JP2018112220A - Spacer member, and bearing device for axle having the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a spacer member of a bearing device for an axle capable of stably exhibiting a sealing function for long time.SOLUTION: An annular spacer member 20 arranged between an inner ring 4 of a rolling bearing 3 supporting an axle 2 and a cylindrical rear lid 9 comprises: an annular core metal 21 having first and second contact faces A1, A2 individually brought into contact with an end face M of the inner ring 4 and an inside diameter side end face N1 of the rear lid 9 opposed to each other; and an annular elastic seal member 22 provided at an outer peripheral edge of the core metal 21. The elastic member 22 has first and second seal parts 23, 24 individually provided at both axial sides of the core metal 21, and the first seal part 23 has a pressure contact face C brought into pressure-contact with the end face M of the inner ring 4. The core metal 21 has an annular step face B having a larger isolation distance in an axial direction from the contact face C than the first contact face A1, and at least a part of the step face B is covered by the first seal part 23.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a spacer member and an axle bearing device including the spacer member.

  Patent Document 1 below discloses a bearing device for an axle of a railway vehicle. This axle bearing device is arranged on the outside of the rolling bearing in the axial direction of the rolling bearing that rotatably supports the axle of the railway vehicle, and performs relative positioning in the axial direction of the rolling bearing with respect to the axle (the axis of the rolling bearing). And a set of cylindrical members that regulate directional movement. Of the set of cylindrical members, the first cylindrical member arranged on the free end side of the axle is “oil drainer”, and the second cylindrical member arranged on the axial center side of the axle is It is also called “rear cover”, and both cylindrical members are generally formed of an iron-based metal material having excellent mechanical strength such as carbon steel.

  In the above-described axle bearing device that supports an axle on which a large radial load (bending moment) repeatedly acts, when the inner ring of the rolling bearing and the cylindrical member are brought into direct contact with each other, at the contact portion between the two, Metal wear powder (fretting wear powder) is easily generated due to repeated sliding vibration (fretting). When this wear powder enters the internal space of the rolling bearing, the lubricant filled in the internal space of the rolling bearing is prematurely deteriorated, and as a result, the life of the rolling bearing is shortened. For this reason, the bearing device for axles of patent documents 1 is further provided with the annular spacer member arranged between the inner ring and the cylindrical member.

  FIG. 9A shows a partially enlarged view of the axle bearing device of Patent Document 1, and FIG. 9B shows a partially enlarged view of a spacer member constituting the axle bearing device. As shown in FIGS. 9A and 9B, the spacer member 103 of Patent Document 1 is provided on an annular cored bar 104 made of a soft metal such as a copper alloy, and on an outer peripheral edge of the cored bar 104. And an annular elastic sealing material 105. The metal core 104 has first and second contact surfaces 104a and 104b that contact the end surface 101a of the inner ring 101 and the inner diameter side end surface 102a of the rear lid 102, which are opposed to each other. Suppresses generation of fretting wear powder caused by contact. The elastic seal material 105 includes first and second seal portions 105A and 105B provided on both sides in the axial direction of the cored bar 104. The end surfaces of the first seal portion 105A and the second seal portion 105B are inner rings. The opening between the inner ring 101 and the rear lid 102 is sealed in close contact with (in pressure contact with) the end surface 101a of the 101 and the outer diameter side end surface 102b of the rear lid 102. Thereby, even when fretting wear powder is generated, it is possible to prevent the wear powder from entering the internal space of the rolling bearing as much as possible.

JP 2004-332905 A

  During operation of the railway vehicle, the axle rotates while receiving a radial load while being bent. Therefore, the spacer member 103 is outlined in FIG. 9B from the inner ring 101 and the rear lid 102 arranged on both sides in the axial direction. An axial compressive load (fluctuating compressive load) as indicated by an arrow is repeatedly input. When such a compressive load is input to the spacer member 103, the elastic seal material 105 is formed of a material having a lower rigidity than the core metal 104, and thus is more greatly deformed in the axial direction than the core metal 104. For this reason, when the axial compressive load is repeatedly input to the spacer member 103, the portion of the elastic seal material 105 that is particularly thin in the axial direction (the inner diameter side region 106 of the first seal portion 105A) is the inner ring 101. And the core metal 104 are repeatedly sandwiched, an excessive compressive strain is generated, and the elastic sealing material 105 is easily damaged starting from the portion where the excessive compressive strain is generated. When the elastic sealing material 105 is damaged, the sealing function of the elastic sealing material 105 (fretting wear powder outflow prevention function) is impaired, and as a result, the life of the axle bearing device is shortened.

  As described above, the above problem is not only caused when the first seal portion 105A of the elastic seal material 105 is disposed adjacent to the inner ring 101, but also the right and left sides of the elastic seal material 105 shown in FIG. This can also occur when the first seal portion 105A is disposed adjacent to the rear lid 102.

  In view of the above circumstances, the object of the present invention is to provide a spacer member with a seal that can stably exhibit a sealing function (a function of preventing the outflow of fretting wear powder) over a long period of time. It contributes to the improvement of the durability and reliability of a bearing device for an axle of a vehicle.

  The first invention of the present application, which has been invented to solve the above-mentioned problems, is an axle comprising a rolling bearing that rotatably supports an axle of a railway vehicle, and a cylindrical member that is disposed on the axially outer side of the rolling bearing. 1st and 2nd contact surfaces which are annular spacer members arranged between an inner ring of a rolling bearing and a cylindrical member, and abut against end faces of the inner ring and the cylindrical member facing each other. And an annular elastic sealing material that seals the opening between the inner ring and the cylindrical member, and is provided on both sides in the axial direction of the core metal. Among the first and second seal portions constituting the elastic seal material, in the spacer member having the pressure contact surface where the first seal portion is pressed against the end surface of the inner ring, the core metal is pressed more than the first contact surface. Has an annular step surface with a large axial separation from the surface. And wherein at least a part of the stepped surface is covered with the first sealing portion. The “the end surface of the inner ring” here is specifically the end surface of the inner ring with which the first contact surface of the core metal comes into contact.

  According to the above configuration, in the state where the axle bearing device including the spacer member is attached to the outer periphery of the axle, the axial dimension of the first seal portion of the elastic seal material interposed between the inner ring and the core metal of the spacer member. (Thickness in the axial direction of the first seal portion; the same applies hereinafter) can be increased as compared with the configuration shown in FIGS. Therefore, even if an axial compressive load is repeatedly input to the spacer member, it becomes difficult for compressive strain to occur in the elastic seal material (particularly the first seal portion), and the seal function of the elastic seal material can be stably maintained over a long period of time. Can be maintained.

  In order to effectively reduce the possibility of compressive strain occurring in the first seal portion of the elastic seal material, the crushing margin (tightening allowance) of the first seal portion with respect to the end surface of the inner ring is a, and the axial dimension of the first seal portion Is set to satisfy the relational expression of a / b <0.5, more preferably satisfying the relational expression of a / b <0.2.

  In addition, in order to ensure that the end face of the inner ring and the pressure contact surface of the first seal part are in close contact with each other over the entire circumference, the axial dimension of the first seal part is b, the inner diameter dimension of the first seal part (the diameter dimension of the inner diameter surface). ) Is φd, and the outer diameter dimension (maximum outer diameter dimension) of the core metal is φe, it is preferable that the relational expression of φe−φd> b is satisfied, and the relational expression of φe−φd> 2b is satisfied. More preferably.

  Said 1st invention can be applied preferably, when a 2nd seal | sticker part has a cylindrical inner peripheral surface press-fitted in the cylindrical outer peripheral surface provided in the cylindrical member and extended in the axial direction.

  The second invention of the present application, which was created to solve the above problems, includes a rolling bearing that rotatably supports an axle of a railway vehicle, and a cylindrical member that is disposed on the axially outer side of the rolling bearing. In the bearing device for an axle, an annular spacer member disposed between the inner ring and the cylindrical member of the rolling bearing, the first and second contacts contacting the cylindrical member and the end surface of the inner ring facing each other. An annular cored bar having a contact surface; and an annular elastic sealing material that is provided on the outer peripheral edge of the cored bar and seals an opening between the tubular member and the inner ring, and is provided on both axial sides of the cored bar. Of the first and second seal portions constituting the provided elastic seal material, in the spacer member having a pressure contact surface where the first seal portion is pressed against the end surface of the tubular member, the core metal is the first contact An annular ring with a larger axial separation distance from the pressure contact surface than the surface It has Samen, and at least a part of the stepped surface is covered with the first sealing portion. Note that the “end surface of the cylindrical member” herein is specifically the end surface of the cylindrical member with which the first contact surface of the core metal abuts.

  According to such a structure, the effect similar to 1st invention can be enjoyed.

  Also in the configuration of the second invention, when the crushing margin (tightening margin) of the first seal portion relative to the end surface of the tubular member is a and the axial dimension of the first seal portion is b, a / b <0.5 It is preferable to satisfy the relational expression, and it is more preferable to satisfy the relational expression of a / b <0.2. Further, when the axial dimension of the first seal part is b, the inner diameter dimension of the first seal part is φd, and the outer diameter dimension of the cored bar is φe, the relational expression of φe−φd> b is satisfied. It is preferable to satisfy the relational expression of φe−φd> 2b.

  The second invention can be preferably applied when the second seal portion has a cylindrical inner peripheral surface press-fitted into a cylindrical outer peripheral surface provided in the inner ring and extending in the axial direction.

  In the above configuration, the first seal portion may be provided so as to cover a partial region on the outer diameter side of the step surface (for example, FIG. 2) or may be provided so as to cover the entire region of the step surface. Good (for example, FIG. 5).

  In the above configuration, the entire area of the pressure contact surface of the first seal portion can be provided on the outer diameter side of the cored bar (for example, FIG. 5). If it does in this way, possibility that compression distortion will arise in the 1st seal part can be reduced still more effectively.

  The metal core can be provided with a lubricant holding part capable of holding the lubricant. If a lubricant holding part is provided and the lubricant holding part holds the lubricant, the lubricity between the inner ring and the cylindrical member can be improved, and the wear of the metal core itself can be suppressed. This is advantageous in suppressing the generation of powder.

  A rolling bearing that rotatably supports an axle of a railway vehicle, and a cylindrical member that is disposed on the outer side in the axial direction of the rolling bearing, the spacer member according to the present invention is disposed between the inner ring and the cylindrical member of the rolling bearing. The axle bearing device thus made is rich in durability and reliability because the spacer member according to the present invention can exhibit the above-described effects. The rolling bearing is preferably a double-row tapered roller bearing that can support both a radial load and an axial load and is excellent in these load carrying capacities.

  As described above, according to the present invention, it is difficult for compressive strain to occur in the elastic sealing material, and the durability of the elastic sealing material can be increased, so that the spacer member is excellent in the function of preventing the outflow of fretting wear powder (sealing function). (Spacer member with elastic seal) can be provided. As a result, it is possible to realize an axle bearing device that is rich in durability and reliability.

It is sectional drawing which shows the whole structure of the axle bearing apparatus which concerns on embodiment of this invention. It is the elements on larger scale of the spacer member which comprises the axle shaft bearing apparatus shown in FIG. It is the elements on larger scale of FIG. (A) A figure and (b) figure are the elements on larger scale of the spacer member which concerns on a modification. It is the elements on larger scale of the spacer member which comprises the axle shaft bearing apparatus which concerns on 2nd Embodiment of 1st invention of this application. It is the elements on larger scale of the axle bearing apparatus provided with the spacer member shown in FIG. It is the elements on larger scale of the axle bearing device which concerns on 1st Embodiment of 2nd invention of this application. It is the elements on larger scale of the axle bearing device which concerns on 2nd Embodiment of 2nd invention of this application. (A) is a sectional view showing the entire structure of a conventional axle bearing device, and (b) is a partially enlarged view of a spacer member constituting the axle bearing device shown in (a).

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  FIG. 1 shows the overall structure of an axle bearing device 1 according to an embodiment of the present invention. An axle bearing device 1 shown in FIG. 1 includes a rolling bearing 3 that rotatably supports an axle 2 of a railway vehicle, a pair of seal devices 10 and 10, and first shafts disposed on both sides in the axial direction of the rolling bearing 3. And an oil drainer 8 and a rear lid 9 as a second cylindrical member, and an annular spacer member 20 arranged between the rolling bearing 3 and the rear lid 9.

  The rolling bearing 3 has double-row inner raceway surfaces 4a and 4a, and has an inner ring 4 mounted on the outer periphery of the axle 2 and double-row outer raceway surfaces 5a and 5a. A pair of cages 7 and 7 for holding the outer ring 5 mounted on the circumference, a plurality of tapered rollers 6 disposed between the pair of raceway surfaces 4a and 5a, and each row of the tapered rollers 6 at predetermined intervals in the circumferential direction. Is a so-called double-row tapered roller bearing. In the illustrated example, the inner ring 4 is configured by a pair of split inner rings that are abutted at the axially central portion of the rolling bearing 3, but as the inner ring 4, a spacer is interposed between the pair of split inner rings, What comprised the single member can also be used.

  The internal space of the rolling bearing 3 is filled with a lubricant such as grease, and external leakage of the lubricant and entry of foreign matter into the internal space of the bearing are prevented as much as possible by the pair of seal devices 10 and 10. . Each sealing device 10 includes a seal member 11 and a stepped cylindrical seal cover 12 having an outer diameter side end fixed to the outer ring 5 and an inner diameter side end disposed close to the cylindrical member, The seal member 11 is attached and fixed to the inner diameter surface of the seal cover 12. The seal member 11 may be either a so-called contact type or a non-contact type.

  The oil drain 8 is fixed to the axle 2 by a nut (not shown) fastened to the tip of the axle 2 and is engaged with the inner ring 4 of the rolling bearing 3 in the axial direction. The rear lid 9 is fixed to the axle 2 by engaging with a shoulder surface 2 b provided on the axle 2 in the axial direction, and is engaged with the inner ring 4 of the rolling bearing 3 via the spacer member 20 in the axial direction. With such a configuration, the relative movement in the axial direction of the rolling bearing 3 with respect to the axle 2 is restricted, and the positioning of the rolling bearing 3 in the axial direction is performed.

  As shown in FIG. 3, in the rolling bearing 3 of the present embodiment, the end surface M of the inner ring 4 adjacent to the spacer member 20 is formed as a flat surface in a direction orthogonal to the axial direction. Further, the end surface of the rear lid 9 adjacent to the spacer member 20 is shifted to the inner diameter side end surface N1 formed on a flat surface in a direction orthogonal to the axial direction, and to the axial center side of the axle 2 from the inner diameter side end surface N1. And is divided into an outer diameter side end surface N2 formed on a flat surface in a direction orthogonal to the axial direction, and both end surfaces N1 and N2 are continuously connected via a cylindrical outer peripheral surface N3 extending in the axial direction. Yes.

  FIG. 2 shows a partially enlarged view of the single spacer member (before mounting). The spacer member 20 includes an annular cored bar 21 and an annular elastic sealing material 22 provided on the outer peripheral edge of the cored bar 21.

  The cored bar 21 has a stepped annular shape integrally including an inner diameter side annular portion 21a and an outer diameter side annular portion 21b located closer to the center in the axial direction of the axle 2 than the inner diameter side annular portion 21a. In the state in which the axle bearing device 1 including is attached to the axle 2 (see FIGS. 1 and 3), the inner diameter side annular portion 21a is sandwiched between the inner ring 4 and the rear lid 9 from both sides in the axial direction. Therefore, the one end surface 21a1 and the other end surface 21a2 of the inner diameter side annular portion 21a constitute the first contact surface A1 and the second contact surface A2 referred to in the first invention of the present application, respectively. Further, since the outer diameter side annular portion 21b is provided in the above-described manner, the one end surface 21b1 of the outer diameter side annular portion 21b is more than the one end surface 21a1 of the inner diameter side annular portion 21a as the first contact surface A1. A distance in the axial direction from the pressure contact surface C (details will be described later) of the first seal portion 23 of the elastic seal material 22 is large. Therefore, the one end surface 21b1 of the outer diameter side annular portion 21b constitutes the step surface B referred to in the first invention of the present application.

  The metal core 21 having the above configuration is a so-called press-molded product formed into a predetermined shape by pressing a thin plate made of a metal material softer than the inner ring 4 and the rear lid 9 (for example, copper alloy). It is said.

  The elastic sealing material 22 is provided on the outer diameter side of the core metal 21 with the first and second seal parts 23 and 24 provided on both sides in the axial direction of the core metal 21, and connects both the seal parts 23 and 24. It has the connection part 25 integrally. The first seal portion 23 is provided so as to cover a partial region on the outer diameter side of the one end surface 21b1 (step surface B) of the outer diameter side annular portion 21b of the core metal 21, and the second seal portion 24 is The outer end side annular portion 21b of the cored bar 21 is provided so as to cover the entire other end surface 21b2. The end surface 23a of the first seal portion 23 is located on the free end side of the axle 2 with respect to the one end surface 21a1 (first contact surface A1) of the inner diameter side annular portion 21a of the core metal 21, and the spacer member 20 is disposed on the axle. 2 (see FIG. 3), the first abutment surface A1 of the core metal 21 is pressed against the outer diameter side region of the end surface M of the inner ring 4 that abuts. Therefore, the end surface 23a of the first seal portion 23 constitutes the pressure contact surface C in the first invention of the present application.

  The elastic sealing material 22 having the above configuration is formed of, for example, a rubber material mainly composed of any one selected from the group of nitrile rubber, acrylic rubber, and fluororubber. It is integrally formed with the core metal 21 by vulcanization molding as an insert part.

  The spacer member 20 having the above configuration has an inner peripheral surface (cylindrical inner peripheral surface) 24b of the second seal portion 24 of the elastic sealing material 22 formed in a cylindrical surface shape as shown in an enlarged view in FIG. It is attached to the outer periphery of the axle 2 by press-fitting into the cylindrical outer peripheral surface N3 of the rear lid 9. When the axle bearing device 1 is attached to the axle 2, one end surface 21 a 1 (first contact surface A 1) of the inner diameter side annular portion 21 a of the core metal 21 is on the end surface M (its inner diameter side region) of the inner ring 4. At the same time, the other end surface 21a2 (second contact surface A2) of the inner diameter side annular portion 21a of the core metal 21 contacts the inner diameter side end surface N1 of the rear lid 9. Thus, even in a situation where the axle 2 rotates while receiving a radial load while being bent, direct contact between the inner ring 4 and the rear lid 9 is avoided, and therefore fretting wear powder derived from repeated direct contact between the two. Is prevented as much as possible.

  When the axle bearing device 1 is attached to the axle 2, the end surface 23 a of the first seal portion 23 is on the end surface M (the outer diameter side region) of the inner ring 4, and the end surface 24 a of the second seal portion 24 is The elastic sealing material 22 is interposed between the inner ring 4 and the rear lid 9 in a state of being compressed and deformed in the axial direction so as to be pressed against the outer diameter side end face N2 of the rear lid 9, respectively. Thereby, since the opening part between the inner ring | wheel 4 and the rear cover 9 is sealed, even when abrasion powder generate | occur | produces in the contact part of the inner ring | wheel 4 and the metal core 21, or the contact part of the rear cover 9 and the metal core 21, The possibility that the wear powder flows out to the outer diameter side of the inner ring 4 and enters the internal space of the rolling bearing 3 is effectively reduced.

  In this embodiment, the cored bar 21 of the spacer member 20 has an annular step surface B having a larger axial separation distance from the pressure contact surface C than the first contact surface A1 that contacts the end surface M of the inner ring 4. In addition, at least a part of the step surface B is covered with a first seal portion 23 that constitutes the elastic seal material 22. According to such a configuration, the axial dimension of the first seal portion 23 of the elastic seal material 22 interposed between the inner ring 4 and the core metal 21 of the spacer member 20 is changed to the conventional configuration shown in FIG. It can be increased in comparison. Therefore, even if an axial compressive load is repeatedly input to the spacer member 20 with the rotation of the axle 2, it is difficult for compressive strain to occur in the first seal portion 23 of the elastic seal material 22, and the sealing function of the elastic seal material 22 is achieved. Can be stably maintained over a long period of time. Accordingly, it is possible to realize the axle bearing device 1 having a long life and high reliability.

  In order to secure the sealing function, the crushing allowance (tightening allowance) a of the first seal portion 23 of the elastic seal material 22 with respect to the end face M of the inner ring 4, that is, the axial dimension a (the spacer member 20 shown in FIG. 2). The distance in the axial direction between the first contact surface A1 of the core metal 21 and the pressure contact surface C of the elastic seal material 22 in a single state is preferably 0.05 mm or more (a ≧ 0.05 mm).

  Further, in order to effectively reduce the possibility of compressive strain occurring in the first seal portion 23 of the elastic seal material 22, the crush margin a of the elastic seal material 22 with respect to the end surface M of the inner ring 4 and the first seal portion 23. The step difference between the axial dimension b (see FIG. 2) and the relational expression of a / b <0.5, more preferably the relational expression of a / b <0.2. The position of the surface B in the axial direction is set.

  Moreover, in this embodiment, the elastic sealing material 22 is integrally molded with the core metal 21 by vulcanization molding using the core metal 21 as an insert part. In this case, when the rubber material for molding the sealing material flows out to the first contact surface A1 of the cored bar 21 and cures in the molding process of the elastic sealing material 22, an explanation will be given with reference to FIGS. There is also a possibility that the same problem as in the prior art will occur.

  Therefore, in the present embodiment, the first seal portion 23 of the elastic seal material 22 is provided so as to cover only a partial region on the outer diameter side of the step surface B of the cored bar 21. In order to reliably form the elastic sealing material 22 having such a shape, the outer diameter dimension φc (see FIG. 2) of the inner diameter side annular portion 21a of the core metal 21 and the inner diameter dimension φd of the first seal portion 23 ( The value of (see FIG. 2) is preferably set so that a relational expression of (φd−φc) / 2> 0.5 mm is established, and a relational expression of (φd−φc) / 2> 0.8 mm is established. It is more preferable to set so.

  Furthermore, in order to make the end surface M of the inner ring 4 and the end surface 23a (pressure contact surface C) of the first seal portion 23 of the elastic seal material 22 adhere appropriately over the entire circumference, the outer diameter of the core metal 21 is φe (see FIG. 2), a relational expression of φe−φd> b, more preferably a relational expression of φe−φd> 2b, holds between the axial dimension b and the inner diameter dimension φd of the first seal portion 23. The dimensions of each part are set.

  Of the metal core 21 constituting the spacer member 20 described above, the first and second contact surfaces A1 and A2 that contact the end surface M of the inner ring 4 and the inner end surface N1 of the rear lid 9 respectively have grease or the like. It is possible to provide a lubricant holding part capable of holding the lubricant. 4 (a) and 4 (b) are specific examples thereof. In FIG. 4 (a), the groove 28 provided on both contact surfaces A1 and A2 constitutes a lubricant holding portion, and FIG. ), A concave portion (dimple) 29 provided on both contact surfaces A1 and A2 constitutes a lubricant holding portion. In addition to this, the lubricant holding portion can be configured by, for example, through holes that open to both contact surfaces A1 and A2.

  If the above-described lubricant holding portion is provided and an appropriate lubricant (for example, lubricating oil) is held in the lubricant holding portion, it is between the inner ring 4 and the core metal 21 and between the rear lid 9 and the core metal 21. Therefore, it is advantageous in preventing the generation of fretting wear powder. The lubricant holding portion described above can be molded at the same time as the core metal 21 is molded (press-molded) into a predetermined shape, and is also employed in the spacer member 20 according to another embodiment to be described later. Can do.

  FIG. 5 shows a partially enlarged view of the spacer member 20 according to the second embodiment of the first invention of the present application, and FIG. 6 shows a partially enlarged view of the axle bearing device 1 having the spacer member 20 as a component. . As shown in FIGS. 5 and 6, in this embodiment, the shapes of the cored bar 21 and the elastic sealing material 22 constituting the spacer member 20 are the spacer member 20 of the first embodiment described with reference to FIG. 2 and the like. Is different. More specifically, in this embodiment, the cored bar 21 includes an annular portion (inner diameter side annular portion) 21a and a cylindrical portion 21c extending in the axial direction from the outer diameter end portion of the inner diameter side annular portion 21a. The elastic sealing material 22 is provided integrally with the core metal 21 so as to cover the entire cylindrical portion 21c of the core metal 21.

  Also in this embodiment, the cored bar 21 of the spacer member 20 has a stepped surface B having a larger axial separation distance from the pressure contact surface C than the first contact surface A1 (one end surface 21a1 of the inner diameter side annular portion 21a). And at least part of the step surface B (in the present embodiment, the entire region of the step surface B) is covered with the first seal portion 23 of the elastic seal material 22. Accordingly, in the state where the axle bearing device 1 shown in FIG. 6 is attached to the axle 2, the axial dimension of the first seal portion 23 of the elastic seal material 22 interposed between the end face M of the inner ring 4 and the core metal 21. Can be increased as compared with the conventional configuration shown in FIGS. Thereby, it becomes difficult to produce a compressive strain in the 1st seal | sticker part 23, and the sealing function of the elastic sealing material 22 can be maintained stably over a long period of time. In the present embodiment, the stepped surface B is formed by removing the outer diameter end portion of the one end surface 21a1 of the inner diameter side annular portion 21a of the core metal 21.

  Further, in the spacer member 20 of the present embodiment, the entire end surface 23 a (pressure contact surface C) of the first seal portion 23 of the elastic seal material 22 that is pressed against the end surface M of the inner ring 4 is outside the core metal 21. It is provided on the radial side. That is, as shown in FIG. 5, when the inner diameter dimension of the protruding portion whose end face functions as the pressure contact surface C in the first seal portion 23 is φd ′ and the outer diameter dimension of the cored bar 21 is φe ′, φd ′ The relational expression> φe ′ holds. In this case, even if an axial compressive load is repeatedly input to the spacer member 20 as the axle 2 rotates, the first seal portion 23 is pinched between the inner ring 4 and the core metal 21. The part is virtually gone. For this reason, the possibility that compressive strain is generated in the first seal portion 23 is further effectively reduced.

  Also in this embodiment, in order to ensure the sealing function of the elastic sealing material 22, the crushing allowance (tightening allowance) a ′ of the first seal portion 23 with respect to the end face M of the inner ring 4, that is, the axial dimension a shown in FIG. It is preferable that “′ is 0.05 mm or more (a ′ ≧ 0.05 mm).

  Further, in order to effectively reduce the possibility of compressive strain occurring in the first seal portion 23, the crushing margin a ′ of the elastic seal material 22 (first seal portion 23) with respect to the end face M of the inner ring 4 and the first seal It is preferable that a relational expression of a ′ / b ′ <0.5 is established between the axial dimension b ′ of the portion 23 (see FIG. 5), and a ′ / b ′ <0.2. More preferably, the relational expression is established.

  The elastic sealing material 22 of this embodiment is also molded integrally with the core metal 21 by vulcanization molding using the core metal 21 as an insert part. In order to prevent the rubber material for molding the sealing material 22 from flowing out to the first contact surface A1 and the second contact surface A2 of the core metal 21 during the molding of the sealing material 22, the inner diameter dimension of the first seal portion 23 Is set to φc ′, and the inner diameter dimension of the cylindrical inner peripheral surface 24b of the second seal portion 24 is set to φf ′ (see FIG. 5), it is preferable to set φc ′ = φf ′.

  Hereinafter, an axle bearing device 1 according to an embodiment of the second invention of the present application will be described. Briefly, the axle bearing device 1 according to the embodiment of the second invention has the shape of the end face of the inner ring 4 and the end face of the rear lid 9 as a cylindrical member facing each other with the spacer member 20 in the first invention. This is opposite to the axle bearing device 1 according to the embodiment.

  That is, in the axle bearing device 1 according to the first and second embodiments of the second invention, as shown in FIGS. 7 and 8, the end surface N of the rear cover 9 adjacent to the spacer member 20 is orthogonal to the axial direction. An end face of the inner ring 4 of the rolling bearing 3 adjacent to the spacer member 20 is formed on a flat face in a direction perpendicular to the axial direction, and an inner diameter side end face. It is provided at a position shifted to the free end side of the axle 2 from M1, and is divided into an outer diameter side end face M2 formed on a flat surface in a direction orthogonal to the axial direction. An inner diameter side end surface M1 and an outer diameter side end surface M2 of the inner ring 4 are continuous via a cylindrical outer peripheral surface M3 extending in the axial direction, and the elastic sealing material of the spacer member 20 is provided to the cylindrical outer peripheral surface M3. The cylindrical inner peripheral surface 24 b of the second seal portion 24 that constitutes 22 is press-fitted.

  In the axle bearing device 1 according to the first embodiment of the second invention shown in FIG. 7, the spacer member 20 (see FIG. 2) constituting the axle bearing device 1 according to the first embodiment of the first invention is left and right. It is attached in the state that is reversed. Therefore, in a state where the axle bearing device 1 is attached to the axle 2, the cored bar 21 constituting the spacer member 20 has one end surface 21a1 (first contact surface A1) and the other end surface of the inner diameter side annular portion 21a. 21a2 (second contact surface A2) contacts the end surface N (the inner diameter side region) of the rear lid 9 and the inner diameter side end surface M1 of the inner ring 4, and the elastic seal material 22 constituting the spacer member 20 is a first seal. The end surface 23a (pressure contact surface C) of the portion 23 and the end surface 24a of the second seal portion 24 are respectively pressed against the end surface N (the outer diameter side region) of the rear lid 9 and the outer diameter side end surface M2 of the inner ring 4. The opening between the inner ring 4 and the rear lid 9 is sealed.

  In this embodiment, the metal core 21 of the spacer member 20 has an annular step surface B having a larger axial separation distance from the pressure contact surface C than the first contact surface A1, and the outer diameter side of the step surface B. The region is covered with the first seal portion 23 of the elastic seal material 22. Therefore, like the axle bearing device 1 according to the first embodiment of the first invention shown in FIG. 3, the axle bearing device 1 having a long life and high reliability can be realized. In addition, since the other characteristic structure of the spacer member 20 of this embodiment is based on the spacer member 20 shown in FIG. 2, detailed description is abbreviate | omitted.

  In the axle bearing device 1 according to the second embodiment of the second invention shown in FIG. 8, the spacer member 20 shown in FIG. For this reason, even in a state where the axle bearing device 1 is attached to the axle 2, the core metal 21 constituting the spacer member 20 has one end surface 21a1 (first contact surface A1) of the inner diameter side annular portion 21a and the other. The end surface 21a2 (second contact surface A2) is in contact with the end surface N (inner diameter side region) of the rear lid 9 and the inner diameter side end surface M1 of the inner ring 4, and the elastic sealing material 22 constituting the spacer member 20 is the first The end surface 23a (pressure contact surface C) of the seal portion 23 and the end surface 24a of the second seal portion 24 are respectively pressed against the end surface N (the outer diameter side region) of the rear lid 9 and the outer diameter side end surface M2 of the inner ring 4. The opening between the inner ring 4 and the rear lid 9 is sealed.

  Also in this embodiment, the metal core 21 of the spacer member 20 has an annular step surface B having a larger axial separation distance from the pressure contact surface C than the first contact surface A1, and the entire region of the step surface B is the same. The elastic seal material 22 is covered with a first seal portion 23. Therefore, as with the axle bearing device 1 according to the second embodiment of the first invention shown in FIG. 6, the axle bearing device 1 having a long life and high reliability can be realized. In addition, since the other characteristic structure of the spacer member 20 of this embodiment is based on the spacer member 20 shown in FIG. 5, detailed description is abbreviate | omitted.

  In the above description, the axle bearing device 1 in which the spacer member 20 according to the present invention is disposed only between the inner ring 4 of the rolling bearing 3 and the rear lid 9 as the second cylindrical member has been described. It is of course possible to arrange the spacer member 20 between the inner ring 4 and the oil drain 8 as the first cylindrical member. That is, the present invention relates to the axle bearing device 1 in which the spacer member 20 is disposed only between the inner ring 4 and the oil drain 8, the space between the inner ring 4 and the oil drain 8, and the inner ring 4 and the rear lid 9. The present invention can also be applied to the axle bearing device 1 in which the spacer member 20 is disposed between each of them.

  The present invention is not limited to the above-described embodiments, and can of course be implemented in various forms without departing from the gist of the present invention. The scope of the present invention is defined by the terms of the claims, and includes the equivalent meanings recited in the claims and all modifications within the scope.

DESCRIPTION OF SYMBOLS 1 Axle bearing device 2 Axle 3 Rolling bearing 4 Inner ring 5 Outer ring 8 Oil removal (first cylindrical member)
9 Rear lid (second cylindrical member)
DESCRIPTION OF SYMBOLS 10 Sealing device 20 Spacer member 21 Core metal 22 Elastic seal material 23 First seal part 24 Second seal part 28 Groove part (lubricant holding part)
28 Recessed part (lubricant holding part)
A1 First contact surface A2 Second contact surface B Step surface C Pressure contact surface

Claims (13)

Among axle bearing devices comprising a rolling bearing that rotatably supports an axle of a railway vehicle and a cylindrical member that is disposed on the outer side in the axial direction of the rolling bearing, it is disposed between the inner ring of the rolling bearing and the cylindrical member. An annular spacer member,
An annular cored bar having first and second abutting surfaces that respectively contact the inner ring and the end surface of the cylindrical member facing each other, and an opening between the inner ring and the cylindrical member provided on the outer peripheral edge of the cored bar Of the first and second seal portions constituting the elastic seal material provided on both sides in the axial direction of the core metal, the first seal portion is in pressure contact with the end surface of the inner ring. In the spacer member having the pressure contact surface to be
The metal core has an annular step surface having a larger axial separation distance from the pressure contact surface than the first contact surface, and at least a part of the step surface is covered with the first seal portion. A spacer member.   2. The spacer member according to claim 1, wherein when the crushing margin of the first seal portion with respect to the end face of the inner ring is a and the axial dimension of the first seal portion is b, a relational expression of a / b <0.5 is satisfied.   The axial direction dimension of the first seal part is b, the inner diameter dimension of the first seal part is φd, and the outer diameter dimension of the cored bar is φe, and the relational expression of φe−φd> b is satisfied. Spacer member.   The spacer member as described in any one of Claims 1-3 in which a 2nd seal | sticker part has a cylindrical inner peripheral surface press-fitted in the cylindrical outer peripheral surface provided in the cylindrical member and extended in the axial direction. Among axle bearing devices comprising a rolling bearing that rotatably supports an axle of a railway vehicle and a cylindrical member that is disposed on the outer side in the axial direction of the rolling bearing, it is disposed between the inner ring of the rolling bearing and the cylindrical member. An annular spacer member,
An annular cored bar having first and second abutting surfaces that abut against the end faces of the cylindrical member and the inner ring facing each other, and an opening between the cylindrical member and the inner ring provided on the outer peripheral edge of the cored bar Of the first and second seal portions constituting the elastic seal material provided on both sides in the axial direction of the metal core, the first seal portion being the end surface of the tubular member. In the spacer member having a pressure contact surface pressed against
The metal core has an annular step surface having a larger axial separation distance from the pressure contact surface than the first contact surface, and at least a part of the step surface is covered with the first seal portion. A spacer member.   6. The spacer according to claim 5, wherein when the crushing margin of the first seal portion with respect to the end surface of the tubular member is a and the axial dimension of the first seal portion is b, the relation of a / b <0.5 is satisfied. Element.   The axial direction dimension of the first seal part is b, the inner diameter dimension of the first seal part is φd, and the outer diameter dimension of the cored bar is φe, and the relational expression of φe−φd> b is satisfied. Spacer member.   The spacer member as described in any one of Claims 5-7 in which a 2nd seal | sticker part has a cylindrical internal peripheral surface press-fit in the cylindrical outer peripheral surface provided in the inner ring | wheel extended in the axial direction.   The spacer member as described in any one of Claims 1-8 with which the partial area | region by the side of the outer diameter of the said level | step difference surface is coat | covered with the said 1st seal | sticker part.   The spacer member as described in any one of Claims 1-8 with which the whole area of the said level | step difference surface is coat | covered with the said 1st seal | sticker part.   The spacer member as described in any one of Claims 1-10 in which the whole region of the said press-contact surface is provided in the outer diameter side rather than the core metal.   The spacer member as described in any one of Claims 1-11 in which a metal core has the lubricant holding part which can hold | maintain a lubricant.   The rolling bearing which rotatably supports the axle of a railway vehicle, the cylindrical member arrange | positioned at the axial direction outer side of a rolling bearing, and any one of Claims 1-12 arrange | positioned between the inner ring | wheel and cylindrical member of a rolling bearing. An axle bearing device comprising the spacer member according to claim 1.

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