WO2022225086A1 - 하중 가변형 구름 베어링 및 하중 가변형 구름 베어링용 전동체 - Google Patents

하중 가변형 구름 베어링 및 하중 가변형 구름 베어링용 전동체 Download PDF

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Publication number
WO2022225086A1
WO2022225086A1 PCT/KR2021/005161 KR2021005161W WO2022225086A1 WO 2022225086 A1 WO2022225086 A1 WO 2022225086A1 KR 2021005161 W KR2021005161 W KR 2021005161W WO 2022225086 A1 WO2022225086 A1 WO 2022225086A1
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WO
WIPO (PCT)
Prior art keywords
contact portion
variable
ring raceway
rolling element
outer ring
Prior art date
Application number
PCT/KR2021/005161
Other languages
English (en)
French (fr)
Korean (ko)
Inventor
이영근
신현의
Original Assignee
이영근
신현의
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 이영근, 신현의 filed Critical 이영근
Priority to PCT/KR2021/005161 priority Critical patent/WO2022225086A1/ko
Priority to DE112021006741.9T priority patent/DE112021006741T5/de
Priority to JP2023564043A priority patent/JP2024514680A/ja
Priority to CN202180093393.3A priority patent/CN117083466A/zh
Publication of WO2022225086A1 publication Critical patent/WO2022225086A1/ko

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Classifications

    • 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
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—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
    • 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
    • F16C33/34—Rollers; Needles
    • F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • 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
    • F16C33/46—Cages for rollers or needles
    • F16C33/49—Cages for rollers or needles comb-shaped
    • 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
    • F16C33/583—Details of specific parts of races
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the 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
    • F16C19/24—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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts

Definitions

  • the present invention relates to a variable load type rolling bearing and a rolling element for a variable load type rolling bearing, and more particularly, to a rolling element for a variable load type rolling bearing and a variable load type rolling bearing in which the rated capacity of the bearing is varied by an external force applied to the bearing.
  • a ball bearing refers to a bearing that uses a ball as a rolling element between an inner ring and an outer ring to drive the bearing, and a retainer (aka, cage) that maintains the circumferential distance between the rolling elements is installed in a general ball bearing.
  • the conventional ball bearing 1 has a ring-shaped outer ring 10 in which an outer ring raceway 11 is formed on the inner diameter side so as to be driven in contact with a ball 30 which is a rolling element, and the ball 30 is in contact.
  • a ring-shaped inner ring 20 in which an inner raceway 21 is formed on the outer diameter side to be driven by It consists of a plurality of rolling balls 30 and a retainer 40 installed between the outer ring 10 and the inner ring 20 so as to maintain a circumferential distance between the balls 30 .
  • the rated capacity (static load rating, dynamic load rating), which is the support capacity of rolling bearings such as ball bearings against external loads, depends on the number of rolling elements and the size of rolling elements (ball diameter, roller diameter in the case of roller bearings). ) will vary depending on
  • the contact area of the rolling element is smaller than that of a roller bearing such as a tapered roller bearing disclosed in Korean Patent Application Laid-Open No. 10-2009-0041103.
  • the contact resistance is small and the rotational torque is low, the bearing capacity for the load acting on the bearing is smaller than that of the roller bearing.
  • the transmission has a characteristic that the load acting on the bearing is large at the low stage (for example, 1st to 3rd gear) and the load acting on the bearing at the high stage (5th gear or more) is very small. It is less than 10%, and it is mainly operated over 90% in high stages.
  • the bearing installed in the transmission has an operating rate of less than 10%, but since it must be designed for the low stage with a large load, bearings with unnecessarily large rated capacity are used at the high stage where more than 90% of the operation is performed. In addition, there was a big problem in the weight and rotational torque of the bearing to be used at a high stage.
  • the present invention has been proposed to solve the problems of the prior art as described above, and it is an object of the present invention to provide a variable load type rolling bearing and a rolling element for variable load type rolling bearing in which the rated capacity of the bearing is varied according to an external force under a variable load environment. do.
  • the present invention provides a ring-shaped outer ring in which an outer raceway is concavely formed on the inner surface, a ring-shaped inner ring in which an inner raceway is concavely formed on the outer surface, and a circumferential direction between the outer raceway and the inner raceway.
  • the rolling element includes a cylindrical rolling element variable contact portion and a rolling element spherical surface portion provided on both sides of the rolling element variable contact portion and formed as a convex spherical surface;
  • the outer ring raceway includes an outer ring raceway surface contact portion formed in a concave arc shape in cross section, and a cylindrical outer ring raceway variable contact portion positioned adjacent to the outer ring raceway surface contact portion in the axial direction;
  • the inner ring raceway includes an inner ring raceway surface contact portion formed in a concave arc shape in cross section, and a cylindrical inner ring raceway variable contact portion adjacent to the inner ring raceway surface contact portion in the axial direction;
  • the rolling body spherical surface portion is located between the outer ring raceway surface contact portion and the inner ring raceway surface contact portion, and the rolling element variable contact portion is located between the outer ring raceway variable contact portion and the inner ring raceway variable contact portion.
  • the outer ring raceway surface contact portion is provided with two spaced apart in the axial direction, and the inner ring raceway surface contact portion is provided with two inner ring raceway surface contact portions spaced apart in the axial direction;
  • the outer ring raceway variable contact portion is located between the outer ring raceway surface contact portion;
  • the inner race variable contact portion is located between the inner race track surface contact portions, and is spaced apart from the outer race variable contact portion in a radial direction;
  • the outer ring raceway surface contact portion and the inner ring raceway surface contact portion face each other in a diagonal direction.
  • the rolling element spherical surface portion when the bearing is assembled, the rolling element spherical surface portion is in contact with the outer ring raceway surface contact portion and the inner ring raceway surface contact portion on both sides before the rolling element variable contact portion comes into contact with the outer ring raceway variable contact portion and the inner ring raceway variable contact portion on both sides. characterized.
  • the rolling element spherical surface portion is in contact with the outer ring raceway surface contact portion and the inner ring raceway surface contact portion on both sides, and the rolling element variable contact portion is spaced apart from the outer ring raceway variable contact portion and the inner ring raceway variable contact portion on both sides. do.
  • the outer ring track variable contact portion and the inner ring track variable contact portion are formed in the form of a crowning protruding center in the axial direction.
  • the rolling element variable contact portion is characterized in that the longitudinal center is formed in the form of a protruding crowning.
  • a concave outer ring undercut portion extending in the circumferential direction is formed between the outer ring raceway surface contact portion and the outer ring raceway variable contact portion, and a concave inner ring undercut extending along the circumferential direction between the inner ring raceway surface contact portion and the inner ring raceway variable contact portion. It is characterized in that the addition is formed.
  • a concave outer ring undercut portion extending in the circumferential direction is formed between the outer ring raceway surface contact portion and the outer ring raceway variable contact portion, and a concave inner ring undercut extending along the circumferential direction between the inner ring raceway surface contact portion and the inner ring raceway variable contact portion. It is characterized in that the addition is formed.
  • FIG. 1 is a partially cut-away perspective view showing a ball bearing according to the prior art
  • FIG. 2 is a half cross-sectional view of a load variable type rolling bearing according to the present invention.
  • FIG. 5 is a cross-sectional view showing a rolling element provided in the load variable type rolling bearing of the present invention.
  • variable load type rolling bearing and a rolling element for a load variable type rolling bearing according to the present invention will be described in detail with reference to the accompanying drawings.
  • FIG. 2 is a half cross-sectional view of a variable load type rolling bearing according to the present invention
  • FIG. 3 is an enlarged view of part “A” of FIG. 2
  • FIG. 4 is an enlarged view of part “B” of FIG. 2
  • FIG. 5 is this view It is a cross-sectional view showing a rolling element provided in the invention variable load type rolling bearing.
  • a vertical direction in FIG. 2 is a radial direction.
  • variable load rolling bearing 100 has a ring-shaped outer ring 110 in which the outer raceway 111 is concavely formed on the inner surface, and the inner raceway 121 is concave on the outer surface.
  • a ring-shaped inner ring 120 is formed, and a plurality of rolling elements 130 are arranged along the circumferential direction between the outer ring track 111 and the inner ring track 121 .
  • Reference numeral 140 denotes a cage for maintaining the circumferential spacing of the rolling elements 130 .
  • the variable load rolling bearing 100 according to the present invention may further include a cage 140 .
  • the cage 140 has a ring shape, and is spaced apart along the circumferential direction to form a plurality of pockets in which the rolling elements 130 are accommodated.
  • a seal (not shown) for sealing may be provided in the openings formed on both sides in the axial direction between the inner ring 120 and the outer ring 110 .
  • the rolling element 130 is provided on both sides of the cylindrical rolling element variable contact portion 133 and the longitudinal direction (transverse direction in FIG. 5) of the rolling element variable contact portion 133, and the rolling element spherical surface portion 131 formed as a convex spherical surface.
  • the rolling element 130 is formed in a cylindrical shape with a part removed from the sphere.
  • the diameter (H) of the rolling element variable contact portion 133 may be formed in the range of 80% to 95% of the value (2 ⁇ R) multiplied by the radius of curvature of the spherical rolling element spherical surface portion 131 .
  • a larger number (for example, one or two) of the rolling element 130 is assembled to the bearing when necessary compared to the spherical rolling element. can be
  • the rolling element variable contact portion 133 may be formed in a cylindrical shape, and may be formed in the form of a crowning protruding outward. Since the specific form of the crowning is a conventionally known technique, a description thereof will be omitted.
  • the rolling element spherical surface portion 131 is provided with a spherical surface in a form in which the diameter decreases from the portion connected to the rolling element variable contact portion 133 .
  • the rolling element 130 is manufactured in the form of a sphere having a sphericity of 3 ⁇ m or less, and the cylindrical rolling element variable contact portion 133 may be formed by grinding the middle part while chucking and rotating both sides of the sphere, The cylindrical rolling element may form the variable contact portion 133 by passing the sphere between the rubber grindstone (for rotational driving) and the grinding grindstone (for grinding processing).
  • the cylindrical rolling element variable contact portion 133 is formed in a cylindrical shape from which a part of the sphere is removed, so that the centers of curvature of the rolling element spherical surface portions 131 on both sides coincide with each other.
  • the outer ring track 111 includes an outer ring track surface contact portion 111-1 and an outer ring track variable contact portion 111-3.
  • the outer ring raceway surface contact portion 111-1 extends along the circumferential direction and has a cross-sectional shape in the form of a concave arc as shown in FIG. 2 .
  • the outer ring track variable contact portion 111-3 is adjacent to the outer ring track surface contact portion 111-1 in the axial direction to form a concave bottom of the outer ring track 111 .
  • the outer ring raceway surface contact portion 111-1 is provided with two spaced apart in the axial direction, and the outer ring raceway variable contact portion 111-3 is located between the outer ring raceway surface contact portion 111-1 and the outer ring raceway 111. form the bottom of
  • the outer ring track variable contact portion 111-3 is formed in a cylindrical shape.
  • the outer ring track variable contact portion 111-3 may be formed in a convex crowning shape.
  • an external force acts on the bearing, and when the outer ring track variable contact part 111-3 and the rolling element come into contact with the variable contact part 133, the contact stress from the center Concentration can be prevented.
  • the radius of curvature of the arc of the cross section shown in FIG. 2 of the outer ring raceway surface contact portion 111-1 is greater than the radius of curvature R of the rolling element spherical surface portion 131 .
  • the radius of curvature of the outer ring raceway surface contact portion 111-1 is formed in the range of 102 to 200% of the radius of curvature of the rolling element spherical surface portion 131 .
  • the rolling element spherical surface portion 131 contacts the outer ring raceway surface contact portion 111-1 (reference numeral P1 in FIG. 2 ). With the outer ring raceway variable contact portion 111-3 interposed therebetween, the outer ring raceway surface contact portion 111-1 and the rolling element spherical surface portion 131 are in contact on both sides in the axial direction.
  • the outer ring raceway variable contact part 111-3 which is in contact with the outer ring raceway surface contact part 111-1 and the rolling body spherical surface part 131 on both sides in the axial direction, and is located between the outer ring raceway surface contact part 111-1, is a rolling element variable contact part. (133) and a minute gap (Do; for example, 100 ⁇ m) are spaced apart.
  • the distance between the outer ring raceway surface contact portion 111-1 and the rolling element spherical surface portion 131 is large on both sides. do.
  • a concave outer ring undercut portion 111-5 extending in the circumferential direction is formed between the outer ring raceway surface contact portion 111-1 and the outer ring raceway variable contact portion 111-3.
  • reference numeral Go denotes an interval between the outer ring raceway surface contact portion 111-1 and the rolling element spherical surface portion 131 .
  • the outer ring raceway surface contact portion 111-1 and the rolling element spherical surface portion 131 are in contact with the middle point P1 of the arc of the outer ring raceway surface contact portion 111-1 in the axial direction, and are spaced apart as the distance from the intermediate point increases. The distance Go increases.
  • the inner ring raceway 121 includes an inner ring raceway surface contact portion 121-1 and an inner ring raceway variable contact portion 121-3.
  • the inner ring raceway surface contact portion 121-1 extends along the circumferential direction and has a cross-sectional shape in the form of a concave arc as shown in FIG. 2 .
  • the inner ring raceway variable contact portion 121-3 is adjacent to the inner ring raceway surface contact portion 121-1 in the axial direction to form a concave bottom of the inner ring raceway 121 .
  • the inner ring raceway surface contact portion 121-1 is provided with two spaced apart in the axial direction, and the inner ring raceway variable contact portion 121-3 is located between the inner ring raceway surface contact portion 121-1, and the inner ring raceway 121 form the bottom of
  • the inner race variable contact part 121-3 faces the outer race variable contact part 111-3, and is spaced apart from the outer race variable contact part 111-3 in a radial direction inward.
  • the inner ring raceway surface contact portion 121-1 faces the outer ring raceway surface contact portion 111-1 in a diagonal direction.
  • the inner ring track variable contact portion 121-3 is formed in a cylindrical shape.
  • the cross-sectional shape of the inner ring track variable contact portion 121-3 may be formed in the form of a convex crowning center in the axial direction. Since the inner race variable contact part 121-3 is formed in a crowning shape, when the inner race variable contact part 121-3 and the rolling element come into contact with the variable contact part 133, the contact stress concentration can be prevented by contacting from the center. .
  • the radius of curvature of the arc cross section of the inner ring raceway surface contact portion 121-1 shown in FIG. 2 is greater than the radius of curvature of the rolling element spherical surface portion 131 .
  • the radius of curvature of the inner ring raceway surface contact portion 121-1 is formed in the range of 102 to 200% of the radius of curvature of the rolling element spherical surface portion 131 .
  • the inner ring raceway variable contact part 121-3 which is in contact with the inner ring raceway surface contact part 121-1 and the rolling body spherical surface part 131 on both sides in the axial direction, and is located between the inner ring raceway surface contact part 121-1, is the rolling body variable
  • the contact portion 133 is spaced apart from each other by a minute distance (Di; for example, 100 ⁇ m).
  • the gap between the inner ring raceway surface contact portion 121-1 and the rolling element spherical surface portion 131 is formed to be large on both sides.
  • a concave inner ring undercut portion 121-5 extending in the circumferential direction is formed between the inner ring raceway surface contact portion 121-1 and the inner ring raceway variable contact portion 121-3.
  • reference numeral Gi denotes an interval between the inner ring raceway surface contact portion 121-1 and the rolling element spherical surface portion 131 .
  • Two of the outer ring raceway surface contact parts 111-1 are provided to be spaced apart in the axial direction, and two inner ring raceway surface contact parts 121-1 are provided to be spaced apart from each other in the axial direction.
  • the outer ring raceway variable contact portion 111-3 is located between the outer ring raceway surface contact portions 111-1, and the inner ring raceway variable contact portion 121-3 is located between the inner ring raceway surface contact portion 121-1, and the The outer ring raceway variable contact portion 111-3 is spaced apart from each other in the radial direction, and the outer ring raceway surface contact portion 111-1 and the inner ring raceway surface contact portion 121-1 face each other in a diagonal direction.
  • the inner ring 120 of the bearing When a large load is applied to the bearing, the inner ring 120 of the bearing is in contact with the inner ring raceway surface contact portion 121-1 and the rolling element spherical surface portion 131, and in addition, the inner ring raceway variable contact portion 121-3 and the rolling element variable contact portion ( 133) is in contact, and the outer ring 110 is in contact with the outer ring raceway surface contact portion 111-1 and the rolling body spherical surface portion 131, in addition to the outer ring raceway variable contact portion 111-3 and rolling element variable contact portion 133 It works while being in contact with it, so the rated load increases.
  • the inner ring 120 does not have the inner ring raceway variable contact portion 121-3 in contact with the rolling element variable contact portion 133, and the inner ring raceway surface contact portion 121-1).
  • the outer ring raceway variable contact part 111-3 does not contact the rolling element variable contact part 133, and the outer ring raceway surface contact part 111-1 and
  • the rolling element spherical surface part 131 rotates in a contact state, and rotates in a four-point contact state (P1, P2).
  • the inner ring 120 has the inner ring raceway variable contact portion 121-3 in contact with the rolling element variable contact portion 133, and the inner ring raceway surface contact portion 121-1 also has the rolling element spherical surface portion 131.
  • the outer ring track variable contact portion 111-3 is in contact with the rolling element variable contact portion 133, and the outer ring track surface contact portion 111-1 is also in contact with the rolling element spherical surface portion 131 rotate in Therefore, when a large load such as a low-speed operation of the transmission is applied, the load-bearing capacity is increased, and in a state of a small load such as a high-speed operation, the four-point contact rotation causes the rolling elements inside and outside the radial direction to contact and rotate in contact with the variable contact portion 133. The rotational torque is reduced compared to the case where unnecessary torque increase or a decrease in efficiency (fuel efficiency, etc.) due to the use of a large bearing is prevented. Since the rated capacity is increased for high loads in a variable load environment, large loads can be supported without increasing the bearing size (rolling body size, etc.).
  • the gap Di between the inner ring raceway surface contact portion 121-1 and the rolling element spherical surface portion 131 or the distance Do between the outer ring raceway variable contact portion 111-3 and the rolling element variable contact portion 133 is a bearing It is manufactured by setting it according to the magnitude of the variable load acting on it.
  • the present invention is not limited thereto, and the present invention also includes two or more double rows.
  • the initial torque is not large and the load capacity can be increased.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
PCT/KR2021/005161 2021-04-23 2021-04-23 하중 가변형 구름 베어링 및 하중 가변형 구름 베어링용 전동체 WO2022225086A1 (ko)

Priority Applications (4)

Application Number Priority Date Filing Date Title
PCT/KR2021/005161 WO2022225086A1 (ko) 2021-04-23 2021-04-23 하중 가변형 구름 베어링 및 하중 가변형 구름 베어링용 전동체
DE112021006741.9T DE112021006741T5 (de) 2021-04-23 2021-04-23 Lastvariables Wälzlager und Wälzkörper für das lastvariable Wälzlager
JP2023564043A JP2024514680A (ja) 2021-04-23 2021-04-23 荷重可変型転がり軸受及び荷重可変型転がり軸受用の転動体
CN202180093393.3A CN117083466A (zh) 2021-04-23 2021-04-23 荷重可变形滚动轴承及荷重可变形滚动轴承用传动体

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/KR2021/005161 WO2022225086A1 (ko) 2021-04-23 2021-04-23 하중 가변형 구름 베어링 및 하중 가변형 구름 베어링용 전동체

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WO2022225086A1 true WO2022225086A1 (ko) 2022-10-27

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PCT/KR2021/005161 WO2022225086A1 (ko) 2021-04-23 2021-04-23 하중 가변형 구름 베어링 및 하중 가변형 구름 베어링용 전동체

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JP (1) JP2024514680A (zh)
CN (1) CN117083466A (zh)
DE (1) DE112021006741T5 (zh)
WO (1) WO2022225086A1 (zh)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11182540A (ja) * 1997-12-22 1999-07-06 Mitsubishi Heavy Ind Ltd 針状ころ軸受
JP2004251323A (ja) * 2003-02-18 2004-09-09 Ntn Corp 円筒ころ軸受
KR100724826B1 (ko) * 2001-09-26 2007-06-04 에누티에누 가부시기가이샤 스러스트 롤러 베어링
JP2009074600A (ja) * 2007-09-20 2009-04-09 Jtekt Corp ころ軸受
CN203962681U (zh) * 2014-07-14 2014-11-26 洛阳百思特精密机械制造有限公司 一种球基面圆柱滚子推力轴承
KR20210098633A (ko) * 2020-02-03 2021-08-11 이영근 하중 가변형 구름 베어링 및 하중 가변형 구름 베어링용 전동체

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20090041103A (ko) 2007-10-23 2009-04-28 현대자동차주식회사 자동변속기용 더블 테이퍼 롤러 베어링

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11182540A (ja) * 1997-12-22 1999-07-06 Mitsubishi Heavy Ind Ltd 針状ころ軸受
KR100724826B1 (ko) * 2001-09-26 2007-06-04 에누티에누 가부시기가이샤 스러스트 롤러 베어링
JP2004251323A (ja) * 2003-02-18 2004-09-09 Ntn Corp 円筒ころ軸受
JP2009074600A (ja) * 2007-09-20 2009-04-09 Jtekt Corp ころ軸受
CN203962681U (zh) * 2014-07-14 2014-11-26 洛阳百思特精密机械制造有限公司 一种球基面圆柱滚子推力轴承
KR20210098633A (ko) * 2020-02-03 2021-08-11 이영근 하중 가변형 구름 베어링 및 하중 가변형 구름 베어링용 전동체

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JP2024514680A (ja) 2024-04-02
DE112021006741T5 (de) 2023-10-12
CN117083466A (zh) 2023-11-17

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