WO2015122099A1 - Roulement à billes avec joint d'étanchéité - Google Patents

Roulement à billes avec joint d'étanchéité Download PDF

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Publication number
WO2015122099A1
WO2015122099A1 PCT/JP2014/083470 JP2014083470W WO2015122099A1 WO 2015122099 A1 WO2015122099 A1 WO 2015122099A1 JP 2014083470 W JP2014083470 W JP 2014083470W WO 2015122099 A1 WO2015122099 A1 WO 2015122099A1
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WO
WIPO (PCT)
Prior art keywords
seal
bearing
lip
seal member
ball bearing
Prior art date
Application number
PCT/JP2014/083470
Other languages
English (en)
Japanese (ja)
Inventor
渡邊　聡
信一 平賀
Original Assignee
日本精工株式会社
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 日本精工株式会社 filed Critical 日本精工株式会社
Priority to KR1020167018225A priority Critical patent/KR20160097280A/ko
Priority to JP2015562705A priority patent/JP6504060B2/ja
Priority to CN201480075295.7A priority patent/CN106030135A/zh
Publication of WO2015122099A1 publication Critical patent/WO2015122099A1/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
    • 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
    • F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
    • F16C33/7843—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc
    • F16C33/7846—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with a gap between the annular disc and the inner race
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • 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
    • F16C33/32—Balls
    • 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
    • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
    • F16C33/782—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region
    • 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
    • F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
    • F16C33/7843—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc
    • F16C33/7853—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with one or more sealing lips to contact the inner race
    • F16C33/7856—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with one or more sealing lips to contact the inner race with a single sealing lip

Definitions

  • the present invention relates to a ball bearing with a seal.
  • cleaners electric vacuum cleaners
  • various technologies have been proposed to improve suction performance and reduce power consumption (for example, patents).
  • Patent Document 1 it is possible to improve the suction performance by blocking the air passing through the inside of the bearing by providing two seal plates covering the upper and lower sides of the outer ring and the inner ring in the bearing used for the motor of the cleaner.
  • One of the two seal plates is a contact-type seal plate that contacts the inner ring, and the other is a non-contact type seal plate.
  • Patent Document 2 it is described that the efficiency of the cleaner is improved by interposing a sealing plate between the race rings of the inner ring and the outer ring on both ends in the axial direction of the bearing. In this sealing plate, the direction in contact with the raceway is the same direction on both ends of the bearing.
  • the suction efficiency of the cleaner is improved by reducing the mechanical friction loss of the bearing with a seal plate or a sealing plate, thereby reducing the current consumption.
  • a ball bearing 100 with a seal of Conventional Example 1 shown in FIG. 16 includes a shield plate 140 fixed to the outer ring 120 on one end side in the axial direction, and a seal member 150 fixed to the outer ring 120 on the other end side in the axial direction.
  • the seal member 150 includes a metal core 151 and an elastic member 153 that covers the metal core 151, and a seal lip 156 is formed by the elastic member 153.
  • the seal lip 156 is in sliding contact with the outer side of the bearing mainly in the seal groove 136 of the inner ring 130, thereby blocking the air flow in the bearing and ensuring the sealing performance.
  • a frictional force is generated between the seal lip 156 and the seal groove 136, which increases the rotational torque of the bearing.
  • the 17 is provided with a seal member 150A fixed to the outer ring 120 on one side in the axial direction.
  • the seal member 150A includes a metal core 151A and an elastic member 153A that forms a seal lip 156A.
  • the seal lip 156A is slidably contacted mainly inside the bearing in the seal groove 136 of the inner ring 130, thereby blocking the air flow in the bearing and ensuring the sealing performance.
  • the seal member 150B of Conventional Example 3 includes a cored bar 151B and an elastic member 153B that forms a seal lip 156B.
  • the seal lip 156B is a non-contact type seal member that does not contact the inner ring 130.
  • the seal member 150 ⁇ / b> C includes a core metal 151 ⁇ / b> C and an elastic member 153 ⁇ / b> C that forms a seal lip 156 ⁇ / b> C, and the seal lip 156 ⁇ / b> C is a non-contact type seal member that does not contact the inner ring 130. Further, since the seal lip 156C of the seal member 150C is disposed in a non-contact state in the seal groove 136 of the inner ring 130, the labyrinth structure can improve the sealing performance.
  • the sealing members shown in the conventional examples 1 and 2 are in contact with the inner ring, it is possible to ensure sealing performance.
  • a frictional resistance is generated between the seal groove and the seal lip, resulting in a mechanical loss that increases the rotational torque of the bearing.
  • the suction efficiency of the cleaner may be reduced, and power consumption may increase.
  • the non-contact seal member shown in the conventional example 3 can reduce the mechanical loss.
  • the seal lip is deformed by the air pressure passing through the inside of the bearing, the sealing performance of the bearing is not stable, and there is a possibility that the suction efficiency of the cleaner will vary.
  • the seal lip deformed by receiving the air pressure passing through the inside of the bearing is brought into contact with the seal groove, so that frictional resistance is generated and mechanical loss of the bearing is caused. May occur, leading to a reduction in cleaner suction efficiency.
  • seal member for ball bearings with seals, there is also a type in which a seal member is used that optimizes the contact pressure between the seal lip and the inner ring according to the pressure load direction of the air pressure received by the bearing.
  • one of two types of seal members having different contact directions between the seal lip and the inner ring is selected, and the selected seal member is attached to the bearing. Therefore, not only a process of selectively attaching the seal member to the bearing is required, but also a plurality of types of seal members must be prepared in advance, and the manufacturing process of the bearing becomes complicated.
  • the present invention has been made in view of the above circumstances, and provides a sealed ball bearing capable of ensuring both the sealing performance of the bearing and the reduction of mechanical loss between the seal member and the inner ring.
  • the second object is to provide a ball bearing with a seal that does not complicate the manufacturing process of the bearing.
  • the present invention has the following configuration. (1) An outer ring having an outer ring raceway surface formed on an inner peripheral surface, an inner ring having an outer ring raceway surface formed on an outer peripheral surface, and a circumferentially movable manner between the outer ring raceway surface and the inner ring raceway surface.
  • a ball bearing with a seal comprising a plurality of balls, and a seal member fixed to the inner peripheral surface of the outer ring
  • the seal member comprises an annular cored bar and an annular elastic part that covers the cored bar
  • the inner diameter ⁇ Dc of the core metal of the seal member and the inner diameter ⁇ Dr of the elastic portion satisfy 1.0 ⁇ ⁇ Dc / ⁇ Dr ⁇ 1.1
  • the inner peripheral edge of the elastic part is located in a seal groove formed on the outer peripheral surface of the inner ring, The sealed ball bearing according to (1), wherein an axial distance ⁇ d between the inner peripheral edge of the elastic portion and the seal groove is half the axial internal clearance.
  • the elastic portion is located in a seal groove formed on the outer peripheral surface of the inner ring, The sealed ball bearing according to (1), wherein the seal member is fixed to the outer ring in a non-contact state at all times with the seal groove.
  • the sealed ball bearing according to (2) wherein the seal member is fixed to the outer ring so as to be in contact with the seal groove.
  • the elastic portion includes an inner lip on the inner side of the bearing and an outer lip on the outer side of the bearing, which are disposed in a seal groove formed on the outer peripheral surface of the inner ring, and the inner lip and the outer side.
  • each of the lips has an arcuate cross section in an axial cross section.
  • the present invention it is possible to ensure both the sealing performance of the bearing and the reduction of mechanical loss between the seal member and the inner ring. Moreover, it can be set as the structure which does not make the manufacturing process of a bearing complicated.
  • FIG. 5 It is a principal part expanded sectional view of FIG. 5 of the state which loaded the air pressure after preload provision. It is sectional drawing which shows the ball bearing with a seal concerning 4th Embodiment. It is sectional drawing which shows the ball bearing with a seal concerning a 5th embodiment. It is a principal part enlarged view of FIG. It is a partially expanded sectional view of a seal lip. It is a principal part expanded sectional view which shows the state of the sealing member at the time of applying a preload and an air pressure to the ball bearing with a seal shown in FIG. It is a principal part expanded sectional view which shows the state of the seal member when the seal member of the ball bearing with seal shown in FIG. 12A is provided at the opposite bearing end and preload and air pressure are applied. FIG.
  • FIG. 10 is an enlarged view of a main part of FIG. 9 showing another seal groove shape.
  • 6 is a graph showing the relationship between the load pressure and the motor current consumption and the relationship between the load pressure and the leakage air pressure for Examples 1 to 4 and Conventional Examples 1 to 4.
  • 6 is a graph showing the relationship between the load pressure and the motor current consumption and the relationship between the load pressure and the leakage air pressure for Example 5 and Conventional Examples 1 to 3.
  • It is sectional drawing of the ball bearing with a seal
  • the sealed ball bearing 10 of the present embodiment includes an outer ring 20 having an outer ring raceway surface 22 on an inner circumferential surface, an inner ring 30 having an inner ring raceway surface 32 on an inner ring outer circumferential surface 31, an outer ring raceway surface 22 and an inner ring raceway surface 32.
  • a plurality of balls 15 provided in the circumferential direction so as to be freely rollable between them, a shield plate 40 disposed on one end side in the axial direction so as to close the space between the outer ring 20 and the inner ring 30, and on the other end side in the axial direction. And a sealing member 50 arranged in the same manner.
  • the shield plate 40 is formed, for example, by forming a thin metal plate into an annular shape, and an outer peripheral portion 42 of the shield plate 40 is press-fitted into a groove 24 provided on one end side in the axial direction of the inner peripheral surface of the outer ring 20. It is fixed.
  • the inner peripheral portion 44 of the shield plate 40 is bent inward of the bearing along the axial direction, and is disposed close enough to have a labyrinth clearance and a groove 34 provided at one end portion in the axial direction on the outer peripheral surface of the inner ring 30. Has been.
  • the seal member 50 includes a cored bar 51 in which a metal thin plate is formed in an annular shape, and an elastic part 53 formed of an elastic material such as a synthetic resin that covers the cored bar 51.
  • the outer peripheral portion 52 of the seal member 50 (elastic portion 53) is press-fitted and fixed in the groove 26 provided on the other axial end side of the inner peripheral surface of the outer ring 20.
  • a seal lip 56 serving as an inner peripheral side edge of the seal member 50 (elastic portion 53) is disposed in a seal groove 36 provided on the other end side in the axial direction on the outer peripheral surface of the inner ring 30.
  • the seal member 50 is a non-contact type seal member in which the seal lip 56 does not contact the inner ring 30 (the seal groove 36).
  • the seal member 50 of this configuration is fixed to the outer ring 20 in a non-contact state with the seal groove 36, and the non-contact state with the seal groove 36 is maintained even when the bearing rotates. That is, the seal member 50 is fixed to the outer ring 20 in a non-contact state with the seal groove 36 at all times. Thereby, contact resistance does not generate
  • the relationship between the inner diameter dimension of the core metal 51 of the seal member 50 (the inner diameter dimension of the inner peripheral edge 54 of the core metal 51) ⁇ Dc and the inner diameter dimension ⁇ Dr of the seal lip 56 of the seal member 50 is 1.0. ⁇ ⁇ Dc / ⁇ Dr ⁇ 1.1 is satisfied.
  • FIG. 2 shows the ratio ( ⁇ Dc / ⁇ Dr) between the inner diameter dimension ⁇ Dc of the core metal 51 of the seal member 50 and the inner diameter dimension ⁇ Dr of the seal lip 56 of the seal member 50 when the pressure (air pressure) applied to the bearing is 10 kPa. ) And the leakage pressure.
  • the ratio of ⁇ Dc / ⁇ Dr is less than 1.0, the inner diameter of the core metal becomes larger than the inner diameter of the seal, and the core metal is exposed. Then, a seal lip cannot be provided on the inner peripheral side.
  • the ratio of ⁇ Dc / ⁇ Dr exceeds 1.1, the rigidity of the seal lip 56 is lowered, and the seal lip 56 is deformed when the bearing receives air pressure. In that case, the amount of air leakage increases.
  • the relationship between the inner diameter ⁇ Dc of the core metal 51 of the seal member 50 and the outer diameter ⁇ DB of the inner ring outer peripheral surface 31 of the inner ring 30 satisfies ⁇ Dc / ⁇ DB ⁇ 1.0.
  • the ratio between the inner diameter of the core metal and the outer diameter of the inner ring ( ⁇ Dc / ⁇ DB) is less than 1.0, the flow of air passing through the bearing from the opposite side of the seal member 50 is received by the highly rigid core metal 51. . Therefore, deformation of the seal lip 56 can be prevented.
  • the contact between the seal lip 56 and the seal groove 36 can be prevented, so that mechanical loss during rotation of the bearing can be reduced. Further, by preventing the seal lip 56 from being deformed, the clearance between the seal lip 56 and the seal groove 36 can be maintained at an appropriate size, and the sealability of the bearing can be stabilized. In addition, leakage of a lubricant such as grease enclosed in the bearing can be prevented.
  • the ball bearing 10 with a seal of the present embodiment it is possible to achieve both of ensuring the sealability of the bearing and reducing mechanical loss between the seal lip of the seal member and the inner ring. is there. Thereby, when the ball bearing 10 with a seal
  • the seal member 50A has an inner lip 57 that protrudes inward in the bearing along the axial direction in addition to the seal lip 56A at the inner peripheral edge located in the seal groove 36. .
  • the seal member 50A is a non-contact type seal member as in the first embodiment, and no contact resistance is generated between the seal lip 56A and the inner ring 30, so that mechanical loss can be reduced. Also with the seal member 50A having such a shape, the rigidity of the seal lip 56A can be improved, and the sealability of the bearing can be secured.
  • the seal lip 56A1 of the seal member 50A1 is branched into two in the seal groove 36. That is, the seal lip 56A1 extends toward the bearing rotation axis inward of the bearing along the axial direction, and extends toward the bearing rotation axis in parallel with the inner lip 56a1 outside the bearing from the inner lip 56a1. And an outer lip 56a2.
  • the seal member 50A1 is a non-contact type seal member as in the first embodiment, and no contact resistance is generated between the seal lip 56A1 and the inner ring 30, so that mechanical loss can be reduced.
  • the seal member 50A1 receives air pressure from the inside of the bearing, for example, the outer lip 56a2 is deformed by the influence of the air pressure. However, the inner lip 56a1 is not deformed because the received air pressure is lowered, and the pressure resistance performance can be maintained. Also with the seal member 50A1 having such a shape, the rigidity of the seal lip 56A1 (the inner lip 56a1 and the outer lip 56a2) can be improved, and the sealability of the bearing can be ensured.
  • the contact pressure with respect to the seal groove 36 of the seal lip 56B is determined in consideration of the contact pressure when the bearing is built in the motor. Further, in the seal member 50B of this configuration, in the nominal state, the seal lip 56B is positioned in the seal groove 36 formed on the outer peripheral surface of the inner ring 30, and the seal lip 56B can come into contact with the seal groove 36. It is fixed to.
  • FIG. 6 shows a partially enlarged sectional view of the seal lip 56B.
  • the inner lip 56a1 of the inner peripheral edge 56a of the seal lip 56B has an arcuate cross section with a radius R1 in the axial cross section of the bearing.
  • FIG. 7A is an enlarged cross-sectional view of a main part showing a state of the seal member 50A1 before applying preload in the ball bearing 10B with seal shown in FIG. 5, and FIG. 7B shows the seal member 50A1 after applying preload in the ball bearing 10B with seal.
  • FIG. 7C is a principal part enlarged sectional view showing a state in which air pressure is applied after the preload is applied to the ball bearing 10B with the seal.
  • the seal lip 56B and the seal groove 36 are separated in the axial direction and the radial direction.
  • the distance ⁇ d between the seal lip 56B and the inner wall portion 38 inside the bearing of the seal groove 36 is half the axial internal clearance (nominal value) of the sealed ball bearing 10B.
  • the seal member 50B of this embodiment is a contact-type seal member in which the seal lip 56B is in a light contact state with the inner wall portion 38 of the seal groove 36.
  • the sealability of the bearing can be ensured.
  • the contact pressure between the seal lip 56B and the seal groove 36 can be maintained at a very small value in a preload state in which the ball bearing 10B with seal is incorporated in the motor, and mechanical loss during rotation of the bearing can be suppressed.
  • the seal lip 56B and the seal groove 36 reliably contact over the entire circumference even in a light contact state. Stable sealing performance is obtained.
  • the seal lip 56C and the seal groove 36 are separated in the axial direction and the radial direction before the preload is applied to the bearing.
  • the distance between the seal lip 56C and the outer wall 39 inside the bearing of the seal groove 36 is set to a half of the axial internal clearance (nominal value) of the sealed ball bearing 10C.
  • the contact pressure between the seal lip 56C and the seal groove 36 is reduced by the synergistic effect of the preload and the pneumatic load. It can be further suppressed.
  • the ball bearing 10D with a seal includes an outer ring 20, an inner ring 30, a ball 15, a shield plate 40, and a seal member 50D, as in the first embodiment.
  • the seal member 50 ⁇ / b> D includes a cored bar 51 in which a thin metal plate is formed in an annular shape, and an annular shaped elastic part 53 formed of an elastic material such as a synthetic resin that covers the cored bar 51.
  • the seal lip 56D is located in the seal groove 36 formed on the outer peripheral surface of the inner ring 30 in the nominal state. Further, the seal lip 56D does not contact the inner ring 30 (seal groove 36) in the nominal state, but in both the bearing non-rotation state after applying preload and the bearing rotation state when receiving air pressure, It is fixed to the outer ring 20 so as to be in contact with the seal groove 36 by elastic deformation.
  • the relationship between the inner diameter dimension ⁇ Dc of the cored bar 51 of the seal member 50D (the inner diameter dimension of the inner peripheral side edge 54 of the cored bar 51) and the inner diameter dimension ⁇ Dr of the seal lip 56D of the seal member 50D is 1.0.
  • ⁇ ⁇ Dc / ⁇ Dr ⁇ 1.1 is satisfied.
  • the relationship between the inner diameter ⁇ Dc of the metal core 51 of the seal member 50D and the outer diameter ⁇ of the inner ring outer peripheral surface 31 of the inner ring 30 satisfies ⁇ Dc / ⁇ DB ⁇ 1.0.
  • the ratio of the inner diameter of the core metal to the outer diameter of the inner ring ( ⁇ Dc / ⁇ DB) is less than 1.0, as described above, the flow of air passing through the bearing from the opposite side of the seal member 50D Therefore, deformation of the seal lip 56D can be suppressed. If the ratio of ⁇ Dc / ⁇ DB is 1.0 or more, the seal lip 56D is easily deformed by the air pressure received by the seal member 50D, and the amount of air leakage increases.
  • the contact pressure with respect to the seal groove 36 of the seal lip 56D is determined in consideration of the contact pressure when the bearing motor is incorporated.
  • FIG. 10 shows an enlarged view of the main part of FIG.
  • the seal lip 56D of the seal member 50D is disposed in a seal groove 36 formed on the inner ring outer peripheral surface 31 of the inner ring 30, and is separated from the seal groove 36 in the axial direction and the radial direction.
  • FIG. 11 shows a partially enlarged sectional view of the seal lip 56D.
  • the seal lip 56D has an inner lip 56a1 that is an end of the inner peripheral edge 56a on the bearing inner side (direction toward the center of the bearing width), and an end on the outer side of the bearing (direction toward the bearing outer side along the axial direction).
  • the outer lip 56a2 is a part. At least one of the inner lip 56a1 and the outer lip 56a2 has an arcuate cross section in the axial cross section of the bearing. In the illustrated example, the inner lip 56a1 has an arcuate cross section with a radius R1, and the outer lip 56a2 has an arcuate cross section with a radius R2.
  • the axial distance between the inner lip 56a1 of the seal lip 56D and the inner wall portion 38 inside the bearing of the seal groove 36 is defined as ⁇ din.
  • the axial distance between the outer lip 56a2 of the seal lip 56D and the outer wall portion 39 outside the bearing of the seal groove 36 is represented by ⁇ dout.
  • ⁇ din is set to half the length of the axial internal clearance.
  • ⁇ dout is set to half the axial internal clearance.
  • FIG. 12A is an enlarged cross-sectional view of a main part showing a state of the seal member 50D when preload and air pressure are applied to the sealed ball bearing 10D shown in FIG. 10, and FIG. 12B is a seal of the sealed ball bearing 10D shown in FIG. 12A. It is a principal part expanded sectional view which shows the state of the sealing member 50D at the time of providing a member 50D in the bearing end part of an other side, and loading a preload and an air pressure.
  • the seal member 50 ⁇ / b> D enters a light contact state in which the inner lip 56 a 1 of the seal member 50 ⁇ / b> D contacts the inner wall portion 38 of the seal groove 36 with a low contact pressure from a non-contact state with the seal groove 36.
  • the seal member 50D is pressed toward the outside of the bearing while receiving the air pressure and maintaining the contact state. Thereby, the seal member 50D is in a state in which the contact pressure with the seal groove 36 is further reduced.
  • the sealed ball bearing 10D having this configuration has a clearance of a distance ⁇ din between the seal member 50D and the seal groove 36 shown in FIG. 10 before the preload is applied. For this reason, even if the inner ring 30 is displaced due to the preload, the seal member 50D does not bend because it does not contact the seal member 50D until the displacement amount of the inner ring 30 reaches the distance ⁇ din. Therefore, even if a preload is applied to the inner ring 30, not all of the preload is applied to the deformation of the seal member 50D. As a result, after the preload is applied, the seal member 50D is reduced in deformation to such an extent that it is slightly bent after coming into contact with the seal groove 36, and the contact pressure between the seal member 50D and the seal groove 36 is lowered.
  • the seal member 50D even when the seal member 50D is provided on the bearing end surface on the opposite side of the bearing, the dynamic friction loss of the bearing is reduced as described above. That is, when a preload in the Fa direction is applied to the inner ring 30 of the bearing, the seal member 50D has the clearance of the axial distance ⁇ dout shown in FIG. It contacts the seal groove 36. When air pressure is applied in the Fb direction in this light contact state, the seal member 50D is pressed toward the inside of the bearing, so that the contact pressure between the seal member 50D and the seal groove 36 is synergistically reduced.
  • the sealed ball bearing 10D of this configuration even if the seal member 50D is attached to any one of the bearing end surfaces of the bearing, the seal member 50D and the seal groove are caused by preload and air pressure load. The frictional resistance with 36 is reduced, and the dynamic friction loss of the bearing can be reduced.
  • the inner lip 56a1 and the outer lip 56a2 that are in contact with the seal groove 36 have an arc-shaped cross section in the axial cross section. For this reason, since the seal member 50D and the seal groove 36 are in contact with each other with a narrow contact area at the arc-shaped tip, the frictional resistance can be further reduced, and the dynamic friction loss of the bearing can be further reduced. Further, even in the light contact state as described above, the seal lip 56D and the seal groove 36 are in reliable contact over the entire circumference, and a stable sealing performance is obtained. As a result, the flow of air inside and outside the bearing can be blocked, and leakage of lubricant such as grease enclosed in the bearing to the outside of the bearing can be reliably prevented.
  • the seal groove 36 is not limited to the above-described configuration, and may have another groove shape.
  • FIG. 13 shows an enlarged cross-sectional view of the main part of the bearing in which the shape of the seal groove 36 is such that the inner wall portion 38 inside the bearing and the outer wall portion 39 outside the bearing have the same inclination angle.
  • the inclination angle of the inner wall 38 on the inner side of the bearing with respect to the radial direction of the inner ring 30 is ⁇ 1
  • the inclination angle of the outer wall 39 on the outer side of the bearing with respect to the radial direction of the inner ring 30 is ⁇ 2.
  • the inclination angle ⁇ 1 and the inclination angle ⁇ 2 are equal.
  • the symmetry of the seal groove 36 with respect to the seal member 50D is improved, and the seal member 50D can be easily and accurately disposed at a position where the axial distances ⁇ din and ⁇ dout are equal. Further, the axial distance between the seal groove and the seal lip 56D does not change even if the seal member 50D is attached to either end of the bearing in the axial direction. Therefore, the compatibility of the seal member 50D can be further improved. This also makes it possible to obtain the above-described bearing performance more stably.
  • the sealed ball bearings 10, 10 ⁇ / b> A, 10 ⁇ / b> A ⁇ b> 1, 10 ⁇ / b> B, 10 ⁇ / b> C, 10 ⁇ / b> D of each embodiment described above ensuring the sealability of the bearing and reducing mechanical loss between the seal lip of the seal member and the inner ring. And both. Further, the contact pressure between the seal member and the seal groove can be kept low regardless of the arrangement position of the seal member. Furthermore, it is not necessary to selectively attach different seal members to the bearing according to the pressure load direction, the bearing manufacturing process is simplified, and the cost can be reduced.
  • the results shown in FIG. 14 are graphs comparing Examples 1 to 4 and Conventional Examples 1 to 3 with an average value of five measurement results. Since the seal members of the conventional examples 1 and 2 are contact-type seal members, the motor current consumption value is high due to friction loss at the contact portion when the load air pressure (load pressure) is low. In addition, as the load air pressure increases, the flow of air passing through the inside of the bearing is generated, so that the contact pressure of the seal lip with the inner ring gradually decreases, the friction loss decreases, and the motor current consumption value decreases. However, at the same time, air passes through the inside of the bearing and leaks to the side opposite to the air pressure application side, and the sealing performance of the bearing is reduced.
  • the seal member of Conventional Example 3 is a non-contact type, the dynamic friction loss of the bearing is stably low, and the motor current consumption value is stable. However, immediately after the air pressure is applied, the air passes through the bearing and leaks to the side opposite to the air pressure application side, and the amount of air leakage increases as the load air pressure increases.
  • the seal members of Examples 1 and 2 are non-contact type seal members, the dynamic friction loss of the bearing is stably suppressed low, and the motor current consumption value is stable. Furthermore, by improving the rigidity of the seal lip, the force against the flow of air passing through the inside of the bearing is increased, and an increase in the amount of air leakage due to an increase in load air pressure is suppressed.
  • the seal members of Examples 3 and 4 are contact type, the motor consumption current value representing the bearing dynamic friction loss is lower than that of the non-contact type seal member of Conventional Example 3 when the load air pressure is low. Slightly higher.
  • the dynamic friction loss can be reduced by setting the contact pressure of the seal lip to a minute amount as compared with the contact-type seal members of Conventional Examples 1 and 2.
  • the rigidity of the seal lip is improved, the force against the flow of air passing through the inside of the bearing is increased, and an increase in the amount of air leakage due to an increase in load pressure is suppressed. It turns out that it is possible.
  • the sealed ball bearings of Examples 3 and 4 have the effect that the motor current consumption, that is, the motor power consumption is low when the load air pressure is low, as compared with the sealed ball bearings of Conventional Examples 1 and 2.
  • the sealing member in Examples 3 and 4 has confirmed the effect that the sealing performance of the bearing is improved as compared with the non-contact type sealing member shown in Conventional Example 3. Therefore, according to the ball bearing with seal of each example, it can be understood that both reduction of mechanical loss and sealing performance of the bearing can be realized.
  • the results shown in FIG. 15 are graphs comparing Example 5 and Conventional Examples 1 to 3 with an average value of five measurement results.
  • the seal member of Example 5 is a contact-type seal member, but the dynamic friction loss of the bearing is stably kept low, and the motor current consumption value is stable. Furthermore, by improving the rigidity of the seal lip, the force against the flow of air passing through the inside of the bearing is increased, and an increase in the amount of air leakage due to an increase in load air pressure is suppressed.
  • the sealed ball bearing of Example 5 hardly causes air leakage when the load air pressure is low as compared with the sealed ball bearings of Conventional Examples 1 and 2, and the load air pressure increases.
  • the increase in air leakage is gradual. From this, when the ball bearing 10 with a seal is used for the motor of the cleaner, the fluctuation of the leakage pressure with respect to the fluctuation of the load air pressure can be suppressed, so that the variation in the suction performance of the cleaner can be prevented.
  • the motor power consumption is stably low regardless of the load air pressure. Therefore, according to the sealed ball bearing of this configuration, it can be seen that both reduction of mechanical loss during rotation of the bearing and sealing performance of the bearing can be realized.
  • the present invention is not limited to each of the embodiments described above, and can be appropriately changed and improved.
  • the shield plate 40 is formed of a thin metal plate, but the shield plate 40 is formed by coating a metal core with an elastic material such as rubber or synthetic resin. And you may form so that the whole may become an annular
  • the elastic part of the seal member may be formed of rubber or the like.
  • the ball bearing with seal of the present invention is not limited to an angular ball bearing, and may be another rolling bearing such as a cylindrical roller bearing.
  • the present invention is applicable to, for example, a bearing used in a cleaner motor.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Sealing Of Bearings (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)

Abstract

L'invention concerne un roulement à billes avec un joint d'étanchéité qui comprend : une bague extérieure présentant une surface de chemin de roulement de bague extérieure formée sur la surface périphérique interne de la bague extérieure ; une bague intérieure présentant une surface de chemin de roulement de bague intérieure formée sur la surface périphérique externe de la bague intérieure ; des billes agencées entre la surface de chemin de roulement de bague extérieure et la surface de chemin de roulement de bague intérieure ; et un élément d'étanchéité fixé à la surface périphérique interne de la bague extérieure. L'élément d'étanchéité est pourvu d'un noyau métallique annulaire et d'une section élastique annulaire qui recouvre le noyau métallique. Le diamètre intérieur (φDc) du noyau métallique et le diamètre intérieur (φDr) de la section élastique satisfont la relation 1,0 ≤ φDc/φDr ≤ 1,1, et le diamètre intérieur (φDc) du noyau métallique et le diamètre extérieur (φDB) de la bague intérieure (30) satisfont la relation φDc/φDB < 1,0.
PCT/JP2014/083470 2014-02-17 2014-12-17 Roulement à billes avec joint d'étanchéité WO2015122099A1 (fr)

Priority Applications (3)

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KR1020167018225A KR20160097280A (ko) 2014-02-17 2014-12-17 시일이 형성된 볼 베어링
JP2015562705A JP6504060B2 (ja) 2014-02-17 2014-12-17 クリーナ用単列玉軸受
CN201480075295.7A CN106030135A (zh) 2014-02-17 2014-12-17 带密封件的球轴承

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JP2014-027740 2014-02-17
JP2014027740 2014-02-17
JP2014-059995 2014-03-24
JP2014059995 2014-03-24

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JP2020085128A (ja) * 2018-11-26 2020-06-04 Ntn株式会社 転がり軸受

Families Citing this family (1)

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CN106884877A (zh) * 2017-04-10 2017-06-23 无锡市海峰海林精工机械制造有限公司 一种汽车发动机用防漏气轴承密封结构

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WO2004007983A1 (fr) * 2002-07-12 2004-01-22 Nsk Ltd. Roulement a billes a double rangee pour support de poulie
JP2005147307A (ja) * 2003-11-18 2005-06-09 Koyo Seiko Co Ltd 転がり軸受
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JP2007255682A (ja) * 2006-03-27 2007-10-04 Nakanishi Metal Works Co Ltd 軸受用シールおよび軸受
JP2008169998A (ja) * 2006-09-13 2008-07-24 Nsk Ltd 組合せ玉軸受及び複列玉軸受
JP2010002017A (ja) * 2008-06-23 2010-01-07 Jtekt Corp 転がり軸受
JP2013133853A (ja) * 2011-12-26 2013-07-08 Minebea Co Ltd 転がり軸受

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JPH0538006A (ja) 1991-07-24 1993-02-12 Fuji Electric Co Ltd ケーブル引出ブツシング
JP2004144252A (ja) * 2002-10-28 2004-05-20 Nsk Ltd 一方向クラッチ内蔵型プーリ装置
JP4742834B2 (ja) 2005-05-13 2011-08-10 日本精工株式会社 クリーナモータ用軸受
CN201293046Y (zh) * 2008-11-13 2009-08-19 浙江新昌皮尔轴承有限公司 一种轴承密封结构
JP5493667B2 (ja) * 2009-10-05 2014-05-14 日本精工株式会社 シールリング付転がり軸受
CN203214638U (zh) * 2013-03-04 2013-09-25 嵊州市鼎沃五金机械厂 一种轴承密封圈

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JPH0419423A (ja) * 1990-05-14 1992-01-23 Ntn Corp 転がり軸受の密封装置
WO2004007983A1 (fr) * 2002-07-12 2004-01-22 Nsk Ltd. Roulement a billes a double rangee pour support de poulie
JP2005147307A (ja) * 2003-11-18 2005-06-09 Koyo Seiko Co Ltd 転がり軸受
JP2006250201A (ja) * 2005-03-09 2006-09-21 Nsk Ltd 転がり軸受
JP2007255682A (ja) * 2006-03-27 2007-10-04 Nakanishi Metal Works Co Ltd 軸受用シールおよび軸受
JP2008169998A (ja) * 2006-09-13 2008-07-24 Nsk Ltd 組合せ玉軸受及び複列玉軸受
JP2010002017A (ja) * 2008-06-23 2010-01-07 Jtekt Corp 転がり軸受
JP2013133853A (ja) * 2011-12-26 2013-07-08 Minebea Co Ltd 転がり軸受

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020085128A (ja) * 2018-11-26 2020-06-04 Ntn株式会社 転がり軸受

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JP6504060B2 (ja) 2019-04-24
JPWO2015122099A1 (ja) 2017-03-30
KR20160097280A (ko) 2016-08-17
CN106030135A (zh) 2016-10-12

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