JP2017223283A - Bearing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent torque loss, temperature rise, abnormal wear and the like according to the increase in a tension force of a seal lip.SOLUTION: A seal device is constituted by bringing a seal member 54 provided on an outer ring side of a rolling bearing into contact with a rear lid provided on an inner ring side of the rolling bearing. The seal member 54 is constituted by a core metal 541 and a lip part 542. At the lip part 542, a fixing part 542a fixed to the core metal 541 and a main lip 542b extending from the fixing part 542a are provided, and a tip part 542b1 of the main lip 542b is brought into contact with the rear lid. At the core metal 541, a lip support part 541c is provided which is arranged between a region further on the fixing part 542a side than the tip part 542b1 of the main lip 542b and the rear lid and which is separated with respect to the main lip 542b.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a bearing device having a seal member.

  Some bearing devices are used, for example, for supporting axles of railway vehicles as disclosed in Patent Document 1, and this type of bearing device is illustrated in FIG.

  This bearing device includes a bearing 100 and a seal device 150. The bearing 100 is a kind of double-row tapered roller bearing of a rolling bearing, and includes an outer ring 110 having a raceway surface on the inner periphery, an inner ring 120 having a raceway surface on the outer periphery, and a tapered roller 130 as a rolling element. . The tapered rollers 130 are arranged in double rows between the raceway surface of the outer ring 110 and the raceway surface of the inner ring 120.

  The seal device 150 includes a seal case 152 fitted and fixed to both axial ends of the inner peripheral surface of the outer ring 110, a seal member 154 fixed to the inner periphery of each seal case 152, and both axial sides of the inner ring 120. An oil drain 161 and a rear lid 162 are arranged. The seal member 154 constitutes a contact seal between the oil drain 161 and the rear lid 162. With this configuration, the sealing device 150 seals the space between the outer ring 110 and the inner ring 120 of the bearing 100 (the inner space of the bearing 100) at both axial ends.

  Specifically, as shown in FIG. 7, the seal member 154 includes a main lip 154a, a dust strip 154b, and a metal core 1541 provided with these lips 154a and 154b. Each lip 154a, 154b comes into contact with the rear lid 162 at two locations separated in the axial direction. This prevents leakage of lubricant such as grease from the internal space of the bearing 100 and intrusion of dust, water, and the like into the internal space.

  The shape, rigidity, and the like of the seal lips such as the main lip 154a and the dust lip 154b are set so as to exhibit an appropriate tightening force in accordance with the application and use conditions. However, during the rotation of the axle, the pressure in the bearing internal space (bearing internal pressure) sealed by the seal member 154 increases due to the temperature rise of the bearing. When the bearing internal pressure increases, the main lip 154a (or the dust lip 154b) is pressed against the sliding surface to increase the pressing force, thereby increasing torque and promoting heat generation. In addition, due to the deformation of the seal lip, it is not possible to maintain an appropriate contact state with the sliding surface, and wear of the tip of the seal lip is promoted, and the sealing performance may be deteriorated.

  As an invention for avoiding an increase in the tightening force of the seal lip accompanying an increase in the bearing internal pressure, for example, there is one disclosed in Patent Document 2. The invention is provided with an internal pressure adjusting mechanism (vent) for discharging the internal air to the outside of the bearing device when the internal pressure of the bearing device is increased, and an internal air flow mechanism for flowing the internal air from the bearing installation space to the seal installation space. The present invention relates to a sealing device for a bearing device. Notch that partially enlarges the diameter of the inner periphery of the partition plate as an internal air flow mechanism so that the grease film can be opened by the pressure difference even if the internal air flow mechanism is blocked by the grease film Alternatively, a through hole is formed.

JP 2007-255599 A Japanese Patent No. 4811194

  However, in the configuration of Patent Document 2, since it is necessary to add an internal pressure adjusting mechanism (vent), the cost is increased. In addition, the tightening force of the seal lip varies depending on factors other than fluctuations in the bearing internal pressure. For example, the space surrounded by the main lip 154a, the dust lip 154b, and the rear lid 162 (inter-lip space S ') is heated during the rotation of the axle, so that the pressure in the inter-lip space S' increases. When the pressure in the inter-lip space S ′ exceeds the limit, the tip of the dust lip 154b moves away from the rear lid 162, the air in the inter-lip space S ′ is released to the atmosphere, and the elastic deformation of the dust lip 154b thereafter. The inter-lip space S ′ returns to the original sealed state. When the rotation of the axle is stopped in this state, the pressure in the inter-lip space S ′ decreases as the temperature decreases, the inter-lip space S ′ becomes negative, and the main lip 154a and the dust lip 154b become oily. Adhering to the surface of the cut 161 or the rear lid 162 increases the tightening force of the seal lip. In addition, the suction of the main lip 154a due to the rotation of the oil drain 161 or the rear lid 162 reduces the pressure of the inter-lip space S ′, and the inter-lip space S ′ becomes negative, so that the sealing lip tension is reduced. Increase. If the axle is rotated again from this state, the wear of each lip 154a, 154b will proceed. With the configuration of Patent Document 2, it is impossible to cope with such an increase in tight force due to the adsorption of the seal lip.

  As a means for solving the problems described above, it is conceivable to improve the rigidity of the main lip 154a and the dust strip 154b itself. However, when such a configuration is adopted, if the lip tightening margin is set in the same manner as in the prior art, the tightening force of the main lip 154a and the dust 154b increases. As a result, torque increases and heat generation increases, and wear of the main lip 154a and the dust strip 154b increases. On the other hand, if the tightening margin is reduced, the sealing performance may be reduced.

  In view of the above circumstances, an object of the present invention is to prevent a torcross, a temperature rise, abnormal wear of a seal lip, and the like due to an increase in the tightening force of the seal lip.

  In order to solve the above problems, the present invention includes an outer ring having a raceway surface on the inner periphery, an outer diameter side member serving as one of the rotation side and the fixed side, and an inner ring having a raceway surface on the outer periphery. Including a member on the inner diameter side that is the other of the rotation side and the stationary side, a rolling element interposed between the raceway surface of the outer ring and the raceway surface of the inner ring, a member on the outer diameter side, and a member on the inner diameter side A metal core fixed to one of the members, and a seal member having a lip portion made of an elastic material fixed to the metal core, and a fixed portion fixed to the metal core on the lip portion, and a fixed portion In the bearing device provided with a first lip extending from the tip and having the tip thereof in contact with the other member, the core metal has a region of the first lip closer to the fixed portion than the tip and the other lip. A lip support disposed between the first lip and the first lip. Characterized in that the provided parts.

  According to such a configuration, the bearing internal pressure increases due to a temperature rise in the bearing internal space, and the first lip is supported by the lip support portion even when the first lip is deformed toward the other member due to this pressure. Further deformation of one lip is regulated. Thereby, the increase in the tension force of the first lip can be suppressed. On the other hand, since the first lip is separated from the lip support portion of the core metal, the influence of the rigidity of the core metal on the tension of the first lip is negligible. Further, the first lip can be easily deformed without being restricted in a direction away from the other member. Accordingly, even when the tightening allowance of the first lip is set to the same level as that of the conventional product, an appropriate tightening force can be obtained, and the first lip tightening force can be easily set to an appropriate value.

  The seal member may be provided with a second lip that contacts the other member on the outside of the bearing with respect to the first lip. With such a configuration, a negative pressure is generated in the space defined by the first lip, the second lip, and the other member (the space between the lips), and the first lip is adsorbed to the other member by the negative pressure. At the same time, the first lip is supported by the lip support, and further deformation of the first lip is restricted. Accordingly, it is possible to prevent an increase in the tightening force of the first lip due to such factors.

  From the viewpoint of reducing the manufacturing cost, it is preferable to provide a gap between the first lip and the lip support portion. In order to prevent an increase in tightening force, the width of the gap is preferably as small as possible. Specifically, the width of the gap is 1.5 mm or less.

  In order to obtain a reliable sealing effect, the tightening force of the first lip is preferably 20 N or more.

  In the said structure, it is preferable to provide a through-hole in the said metal core, and to integrate said 1st lip and 2nd lip through the said through-hole. Thereby, both a 1st lip and a 2nd lip can be reliably fixed with respect to a metal core.

  A double row tapered roller can be used as the rolling element. The bearing device described above is preferably used for a railway vehicle axle.

  According to the present invention, even when pressure fluctuations occur in the space defined by the first lip, an increase in the tension force of the first lip can be suppressed. Therefore, problems such as an increase in torque cross, heat generation, and abnormal lip wear associated with this can be avoided.

It is an axial sectional view of the bearing device concerning the embodiment of the present invention. It is an enlarged view of B part of FIG. It is principal part expanded axial sectional drawing of the bearing apparatus which concerns on embodiment of this invention. It is principal part expanded axial sectional drawing of the bearing apparatus which concerns on the modification of this invention. It is principal part expanded axial sectional drawing of the bearing apparatus which concerns on the modification of this invention. It is an axial sectional view of a conventional bearing device. It is an enlarged view of the A part of FIG.

  Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings.

  FIG. 1 shows a bearing device according to an embodiment of the present invention. This bearing device is used for supporting an axle of a railway vehicle, and includes a bearing 1 and a seal device 50. The bearing 1 is a double-row tapered roller bearing that is a kind of rolling bearing, and includes an outer ring 10, two inner rings 20, a plurality of tapered rollers 30 as rolling elements, and a cage 40. The outer ring 10 has a conical raceway surface 12 arranged in a double row on the inner periphery, and the inner ring 20 has a conical raceway surface 22 on the outer periphery. By arranging the end portions on the small diameter side of the two inner rings 20 to face each other, a double-row raceway surface 22 is formed. In addition to directly abutting the small-diameter side end of the inner ring 20, a spacer may be disposed between the small-diameter side ends. Tapered rollers 30 arranged in double rows are interposed between the raceway surface 12 of the outer ring 10 and the raceway surface 22 of the inner ring 20. The cage 40 holds the tapered rollers 30 in each row at equal intervals in the circumferential direction. A space formed between the outer ring 10 and the inner ring 20 (bearing internal space) is filled with a lubricant such as grease, and the sealing device 50 seals this space at both axial ends.

  The outer ring 10 is fixed to the axle box by fitting an outer circumferential surface thereof to an inner circumferential surface of an axle box (not shown) of the railway vehicle and fixing an axial end face in the axial direction. An oil drain 61 and a rear lid 62 as sliding contact members are disposed on the bearing outer sides of the two inner rings 20, respectively. A lid member 64 is fixed to the shaft end of the axle 2 with a bolt 66, and between this lid member 64 and the shoulder portion of the axle 2, an oil drain 61, an inner ring 20, and a rear lid 62 fitted to the outer periphery of the axle 2. Is pinched and fixed.

  As shown in an enlarged view in FIG. 2, the sealing device 50 includes a sealing case 52 having a stepped cylindrical shape, a sealing member 54, an L-shaped partition plate 55, and a rear lid 62. . Each of the two seal cases 52 is press-fitted and fixed to the inner periphery of the opening at both ends in the axial direction of the outer ring 10 at one axial end (end on the bearing inner side). The front ends of the two seal cases 52 are inserted into a recess 62a formed on the end surface of the rear lid 62, thereby forming a non-contact seal. In the following description, the sealing device 50 on one side in the axial direction (the sealing device on the right side in FIG. 1) is described as an example, but not only one sealing device 50 but also the other sealing device 50 is described. A similar configuration can be applied.

  The partition plate 55 is press-fitted and fixed to the inner periphery of the seal case 52, and the seal member 54 is press-fitted and fixed to the inner periphery of the partition plate 55. The inner peripheral edge of the partition plate 55 is adjacent to the outer peripheral surface of the rear lid 62 to form a non-contact seal. The partition plate 55 prevents a lubricant such as grease filled in the internal space of the bearing 1 from directly pressing against the seal member 54.

  Among the members described above, the outer ring 10, the seal case 52, and the partition plate 55 constitute an outer diameter side member that is a fixed side of the bearing device, and the two inner rings 20, the oil drain 61, and the rear The lid 62 constitutes a member on the inner diameter side that becomes the rotation side of the bearing device.

  As shown in FIG. 2, the seal member 54 is a so-called oil seal, and includes a metal core 541, lip portions 542 and 543 made of an elastic material fixed to the core 541, and a garter spring 544. . The metal core 541, the lip portions 542, 543, and the garter spring 544 are all formed in an annular shape.

  The core metal 541 includes a cylindrical press-fit portion 541a that is press-fitted and fixed to the inner periphery of the partition plate 55, a flat plate-like radial portion 541b that extends from the end of the press-fit portion 541a on the bearing outer side toward the inner diameter side, and a radial direction. A conical lip support portion 541c that is inclined so as to be displaced toward the inner diameter side from the inner diameter end portion of the portion 541b toward the inner side of the bearing is integrally provided.

  The lip portions 542 and 543 are formed of a rubber material such as nitrile rubber, acrylic rubber, or fluorine rubber, for example. The lip portions 542 and 543 are fixed to the core metal 541 by means such as vulcanization adhesion. The lip portions 542 and 543 can also be formed of resin.

  As shown in FIG. 3, the seal member 54 of the present embodiment has two lip portions 542 and 543. One lip portion 542 is formed on the surface of the metal core 541 (the surface on the bearing inner side), and the other lip portion 543 is formed on the rear surface of the metal core 541 (the surface on the bearing outer side). One lip portion 542 has a fixed portion 542a fixed to the cored bar 541 and a main lip 542b (first lip) extending from the fixed portion 542a toward the bearing inner side. The other lip portion 543 provided on the back surface side includes a fixing portion 543a fixed to the cored bar 541 and a dust 543b (second lip) extending from the fixing portion 543a toward the outside of the bearing.

  The front end 543b1 of the dust 543b is located on the bearing outer side with respect to the front end 542b1 of the main lip 542b. The tip portions 542b1 and 543b1 of both lips 542b and 543b are in contact with the outer peripheral surface (sliding surface) of the rear lid 62 with a tightening margin. The tip end portion 542b1 of the main lip 542b, the tip end portion 543b1 of the dust lip 543b, and the outer peripheral surface of the rear lid 62 form an inter-lip space S partitioned with respect to other places.

  The garter spring 544 is attached to the outer periphery of the front end portion 542b1 of the main lip 542b. By the cooperation of the elastic force in the diameter-reducing direction of the garter spring 544 and the front tightening allowance, a predetermined amount of compression force (20N or more and 50N or less) is applied to the tip 542b1 of the main lip 542b.

  The tip of the lip support part 541c of the cored bar 541 extends to the inter-lip space S. The lip support part 541c is a region on the fixed part 542a side of the tip part 542b1 of the inner peripheral surface of the main lip 542b. It is located between the rear cover 62 (see FIG. 2) and the outer peripheral surface. Between the inner peripheral surface of the main lip 542b and the outer peripheral surface of the lip support portion 541c, there is an annular gap c opened on the bearing inner side. Therefore, the main lip 542b and the lip support portion 541c are in a separated state. Of the lip portion 542, a region where the gap c does not exist constitutes a fixed portion 542a fixed to the cored bar 541.

  With the configuration described above, the main lip 542b has a tip portion 542b1 in a direction (diameter expansion direction) away from the sliding surface (the outer peripheral surface of the rear lid 62) (see the white arrow in FIG. 3). Deformable. On the other hand, in the direction in which the tip 542b1 is pressed against the sliding surface, the deformation of the main lip 542b is allowed within the range of the gap c, but after the gap c becomes zero, the lip support part of the core metal 541 The deformation is regulated by 541c. Therefore, it is possible to prevent an increase in the tightening force of the main lip tip 542b1.

  For example, when the pressure in the bearing internal space sealed by the seal member 54 (bearing internal pressure) becomes high due to the temperature rise in the bearing internal space during axle rotation, the tip 542b1 of the main lip 542b slides due to the internal pressure. Attempts to deform in a direction that is pressed against the surface. At this time, since the deformation is regulated by the lip support portion 541c as described above, the diameter of the main lip tip portion 542b1 is not reduced, and an increase in the pressing force of the main lip tip portion 542b1 can be avoided. Since this effect can be obtained without adding an internal pressure adjusting mechanism (vent) as in Patent Document 2, it is also effective in reducing the cost of the sealing device. In addition, the air in the inter-lip space S expands and contracts in accordance with the switching from the rotation of the axle to the stop, whereby the inter-lip space S becomes negative pressure, and the main lip 542b is adsorbed on the sliding surface. In this case, an increase in the tightening force of the main lip tip 542b1 can be prevented by the same action. Further, when the space between the lips S is in a negative pressure state due to the suction action of the main lip 542b due to the rotation of the oil drain 61 or the rear lid 62, the tightening force of the main lip tip 542b1 is increased by the same action. Can be prevented.

  As described above, according to the present invention, it is possible to avoid an increase in the tightening force of the main lip 542b and further the dust 543b due to pressure fluctuation in the space defined by the main lip 542b. Accordingly, it is possible to avoid problems such as torcross, temperature rise, and abnormal wear due to increased tension.

  On the other hand, the main lip 542b is freely deformable in a direction in which the tip end portion 542b1 is separated from the sliding surface, and therefore by giving a predetermined tightening margin between the main lip tip portion 542b1 and the sliding surface, Appropriate tension can be obtained. At this time, the tightness of the main lip tip 542b1 is not affected by the rigidity of the cored bar 541. Therefore, the relationship between the existing tightening allowance and the tension force can be utilized as it is, and the design of the seal member 54 becomes easy.

  In order to obtain the above effects, it is preferable to make the gap c between the lip support portion 541c of the cored bar 541 and the main lip 542b as small as possible. Specifically, the width of the gap c is preferably 1.5 mm or less. In order to obtain the above effect, it is sufficient that the lip support portion 541c and the main lip 542b are separated from each other, and the gap may be set to 0 as long as they are separated. The separation of the two is performed by forming a gap c between the lip support portion 541c and the main lip 542b at the time of vulcanization adhesion, and separating the main lip 542b and the lip support portion 541c of the cored bar 541 with a blade or the like after vulcanization adhesion. It can also be done.

  In the embodiment shown in FIG. 4, a through hole 541d is provided in a cored bar 541, and two lip portions 542 and 543 are integrated through the through hole 541d. In such a configuration, the main lip 542b of one lip portion 542 and the dust 543b of the other lip portion 543 are formed in the same lip portion.

  In the embodiment described above, the gap c is formed between the lip support portion 541c of the core metal 541 and the main lip 542b. However, as shown in FIG. 5, the lip support portion 541c is covered with one lip portion 542. In addition, a gap c may be formed between the covering portion 542c and the main lip 542b.

  The present invention is not limited to the above embodiment, and various modifications are possible within the scope of the technical idea. For example, in the above embodiment, the vent for releasing the internal pressure is not provided in the seal member 54, but the vent may be provided in the seal member 54. In this case, even if the vent is blocked by grease or the like, the effect of the pressure on the seal member 54 can be prevented by the effect of the seal member 54 described above. Further, the dust lip 543b can be omitted, and the seal lip can be formed only by the main lip 542b. Even in such a configuration, it is possible to prevent a situation in which the tightening force of the main lip 542b increases due to an increase in bearing internal pressure.

  Moreover, in the said embodiment, although the sealing member 54 is being fixed to the sealing case 52 via the partition plate 55, the member which fixes the sealing member 54 can be arbitrarily selected from the above-mentioned members on the outer diameter side. For example, the seal member 54 can be fixed to the inner peripheral surface of the outer ring 10. Further, a member for slidingly contacting the main lip 542b and the dust lip 543b can be arbitrarily selected from the above-mentioned members on the inner diameter side. For example, the lip tip portions 542b1 and 543b1 are directly slidably contacted with the outer peripheral surface of the inner ring 20. You can also.

DESCRIPTION OF SYMBOLS 1 Bearing 10 Outer ring 12 Raceway surface 20 Inner ring 22 Raceway surface 30 Tapered roller (rolling element)
52 Seal case (member on the outer diameter side)
54 Seal member 541 Core metal 541c Lip support portion 542 Lip portion 543 Lip portion 542a Fixing portion 542b Main lip (first lip)
542b1 Tip 543a Fixing 543b Dustrip (second lip)
543b1 Front end portion 541d Through hole 55 Partition plate (member on outer diameter side)
61 Oil drainer (inner diameter side member)
62 Rear lid (member on the inner diameter side)
c Clearance

Claims (8)

Including an outer ring having a raceway surface on the inner periphery, including an outer diameter side member that is one of the rotation side and the fixed side, and an inner ring having a raceway surface on the outer periphery, the other being the rotation side and the fixed side A core fixed to one of an inner diameter side member, a rolling element interposed between the raceway surface of the outer ring and the raceway surface of the inner ring, and an outer diameter side member and an inner diameter side member And a seal member having a lip portion made of an elastic material fixed to the metal core, the lip portion having a fixed portion fixed to the metal core, and extending from the fixed portion, and the tip portion of the other member In a bearing device provided with a first lip in contact with
The cored bar is provided with a lip support portion that is disposed between a region of the first lip closer to the fixed portion than the tip portion and the other member and separated from the first lip. A bearing device.   The bearing device according to claim 1, wherein the seal member is provided with a second lip that contacts the other member on the outer side of the bearing with respect to the first lip.   The bearing device according to claim 1, wherein a gap is provided between the first lip and the lip support portion.   The bearing device according to claim 3, wherein a width of the gap is 1.5 mm or less.   The bearing device according to any one of claims 1 to 4, wherein a tension force of the first lip is 20 N or more.   The bearing device according to claim 2, wherein the cored bar is provided with a through hole, and the first lip and the second lip are integrated via the through hole.   The bearing device according to claim 1, wherein a double row tapered roller is used as the rolling element.   The bearing apparatus of any one of Claims 1-7 used for a railway vehicle axle.

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