreign matter enters from the outside. This can be effectively suppressed.
[Selection] Figure 4

Description

  The present invention relates to a bearing device provided with a lubricating oil supply apparatus that mixes and feeds lubricating oil and gas, and particularly relates to a bearing apparatus suitable for supporting a rolling roller of a steel facility.

  In steelworks, molten steel that has been refined is often cast into slabs, blooms, billets, and the like by a continuous casting method. The outline of the continuous casting equipment is as follows. First, the molten steel is poured from a ladle into a tundish and from there into a further water-cooled mold. And the slab which only the surface layer part solidified within the casting_mold | template is pulled out by the pinch roll to a spray part (cooling water is spread | dispersed), and the whole inside solidifies. Then, it cut | disconnects to predetermined length with a cutting device, and is conveyed by the next process with a slab guide roll.

  In the continuous casting equipment as described above, generally, rolls such as a pinch roll and a slab guide roll are rotatably supported by a roller bearing. Such a roll support device is operated at a high temperature and in a poor environment where there are many foreign substances such as cooling water, water vapor, scales, etc., and therefore has a structure in particular that ensures the lubricity and sealability of the bearing portion. ing. For example, in a slab guide roll support device, a self-aligning roller bearing with both ends open is accommodated in a housing, and grease is continuously supplied from the housing side, and between the roll and the housing, both sides of the bearing are provided. In many cases, sealing with a sealing mechanism (oil seal or the like) ensures good lubricity of the bearing portion and at the same time prevents foreign matter from entering the bearing.

  In the conventional roll support device described above, in addition to the original sealing function of the sealing mechanism, grease that continuously leaks from the sealing mechanism can also be expected to function as a grease seal (even after 100% of the grease is sealed in the housing). Furthermore, since the grease is continuously supplied, the seal mechanism continuously leaks to the outside, which functions as a grease seal.) A relatively good sealing performance can be obtained. However, since the roll support device is in contact with many foreign substances during the operation of the facility, it is difficult to completely prevent the foreign substances from entering the housing through the seal mechanism. In particular, in the seal mechanism located on the center side of the roll, the sprayed cooling water falls directly, or foreign matter such as cooling water adhering to the slab or roll flows along the roll, so from this part Foreign objects are easy to enter. Once the foreign matter enters the housing through the seal mechanism, the bearing portion is open at both ends. Therefore, the foreign matter easily enters the bearing and mixes with the grease inside the bearing. Deterioration of the lubricity of the part, rusting of the contact surface, etc. are caused and the life of the bearing part is reduced.

  In order to prevent such harmful effects, it is conceivable that the roller bearing housed in the housing is sealed at both ends. However, since the inside of the bearing is lubricated with the encapsulated grease, Prone to lack of lubrication. Further, in order to completely prevent foreign matter from entering the inside of the bearing, it is necessary to increase the width dimension of the seal body attached to both ends to strengthen the seal structure. Therefore, an increase in the bearing width dimension, resulting in an increase in the size of the roll support device, or an attempt to increase the width dimension of the seal body within the determined bearing dimension, it is necessary to reduce the roller length, As a result, the bearing load capacity is reduced. Therefore, it is difficult to say that it is practical to use a both-end sealed roller bearing for this type of roll support device.

On the other hand, in Patent Documents 1 and 2, oil-air lubrication is performed from one end side of the double row roller bearing, a seal body is provided at the other end of the bearing, and an air vent passage is provided in the seal body. A bearing device in which is formed. “Oil-air lubrication” is a type of micro-lubrication lubrication method, and as is well known, a small amount of lubricating oil is intermittently injected into a compressed air flow at regular time intervals, and a high-speed air flow is applied to the lubrication site. It is a lubrication method to be supplied. Such an air flow containing a small amount of lubricating oil is called “oil air”. Lubricating oil in the oil air does not become mist, but is carried to the lubrication site through the inner wall of the pipe. The oil-air lubrication method is aimed at suppressing the intrusion of foreign matter by increasing the internal pressure, has no problem of environmental pollution, and has the advantage that an optimal amount of lubricating oil and air can be supplied to each individual bearing. .
Japanese Patent Application Laid-Open No. 11-342459 Japanese Patent No. 3818314

  By the way, there is a problem of how to adjust the amount of lubricating oil supplied to the housing by oil-air lubrication. That is, according to the oil-air lubrication, since a constant amount of lubricating oil and air are always supplied, if the oil and oil are stored in the same housing, the lubricating oil will eventually overflow, and its handling becomes a problem. Further, when the inside of the housing is simply opened to the atmosphere, there is a problem that foreign matters such as cooling water easily enter from the outside.

  An object of the present invention is to provide a bearing device that can maintain lubrication performance for a long period of time in view of the problems of the prior art.

A bearing device according to a first aspect of the present invention is a bearing device used in a roll support device for steel equipment, a housing capable of storing lubricating oil, a rolling bearing disposed in the housing and supporting a rotating shaft. In the bearing device having a lubricating oil supply device that supplies the rolling bearing with a mixture of lubricating oil and a gas, and a seal device that seals between the rotating shaft and the housing,
The seal device has an annular seal lip that is fixed to the housing and abuts against the rotating shaft in order to maintain the oil level position of the lubricating oil in the housing,
The inner diameter of the seal lip is smaller than the PCD of the rolling bearing,
The seal lip has a pressing force that prevents fluid from entering the interior of the housing through the seal lip when the pressure inside the housing is lower than the pressure outside the housing. It is characterized by that.

The second bearing device is a bearing device used in a roll support device for steel equipment, a housing capable of storing lubricating oil, a rolling bearing disposed in the housing and supporting a rotating shaft, and the rolling device. In a bearing device having a lubricant supply device that supplies a lubricant mixed with gas to a bearing, and a seal device that seals between the rotating shaft and the housing,
The seal device has an annular seal lip that is fixed to the housing and abuts against the rotating shaft,
A lid member capable of changing the assembly phase for the housing, and the throttle hole for adjusting the pressure inside is formed to an external pressure of the housing,
The assembly phase of the lid member is adjusted so that the throttle hole is disposed at a position not less than the inner diameter of the seal lip and not more than the PCD of the rolling bearing .

  According to the bearing device of the first aspect of the present invention, lubricating oil is stored in the housing in order to lubricate the rolling bearing, and the inner diameter of the seal lip is smaller than the PCD of the rolling bearing. The lubricating oil stored in the housing leaks outward from between the seal lip and the rotary shaft. Therefore, the position of the lubricating oil surface is always the same height, and the rolling bearing can be lubricated in the same state. Further, since the inside of the housing is pressurized by the gas supplied from the lubricating oil supply device, the inner pressure is higher than the outer pressure across the seal lip, so that foreign matter enters from the outside. This can be effectively suppressed. “PCD” refers to the pitch circle diameter of the rolling elements. For example, in the case of a self-aligning roller bearing, measurement is performed based on the center of the roller length. When a plurality of types of seal devices are provided, the seal lip indicates the one having the largest inner diameter.

  The seal lip has a pressing force that prevents fluid from entering the interior of the housing through the seal lip when the pressure inside the housing is lower than the pressure outside the housing. Then, it is preferable because entry of foreign matter from the outside can be suppressed at the time of abnormality.

  According to the bearing device of the second aspect of the present invention, since the throttle hole for adjusting the internal pressure with respect to the external pressure is formed in the housing, the pressure inside the housing is reduced by the throttle hole. Can be adjusted. If the sealing force of the seal lip is too high, it becomes difficult for gas to escape from between the seal lip and the rotating shaft, so that the amount of gas passing through decreases and the internal pressure of the housing increases. On the other hand, if the tension force is too weak, gas easily escapes, so that the amount of gas passing through increases and the internal pressure of the housing decreases. The tightening force of the seal lip varies depending on the product due to dimensional accuracy at the time of manufacturing the seal device, hardness due to aging, differences in the wear state of the seal lip, etc., so when there is no throttle hole in the housing The internal pressure varies with each hiding due to the influence of this variation in tension, and the amount of gas supplied also changes. That is, there is a risk that a bearing device for a housing with a high internal pressure will cause a lubrication failure due to insufficient supply of oil and air, and a bearing for a housing with a low internal pressure may cause a lubrication failure due to external water or foreign matter intrusion. By providing the throttle hole, it is possible to exhaust gas with little variation, that is, it is possible to stably supply oil air to each bearing.

  When the throttle hole is disposed radially outside the inner diameter of the seal lip and radially inward from the PCD of the rolling bearing, the throttle hole is disposed at a position lower than the lubricant surface, so that the lubricating oil is lower than the seal lip. Can be prevented from being discharged.

  When a check valve is provided in the throttle hole, it is possible to prevent foreign matter from entering from the throttle hole. The “check valve” means a valve having a function that the amount of fluid flowing in one direction is smaller than the amount of fluid flowing in the other direction, and in particular, the amount of fluid flowing in one direction is close to zero. preferable.

  It is preferable that the inside of the housing communicates with the outside only through the throttle hole. For example, an O-ring or packing is preferably interposed between the housing and a lid member attached to the housing.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a perspective view schematically showing a continuous casting facility using the bearing device according to the first embodiment. FIG. 2 is a perspective view of a roller unit used for continuous casting equipment.

  In FIG. 1, the molten steel material FE is supplied from the upper introduction part 1, and is discharged | emitted in plate shape toward the perpendicular direction possible from the discharge part 2 of 2 rows. The plate-shaped steel material FE passes between the roller units 3 arranged to face each other, and is adjusted so that the plate thickness is gradually adjusted by the rollers and gradually becomes horizontal. The roller units 3 arranged on both sides of the steel material FE are shielded by a chamber 9 as schematically shown by a dotted line, and the interior thereof is exposed to the high temperature of the steel material FE and the water for cooling. It has become.

  The roller unit 3 includes a roller 4 for rolling the steel material FE and a bearing device 10 that supports both ends of the roller 4 that is a rotating shaft. For example, as shown in FIG. A pair of roller units 3 are arranged facing both sides of the steel material FE.

  FIG. 3 is a cross-sectional view of the bearing devices 10 and 10 that support one roller 4 disposed on the lower side with respect to the steel material FE. In addition, since the support structure of the roller arrange | positioned above steel material FE is also the same, description is abbreviate | omitted. In the present embodiment, the same bearing devices 10 and 10 are used, but different rolling bearings may be used. In FIG. 3, the roller 4 includes a first cylindrical portion 4 b, a second cylindrical portion 4 c, and a first cylindrical portion 4 c that are smaller in diameter than the rolled portion 4 a and coaxially arranged on both sides in the axial direction of the rolled portion 4 a that rolls the steel material FE. Three cylindrical portions 4d are provided from both ends in this order.

  4 is an enlarged cross-sectional view of the left bearing device 10 in FIG. In addition, since the right side bearing apparatus 10 is the same structure in FIG. 3, description is abbreviate | omitted. In FIG. 4, a large-diameter portion 11a and a small-diameter portion 11b are coaxially formed inside the housing main body 11 whose lower surface is fixed. A self-aligning roller bearing 12 is disposed in the large-diameter portion 11a. The self-aligning roller bearing 12 includes an outer ring 12a fitted to the large-diameter portion 11a, an inner ring 12b fitted to the second cylindrical portion 4c of the roller 4, and rollers 12c arranged in a double row between both the wheels 12a and 12b. 12c and a spacer 12d disposed between the rollers 12c and 12c. At the center of the outer ring 12a, a hole 12e for allowing the lubricating oil to pass is formed.

  Two seals (seal devices) 13A and 13B are fixed to the inner periphery of the small diameter portion 11b of the housing body 11, and the seal lips 13a and 13b are the third cylindrical portion of the roller 4 facing the small diameter portion 11b. It is in contact with the outer peripheral surface of 4d. The contact positions of the seal lips 13a, 13b are radially inward from the center positions of the rollers 12c, 12c of the self-aligning roller bearing 12. In other words, the seal lip diameter φS of the seals 13A and 13B is smaller than the PCD (pitch circle diameter) φP of the rollers 12c and 12c.

  The large diameter portion 11 a of the housing body 11 is shielded by the lid member 14. The lid member 14 is fixed to the housing body 11 with a plurality of (six here) bolts B arranged at equal intervals in the circumferential direction. The housing body 11 and the lid member 14 constitute a housing. A circumferential groove 11e is formed on an end surface of the housing body 11 facing the lid member 14, and the housing body 11 and the lid member 14 are sealed by an O-ring OR arranged therein.

  Further, a seal 15 is fixed to the inner periphery of the central opening 14a of the lid member 14, and the lip of the first cylindrical portion 4b (smaller diameter than the third cylindrical portion 4d) of the roller 4 facing the central opening 14a. It is in contact with the outer peripheral surface. Therefore, the seals 13A, 13B, and 15 prevent water and the like for cooling the steel material FE from entering the housing main body 11, so that the long life of the self-aligning roller bearing 12 can be secured. Here, the lubricating oil and air supplied to the inside of the housing are discharged to the outside only from between the seal lips 13a and 13b and the roller 4. For example, the diameter of the lubricating oil and air suitable for a position higher than the lubricating oil surface of the lid member 14 The pressure inside the housing may be adjusted by providing the throttle hole.

  On the lower surface side of the large-diameter portion 11 a of the housing body 11, a lubricating oil supply path whose inner end portion opens into the large-diameter portion 11 a and communicates with the hole 12 e and whose outer end portion opens in the side surface of the housing body 11. 11c is formed. An outer end portion of the lubricating oil supply passage 11c is connected to the pipe 7 (see FIG. 3) via a check valve 16 disposed outside the housing body 11.

  FIG. 5 is a cross-sectional view of the check valve 16. In FIG. 5, the pipe-joint check valve 16 has a small-diameter passage 16b, a large-diameter passage 16c, and a tapered seat surface 16d connecting the passages formed in a hollow cylindrical main body 16a. In the large-diameter passage 16c, a poppet 16f is disposed as a valve body having a contact surface 16e that can be in close contact with the seat surface 16d on the tip side. The poppet 16f is movable in the large-diameter passage 16c between a position where the contact surface 16e is in close contact with the sheet surface 16d and a position separated from the sheet surface 16d. A flange portion 16g for receiving a spring is formed on the side surface of the poppet 16f. On the other hand, a disc-shaped spring receiver 16h is screwed to the open end side of the large-diameter passage 16c. Here, a fluid passage hole 16i is formed in the spring receiver 16h. A coil spring 16j that biases the poppet 16f toward the seat surface 16d is disposed between the spring receiver 16h and the flange portion 16g of the poppet 16f. As a result, of the both ends of the check valve 16, the end on the biasing direction side of the coil spring 16j is the inlet IN, and the end on the reverse direction is the outlet OUT.

  According to the check valve 16, the flow of the lubricating oil in the direction of arrow A from the inlet IN to the outlet OUT is pushed by the poppet 16f against the urging force of the coil spring 16j by the air pressure on the pipe 7 side, and the seat surface 16d Further, the contact surface 16e is allowed to be separated, which is permitted. On the other hand, the flow of lubricating oil in the direction of arrow B from the outlet OUT to the inlet IN is prevented because the contact surface 16e remains in contact with the seat surface 16d even if the internal pressure of the lubricating oil supply passage 11c increases. The Rukoto. Thereby, the check valve 16 allows the flow of the lubricating oil only in one direction.

  In FIG. 3, the lubricating oil supply path 11 c of the housing body 11 is connected to the mixer 5 via a check valve 16 and a pipe 7. The mixer 5 serving as a supply unit has a function of mixing oil (lubricating oil) and pressurized air separately supplied from the oil / air lubrication device 6 and pumping them through a pipe 7. The piping 7 and the lubricating oil supply path 11c constitute a lubricating oil supply system path. The mixer 5, the pipe 7, the check valve 16, and the lubricating oil supply path 11c constitute a lubricating oil supply device.

  The operation of this embodiment will be described. In the continuous casting facility shown in FIG. 1, the roller 4 rotates at an extremely low speed of about 3 rotations per minute in response to the supply of the steel material FE. When the spherical roller bearing 12 rotatably supports the roller 4 with respect to the housing body 11 and the roller 4 bends due to a large load generated when the steel material FE is rolled, the bearing device 10 The self-aligning roller bearing 12 swings in accordance with the bending, so that problems such as twisting do not occur.

  During rolling, the inside of the chamber 9 is in a state of high temperature and water droplets scattered. According to the present embodiment, the lubricating oil supplied from the mixer 5 through the pipe 7 into the housing main body 11 is simultaneously pressurized by the pressurized air, via the lubricating oil supply path 11c and the hole 12e. It is supplied to the inside of the self-aligning roller bearing 12 and lubricates the rolling surfaces of the rollers 12c and 12c. Thus, by using oil-air lubrication that supplies lubricating oil using pressurized air, it is possible to always supply clean lubricating oil and to increase the internal pressure of the housing body 11 and to suppress the entry of foreign matter. . The lubricating oil supplied to the inside of the self-aligning roller bearing 12 is stored in the large diameter portion 11 a of the housing body 11, but the excess lubricating oil is transferred to the outside from between the seal lips 13 a and 13 b and the roller 4. And are collected in a tank (not shown).

  According to the present embodiment, lubricating oil is stored in the housing in order to lubricate the self-aligning roller bearing 12, and the inner diameter φS of the seal lips 13a and 13b is the PCD of the self-aligning roller bearing 12. Since it is smaller than φP, the lubricating oil stored in the housing leaks outward from between the seal lips 13a, 13b and the roller 4. Therefore, the position of the lubricating oil surface is always the same height, and the self-aligning roller bearing 12 can be lubricated in the same state. Furthermore, since the inside of the housing is pressurized by the gas supplied from the lubricating oil supply device, the inner pressure is higher than the outer pressure across the seal lips 13a and 13b, so that foreign matter enters from the outside. This can be effectively suppressed.

As shown in FIG. 17, the tightening force (tightening force) F of the seal 13A (13B) is mainly generated by the tension of the annular coil ring 13c (13d) provided therein. Usually, since the internal pressure Pi is higher than the external pressure Po (Pi> Po), there is a low possibility that foreign matter enters from the outside. On the other hand, if a problem occurs in the oil / air lubrication device 6 or its piping, the internal pressure Pi may be lower than the external pressure Po (Pi <Po). Therefore, even in such a case, the tension force F of the seal 13A is set to a predetermined value (for example, 0.1 kgf / cm ² or more) so that foreign matter does not enter from the outside.

  Furthermore, even when the mixer 5 and the pipe 7 are damaged due to an accident, and the supply of oil-air lubrication is interrupted, the supply of the steel material FE cannot be stopped immediately. In such a case, until the restoration, the self-aligning roller bearing 12 is lubricated with the lubricating oil stored in the large diameter portion 11a. However, in the case of the continuous casting equipment shown in FIG. 1, the steel material FE is first supplied downward in the vertical direction and then gradually oriented to be horizontal. Therefore, the housing body 11 of the bearing device 10 is As shown in FIG. 6, the top-to-bottom direction changes according to the installation position. In FIG. 6, the housing body 11 is shown in a trapezoidal shape, with the narrower side being the top side (steel material side) and the wider side being the ground side.

  As is clear from FIG. 6, most of the bearing device 10 provided on the lower side of the steel material FE has a non-return check because the lubricating oil supply passage 11 c is located below the large diameter portion 11 a (see FIG. 4) in the direction of gravity. If the valve 16 is not provided, when the oil-air lubrication is interrupted, the lubricant may flow backward through the pipe 7, and the lubricating oil stored in the large diameter portion 11a may flow out to the outside. According to the present embodiment, as shown in FIG. 5, the check valve 16 prevents the lubricating oil from leaking out from the lubricating oil supply passage 11 c side of the housing main body 11, so that the posture of the housing main body 11 is affected. Even if the mixer 5 or the pipe 7 is damaged, the self-aligning roller bearing 12 can be lubricated. Accordingly, it is sufficient to prepare the housing main body 11 having the same position of the lubricating oil supply passage 11c, the cost is greatly reduced, parts management is simplified, and spare parts are easily secured.

  FIG. 7 is a cross-sectional view of a bearing device 10 ′ according to the second embodiment. The present embodiment is different only in that a check valve 16 ′ using a ball as a poppet is built in the housing body 11. Bolts are not shown. Since common points are the same as those in the above-described embodiment, description thereof is omitted. According to this Embodiment, the piping 7 from the mixer 5 to the housing main body 11 is simplified, and installation becomes easy. In the present embodiment, a packing PK is disposed between the housing main body 11 and the lid member 14 to seal between the two.

  18 is a cross-sectional view of the bearing device according to the third embodiment, and FIG. 19 is a view of the configuration of FIG. 18 as viewed in the direction of the arrow IXX. This embodiment is mainly different from the embodiment shown in FIG. 4 in that the lid member 14 is provided with a throttle hole 14b penetrating in the axial direction. The throttle hole 14b is disposed radially outside the inner diameter φS of the seal lips 13a, 13b and radially inner than the PCD φP of the self-aligning roller bearing 12. The throttle hole 14b has a function of discharging the lubricating oil inside the housing and a function of adjusting the pressure inside the housing. Therefore, it is inappropriate that the diameter (cross-sectional area) of the throttle hole 14b is too large or too small.

  When lubricating oil is discharged from the seal lips 13a and 13b, there is a problem that recovery is difficult. On the other hand, if the lubricating oil is discharged from the throttle hole 14b, as shown in FIG. 18, the pipe H is connected to the throttle hole 14b, so that the lubricating oil can be efficiently recovered in the recovery tank T without leaking. it can. In addition, the amount of lubricating oil leaked from the seal lips 13a and 13b varies depending on the tightening force and tends to vary widely. However, by providing the throttle hole 14b, an appropriate amount of lubricating oil can be discharged stably. can do. When opening the throttle hole 14b to the atmosphere, as shown by the dotted line, a check valve CV (same configuration as the check valve 16) is provided to allow foreign matter to enter the housing through the throttle hole 14b. Can be suppressed.

  In the state shown in FIG. 19, the position of the lowest inner peripheral surface of the throttle hole 14b coincides with the lowest position of the PCD of the rollers 12c and 12c. Accordingly, in such a state, the lubricating oil supplied from the outside through the lubricating oil supply passage 11c is stored at least in the housing body 11 up to the position of the PCD of the rollers 12c, 12c. When the supply of oil-air lubrication is interrupted due to a failure, the rolling surfaces of the rollers 12c and 12c can be lubricated with the lubricating oil stored up to the PCD position.

  Here, it is assumed that the housing main body 11 is tilted within a range of 30 degrees in either the left or right direction. Then, the position of the throttle hole 14b increases in accordance with the inclination, but the position of the inner peripheral surface of the throttle hole 14b that is the lowest at the maximum is the position where the seal lip diameter of the seals 13A and 13B is the lowest (or slightly lower). (See the dotted line in FIG. 19). As a result, the lubricating oil supplied from the outside through the lubricating oil supply passage 11c is discharged from the throttle hole 14b instead of from the seals 13A and 13B, and the throttle hole 14b is connected to a pipe (not shown). By connecting to the tank or the like, all the lubricating oil discharged from the housing body 11 can be recovered.

  When the inclination of the housing body 11 exceeds 30 degrees, the phase between the lid member 14 and the housing body 11 can be appropriately changed (relatively rotated) every 60 degrees by removing the bolt B. Thereby, the position of the aperture 14b can be adjusted so that it is always within ± 30 degrees with respect to the lowest state shown in FIG. Obviously, if the number of bolts B is 8, the phase can be adjusted every 45 degrees, and if it is 10, the phase can be adjusted every 36 degrees.

  FIG. 8 is a schematic diagram showing the entire system of an oil / air supply device (also referred to as a lubricating oil supply device) including the bearing device according to the above-described embodiment. In FIG. 8, a mixer 5 commonly used as an oil / air supply unit mixes compressed air supplied from a main unit (not shown) and lubricating oil (oil) as a target fluid to generate oil / air. The oil-air is evenly distributed and sent out to a plurality of pipes.

  A plurality of pipes 7a to 7f (corresponding to the pipe 7 in FIG. 3, the same applies hereinafter) are connected to the mixer 5, but some of the pipes 7b to 7e are omitted (the same applies hereinafter). Here, in an example in which a distributor is not provided, an oil supply pipe 50a is connected to the pipe 7a, and the oil supply pipe 50a is connected to, for example, a housing body serving as a supply destination of the target fluid via a check valve 16A. 11 (object to be lubricated) is connected.

  On the other hand, in the example in which the distributor 32 is provided, for example, the distributor 32 is connected to the pipe 7f, and the distributor 32 is provided with a plurality of distribution ports. A pipe 50n and the like are connected, and a housing body 11 (lubrication object) as an object to which a target fluid is supplied is connected to the oil supply pipe 50n via a check valve 16N, for example.

  The mixer 5 is connected with a compressed air pipe 20 for supplying compressed air, and an electromagnetic on-off valve 21 is interposed in the compressed air pipe 20. According to the present embodiment, the check valves 16A to 16N (corresponding to the check valve 16 in FIG. 5, the same applies hereinafter) connected to the oil supply pipes 50a to 50n prevent the backflow of the lubricating oil as described above. It is supposed to be.

  FIG. 9 is a schematic diagram illustrating an oil / air supply device (also referred to as a lubricating oil supply device) and an abnormality detection method thereof that can be used in the bearing device according to the above-described embodiment. In the embodiment described below, in addition to preventing the backflow of the lubricating oil according to the effect of the above-described embodiment, an abnormality can be detected. In FIG. 9, a mixer 5 mixes compressed air supplied from a main unit (not shown) and lubricating oil (oil) as a target fluid to generate oil air, and distributes the oil air evenly. It is a sending device.

  A plurality of pipes 7 a to 7 f are connected to the mixer 5. Here, in an example in which a distributor is not provided, an oil supply pipe 50a is connected to the pipe 7a, and the oil supply pipe 50a is connected to, for example, a housing body serving as a supply destination of the target fluid via a check valve 16A. 11 (object to be lubricated) is connected.

  On the other hand, in the example in which the distributor 32 is provided, for example, the distributor 32 is connected to the pipe 7f, and the distributor 32 is provided with a plurality of distribution ports. A pipe 50n and the like are connected, and a housing body 11 (lubrication object) as an object to which a target fluid is supplied is connected to the oil supply pipe 50n via a check valve 16N, for example.

  The mixer 5 is connected with a compressed air pipe 20 for supplying compressed air, and an electromagnetic on-off valve 21 is interposed in the compressed air pipe 20.

  In the present embodiment, upstream check valves 30a to 30f are interposed in the flow direction in the pipes 7a to 7f, respectively. Further, downstream check valves 16A to 16N are interposed in the flow direction in the oil supply pipes 50a to 50n, respectively.

  Pressure sensors 40a to 40f are interposed between the upstream check valves 30a to 30f and the corresponding downstream check valves 16A to 16N, respectively. That is, in the present embodiment, the upstream check valve 16A to 16N corresponding to each upstream check valve 30a to 30f and the upstream check valve 16 when there is a distributor 32. Pressure sensors 40a to 40f are respectively interposed between the valves and the corresponding distributors. Thereby, the pressures in the pipes 7a to 7f and 50a to 50n from the mixer 5 to the housing body 11 or from the mixer 5 to the distributor 32 to the housing body 11 can be monitored.

  Next, FIG. 10A is a graph showing the movement of the electromagnetic on-off valve 21. FIG. 10 (B) is a graph showing the normal pressure (no leakage) in the oil supply pipes 50a to 50n. FIG. 10C is a graph illustrating the pressures in the oil supply pipes 50a to 50n when there is an abnormality (with leakage). FIG. 10D is a graph showing an abnormal display due to leakage.

  During the system operation, the electromagnetic on-off valve 21 is always opened, and the electromagnetic on-off valve 21 is closed for a certain period of time as shown in FIG.

  During normal operation (no leakage), as shown in FIG. 10B, the supply of compressed air is somewhat reduced because the supply of compressed air is stopped by closing the electromagnetic on-off valve 21.

  However, the pressure in the pipes 7a to 7f and 50a to 50n is caused by the check valves 16A to 16N on the downstream side corresponding to the pair of upstream check valves 30a to 30f. Kept in pressure. In addition, since the compressed air flows when the electromagnetic opening / closing valve 21 is opened again, the supply pressure rises again to the normal time.

  On the other hand, when there is an abnormality (leak is present), the supply pressure is reduced to atmospheric pressure by closing the electromagnetic on-off valve 21 as shown in FIG.

  For this reason, before the electromagnetic on-off valve 21 is opened, the pressure in the pipes 7a to 7f and 50a to 50n is lower than the set values of the respective pressure sensors 40a to 40f, so that the system is as shown in FIG. This error is displayed.

  In the present embodiment, when the distributor 32 is used, the number of pressure sensors used can be reduced.

  As described above, in the present embodiment, upstream check valves 30a to 30f are respectively installed in the pipes 7a to 7f in the vicinity of the mixer 5, and downstream of the pipes 50a to 50n in the vicinity of the housing body 11. Check valves 16A to 16N are respectively installed, and the supply of oil and air is intentionally suspended during operation, and compressed oil and air lubrication is performed on upstream check valves 30a to 30f and downstream check valves 16A to 16N. The pressure sensors 40a to 40f that are confined between them and the upstream check valves 30a to 30f and the corresponding ones of the downstream check valves 16A to 16N. By measuring the pressure, it is possible to measure the leakage state of oil air from the joint portions of the pipes 7a to 7f and 50a to 50n from the mixer 5 to the housing body 11.

  In other words, the present embodiment intentionally shuts off the supply of compressed air at certain intervals during operation for a certain period of time, so that the upstream check valves 30a to 30f and the downstream check valves 16A to 16N Enclose the compressed air between the corresponding ones. In this state, the pipes 7a to 7f and 50a to 50n are provided by pressure sensors 40a to 40f installed between the upstream check valves 30a to 30f and the corresponding ones of the downstream check valves 16A to 16N. By measuring the internal pressure, the leakage state from the mixer 5 to the housing body 11 or from the mixer 5 to the distributor 32 to the housing body 11 can be measured. That is, when there is no leak, there is no pressure drop, and when there is a leak, the pressure drops to atmospheric pressure.

  FIG. 11 is a schematic diagram showing an oil / air supply apparatus according to a first modification of the present embodiment. In this modification, the electromagnetic on-off valve 21 is normally in a “closed” state when stopped, and is configured to switch to an “open” state when supplying compressed air.

  Further, no upstream check valve is provided, and a pressure sensor 40 is provided between the electromagnetic on-off valve 21 and the mixer 5. The pressure sensor 40 can detect the pressure from the downstream side of the electromagnetic on-off valve 21 to the upstream side or downstream side of the mixer 5 and the downstream check valves 16A to 16N.

  In this case, in the “closed state” of the electromagnetic on-off valve 21, between the downstream side of the electromagnetic on-off valve 21 and the upstream or downstream side of the mixer 5 and the downstream check valves 16A to 16N, If a leak has occurred, the pressure can be detected by the pressure sensor 40. Therefore, the number of pressure sensors 40 can be reduced, and the cost can be reduced.

  FIG. 12 is a schematic diagram showing an oil / air supply apparatus according to a second modification of the present embodiment. In this modification, an upstream check valve 30 is interposed between the downstream side of the electromagnetic on-off valve 21 and the upstream side of the mixer 5.

  A pressure sensor 40 is provided between the upstream check valve 30 and the mixer 5. The pressure sensor 40 can detect the pressure from the downstream side of the upstream check valve 30 to the upstream side or downstream side of the mixer 5 and the downstream check valves 16A to 16N.

  In this case, when the electromagnetic on-off valve 21 is in the “closed state”, from the downstream side of the upstream check valve 30 to the upstream side or downstream side of the mixer 5 and the downstream check valves 16A to 16N. If a leak occurs in the meantime, the pressure can be detected by the pressure sensor 40. Therefore, the number of pressure sensors 40 can be reduced, and the cost can be reduced.

  Next, an incompressible fluid conveyance device and an abnormality detection method thereof according to another embodiment for conveying and supplying an incompressible fluid such as oil or grease to an object under pressure will be described with reference to FIG.

  The distributor 101 is a device that appropriately distributes and sends out incompressible fluid such as oil and grease (hereinafter, referred to as oil) supplied by pressure from an incompressible fluid supply source 100 such as oil and grease.

  A plurality of pipes 7 a to 7 f are connected to the distributor 101. A pipe 105a is connected to the pipe 7a, and a housing body 11 serving as an oil supply destination of the target fluid is connected to the pipe 105a via a check valve 16A, for example.

  In the example in which the child distributor 102 is provided as shown in the pipe 7f, for example, the child distributor 102 is connected to the pipe 7f, and the child distributor 102 is provided with a plurality of distribution ports. Each distribution port is connected to a pipe 105n or the like, and the pipe 105n is connected to, for example, a housing main body 11 as an object to be a target fluid oil supply destination via a check valve 16N. .

  In addition, an electromagnetic on-off valve 121 is interposed in the oil supply pipe 120 from the oil supply source 100 to the distributor 101.

  In the present embodiment, upstream check valves 130a to 130f are interposed in the flow direction in the pipes 7a to 7f, respectively. Further, downstream check valves 16A to 16N are interposed in the flow direction in the downstream pipes 105a to 105n, respectively.

  Accumulators 150a to 150f and pressure sensors 140a to 140f are interposed between the upstream check valves 130a to 130f and the corresponding downstream check valves 16A to 16N, respectively. That is, in the second embodiment, when there is the child distributor 102 between the upstream check valves 130a to 130f and the corresponding downstream check valves, the upstream check valve is provided. Pressure sensors 140a to 140f are interposed between the stop valve and the corresponding child distributor 102, respectively. Thereby, the pressures in the pipes 104 and 105a to 105n up to the check valves 16A to 16N or the check valves 130f to 131n can be monitored.

  During system operation, the electromagnetic on-off valve 121 is always opened, and the electromagnetic on-off valve 121 is closed for a certain period of time at a certain period.

  When normal (no leakage), the supply of oil is somewhat reduced because the oil supply is stopped by closing the electromagnetic on-off valve 121.

  However, the pressure in the pipes 104, 105a to 105n is such that the supply paths between the pair of upstream check valves 130a to 130f and the corresponding downstream check valves 16A to 16N are sealed. The pressure is accumulated by the corresponding accumulators 150a to 150f and maintained at a pressure in the vicinity of the check valve cracking pressure. In addition, since the compressed air flows when the electromagnetic on-off valve 121 is opened again, the supply pressure rises again to the normal time.

  On the other hand, when there is an abnormality such as a leak in the pipe, when a certain amount of volume accumulated by the accumulators 150a to 150f due to the internal pipe pressure during operation leaks out of the pipe due to the closing of the on-off valve 121. The pressure in the pipe is reduced to atmospheric pressure.

  For this reason, before the electromagnetic on-off valve 121 opens, the system can display an abnormality because the pressure in the pipes 104 and 105a to 105n is lower than the set values of the pressure sensors 140a to 140f.

  In the present embodiment, when the child distributor 102 is used, the number of pressure sensors used can be reduced.

  As described above, in the present embodiment, the upstream check valves 130a to 130f are installed in the pipes 7a to 7f in the vicinity of the distributor 101, but the check valves 130a to 130f are used instead of the pipes 7a to 7f. It is also possible to attach 130f directly to the distributor 101.

  Further, downstream check valves 16A to 16N are respectively installed in the pipes 105a to 105n in the vicinity of the housing body 11, and the supply of oil is intentionally stopped during operation, and the compressed oil is checked upstream. It is confined in the accumulators 150a to 150f provided between the valves 130a to 130f and the corresponding ones of the downstream check valves 16A to 16N, and the upstream check valves 130a to 130f and the downstream check valve Pipes and joints between the check valves 130a to 16A and between the check valves 130f to 16N by measuring the pressure with the pressure sensors 140a to 140f installed between the corresponding ones with the valves 16A to 16N It is possible to measure the leakage state of oil from the part.

  In place of the accumulator, a flexible pipe having a pressure accumulation function as shown in FIG. 16 in the oil supply path between the upstream check valves 130a to 130f and the corresponding one of the downstream check valves 16A to 16N. You may use the path 330, for example, the steel pipe flexible hose wound helically.

  Next, FIG. 14 is a schematic diagram illustrating an oil supply apparatus according to a first modification of another embodiment. In this modification, the electromagnetic on-off valve 121 is normally in a “closed” state when stopped, and is configured to be switched to an “open” state when supplying oil from the oil supply source 100.

  Further, the upstream check valve shown in FIG. 13 is not provided here, and an accumulator 150 is provided between the electromagnetic on-off valve 121 and the distributor 101 and the pressure sensor 140 is provided. The pressure sensor 140 can detect the pressure from the downstream side of the electromagnetic on-off valve 121 to the upstream side or downstream side of the distributor 101 and the check valves 16A to 16N on the downstream side.

  In this case, in the “closed state” of the electromagnetic on-off valve 121, any leakage should occur between the downstream side of the electromagnetic on-off valve 121 and the upstream side or downstream side of the distributor 101 and the check valves 16A to 16N. Can be detected by the pressure sensor 140. Therefore, the number of pressure sensors 140 can be reduced, and the cost can be reduced.

  Moreover, in this modification, it can replace with the accumulator 150 by making the at least one part of the oil supply path of non-return valve 16A-16N into the appropriate flexible pipe line which has a pressure accumulation function. In the above embodiments, check valves are used. However, all or a part of these check valves may be safety valves 230 such as relief valves as shown in FIG. It may be a connector for pipe connection.

  The present invention has been described above with reference to the embodiments. However, the present invention should not be construed as being limited to the above-described embodiments, and can be changed or improved as appropriate. For example, not only a self-aligning roller bearing but various rolling bearings can be used.

It is a perspective view showing the outline of the continuous casting equipment using the bearing device concerning a 1st embodiment. It is a perspective view of the roller unit used for a continuous casting installation. It is sectional drawing of the bearing apparatuses 10 and 10 which support the one roller 4 arrange | positioned below with respect to the steel material FE. It is sectional drawing which expands and shows the left bearing apparatus 10 in FIG. 2 is a cross-sectional view of a check valve 16. FIG. It is the schematic which shows the state from which the top-and-bottom direction changes according to an installation position. It is sectional drawing of the bearing apparatus 10 'concerning 2nd Embodiment. It is the schematic which shows the system of the oil air supply apparatus (it is also called lubricating oil supply apparatus) containing the bearing apparatus which concerns on this Embodiment. It is a schematic diagram which shows about the oil-air supply apparatus which can be used for the bearing apparatus which concerns on another this Embodiment, and its abnormality detection method. FIG. 10A is a graph showing the movement of the electromagnetic on-off valve 21. FIG. 10 (B) is a graph showing the normal pressure (no leakage) in the oil supply pipes 50a to 50n. FIG. 10C is a graph illustrating the pressures in the oil supply pipes 50a to 50n when there is an abnormality (with leakage). FIG. 10D is a graph showing an abnormal display due to leakage. It is a schematic diagram which shows the oil-air supply apparatus which concerns on the 1st modification of this Embodiment. It is a schematic diagram which shows the oil-air supply apparatus which concerns on the 2nd modification of this Embodiment. It is a schematic diagram shown about the incompressible fluid conveyance apparatus which concerns on another embodiment, and its abnormality detection method. It is a schematic diagram which shows the oil supply apparatus which concerns on the 1st modification of another embodiment. It is a figure which shows the safety valve 230 which can be used instead of a non-return valve. It is a figure of the steel pipe flexible hose which can be used instead of an accumulator, for example, was wound spirally. It is sectional drawing of a seal lip. It is sectional drawing of the bearing apparatus 10 '' concerning 3rd Embodiment. It is the figure which looked at the bearing apparatus shown in FIG. 18 in the arrow IXX direction.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Introduction part 2 Discharge part 3 Roller unit 4 Roller 4a Rolling part 4b 1st cylindrical part 4c 2nd cylindrical part 4d 3rd cylindrical part 5 Mixer 6 Oil-air lubrication apparatus 7 Piping 7a-7f Piping 7a-7f, 50a-50n Piping DESCRIPTION OF SYMBOLS 9 Chamber 10 Bearing apparatus 11 Housing main body 11a Large diameter part 11b Small diameter part 11c Lubricating oil supply path 12 Self-aligning roller bearing 12a Outer ring 12b Inner ring 12c Roller 12d Spacer 12e Hole 13A, 13B Seal 14 Cover member 14a Central opening 14b Restriction hole DESCRIPTION OF SYMBOLS 15 Seal 16,16A-16N Check valve 16a Main body 16b Small diameter passage 16c Large diameter passage 16d Seat surface 16e Contact surface 16f Poppet 16g Flange part 16h Spring receiver 16i Fluid passage hole 16j Coil spring 20 Compressed air piping 21 Electromagnetic switching valve 30 Check valve Valve 31 Check 32 Distributor 40 Pressure sensor 50a Oil supply pipe 100 Oil supply source 101 Distributor 102 Child distributor 104 Pipe 105a to 105n Pipe 120 Oil supply pipe 121 Electromagnetic on-off valve 130a to 130f Check valve 140 Pressure sensor 140a to 140f Pressure sensor 150 Accumulator 150a to 150f Accumulator 230 Safety valve 330 Pipe line CV Check valve FE Steel material IN Inlet OUT Outlet H Pipe T Recovery tank OR O-ring PK Packing

Claims (4)

A bearing device used for a roll support device for steel equipment, a housing capable of storing lubricating oil, a rolling bearing disposed in the housing and supporting a rotating shaft, and lubricating oil gas in the rolling bearing. In a bearing device having a lubricating oil supply device that supplies a mixture and a seal device that seals between the rotating shaft and the housing,
The seal device has an annular seal lip that is fixed to the housing and abuts against the rotating shaft in order to maintain the oil level position of the lubricating oil in the housing,
The inner diameter of the seal lip is smaller than the PCD of the rolling bearing,
The seal lip has a pressing force that prevents fluid from entering the interior of the housing through the seal lip when the pressure inside the housing is lower than the pressure outside the housing. A bearing device characterized by that. A bearing device used for a roll support device for steel equipment, a housing capable of storing lubricating oil, a rolling bearing disposed in the housing and supporting a rotating shaft, and lubricating oil gas in the rolling bearing. In a bearing device having a lubricating oil supply device that supplies a mixture and a seal device that seals between the rotating shaft and the housing,
The seal device has an annular seal lip that is fixed to the housing and abuts against the rotating shaft,
A lid member capable of changing the assembly phase for the housing, and the throttle hole for adjusting the pressure inside is formed to an external pressure of the housing,
A bearing device , wherein an assembly phase of the lid member is adjusted so that the throttle hole is disposed at a position not less than an inner diameter of the seal lip and not more than a PCD of the rolling bearing. The bearing device according to claim 2 , wherein a check valve is provided in the throttle hole. The bearing device according to claim 2 or 3 , wherein the inside of the housing communicates with the outside only through the throttle hole.

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