JP2007255637A - Rolling bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a low cost rolling bearing capable of keeping sealing performance of an inside of a bearing constant for a long period of time by improving installation properties and wear resistance of a sealing plate during rotation of the bearing. <P>SOLUTION: An annular sealing member 36 is provided to cover one side space area of annular space area surrounded by a rotary wheel 28 and stationary wheel 30 is provided on both sides of a plurality of rolling elements 32. The sealing member is installed in a seal groove 28g of the rotary wheel at a base end 36e thereof and extends toward the stationary wheel at a tip 36f thereof, is provided with a foreign matter intrusion prevention mechanism, and includes an annular core bar 42 extending from the base end toward the tip. The annular core bar forms a curl shape having the base end 42e bent along a shape of the seal groove, has at least surface of the base end covered by an elastic body 44. The elastic body covering the base end of the core bar is press-fitted and adheres in the seal groove without a gap under a condition where the base end is caulked toward the seal groove and the base end of the sealing member is installed in the seal groove. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a rolling bearing that supports a rotating shaft that rotates at a high speed.

  Conventionally, in various devices such as submersible pumps and motors having a rotating shaft that rotates at high speed, various types of rolling in which foreign matters (e.g. lubricants such as oil and grease, water, dust) are prevented from entering the bearings are included. Bearings are incorporated. As an example, Patent Document 1 discloses a rolling in which annular sealing plates 6 and 8 are arranged in a double manner between an inner ring 2 and an outer ring 4 which are opposed to each other so as to be relatively rotatable as shown in FIG. Bearings have been proposed (first prior art). In this case, one sealing plate (outer sealing plate) 6 is arranged outside (bearing outer side) of the other sealing plate (inner sealing plate) 8, and the outer sealing plate 6 has a base end 6e. It is fixed to a locking groove 2g formed on the outer peripheral surface 2s of the inner ring 2 with a latch, and its tip 6f is in sliding contact with the inner peripheral surface 4s of the outer ring 4 (first sliding contact portion).

  On the other hand, the inner sealing plate 8 has a base end 8e fixed to a locking groove 4g formed on the inner peripheral surface 4s of the outer ring 4, and has two lips 8a and 8b provided at the tip. It has been. In this case, one lip 8a is in sliding contact with the inner surface 6n of the outer sealing plate 6 (second sliding contact portion), and the other lip 8b is in sliding contact with the outer peripheral surface 2s of the inner ring 2 (first contact). 3 sliding contact part). According to such a configuration, the first to third sliding contact portions exist in series with each other from the outside of the bearing to the inside of the bearing with respect to the foreign matter intrusion path. Prevents intrusion into the bearing. In addition to this, for example, Patent Documents 2 and 3 propose a rolling bearing in which sealing plates are arranged in double between inner and outer rings.

  Further, for example, FIG. 5B proposes a bearing configuration example in which sealing plates 10 and 12 for preventing entry of foreign substances are provided on the output shaft side of the commutator motor of the electric tool (second prior art). ). In such a bearing configuration example, the two rotary shafts 14 and 16 are rotatably supported with respect to the housing 22 via the rolling bearings 18 and 20, and the rotary motion of one of the rotary shafts 14 is a gear mechanism. It is transmitted to the other rotating shaft 16 via. As a gear mechanism, a first gear 24 fixed to one rotating shaft 14 and a second gear 26 meshed with the first gear 24 and fixed to the other rotating shaft 16 are applied. Has been.

  In such a bearing configuration example, one sealing plate 10 is interposed between the other rotating shaft 16 and the housing 20, and the other sealing plate 12 allows the other rotating shaft 16 to rotate freely. It is incorporated between the inner and outer rings 20a, 20b of the rolling bearing 20 to be supported. As a result, entry of the foreign matter into the bearing is prevented.

  By the way, in the first prior art (FIG. 5 (a)), since the base ends 6e, 8e of the sealing plates 6, 8 are fixed to the locking grooves 2g, 4g by locking, the rolling bearing rotates at high speed. In this case, the base ends 6e and 8e of the sealing plates 6 and 8 are easily detached from the locking grooves 2g and 4g due to the centrifugal force, and the sealing plates 6 and 4g with respect to the locking grooves 2g and 4g of the inner and outer rings 2, 4 There is a case where the wearability of the base ends 6e, 8e of 8 is lowered. Thereby, for example, when a gap is formed between the base ends 6e, 8e of the respective sealing plates 6, 8 and the locking grooves 2g, 4g, foreign matter enters the bearing from the gap. There is a fear.

  Further, when centrifugal force accompanying high-speed rotation of the bearing acts on the tips 6f, 8a, 8b of the sealing plates 6, 8, the sliding contact pressure between the tip 6f of the sealing plate 6 and the inner peripheral surface 4s of the outer ring 4, and The sliding contact pressure between the tip (lip 8a, 8b) of the sealing plate 8 and the inner side surface 6n of the outer sealing plate 6 and the outer peripheral surface 2s of the inner ring 2 is increased, for example, the tip 6f of each sealing plate 6, 8 , 8a and 8b may become difficult to maintain the sealability inside the bearing constant over a long period of time.

Further, in the second prior art (FIG. 5B), the sealing plates 10 and 12 are required between the rotating shaft 16 and the housing 20 in addition to the inner and outer rings 20a and 20b of the rolling bearing 20, respectively. There is a problem in that the number of parts for preventing the intrusion of foreign matter into the bearing increases, thereby increasing the manufacturing cost.
JP-A-9-196071 JP 2002-339999 A Japanese Patent Laid-Open No. 11-210771

  The present invention has been made to solve such a problem, and its object is to improve the mounting performance and wear resistance of the sealing plate during rotation of the bearing, thereby improving the sealing performance inside the bearing over a long period of time. The object is to provide a low-cost rolling bearing that can be kept constant.

  In order to achieve such an object, the present invention provides a rotating wheel that can rotate in a predetermined direction, a stationary wheel that can be fixed to face the rotating wheel, and a rolling wheel that can freely roll between opposing surfaces of the rotating wheel and the stationary wheel. A rolling bearing having a plurality of interposed rolling elements, and covering at least one of the annular space areas surrounded by a rotating wheel and a stationary ring on both sides of the plurality of rolling elements, respectively. An annular sealing member is provided, and the annular sealing member is attached to an annular sealing groove formed at the base end of the rotating wheel, the distal end extends toward the stationary ring, and the inside of the bearing It has a foreign matter intrusion prevention mechanism for preventing foreign matter from entering the base, and has an annular cored bar extending from the base end toward the tip. It has a curl shape that is bent along the shape of the seal groove, At least the base end that forms the curl shape is covered with an elastic material, and the base end of the core metal that forms the curl shape is crimped toward the seal groove, so that the base end of the sealing member is sealed with the seal groove. In this state, the elastic material coated on the base end of the cored bar is pressed against the seal groove and is in close contact with the gap.

  In the present invention, the foreign matter intrusion prevention mechanism may be configured by inclining the tip of the sealing member in a non-contact state along the inclined surface formed on the opposing surface of the stationary ring, or The foreign matter intrusion prevention mechanism may be configured by inclining the tip of the sealing member so as to be in a contact state with a relatively low contact pressure along an inclined surface formed on the opposing surface of the stationary wheel. Further, the foreign matter intrusion prevention mechanism may be configured by arranging a plurality of protrusions having a tapered trapezoidal shape at predetermined intervals along the circumferential direction from the proximal end to the distal end on the bearing inner side of the sealing member.

  According to the present invention, a low-cost rolling bearing capable of maintaining the sealing performance inside the bearing constant over a long period of time by improving the mounting performance and wear resistance of the sealing plate during rotation of the bearing is realized. can do.

Hereinafter, a rolling bearing according to an embodiment of the present invention will be described with reference to the accompanying drawings.
As shown in FIGS. 1A and 1B, the rolling bearing 100 according to the present embodiment can be fixed to a rotating wheel (for example, an inner ring) 28 that can rotate in a predetermined direction and to face the rotating wheel 28. A plurality of rolling wheels interposed between a stationary wheel (for example, an outer ring) 30 and a facing surface between the rotating wheel 28 and the stationary wheel 30 (between the outer peripheral surface 28s of the inner ring 28 and the inner peripheral surface 30s of the outer ring 30). Rolling elements 32 and annular retainers 34 formed with a plurality of pockets (not shown) for rotatably holding the rolling elements 32 one by one, on both sides of the rolling elements 32. An annular sealing member 36 is provided so as to cover at least one of the annular space areas surrounded by the rotating wheel 28 and the stationary wheel 30. As the rolling element 32, for example, a ball or a roller can be applied, but a ball is assumed here as an example.

  In the rolling bearing 100 of the present embodiment, base ends 38e and 40e are fixed to annular seal grooves 30g formed on a stationary ring (outer ring) 30 on both sides of the plurality of rolling elements 32, respectively, and the distal ends are rotating wheels. An annular sealing plate 38, 40 extending toward the (inner ring) 28 is provided. Each of the sealing plates 38 and 40 is made of rubber containing a core metal (shown by hatching), and rubber lips 38f and 40f are provided at the tips thereof. In this case, the sealing plate 38 on one side is interposed between the annular sealing member 36 and the plurality of rolling elements 32, and the tip (lip 38 f) is the opposing surface (outer peripheral surface) 28 s of the rotating wheel 28. Is positioned in sliding contact with.

  The other side sealing plate 40 is provided on the opposite side of the one side sealing plate 38 with the plurality of rolling elements 32 interposed therebetween, and the tip (lip 40f) of the rotating ring (inner ring) 28 is provided. Positioning may be performed by sliding contact with the outer peripheral surface 28s, or may be performed in a non-sliding contact state. In this case, it is preferable that an air hole 40h for communicating the inside of the bearing and the outside of the bearing is formed in the base end 40e of the other sealing plate 40, for example. Thereby, since air can be circulated through the air hole 40h, it is possible to achieve a balance between the pressure inside the bearing and the pressure outside the bearing. As a result, for example, the sealing plate 40 is detached (dropped off, loosened). ) And the lip 40f can be prevented.

  Here, it is preferable to grind the outer peripheral surface 28 s of the rotating wheel (inner ring) 28. Grinding is a known processing method for applying a high-precision smooth finish to the surface (outer peripheral surface 28s) of the object to be ground (rotating wheel 28). By applying such grinding to the outer peripheral surface 28s of the rotating wheel 28, grinding is performed. The frictional resistance between the outer peripheral surface 28s and the tips of the sealing plates 38, 40 (the lips 38f, 40f) can be reduced to improve the slidability. As a result, the rotational performance during the rotation of the bearing can be maintained constant over a long period of time.

  In addition, it is preferable to interpose the lubricant J along the circumferential direction between the sealing plate 38 on one side and the annular sealing member 36. In this case, as the lubricant J, for example, oil or grease sealed in the bearing may be applied. In FIG. 1 (a), the interposition position of the lubricant J is schematically shown by hatching, but is not necessarily limited to this, and is not necessarily limited to this, and between the sealing plate 38 on one side and the annular sealing member 36. The lubricant J may be interposed over the entire space region.

  The annular sealing member 36 has a base end 36e attached to an annular seal groove 28g formed in the rotating wheel (inner ring) 28, a tip 36f extending toward the stationary ring (outer ring) 30, and It has a foreign matter intrusion prevention mechanism for preventing foreign matter (for example, lubricant such as oil and grease, water, dust) from entering the inside of the bearing, and an annular shape extending from the base end 36e toward the tip 36f. The core metal 42 is provided.

  The annular cored bar 42 has a curl shape whose base end 42e is bent along the shape of the seal groove 28g, and at least the base end 42e having the curl shape is covered with an elastic material 44 on the surface thereof. Has been. In the illustrated configuration example, as an example, the entire surface of the cored bar 42 extending from the base end 42e to the tip 42f is covered with an elastic material 44. For example, rubber or resin may be applied as the elastic member 44. In this case, when the base end 36e of the sealing member 36 is attached to the seal groove 28g, the base end 42e of the core bar 42 having a curl shape is caulked toward the seal groove 28g, so that the base end 42e of the core bar 42 is obtained. The elastic material 44 coated on the inside enters the seal groove 28g and presses against the seal groove 28g.

  In this state where the base end 36e of the sealing member 36 is attached to the seal groove 28g, the elastic material 44 that has entered the seal groove 28g together with the base end 42e of the core metal 42 attached by caulking is attached to the seal groove 28g. It adheres firmly and firmly without gaps. As a result, for example, even if the rotating wheel (inner ring) 28 rotates at a high speed or the vibration of the sealing member 36 increases accordingly, the base end 36e of the sealing member 36 does not easily come off from the seal groove 28g. The mounting property of the base end 36e of the sealing member 36 to the seal groove 28g can be kept constant. This prevents a conventional gap from being formed between the base end 36e of the sealing member 36 and the seal groove 28g, so that foreign matter does not enter the bearing from the outside of the bearing.

  In the present embodiment, the foreign matter intrusion prevention mechanism moves the tip 36f of the sealing member 36 along the inclined surface 30k formed at the end of the opposing surface (inner peripheral surface) 30s of the stationary ring (outer ring) 30. It is comprised by making it incline so that it may become a non-contact state. More specifically, a lip 46 is formed on the tip 36 f of the sealing member 36 by covering the tip 42 f of the core metal 42 with the elastic material 44, and the lip 46 extends along the inclined surface 30 k of the stationary wheel 30. Is positioned in a non-contact state. In this case, as shown in FIG. 1 (b), an extremely slight labyrinth L is formed between the lip 46 and the inclined surface 30k, so that the bearing is stationary (rotation stopped) and the bearing is rotated. Intrusion of foreign matter into the bearing can be reliably prevented.

  When the bearing rotates, the lip 46 made of the elastic material 44 is elastically deformed by the centrifugal force applied to the lip 46 from the sealing member 36 and is kept in a sliding contact state in which the lip 46 is slightly in contact with the inclined surface 30k. Since such a state is maintained even if the rotational speed of the bearing is increased, it is possible to reliably prevent foreign matter from entering the bearing during high-speed rotation. In this case, the lubricant J is applied to the lip 46 at least on the part facing the inclined surface 30k of the stationary wheel 30 (specifically, the sliding contact surface of the lip 46 that contacts the inclined surface 30k when the bearing rotates). Is preferred.

  As a result, the sliding contact pressure (friction resistance) between the lip 46 and the inclined surface 30k during the rotation of the bearing can be reduced, so that wear of the lip 46 can be prevented. In this case, the slidable contact state between the lip 46 and the inclined surface 30k can be kept constant, so that the sealability inside the bearing can be kept constant over a long period of time. In addition, as the lubricant J applied to the lip 46, for example, oil or grease sealed in the bearing may be applied.

  Further, as described above, the lubricant J is interposed along the circumferential direction between the sealing plate 38 on one side and the annular sealing member 36, so that the lip 46 is applied by the centrifugal force acting on the sealing member 36 when the bearing rotates. When contacting along the inclined surface 30k, the pressure (internal pressure) of the space between the sealing plate 38 and the sealing member 36 increases. Since the internal pressure at this time is higher than the pressure inside and outside the bearing (external pressure), the foreign matter trying to enter the bearing from between the lip 46 and the inclined surface 30k is prevented from entering by the action of the internal pressure. At the same time, a lubricant (lubricant enclosed in the bearing) that leaks to the outside of the bearing from between the front end (lip 38f) of the sealing plate 38 and the outer peripheral surface 28s of the rotating ring (inner ring) 28 The leakage is prevented by the action of. As a result, the sealability and lubricity inside the bearing can be maintained constant, and therefore the rotational performance during rotation of the bearing can be maintained constant over a long period of time.

  As described above, according to the present embodiment, the rolling bearing 100 capable of maintaining the sealing performance inside the bearing constant over a long period of time by improving the mounting property and wear resistance of the sealing plate during rotation of the bearing. Since the number of parts can be reduced as compared with the prior art, the manufacturing cost of the bearing can be greatly reduced.

Here, an embodiment in which such a rolling bearing 100 is applied to a submersible pump will be described with reference to FIG.
The submersible pump shown in FIG. 4 has a water suction port 48a and a discharge port 48b, a pump casing 48 in which an impeller 50 is rotatably arranged, and a vertical type disposed on the pump casing 48. And a housing 54 that houses a rotating shaft 52 to which the impeller 50 is attached.

  The housing 54 includes a motor chamber 54 a in which a motor (electric motor) that controls the rotating shaft 52 is accommodated, and an oil chamber 54 b provided in the housing 54 between the motor chamber 54 a and the pump casing 48. Has been. In this case, the rotating shaft 52 extends from the motor chamber 54a through the oil chamber 54b in the pump casing 48 along the vertical direction, and the impeller 50 is attached to the extending end.

  In the configuration example shown in the figure, the rolling bearing 100 (FIG. 1 (a)) according to the above-described embodiment is provided on the upper and lower sides of the motor chamber 54a in order to rotatably support the rotating shaft 52. It can be incorporated as a bearing. Note that the rolling bearing 56 disposed on the upper side of the motor chamber 54 a does not necessarily have the same configuration as the rolling bearing 100. In this case, the rolling bearing 100 disposed below the motor chamber 54a is preferably disposed so that the annular sealing member 36 is positioned on the impeller 50 side.

  The motor (electric motor) accommodated in the motor chamber 54 a includes a rotor (for example, a permanent magnet) 58 fixed to the rotating shaft 52 and a stator (for example, an electromagnet) fixed to the housing 54 so as to face the rotor 58. 60. On the other hand, in the oil chamber 54b, a mechanical seal 62 for sealing the motor chamber 54a in a liquid-tight state is fixed to the rotating shaft 52, and in order to improve wear resistance, lubricity, and the like of the mechanical seal 62. A fixed amount of lubricant (for example, mineral oil-based lubricant) 64 is enclosed.

  In such a submersible pump, when a motor (electric motor) is driven and a current is passed through a coil (not shown) of a stator (electromagnet) 60, the framing is caused by the magnetic interaction between the electromagnet 60 and the rotor (permanent magnet) 58. The rotational force can be applied to the rotating shaft 52 through the permanent magnet 58 in accordance with the left hand rule. At this time, the impeller 50 attached to the rotary shaft 52 rotates together with the rotary shaft 52, so that the water W1 sucked from the water suction port 48a moves along the pump casing 48 (W2), and then the discharge port. It is discharged from 48b (W3).

  In this case, for example, when the mechanical seal 62 is worn, the lubricant (foreign matter mixed lubricant) 64 in which foreign matter such as wear powder or water is mixed reaches the sealing member 36 of the rolling bearing 100 even in the seal groove 28g. At the base end 36e of the mounted sealing member 36, the elastic material 44 covered by the base end 42e of the cored bar 42 is firmly and firmly (tightly) in close contact with the seal groove 28g. It is possible to reliably prevent the lubricant 64 from entering the inside of the bearing from the base end 36e of the member 36.

  At the same time, an extremely slight labyrinth L is formed between the lip 46 and the inclined surface 30kt of the stationary ring 30 at the tip 36f of the sealing member 36 when the bearing is stationary (rotation stopped state), and the lip 46 is at the time of rotation of the bearing. Since it is elastically deformed and is kept in a slidable contact state slightly along the inclined surface 30k, the internal pressure between the sealing member 36 and the sealing plate 38 becomes higher than the external pressure outside the bearing. It is possible to reliably prevent the lubricant 64 from entering into the bearing from 36f.

  Further, regarding the annular retainer 34 provided between the rotating wheel (inner ring) 28 and the stationary wheel (outer ring) 30, no particular mention was made regarding the shape or orientation thereof. In the case of applying 34, as shown in FIG. 1 (a), a plurality of openings 34p for inserting the rolling elements 32 into pockets (not shown) are provided on one side of the crown-shaped cage 34. It is formed and the other side is closed.

  In this case, it is preferable that the crown-shaped cage 34 is disposed with the other closed side facing the annular sealing member 36 and the lubricant J is sealed on one side where the plurality of openings 34p are formed. When the rolling bearing 100 is incorporated into the submersible pump (FIG. 4) in such an arrangement, the crown-shaped cage 34 is located upward (on the side where the opening 34p is formed) on which one side of the lubricant J is sealed (ie, the side where the opening 34p is formed). It will be arranged toward the anti-impeller 50).

  As a result, a large amount of lubricant J encapsulated in the upward direction of the rolling bearing 100 adheres to the vicinity of the crown-shaped cage 34 and the back surface of the sealing plate 40 facing the opening 34p as the rotating wheel (inner ring) 28 rotates. Therefore, a sufficient amount of lubricant for lubricating the friction surface (for example, the sliding contact portion between the rolling element 32 and the inner and outer rings 28, 30) can be continuously supplied over a long period of time. As a result, the lubrication performance and rotational performance of the bearing can be kept constant over a long period of time, and the reliability of the bearing can be improved by extending the life of the bearing.

The present invention is not limited to the above-described embodiments, and the following modifications are also included in the technical scope of the present invention.
In the rolling bearing 100 shown in FIGS. 2A and 2B as a first modification, the foreign matter intrusion prevention mechanism is provided along an inclined surface 30k formed on the inner peripheral surface 30s of the stationary ring (outer ring) 30. Thus, the front end 36f of the sealing member 36 is inclined so as to be in a contact state with a relatively low contact pressure (light contact state). Specifically, at the tip 36 f of the sealing member 37, the lip 46 is positioned in contact along the inclined surface 30 k of the stationary wheel 30.

  In this case, the contact length N with which the lip 46 contacts the inclined surface 30k is set to be approximately 1.2 times or more the thickness dimension T of the lip 46. Further, the thickness dimension Y of the elastic member 44 around the tip 42f of the core metal 42 is set to be approximately 1.2 times or more than the thickness dimension T of the lip 46, and the inclination of the inclined surface 30k of the stationary ring 30 is increased. The angle θ is set to approximately 20 ° or more. In this case, the inclination angle θ is an angle formed by the inner peripheral surface 30s of the stationary wheel 30 and the inclined surface 30k. Furthermore, the surface roughness of the inclined surface 30k of the stationary wheel 30 is set to approximately 3.2 μm or less. Since other configurations are the same as those of the above-described embodiment, the same configurations as those of the embodiment are denoted by the same reference numerals in the drawings, and the description thereof is omitted.

  As described above, according to the present modification, the contact length N with which the lip 46 contacts the inclined surface 30k is set to approximately 1.2 times or more the thickness dimension T of the lip 46, so that the lip 46 of the sealing member 36 is obtained. It is possible to compensate for a decrease in sealing performance due to a slight contact state between the stationary wheel 30 and the inclined surface 30k of the stationary wheel 30. Thereby, when the bearing is stationary (rotation stopped state), it is possible to prevent foreign matter from entering between the lip 46 and the inclined surface 30k. Further, during the rotation of the bearing, the lip 46 is slightly pressed against the inclined surface 30k by the centrifugal force acting on the sealing member 36, but the contact length N of the lip 46 with respect to the inclined surface 30k is increased to disperse the pressing force. Can be made. As a result, the slidability of the lip 46 with respect to the inclined surface 30k can be made smooth, so that the rotational performance of the bearing can be kept constant.

  Further, according to this modification, the thickness dimension Y of the elastic member 44 around the tip 42f of the core metal 42 is set to be approximately 1.2 times or more the thickness dimension T of the lip 46, and the inclination of the stationary ring 30 is increased. By setting the inclination angle θ of the surface 30k to approximately 20 ° or more, it is possible to reduce the strong pressing of the lip 46 against the inclined surface 30k due to the centrifugal force that acts on the lip 46 from the sealing member 36 when the bearing rotates. it can. Thereby, since the slidability of the lip 46 with respect to the inclined surface 30k can be smoothed, it is possible to maintain the rotational performance of the bearing constant.

  Furthermore, according to this modification, the surface roughness of the inclined surface 30k of the stationary wheel 30 is set to about 3.2 μm or less, and the lubricant J is applied to the sliding surface of the lip 46 that is in sliding contact with the inclined surface 30k. Thus, the sliding contact pressure between the lip 46 and the inclined surface 30k during the rotation of the bearing can be reduced. As a result, wear of the lip 46 is prevented, and the sliding contact state between the lip 46 and the inclined surface 30k can be kept constant, so that the sealability inside the bearing can be kept constant over a long period of time. Become. Since other effects are the same as those of the above-described embodiment, description thereof is omitted.

  In the rolling bearing 100 shown in FIGS. 3 (a) and 3 (b) as a second modification, instead of providing the lip 46, the foreign matter intrusion prevention mechanism is provided on the inner side of the bearing of the sealing member 36 from the base end 36 e. A plurality of projecting portions 66 each having a tapered trapezoidal shape toward the tip 36f are arranged at predetermined intervals along the circumferential direction. In this case, the height dimension H of each protrusion 66 is set to approximately 50 to 90% of the labyrinth gap formed between the sealing plate 38 and the sealing member 36 on one side. Here, each protrusion 66 may be integrally formed of the same material as the elastic material 44, or may be formed separately and attached to the cored bar 42 (for example, bonding, welding, or screwing). . Since other configurations are the same as those of the above-described embodiment, the same configurations as those of the embodiment are denoted by the same reference numerals in the drawings, and the description thereof is omitted.

  As described above, according to the present modified example, when the bearing rotates (the rotating state of the rotating wheel 28), even if a foreign object tries to enter the inside of the bearing from the outside of the bearing, each protrusion 66 follows the rotation of the sealing member 36. Foreign matter can be scraped out of the bearing while turning in the direction. More specifically, as shown in FIG. 3 (b), each projection 66 is formed with scraped surfaces 66a, 66b that taper and incline toward the stationary wheel 30 on both sides thereof. It is configured so that foreign matter can be scraped to the outside of the bearing by the scraping surfaces 66a and 66b in both the forward and reverse rotation states of the wheel 28.

  Here, if it is assumed that the rotating wheel 28 is rotating forward in the direction of the arrow R, the sealing member 36 rotates together with the rotating wheel 28, so that the protrusions 66 also turn in the same direction. At this time, the foreign matter that is about to enter the inside of the bearing from the outside of the bearing is scraped to the outside of the bearing by one of the protruding surfaces 66a of each projection 66. For example, assuming that the rolling bearing 100 is incorporated in the submersible pump of FIG. 4, the foreign matter is a lubricant (foreign matter mixed lubricant) 64 in which foreign matter such as wear powder or water of the mechanical seal 62 is mixed.

  In this case, the lubricant (foreign matter) 64 is scraped to the outside of the bearing by one scraping surface 66a of each projection 66, and as a result, the sealing performance and lubricity inside the bearing can be maintained constant. Thus, it is possible to keep the rotational performance constant during the rotation of the bearing over a long period of time. On the other hand, when the rotating wheel 28 rotates in the direction opposite to the arrow R, the lubricant (foreign matter) 64 is scraped out of the bearing by the other scraping surface 66b of each protrusion 66. It will be. Since other effects are the same as those of the above-described embodiment, description thereof is omitted.

  Further, in the above-described embodiment and the first and second modifications, the explanation has been made assuming that the rotating wheel 28 is an inner ring and the stationary wheel 30 is an outer ring, but conversely, the rotating wheel 28 is an outer ring. When the stationary ring 30 is an inner ring, for example, in the configuration shown in FIG. 1A, the arrangement of the sealing member 36 and the sealing plates 38 and 40 is reversed upside down on the drawing and applied to the outer peripheral surface 28s of the inner ring 28. What is necessary is just to reverse the structure performed to the inner peripheral surface 30s of the outer ring | wheel 30, and to reverse the structure given to the inner peripheral surface 30s of the outer ring | wheel 30 to the outer peripheral surface 28s of the inner ring | wheel 28.

  Furthermore, in the above-described embodiment and the first and second modifications, the annular sealing member 36 is provided so as to cover one side of the annular space region surrounded by the rotating wheel 28 and the stationary wheel 30. However, the present invention is not limited to this, and the sealing member 36 is provided so as to cover both the annular space regions surrounded by the rotating wheel 28 and the stationary wheel 30 on both sides of the plurality of rolling elements 32. May be provided.

(a) is sectional drawing which partially expands and shows the structure of the rolling bearing which concerns on one embodiment of this invention, FIG. (b) is an expanded sectional view of the part enclosed with the dashed-dotted line X of the same figure (a). Figure. (a) is sectional drawing which partially expands and shows the structure of the rolling bearing which concerns on the 1st modification of this invention, FIG. (b) is an expansion of the part enclosed with the dashed-dotted line X of the same figure (a). Sectional drawing. (a) is sectional drawing which partially expands and shows the structure of the rolling bearing which concerns on the 2nd modification of this invention, FIG.5 (b) is sectional drawing which follows the XX line of the same figure (a). Sectional drawing which shows the structure of the submersible pump in which the rolling bearing of this invention was integrated. (a) is sectional drawing which expands and shows the example of a structure of 1st prior art partially, (b) is sectional drawing which expands and partially shows the example of a structure of 2nd prior art.

Explanation of symbols

28 Rotating wheel 28g Sealing groove 30 Stationary wheel 32 Rolling body 34 Cage 36 Sealing member 36e Base end 36f of sealing member Tip of sealing member
38,40 Sealing plate 42 Core metal 42e Core metal base end 42f Core metal tip 44 Elastic material 46 Lip

Claims (14)

A rolling wheel having a rotating wheel that can rotate in a predetermined direction, a stationary wheel that can be fixed to face the rotating wheel, and a plurality of rolling elements that are movably interposed between facing surfaces of the rotating wheel and the stationary wheel. A bearing,
An annular sealing member is provided so as to cover at least one space area of the annular space area surrounded by the rotating wheel and the stationary wheel on both sides of the plurality of rolling elements, respectively.
The annular sealing member is attached to an annular seal groove formed on the rotating wheel at its base end, its distal end extends toward the stationary ring, and foreign matter intrusion to prevent foreign matter from entering the bearing. It has a prevention mechanism, and has an annular cored bar that extends from the base end toward the tip,
The annular cored bar has a curled shape whose base end is bent along the shape of the seal groove, and at least the base end forming the curled shape is coated with an elastic material on its surface,
In the state where the base end of the sealing member is attached to the seal groove by caulking the base end of the core metal having a curl shape toward the seal groove, the elastic material coated on the base end of the core metal is sealed. A rolling bearing characterized by being in pressure contact with a groove and closely contacting with no gap.   The foreign matter intrusion prevention mechanism is configured by inclining the tip of the sealing member so as to be in a non-contact state along an inclined surface formed on an opposing surface of the stationary wheel. The rolling bearing described.   The tip of the sealing member is formed with a lip formed by covering the tip of the metal core with an elastic material, and the lip is positioned in a non-contact state along the inclined surface of the stationary ring. Item 3. A rolling bearing according to Item 2.   The foreign matter intrusion prevention mechanism is configured by inclining the tip of the sealing member so as to be in a contact state at a relatively low contact pressure along an inclined surface formed on the opposing surface of the stationary wheel. The rolling bearing according to claim 1.   At the tip of the sealing member, a lip is formed by covering the tip of the metal core with an elastic material with a predetermined thickness, and the lip is positioned in contact along the inclined surface of the stationary ring. The rolling bearing according to claim 4, wherein a contact length with which the lip contacts the inclined surface is set to be approximately 1.2 times or more of a thickness dimension of the lip.   The thickness of the elastic material around the tip of the metal core is set to about 1.2 times or more of the thickness of the lip, and the inclination angle of the inclined surface of the stationary ring is set to about 20 ° or more. The rolling bearing according to claim 4, wherein the rolling bearing is provided.   The rolling bearing according to any one of claims 4 to 6, wherein the surface roughness of the inclined surface of the stationary ring is set to approximately 3.2 µm or less.   The rolling bearing according to claim 3 or 5, wherein a lubricant is applied to at least a portion of the lip formed at the tip of the sealing member that faces the inclined surface of the stationary ring. On both sides of the plurality of rolling elements, an annular sealing plate having a base end fixed to an annular seal groove formed on the stationary ring and a distal end extending toward the rotating ring is provided. The sealing plate on one side is interposed between the annular sealing member and the plurality of rolling elements, and the tip thereof is in sliding contact with the opposing surface of the rotating wheel,
The rolling bearing according to any one of claims 1 to 8, wherein a lubricant is interposed along a circumferential direction between the sealing plate on one side and the sealing member.   The foreign matter intrusion prevention mechanism is configured by arranging a plurality of protrusions having a tapered trapezoidal shape at predetermined intervals along the circumferential direction from the base end to the tip end on the bearing inner side of the sealing member. The rolling bearing according to claim 1. On both sides of the plurality of rolling elements, an annular sealing plate having a base end fixed to an annular seal groove formed on the stationary ring and a distal end extending toward the rotating ring is provided. The sealing plate on one side is interposed between the annular sealing member and the plurality of rolling elements, and the tip thereof is in sliding contact with the opposing surface of the rotating wheel,
11. The rolling bearing according to claim 10, wherein a height dimension of each protrusion is set to approximately 50 to 90% of a labyrinth gap formed between the sealing plate on one side and the sealing member. .   The rolling bearing according to claim 9 or 11, wherein an air hole is formed in the other sealing plate in order to balance the pressure inside the bearing and the pressure outside the bearing.   The rolling bearing according to claim 9 or 11, wherein the facing surface of the rotating wheel is ground. Between the rotating wheel and the stationary wheel, there is provided an annular retainer in which a plurality of pockets for rotatably retaining a plurality of rolling elements one by one are provided, and on one side of the retainer, A plurality of openings for inserting the rolling elements into the pockets are formed, and the other side is closed,
The rolling bearing according to any one of claims 1 to 13, wherein the retainer is disposed with the other closed side facing the annular sealing member.

Images