WO2018131359A1 - Élément d'espacement et dispositif de palier d'essieu équipé de celui-ci - Google Patents

Élément d'espacement et dispositif de palier d'essieu équipé de celui-ci Download PDF

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Publication number
WO2018131359A1
WO2018131359A1 PCT/JP2017/044344 JP2017044344W WO2018131359A1 WO 2018131359 A1 WO2018131359 A1 WO 2018131359A1 JP 2017044344 W JP2017044344 W JP 2017044344W WO 2018131359 A1 WO2018131359 A1 WO 2018131359A1
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WO
WIPO (PCT)
Prior art keywords
spacer member
inner ring
seal portion
seal
axle
Prior art date
Application number
PCT/JP2017/044344
Other languages
English (en)
Japanese (ja)
Inventor
上野　正典
鈴木　健吾
英一 浦上
義雄 川竹
Original Assignee
Ntn株式会社
中西金属工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ntn株式会社, 中西金属工業株式会社 filed Critical Ntn株式会社
Priority to CN201780082836.2A priority Critical patent/CN110192042B/zh
Publication of WO2018131359A1 publication Critical patent/WO2018131359A1/fr

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
    • B61F15/00—Axle-boxes
    • B61F15/20—Details
    • B61F15/22—Sealing means preventing entrance of dust or leakage of oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/10—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing
    • F16J15/12—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing with metal reinforcement or covering

Definitions

  • the present invention relates to a spacer member and an axle bearing device including the spacer member.
  • Patent Document 1 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).
  • a set of cylindrical members that regulate directional movement.
  • 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.
  • axle bearing device that supports an axle on which a large radial load (bending moment) repeatedly acts
  • Metal wear powder (fretting wear powder) is easily generated due to repeated sliding vibration (fretting).
  • 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.
  • 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
  • FIG. 9B shows a partially enlarged view of the spacer member constituting the axle bearing device.
  • the spacer member 103 of Patent Document 1 includes an annular cored bar 104 made of a soft metal such as a copper alloy, and an annular elastic member provided on the outer peripheral edge of the cored bar 104. And a 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.
  • the spacer member 103 is indicated by a white arrow in FIG. 9B from the inner ring 101 and the rear cover 102 arranged on both sides in the axial direction.
  • Such axial compressive load (variable compressive load) is repeatedly input.
  • 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.
  • 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.
  • 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.
  • 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.
  • the above problem is not limited to the case where the first seal portion 105A of the elastic seal material 105 is disposed adjacent to the inner ring 101, but the left and right sides of the elastic seal material 105 shown in FIG. The same may occur when the seal portion 105A is disposed adjacent to the rear lid 102.
  • 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.
  • 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.
  • the core metal is pressed more than the first contact surface.
  • An annular stepped surface with a large axial separation from the surface And, for 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.
  • 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. can be increased compared to the configuration shown in FIGS. 9A and 9B. 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.
  • 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.
  • 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).
  • the outer diameter dimension (maximum outer diameter dimension) of the cored bar is ⁇ e
  • the relational expression of ⁇ e ⁇ d> b is satisfied, and the relational expression of ⁇ e ⁇ d> 2b is satisfied. More preferably.
  • the first invention can be preferably applied when the second seal portion has a cylindrical inner peripheral surface that is press-fitted into a cylindrical outer peripheral surface provided in the cylindrical member and extending 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.
  • 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.
  • 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.
  • the core metal is the first contact
  • An annulus with a larger axial separation distance from the pressure contact surface than the surface It has a step surface, and at least a part of the stepped surface is covered with the first sealing portion.
  • 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.
  • the second invention can be preferably applied when the second seal portion has a cylindrical inner peripheral surface that is press-fitted into an axial outer peripheral surface provided in the inner ring.
  • 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).
  • the entire 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.
  • 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.
  • 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.
  • 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 drainer 8 is fixed to the axle 2 by a nut (not shown) fastened to the end 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.
  • the end face 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 spacer member 20 as a single unit (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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • at least a part of the step surface B is covered with a first seal portion 23 that constitutes the elastic seal material 22.
  • 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 increased as compared with the conventional configuration shown in FIG. 9B. be able to.
  • 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).
  • 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 position of the surface B in the axial direction is set.
  • the elastic sealing material 22 is molded integrally with the core metal 21 by vulcanization molding using the core metal 21 as an insert part.
  • 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, the prior art described with reference to FIGS. 9A and 9B. The same problem may occur.
  • 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 stepped surface B of the core metal 21.
  • the outer diameter dimension ⁇ c (see FIG. 2) of the inner diameter side annular portion 21a of the core metal 21 and the inner diameter dimension ⁇ d of the first seal portion 23 ( The value of (see FIG. 2) is preferably set so that a relational expression of ( ⁇ d ⁇ c) / 2> 0.5 mm is established, and a relational expression of ( ⁇ d ⁇ c) / 2> 0.8 mm is established. It is more preferable to set so.
  • the outer diameter of the core metal 21 is ⁇ e (see FIG. 2)
  • a relational expression of ⁇ e ⁇ d> b, more preferably a relational expression of ⁇ e ⁇ d> 2b is established between the axial dimension b and the inner diameter dimension ⁇ d of the first seal portion 23. The dimensions of each part are set.
  • the groove 28 provided on both contact surfaces A1 and A2 constitutes the lubricant holding portion
  • the lubricant contact portions are provided on both contact surfaces A1 and A2.
  • the concave portion (dimple) 29 constitutes a lubricant holding portion.
  • the lubricant holding portion can be configured by, for example, through holes that open to both contact surfaces A1 and A2.
  • 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
  • FIG. 6 shows a partially enlarged view of the axle bearing device 1 having the spacer member 20 as a component.
  • 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.
  • 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 from the conventional configuration shown in FIGS. 9A and 9B.
  • 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.
  • 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 ⁇ d ′ and the outer diameter dimension of the cored bar 21 is ⁇ e ′, ⁇ d ′ The relational expression> ⁇ e ′ holds.
  • 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.
  • 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.
  • 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.
  • the spacer member 20 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.
  • 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.
  • 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
  • the spacer member 20 shown in FIG. 8 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.
  • 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.
  • 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
  • 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.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Sealing Of Bearings (AREA)

Abstract

L'invention concerne un élément d'espacement (20) annulaire disposé entre une bague intérieure (4) d'un palier à roulement (3) et un couvercle arrière cylindrique (9), l'élément d'espacement comprenant : une barre centrale annulaire (21) comportant une première et une seconde surface d'appui (A1, A2) en appui respectivement contre une surface d'extrémité (M) de la bague intérieure (4) et une surface d'extrémité côté diamètre intérieur (N1) du couvercle arrière (9) ; et un matériau d'étanchéité (22) élastique annulaire disposé sur une section de bord périphérique extérieure de la barre centrale (21). Le matériau d'étanchéité (22) élastique comporte une première et une seconde section d'étanchéité (23, 24) disposées respectivement sur les deux côtés de direction axiale de la barre centrale (21), et la première section d'étanchéité (23) présente une surface de sertissage (C) qui est sertie sur la surface d'extrémité (M) de la bague intérieure (4). La barre centrale (21) comporte une surface formant épaulement (B) annulaire configurée de telle sorte que la distance de séparation de direction axiale par rapport à la surface de sertissage (C) soit supérieure à celle de la première surface d'appui (A1), et au moins une partie de la surface formant épaulement (B) est recouverte par la première section d'étanchéité (23).
PCT/JP2017/044344 2017-01-10 2017-12-11 Élément d'espacement et dispositif de palier d'essieu équipé de celui-ci WO2018131359A1 (fr)

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JP2017001845A JP6794271B2 (ja) 2017-01-10 2017-01-10 スペーサ部材およびこれを備える車軸用軸受装置
JP2017-001845 2017-01-10

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CN110998769B (zh) 2017-07-21 2022-07-01 日本精工株式会社 染料敏化型光电转换元件

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004332905A (ja) * 2003-05-12 2004-11-25 Ntn Corp 鉄道車両用軸受装置
JP2005337302A (ja) * 2004-05-24 2005-12-08 Ntn Corp 鉄道車両用軸受装置

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN201322044Y (zh) * 2009-03-10 2009-10-07 青岛四方车辆研究所有限公司 高承载铁路货车轴承
US8356941B2 (en) * 2010-03-08 2013-01-22 Amsted Rail Company, Inc. Railway car bearing seal

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004332905A (ja) * 2003-05-12 2004-11-25 Ntn Corp 鉄道車両用軸受装置
JP2005337302A (ja) * 2004-05-24 2005-12-08 Ntn Corp 鉄道車両用軸受装置

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JP2018112220A (ja) 2018-07-19
JP6794271B2 (ja) 2020-12-02
CN110192042B (zh) 2021-03-12

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