WO2018230641A1 - Roulement à rouleaux - Google Patents

Roulement à rouleaux Download PDF

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Publication number
WO2018230641A1
WO2018230641A1 PCT/JP2018/022722 JP2018022722W WO2018230641A1 WO 2018230641 A1 WO2018230641 A1 WO 2018230641A1 JP 2018022722 W JP2018022722 W JP 2018022722W WO 2018230641 A1 WO2018230641 A1 WO 2018230641A1
Authority
WO
WIPO (PCT)
Prior art keywords
roller bearing
seal member
flange portion
peripheral surface
flange
Prior art date
Application number
PCT/JP2018/022722
Other languages
English (en)
Japanese (ja)
Inventor
将 土屋
智秋 寺田
聖也 丸亀
Original Assignee
Ntn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
Priority claimed from JP2018097150A external-priority patent/JP2019002560A/ja
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Priority to EP18818789.2A priority Critical patent/EP3640489A4/fr
Publication of WO2018230641A1 publication Critical patent/WO2018230641A1/fr

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    • 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
    • F16C19/24—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 radial load mainly
    • F16C19/26—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 radial load mainly with a single row 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
    • 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
    • F16C19/44—Needle bearings
    • F16C19/46—Needle bearings with one row or needles
    • 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
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members

Definitions

  • the present invention relates to a roller bearing, and more particularly to a roller bearing provided with a seal member.
  • roller bearing provided with a seal member for the purpose of sealing lubricating oil inside the bearing or preventing intrusion of fluid or foreign matter from the outside.
  • Patent Document 1 thin edge portions are provided at both axial end portions of a cylindrical outer ring that does not have a flange extending radially inward.
  • a seal member having a substantially S-shaped cross section is fitted.
  • This needle roller bearing is fitted in a housing of a fluid control valve of an internal combustion engine (engine), and a seal member having a substantially S-shaped cross section is disposed in close contact with the housing, thereby allowing fluid (exhaust gas). ) Is prevented from entering the bearing.
  • a metal core may be provided on the seal member.
  • the manufacturing cost of the sealing member increases. Therefore, when a core metal is provided on the seal member, there is a problem that the manufacturing cost of the roller bearing increases.
  • the present invention has been made in order to solve the above-described problems, and an object of the present invention is to reinforce the seal member without providing a cored bar and to prevent wear of the seal member. It is to provide a roller bearing.
  • the roller bearing according to an aspect of the present invention includes an outer ring, a plurality of rollers, and a seal member.
  • the outer ring has a cylindrical portion whose inner peripheral surface forms a raceway surface, and a flange portion connected to at least one axial end of the cylindrical portion.
  • the plurality of rollers roll on the raceway surface of the cylindrical portion, and rotatably support the rotating element.
  • the seal member is held by the flange portion.
  • the flange portion includes a first portion extending radially inward from the end of the cylindrical portion, and a second portion extending axially outward from the radially inner end of the first portion.
  • the roller bearing may further include a cage that accommodates the roller.
  • the flange portion be disposed so as to restrict the axial movement of the cage.
  • the cage is opposed to the radially inner end of the first portion of the flange portion in the axial direction.
  • the seal member includes an inner diameter side seal portion disposed between the outer peripheral surface of the rotating element and the second portion of the flange portion.
  • the seal member When the outer ring is fitted in the housing, the seal member preferably includes an outer diameter side seal portion disposed between the inner peripheral surface of the housing and the second portion of the flange portion.
  • the seal member When the outer ring is fitted in the housing, the seal member may be disposed so as to surround the second portion of the flange portion between the outer peripheral surface of the rotating element and the inner peripheral surface of the housing. desirable.
  • the thickness of the second portion of the flange portion is equal to or less than the thickness of the first portion.
  • the seal member includes a lip in contact with the outer peripheral surface of the rotating element.
  • the seal member includes a first region disposed between an inner peripheral surface of the housing into which the outer ring is fitted and the second portion of the flange portion, and an axially outer side of the first region.
  • a second region having a lip disposed between the inner peripheral surface and the outer peripheral surface of the rotating element and in contact with the outer peripheral surface of the rotating element.
  • the first region is disposed in contact with the outer surface of the first portion of the flange portion, and the second region faces the axially outer end surface of the second portion of the flange portion in a non-contact state. It is desirable to have a part.
  • the facing part includes the base part of the lip.
  • the axis of the outer diameter surface or inner diameter surface of the second portion of the flange portion is disposed inside a virtual circle having a diameter of 0.5 mm centering on the axis of the inner peripheral surface of the housing.
  • the outer ring has a flange portion only on one axial side of the cylindrical portion, and has an inward flange portion extending radially inward on the other axial side of the cylindrical portion.
  • the first portion extending radially inward from the end of the cylindrical portion of the outer ring, and the second portion extending radially outward from the radially inner end of the first portion;
  • the seal member is held by the flange portion having. Therefore, the seal member can be reinforced by the flange portion of the outer ring without providing a separate cored bar.
  • FIG. 1 is a cross-sectional view schematically showing a configuration of a roller bearing 4 according to the present embodiment.
  • FIG. 2 is a partial cross-sectional view showing an enlarged region II of FIG.
  • the roller bearing 4 is a shell-type roller bearing housed in a cylindrical hole of the housing 1, and includes a shell-type outer ring (hereinafter abbreviated as “outer ring”) 5 and a plurality of rollers. 6 and an annular seal member 7.
  • outer ring shell-type outer ring
  • the center line of the roller bearing 4 is indicated by a one-dot chain line.
  • axial direction the direction along the center line of the roller bearing 4
  • radial direction the direction orthogonal to the center line of the roller bearing 4
  • the outer ring 5 is press-fitted into the hole portion of the housing 1 and has a cylindrical portion 51 and a pair of flange portions 52 and 53 provided at both ends of the cylindrical portion 51 in the axial direction.
  • the inner peripheral surface of the cylindrical portion 51 constitutes the raceway surface of the roller 6.
  • the flange portion 52 on one axial side (the left side in the drawing) of the pair of flange portions 52, 53 is a first portion extending radially inward from the end portion of the cylindrical portion 51. 52a and a second portion 52b extending outward in the axial direction from the radially inner end of the first portion 52a.
  • the flange portion 53 on the other axial side (the right side in the drawing) of the pair of flange portions 52 and 53 corresponds to an inward flange of a general shell-shaped outer ring, and extends straight inward in the radial direction.
  • the general flange-shaped flange portion 53 is referred to as an “inward flange portion 53” in order to easily distinguish the flange portions 52 and 53.
  • the first portion 52 a of the flange portion 52 is disposed substantially parallel to the inward flange portion 53. That is, the first portion 52a extends in the radial direction so that the angle with the cylindrical portion 51 is substantially a right angle.
  • the first portion 52 a and the inward flange portion 53 of the flange portion 52 face the end surface of the roller 6.
  • the second portion 52 b of the flange portion 52 is disposed substantially parallel to the cylindrical portion 51. That is, the second portion 52b extends in the axial direction so that the angle with the first portion 52a is substantially a right angle.
  • the boundary part between the cylindrical part 51 and the first part 52a and the boundary part between the first part 52a and the second part 52b are R-shaped for processing.
  • the plate thickness D13 of the second portion 52b is preferably equal to or less than the plate thickness D12 of the first portion 52a.
  • the plate thickness D12 of the first portion 52a may be the same as or greater than the plate thickness D11 of the cylindrical portion 51.
  • the plurality of rollers 6 roll on the raceway surface of the outer ring 5 and rotatably support the rotating shaft 2.
  • the roller 6 is a needle roller. That is, the roller bearing 4 according to the present embodiment is a shell needle roller bearing.
  • the rotating element that is rotatably supported by the plurality of rollers 6 is not limited to the rotating shaft 2 and may be an inner ring (not shown) provided in the roller bearing 4.
  • the roller bearing 4, the rotating shaft 2 supported by the roller bearing 4, and the housing 1 constitute a rotating shaft support structure.
  • the plurality of rollers 6 are held by the cage 60.
  • the cage 60 has a plurality of pockets for accommodating the plurality of rollers 6 respectively. Since the plurality of pockets are provided at regular intervals in the circumferential direction, the distance between the plurality of rollers 6 is kept constant by the cage 60.
  • the cage 60 faces the radially inner end portion of the first portion 52a of the flange portion 52 in the axial direction.
  • the seal member 7 is held by the flange portion 52 and includes at least a lip 74 that is in sliding contact with the rotating shaft 2.
  • the seal member 7 is sandwiched between the outer peripheral surface of the rotating shaft 2 and the inner peripheral surface of the housing 1 and is disposed so as to surround the second portion 52 b of the flange portion 52. Further, the entire seal member 7 is disposed on the outer side in the axial direction than the first portion 52 a of the flange portion 52.
  • the seal member 7 is an elastic body, and examples of the material thereof include nitrile rubber, acrylic rubber, silicone rubber, and fluorine rubber. A specific configuration example of the seal member 7 will be described later. In the present embodiment, no seal member is disposed on the inward flange portion 53 side.
  • the (minimum) inner diameter dimension D1 of the second portion 52b of the flange portion 52 is smaller than the outer diameter dimension D2 of the cage 60. Therefore, movement (detachment) of the roller 6 and the cage 60 to one side in the axial direction is restricted by the flange portion 52.
  • the flange part 52 is arrange
  • the outer ring 5 As a manufacturing method of the outer ring 5, for example, there is a method of increasing hardness by heat treatment after cold-rolling steel sheet is drawn by a press. In this case, after punching the center part of the bottom part of the cup formed by drawing, the second part of the flange part 52 is subjected to burring while thinning the inner peripheral side part of the annular bottom part. 52b is formed. The remaining portion of the annular bottom portion, that is, the outer peripheral side portion corresponds to the first portion 52 a of the flange portion 52.
  • the elastic restoration after the plastic processing can be prevented by performing the ironing simultaneously with the burring.
  • the angle and the plate thickness of the second portion 52b of the flange portion 52 can be stabilized, so that the mounting performance of the seal member 7 is improved, the rigidity of the seal member 7 is stabilized, and the seal member 7 is sealed. It is possible to stabilize the stopping force.
  • the inward flange portion 53 can be formed by bending.
  • the inward flange portion 53 may be thinner than the cylindrical portion 51 in order to facilitate bending.
  • the formation method of the flange part 52 is not limited to an above-described burring process.
  • a method may be employed in which a cup bottom including the first portion 52a and the second portion 52b is formed at the time of drawing and the center portion of the cup bottom is punched out with a mold.
  • the manufacturing method of the outer ring 5 is not limited to the drawing process as described above, and may be manufactured by cutting the outer ring from a steel material.
  • the thickness of the second portion 52b of the flange portion 52 is not particularly limited.
  • the cage 60 for example, there is a method of punching a pocket from a rolled steel plate, bending the rolled steel plate into an annular shape, and welding the end portions. According to this manufacturing method, the manufacturing cost of the cage 60 can be suppressed.
  • the annular shape may be drawn by pressing, or may be manufactured by cutting a steel pipe.
  • the material of the cage 60 is not limited to metal, and may be resin.
  • the seal member 7 is disposed between the outer peripheral surface of the rotary shaft 2 and the inner peripheral surface of the housing 1 so as to surround the second portion 52 b of the flange portion 52. Therefore, the seal member 7 includes an inner diameter side seal portion 71 positioned between the outer peripheral surface of the rotary shaft 2 and the second portion 52 b of the flange portion 52, and the inner peripheral surface of the housing 1 and the second portion of the flange portion 52. And an outer diameter side seal portion 72 located between the portion 52b. The inner diameter side seal portion 71 and the outer diameter side seal portion 72 are integrally connected by an outer seal portion 73 located on the outer side in the axial direction than the second portion 52 b of the flange portion 52.
  • the inner diameter side seal portion 71 is disposed in close contact with the inner diameter surface of the second portion 52 b of the flange portion 52.
  • the inner diameter side seal portion 71 does not overlap with the first portion 52a of the flange portion 52 in the axial direction position. That is, the inner diameter side seal portion 71 is disposed offset in the axial direction to the outside of the position of the first portion 52a.
  • the base portion 74b of the lip 74 is included in the inner diameter side seal portion 71, and the lip 74 extends obliquely outward in the axial direction.
  • the outer diameter side seal portion 72 is in close contact with both the inner peripheral surface of the housing 1 and the outer diameter surface of the second portion 52b. In addition, at least a part of the axial inner surface of the outer diameter side seal portion 72 is in close contact with the axial outer surface of the first portion 52 a of the flange portion 52.
  • the outer seal portion 73 is in close contact with the axially outer end surface of the second portion 52b, and is in close contact with the inner peripheral surface of the housing 1 together with the outer diameter side seal portion 72.
  • the entire second portion 52 b of the flange portion 52 is in a state of entering the inside of the seal member 7. Further, the second portion 52 b of the flange portion 52 extends outward in the axial direction from the axial position (position of the axial outer edge) L of the base portion 74 b of the lip 74. Thereby, according to this Embodiment, the 2nd part 52b of the flange part 52 can be functioned as a metal core of the sealing member 7.
  • the contact force of the lip 74 of the seal member 7 to the rotating shaft 2 and the contact force of the outer diameter side seal portion 72 of the seal member 7 to the housing 1 can be increased.
  • the sealing force of the sealing member 7 can be increased as in the case where the core member is provided on the sealing member.
  • the manufacturing cost of the sealing member 7 it is not necessary to incorporate a cored bar in the sealing member 7 itself, so that the manufacturing cost of the sealing member 7 can be reduced.
  • a part of the flange portion 52 of the outer ring 5 that is a shell-shaped outer ring fulfills the function of a metal core, the manufacturing cost of the roller bearing 4 as a whole can be reduced.
  • the seal member 7 since the inner diameter side seal portion 71 is arranged without protruding inward in the axial direction from the position of the first portion 52 a of the flange portion 52, the seal member 7 does not come into contact with the cage 60. . Therefore, wear of the seal member 7 can be prevented.
  • the seal member 7 may further include one or more lips in addition to the lip 74 described above. That is, the seal member 7 may have a plurality of lips. For example, by providing a lip (not shown) on the outer peripheral surface of the seal member 7, the contact force of the seal member 7 on the housing 1 side can be more sufficiently increased. Even in this case, it is desirable that the axial position of the base portion of the lip is positioned on the inner side in the axial direction than the tip position of the second portion 52b of the flange portion 52.
  • the seal member 7 may be held by increasing the surface roughness of the flange portion 52, or a part of the flange portion 52 may be narrowed to reduce the seal member. 7 may be hooked and held. Or you may provide a protrusion with a burr in the part which contacts the flange part 52 of the sealing member 7, and may prevent it from coming off.
  • the seal member 7 may be fixed using an adhesive, or the seal member 7 including the outer ring 5 may be injection-molded. Is not limited.
  • the shape of the flange portion 52 of the outer ring 5 is not limited to the shape as shown in FIG.
  • the second portion 52b of the flange portion 52A may be slightly inclined.
  • the second portion 52b of the flange portion 52A is slightly inclined so that its inner diameter dimension gradually increases toward the outer side in the axial direction.
  • the first portion 52a of the outer ring 5 may be slightly inclined.
  • the shape of the seal member 7 held by the flange portion 52 of the outer ring 5 is not limited to the shape shown in FIG.
  • the seal member 7 ⁇ / b> A may not have the outer diameter side seal portion 72 shown in FIG. 2.
  • the seal member 7A can be reinforced by the flange portion 52 of the outer ring 5 by bonding the inner diameter side seal portion 71 to the inner diameter surface of the second portion 52b.
  • adhesion of the seal member 7A to the flange portion 52 may be realized by, for example, an adhesive, or may be realized by heat welding.
  • the seal member 7 ⁇ / b> B may not include not only the outer diameter side seal portion 72 but also the outer seal portion 73.
  • the entire lip 74 is included in the inner diameter side seal portion 71, and the tip end portion 74 a of the lip 74 is pressed against the outer peripheral surface of the rotating shaft 2 by the second portion 52 b of the flange portion 52.
  • the seal member 7 ⁇ / b> C may not include the inner diameter side seal portion 71 illustrated in FIG. 2. In this case, the entire lip 74 is included in the outer seal portion 73. Also in this example, the seal member 7C can be reinforced by the flange portion 52 of the outer ring 5 by bonding the outer diameter side seal portion 72 to the outer diameter surface of the second portion 52b.
  • the seal member 7D is arranged so as to surround the second portion 52b of the flange portion 52, the seal shape around the second portion 52b of the flange portion 52 is appropriately set. It may be changed. Thereby, the contact force of the seal member 7D with respect to the housing 1 side and the rotating shaft 2 side can be adjusted, and the fitting (attachment) of the seal member 7D to the second portion 52b of the flange portion 52 can be simplified.
  • the entire lip 74 is included in the outer seal portion 73, at least the root portion 74 b of the lip 74 is included in the inner diameter side seal portion 71 as shown in FIG.
  • the radial dimension from the base 74b to the tip 74a of the lip 74 can be increased. Therefore, from the viewpoint of improving the strength of the lip 74 and the workability of the seal member, it is desirable that the entire lip 74 is included in the outer seal portion 73.
  • FIG. 8 schematically shows another example of the shape of the seal member configured so that the entire lip 74 is included in the outer seal portion 73.
  • a seal member 7E shown in FIG. 8 includes an outer diameter side seal portion 72A and an outer seal portion 73A, similarly to the seal member 7C shown in FIG.
  • the outer diameter side seal portion 72A corresponds to a region (first region) of the seal member 7E disposed between the inner peripheral surface of the housing 1 and the second portion 52b of the flange portion 52 of the outer ring 5.
  • the outer seal portion 73A is located on the outer side in the axial direction than the second portion 52b of the flange portion 52 of the outer ring 5 in the seal member 7E, and is between the inner peripheral surface of the housing 1 and the outer peripheral surface of the rotary shaft 2. This corresponds to the area (second area) to be arranged.
  • the outer-diameter side seal portion 72A and the outer-side seal portion 73A are integrally formed continuously in the axial direction.
  • the outer diameter side seal portion 72A contacts (surface contact) with the outer peripheral surface of the second portion 52b of the flange portion 52, and also contacts (surface contact) with the axially outer surface of the first portion 52a of the flange portion 52. Placed in the state. Note that the outer diameter side seal portion 72A may not be in contact with the axially outer surface of the first portion 52a.
  • the outer seal portion 73A includes a main body portion 75 that is positioned radially outward from the position of the inner peripheral surface of the outer diameter side seal portion 72A (the position of the outer peripheral surface of the second portion 52b of the flange portion 52), Projecting radially inward from the position of the inner peripheral surface of the seal portion 72A and facing the end surface 52c of the second portion 52b of the flange portion 52, and the axial direction from the radially inner end of the facing portion 76 And a lip 74 extending outward (obliquely).
  • the base portion 74 b of the lip 74 is disposed within the thickness range of the second portion 52 b of the flange portion 52.
  • a base portion 74 b of the lip 74 is included in the facing portion 76. Note that the lip 74 may extend obliquely from the radially inner end of the main body 75 toward the axially outer side.
  • the facing portion 76 of the outer seal portion 73 ⁇ / b> A is not in contact with the end surface 52 c of the second portion 52 b of the flange portion 52. In this respect, it is greatly different from the seal member 7C shown in FIG.
  • the axial length L1 from the position of the axially inner end face of the outer diameter side seal portion 72A to the facing portion 76 of the outer seal portion 73A is the axial length of the second portion 52b of the flange portion 52. Longer than L2.
  • the axial length L2 corresponds to the axial length of the second portion 52b starting from the position of the outer surface of the first portion 52a of the flange portion 52.
  • a gap C is formed between the end surface 52c of the flange portion 52 and the facing portion 76 of the outer seal portion 73A (that is, the root portion 74b of the lip 74).
  • the gap C is exaggerated from the viewpoint of facilitating understanding.
  • the difference between the axial lengths L1 and L2 is preferably 0.1 mm or more. That is, the difference between the axial lengths L1 and L2 is preferably 1/20 or more of the interval L12. In consideration of the axial dimension of the entire seal member 7E, the difference between the axial lengths L1 and L2 is preferably 1/10 or less (0.2 mm or less) of the distance L12.
  • the main body portion 75 of the outer seal portion 73A has a protruding portion 77 that protrudes outward in the axial direction from the position of the base portion 74b of the lip 74.
  • the overhanging portion 77 is a portion that faces the outer diameter surface of the lip 74 and receives a reaction force of the lip 74.
  • the outer peripheral surface of the main body 75 including the overhanging portion 77 is disposed in close contact with the inner peripheral surface of the housing 1.
  • the outer peripheral surface of the main body 75 of the outer seal portion 73 forms one cylindrical surface together with the outer peripheral surface of the outer diameter side seal portion 72A.
  • the radial thickness dimension L13 of the overhanging portion 77 is larger than the radial thickness dimension (radial dimension from the root portion 74b to the tip portion 74a) L14 of the lip 74.
  • the strength of the overhanging portion 77 is higher than the strength of the lip 74, so that the deformation of the overhanging portion 77 hardly affects the deformation of the lip 74.
  • the thickness dimension L13 of the protruding portion 77 may be smaller than the thickness dimension L11 of the outer diameter side seal portion 72A. Thereby, the cross-sectional shape of the main-body part 75 becomes a substantially L shape.
  • a space between the projecting portion 77 and the lip 74 is surrounded by an inner peripheral surface of the projecting portion 77, an outer diameter surface of the lip 74, and an annular surface 75a facing outward in the axial direction.
  • a space S is formed.
  • the annular surface 75 a is a surface that extends in the radial direction and has a base portion 74 b of the lip 74 as an inner periphery and an axially inner end edge of the inner peripheral surface of the projecting portion 77 as an outer periphery.
  • the annular surface 75a may be an orthogonal surface orthogonal to the axial direction, or may be a tapered surface that expands toward the outer periphery.
  • the outer diameter side seal portion 72A is in surface contact with the outer surface of the first portion 52a of the flange portion 52.
  • the inner diameter surface of the side seal portion 72 ⁇ / b> A is in surface contact with the outer diameter surface of the second portion 52 b of the flange portion 52.
  • the seal member 7E has a tightening margin on the outer peripheral side. As a result, the seal member 7E is sandwiched between the inner peripheral surface of the housing 1 and the second portion 52b of the flange portion 52. Therefore, also in this embodiment, the second portion 52b of the flange portion 52 is inserted into the seal member 7E. It can function as a metal core.
  • the outer diameter side seal portion 72A is provided on the outer surface of the first portion 52a of the flange portion 52 and the outer diameter surface of the second portion 52b of the flange portion 52. It is desirable to fix to at least one of them by a known method (adhesion with an adhesive, heat fusion, etc.).
  • a gap C is provided between the base portion 74 b of the lip 74 and the end surface 52 c of the flange portion 52.
  • the base portion 74 b of the lip 74 does not hit the end surface 52 c of the flange portion 52. Therefore, even when the thickness of the second portion 52b of the flange portion 52 is thin, the deformation of the second portion 52b due to the pressure from the outside in the axial direction can be prevented.
  • the seal member 7E by preventing the seal member 7E from coming into contact with the end surface 52c of the flange portion 52, damage to the seal member 7E can be prevented even when the entire end surface 52c is not a smooth surface.
  • the outer ring 5 is formed by press shearing, in the process of punching the center part of the bottom of the cup with a punch (jig), a severely broken surface and burrs are generated on the cut surface of the bottom of the cup. Is done. Therefore, the outer surface 52f of the first portion 52a of the flange portion 52 and the outer diameter surface of the second portion 52b are smooth surfaces, whereas the end surface of the second portion 52b is shown in FIG.
  • the fracture surface 52d and the burr 52e remain in 52c.
  • the burr 52e is formed at a corner on the outer diameter side of the end face 52c. In FIG. 9, the unevenness of the fracture surface 52d and the burr 52e are exaggerated.
  • the facing portion 76 including the base portion 74b of the lip 74 does not abut against the end surface 52c of the flange portion 52. Even at times, the seal member 7E can be prevented from being damaged. Further, the force from the outside in the axial direction applied to the outer end surface in the axial direction of the main body portion 75 of the outer seal portion 73A is directed inward in the axial direction and is received by the outer surface of the first portion 52a of the flange portion 52.
  • the seal member 7E has a structure that is less likely to transmit force to the lip 74 than the seal member 7C shown in FIG. Thereby, since the lip 74 can be stably brought into contact with the rotating shaft 2, an increase in the operating torque of the rotating shaft 2 can be prevented.
  • the seal member (7 or 7A,..., 7E) described above is disposed in surface contact with at least one of the outer diameter surface and the inner diameter surface of the second portion 52b of the flange portion 52. There is an advantage that the seal member can be easily aligned with respect to the center.
  • the raceway surface (cylindrical surface) is caused by anisotropy or heat treatment strain of the thin steel strip.
  • the roundness of the inner peripheral surface of the portion increases.
  • the outer diameter of the cylindrical portion of the outer ring is manufactured to be larger than the diameter of the inner peripheral surface of the housing 1, and the cylindrical portion is deformed by the pressure received from the housing 1 when press-fitted into the housing 1. There is. Therefore, it is difficult to use the raceway surface of the shell-shaped outer ring as a reference surface for alignment of the seal member.
  • the flange portion 52 of the outer ring 5 has the second portion 52b that is disposed away from the inner peripheral surface of the housing 1 in the attached state.
  • the outer diameter surface or inner diameter surface of 52b can be used as a reference surface for alignment of the seal member.
  • the comparison is made. High strength. Therefore, even if heat treatment is performed during manufacture of the outer ring 5 according to the present embodiment, there is a low possibility of distortion occurring on the outer diameter surface or inner diameter surface of the second portion 52b.
  • the axis of the outer diameter surface or inner diameter surface of the second portion 52b of the flange portion 52 is used as a housing. What is necessary is just to be arrange
  • the axis J2 of the outer diameter surface or inner diameter surface of the second portion 52b of the flange portion 52 is ideally coincident with the axis J1 of the inner peripheral surface of the housing 1, it is inside the virtual circle. It only has to be arranged.
  • the thickness of the second portion 52b is preferably equal to or greater than the thickness of the cylindrical portion 51.
  • the thickness of the second portion 52b may be equal to or greater than the thickness of the first portion 52a.
  • both the first portion 52a and the second portion 52b may be larger than the thickness of the inward flange portion 53 shown in FIG.
  • the inner diameter dimension of the second portion 52 b may be smaller than the inner diameter dimension of the inward flange portion 53.
  • the processing of the flange portion 52 can be performed as follows. That is, when the outer peripheral surface and the inner peripheral surface of the cylindrical portion 51 are pressed, the second portion 52b of the flange portion 52 is processed at the same time, and the second portion 52 is constrained in the mold.
  • the flange portion 52 may be manufactured so that the shaft center of 52b and the shaft center of the cylindrical portion 51 are aligned.
  • roller bearing 4 can be applied to a fluid control valve such as an EGR (Exhaust Gas Recirculation) control valve. That is, the roller bearing 4 is a roller bearing for an EGR control valve.
  • EGR exhaust Gas Recirculation
  • FIG. 10 is a schematic cross-sectional view schematically showing a main part of an EGR control valve to which the roller bearing 4 according to the present embodiment is applied.
  • the EGR control valve re-opens the exhaust passage from the exhaust passage to the intake passage through the exhaust gas passage 11 by changing the opening area of the exhaust gas passage 11 formed inside the housing 1 continuously or stepwise.
  • This is an exhaust gas flow rate control valve (exhaust throttle valve) that variably controls the flow rate of exhaust gas that is circulated (refluxed).
  • the housing 1 is provided with a cylindrical hole 12 that intersects with the exhaust gas flow path 11, and the rotation shaft 2 and a support mechanism that rotatably supports the rotation shaft 2 are accommodated in the hole 12. Is done.
  • the hole 12 of the housing 1 includes a central hole 12a located at the center in the axial direction, a small-diameter hole 12b located on one axial side (left side of the paper) of the central hole 12a and having a smaller diameter than the central hole 12a. And a large-diameter hole portion 12c which is located on the other axial side of the central hole portion 12a (on the right side in the drawing) and has a larger diameter than the central hole portion 12a.
  • the rotating shaft 2 includes a large diameter portion 21 supported by a support mechanism, and a small diameter portion 22 which is smaller in diameter than the large diameter portion 21 and is located adjacent to one side in the axial direction of the large diameter portion 21. Yes.
  • the tip of the small diameter portion 22 protrudes to the gas flow path 11 and is connected and fixed to the valve body 13 in the gas flow path 11.
  • the large-diameter portion 21 of the rotary shaft 2 is accommodated in the central hole portion 12a and the large-diameter hole portion 12c of the housing 1, and the other axial end portion of the small-diameter portion 22 of the rotary shaft 2 is accommodated in the small-diameter hole portion 12b of the housing 1. Contained.
  • the axis of the rotating shaft 2 is indicated by a one-dot chain line.
  • the valve element 13 has a circular shape in plan view.
  • the posture (position) of the valve body 13 is changed between the fully closed position and the fully open position according to the rotation angle of the rotary shaft 2.
  • the valve element 13 in the fully closed position is indicated by a solid line
  • the valve element 13 in the fully open position is indicated by an imaginary line (two-dot chain line).
  • the exhaust gas flow path 11 has a flow path 11a on the exhaust passage side and a flow path 11b on the intake passage side, and the exhaust gas flows from the flow path 11a side to the flow path 11b side.
  • the flow path 11a has a larger diameter (inner diameter) than the flow path 11b, and a step portion 11c is provided between the flow paths 11a and 11b.
  • the diameter (outer diameter) of the valve body 13 is smaller than the diameter of the flow path 11a and larger than the diameter of the flow path 11b.
  • valve body 13 When the valve body 13 is located at the fully closed position, the valve body 13 is fitted into the step portion 11 c of the exhaust gas passage 11. As a result, the annular gap between the inner peripheral surface of the exhaust gas passage 11 and the outer peripheral end surface of the valve body 13 is completely sealed. In this case, the exhaust gas is not mixed into clean intake air (fresh air) that has passed through the air cleaner.
  • the outer peripheral portion of the valve body 13 does not contact the stepped portion 11c of the gas flow path 11.
  • the exhaust gas is mixed into clean intake air (fresh air) that has passed through the air cleaner.
  • the support mechanism includes one ball bearing 3 and one roller bearing 4 described above.
  • the ball bearing 3 and the roller bearing 4 support the large-diameter portion 21 of the rotating shaft 2 so as to be rotatable with respect to the housing 1.
  • the support mechanism includes not only the roller bearing 4 but also the ball bearing 3, the axial position of the rotating shaft 2 is fixed.
  • the ball bearing 3, the roller bearing 4, the rotating shaft 2 supported by these bearings 3 and 4, and the housing 1 constitute a rotating shaft support structure.
  • the outer diameter of the ball bearing 3 is larger than the outer diameter of the roller bearing 4.
  • the ball bearing 3 is press-fitted into the large-diameter hole 12 c of the housing 1, and the roller bearing 4 is press-fitted into the central hole 12 a of the housing 1.
  • the roller bearing 4 is provided closer to the exhaust gas flow path 11 than the ball bearing 3.
  • the exhaust gas in the exhaust gas passage 11 is caused by an annular gap between the inner peripheral surface of the hole portion 12 (small diameter hole portion 12b) of the housing 1 and the outer peripheral surface of the small diameter portion 22 of the rotary shaft 2. 14 is assumed to enter the central hole portion 12a in which the roller bearing 4 is disposed. Since the roller bearing 4 includes the seal member 7 (7A, 7B, 7C, 7D, 7E) at the end on the gas flow path 11 side, the exhaust gas as a corrosive fluid enters the roller bearing 4. This can be prevented.
  • seal member 7 is reinforced by the second portion 52b of the flange portion 52 of the outer ring 5, according to the present embodiment, the fluid sealing performance by the seal member 7 can be enhanced. Therefore, even the high-pressure fluid can be properly sealed by the seal member 7.
  • the roller bearing 4 when the roller bearing 4 is provided with the seal member 7 for sealing the exhaust gas, it is not necessary to provide a separate seal member that is disposed away from the bearing. Therefore, the axial length of the support mechanism can be shortened as compared with the configuration in which the rotary shaft is rotatably supported by the double ball bearings. As a result, since the housing 1 can be made compact, the EGR control valve can be downsized.
  • roller bearing 4 is not limited to the EGR control valve of an automobile.
  • the fluid control valve to which the roller bearing 4 can be applied includes, for example, i) an intake flow rate control valve such as an electronically controlled throttle valve of an automobile, ii) a low-temperature exhaust gas passage installed on the outlet side of the exhaust gas recirculation cooler, Exhaust gas flow path switching valve for switching a bypass flow path (high temperature exhaust gas flow path) for bypassing the circulating exhaust gas from the exhaust gas recirculation cooler, iii) Exhaust gas flow rate installed in the exhaust pipe of the engine (turbo housing of the turbocharger) (Pressure) control valve.
  • the roller bearing 4 may be applied to other types of exhaust control valves such as an exhaust throttle valve or an exhaust brake valve.
  • the fluid control valve to which the roller bearing 4 is applied may be a control valve of a vehicle or a device other than an automobile.
  • a control valve of a vehicle for example, an air control valve of a fuel cell can be mentioned.
  • the seal member 7 is provided only on one side of the roller bearing 4 in the axial direction.
  • the seal member 8 is a known seal member that is disposed inside the inward flange portion 53 so as to face the roller 6. In this case, grease can be filled inside the bearing.
  • a grease that can be used in a high temperature environment such as urea grease or fluorine grease.
  • the seal member 8 on the other side may come into contact with the cage 60, but at least as compared with the configuration in which both seal members can contact the cage 60. There is an advantage that wear of one seal member 7 can be prevented.
  • the roller bearing may not include the cage 60.
  • the movement of the roller 6 to one side in the axial direction is restricted by the flange portion 52 of the outer ring 5. Therefore, since the seal member 7 does not contact the roller 6, wear of the seal member 7 due to contact with the roller 6 can be prevented.
  • wheel of the roller bearing may have the flange part which can hold
  • the flange itself may not be provided on the other axial side of the outer ring of the roller bearing. That is, the outer ring may have a flange as the flange portion 52 only at one end portion in the axial direction. That is, the roller bearing may be a cylindrical roller bearing instead of a shell roller bearing.

Landscapes

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

Abstract

L'invention concerne un roulement à rouleaux (4) pourvu : d'un chemin de roulement extérieur (5) possédant une partie cylindre (51), dont une surface périphérique interne constitue une partie d'une surface de chemin de roulement, et possédant une partie latérale (52) reliée au moins à une partie d'extrémité dans la direction axiale de la partie cylindre (51) ; d'une pluralité de rouleaux (6) permettant de rouler sur la surface de chemin de roulement de la partie cylindre (51) et supportant de façon rotative un élément rotatif (2) ; et d'un élément d'étanchéité (7) retenu par la partie latérale (52). La partie latérale (52) possède une première partie (52a) s'étendant vers l'intérieur dans la direction radiale à partir d'une partie d'extrémité de la partie cylindre (51) et possède une seconde partie (52b) s'étendant vers l'extérieur dans la direction axiale à partir d'une partie d'extrémité radialement intérieure de la première partie (52a).
PCT/JP2018/022722 2017-06-16 2018-06-14 Roulement à rouleaux WO2018230641A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP18818789.2A EP3640489A4 (fr) 2017-06-16 2018-06-14 Roulement à rouleaux

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2017118253 2017-06-16
JP2017-118253 2017-06-16
JP2018097150A JP2019002560A (ja) 2017-06-16 2018-05-21 ころ軸受
JP2018-097150 2018-05-21

Publications (1)

Publication Number Publication Date
WO2018230641A1 true WO2018230641A1 (fr) 2018-12-20

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3284145A (en) * 1965-06-07 1966-11-08 Mcgill Mfg Company Inc Sealed anti-friction bearing
DE1976866U (de) * 1967-05-24 1968-01-11 Schaeffler Ohg Industriewerk Duennwandige, insbesondere spanlos hergestellte nadellagerbuechse.
JP2008232219A (ja) * 2007-03-19 2008-10-02 Jtekt Corp シェル形ころ軸受及びシェル形ころ軸受の製造方法
US9388772B2 (en) 2011-03-10 2016-07-12 Schaeffler Technologies AG & Co. KG Needle sleeve for pivotably mounting the throttle valve shaft of a control device for recirculating exhaust gas in internal combustion engines

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3284145A (en) * 1965-06-07 1966-11-08 Mcgill Mfg Company Inc Sealed anti-friction bearing
DE1976866U (de) * 1967-05-24 1968-01-11 Schaeffler Ohg Industriewerk Duennwandige, insbesondere spanlos hergestellte nadellagerbuechse.
JP2008232219A (ja) * 2007-03-19 2008-10-02 Jtekt Corp シェル形ころ軸受及びシェル形ころ軸受の製造方法
US9388772B2 (en) 2011-03-10 2016-07-12 Schaeffler Technologies AG & Co. KG Needle sleeve for pivotably mounting the throttle valve shaft of a control device for recirculating exhaust gas in internal combustion engines

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3640489A4 *

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