CN113623322A - Bearing inner ring, rotating equipment and speed reducer - Google Patents

Bearing inner ring, rotating equipment and speed reducer Download PDF

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Publication number
CN113623322A
CN113623322A CN202110476124.7A CN202110476124A CN113623322A CN 113623322 A CN113623322 A CN 113623322A CN 202110476124 A CN202110476124 A CN 202110476124A CN 113623322 A CN113623322 A CN 113623322A
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CN
China
Prior art keywords
seal
bearing
inner ring
inner member
holding surface
Prior art date
Legal status (The legal status 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 status listed.)
Pending
Application number
CN202110476124.7A
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Chinese (zh)
Inventor
桃井直生
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Nabtesco Corp
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Nabtesco Corp
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Publication date
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Publication of CN113623322A publication Critical patent/CN113623322A/en
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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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/082—Planet carriers
    • 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
    • F16C33/4605—Details of interaction of cage and race, e.g. retention or centring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with 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
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/361—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with cylindrical rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/46—Cages for rollers 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
    • F16C33/7803—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling 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
    • F16C33/72—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
    • F16C33/7803—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings
    • F16C33/7809—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings for needle 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
    • F16C33/72—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
    • F16C33/7823—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region of sealing lips
    • 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
    • F16C33/7869—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward
    • F16C33/7873—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a single sealing ring of generally L-shaped cross-section
    • F16C33/7876—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a single sealing ring of generally L-shaped cross-section with sealing lips
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • 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
    • 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
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • F16H2001/325—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear comprising a carrier with pins guiding at least one orbital gear with circular holes
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H2057/085—Bearings for orbital gears

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Retarders (AREA)
  • Sealing Of Bearings (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
  • Gasket Seals (AREA)

Abstract

The invention provides a bearing inner ring, a rotating device and a speed reducer. The bearing inner race of the present invention is used for a bearing interposed between an inner member and an outer cylindrical member which are relatively rotatable with respect to each other, and a seal member. The bearing inner race is disposed at a position adjacent to the seal holding surface on the inner member holding the seal member. The bearing inner ring includes a seal guide surface that is provided on an outer periphery of an end portion of the bearing inner ring adjacent to the seal holding surface and is formed in a tapered shape. The outer diameter of the seal guide surface increases toward a position where the seal holding surface is disposed.

Description

Bearing inner ring, rotating equipment and speed reducer
Technical Field
The invention relates to a bearing inner ring for a rotary apparatus, and a speed reducer.
Background
A reduction gear is used for industrial robots, machine tools, and the like to reduce the rotation of a rotation drive source such as a motor. In some rotating devices such as a reduction gear, an outer cylinder member may be coupled to an outer periphery of an inner member via a bearing so as to be relatively rotatable (see, for example, patent document 1).
As such a rotary machine, a rotary machine is known in which a seal member is interposed between an inner member and an outer cylindrical member together with a bearing. The seal member is often interposed at a position axially outward of the bearing between the inner member and the outer cylindrical member. The seal member seals a space surrounded by the inner member and the outer cylindrical member at a position axially outward of the bearing.
When assembling such a rotary apparatus, there are cases where: the outer cylinder member is assembled to the inner member in the axial direction in a state where the seal member is attached to the seal holding surface of the inner member in advance and the inner ring used for the bearing is attached to a position adjacent to the seal holding surface of the inner member. In this case, when the seal member is mounted on the seal holding surface of the inner member, the inner peripheral surface needs to be moved in the axial direction toward the seal holding surface so as to be outwardly expanded. Therefore, a seal guide surface for smoothly guiding the seal member in the direction of the seal holding surface is provided at a position of the inner member adjacent to the seal holding surface. The outer diameter of the seal guide surface is tapered toward the seal holding surface.
Documents of the prior art
Patent document
Patent document 1: japanese laid-open patent publication No. 2009-36327
Disclosure of Invention
Problems to be solved by the invention
The above-described rotary apparatus is continuously formed with a tapered seal guide surface at a position adjacent to the seal holding surface on the inner member. Therefore, an axially outer region of the bearing (inner ring) on the inner member is occupied by the seal holding surface and the tapered seal guide surface, and the axial length of the inner member is increased. This is one of the main causes of hindering downsizing of the rotary machine.
The invention provides a bearing inner ring capable of shortening the axial length of an inner member of a rotating device, the rotating device and a speed reducer.
Means for solving the problems
The bearing inner race according to one aspect of the present invention is used for a bearing, and the bearing and a seal member are interposed between an inner member and an outer cylinder member that are capable of relative rotation. The bearing inner race is disposed at a position adjacent to the seal holding surface on the inner member holding the seal member. The bearing inner ring includes a seal guide surface that is provided on an outer periphery of an end portion of the bearing inner ring adjacent to the seal holding surface and is formed in a tapered shape. The outer diameter of the seal guide surface increases toward a position where the seal holding surface is disposed.
In the bearing inner race according to one aspect of the present invention, the seal guide surface may be formed on a restricting wall that restricts displacement of the rolling elements of the bearing at an end portion adjacent to the seal holding surface in an axial direction along the relative rotation axes of the inner member and the outer cylindrical member.
A rotating device according to an aspect of the present invention includes: an inner member having a seal retaining surface; an outer cylinder member disposed on an outer peripheral side of the inner member so as to be rotatable relative to the inner member; a sealing member interposed between the inner member and the outer cylindrical member; and a bearing interposed between the inner member and the outer cylindrical member so as to be juxtaposed to the seal member in an axial direction which is an extending direction of the relative rotation axes of the inner member and the outer cylindrical member. The bearing includes an inner ring disposed at a position adjacent to the inner member on the side of the sealed space in the axial direction of the seal holding surface. The inner ring includes a seal guide surface that is provided on an outer periphery of an end portion of the inner ring adjacent to the seal holding surface in the axial direction and is formed in a tapered shape. The outer diameter of the seal guide surface increases toward a position where the seal holding surface is disposed.
In the rotating apparatus according to one aspect of the present invention, the bearing may further include a rolling element. The inner ring is provided with a restricting wall that restricts displacement of the rolling elements at an end portion adjacent to the seal holding surface in the axial direction. The seal guide surface is formed on the restricting wall.
In the rotary machine according to one aspect of the present invention, a protection mechanism for preventing damage to the inner peripheral surface of the seal member may be provided between the seal holding surface and the seal guide surface.
A speed reducer according to an aspect of the present invention includes: an inner member having a seal retaining surface; an outer cylinder member disposed on an outer peripheral side of the inner member so as to be rotatable relative to the inner member; an input member that inputs a rotational driving force; a speed reduction mechanism that reduces the speed of the rotational driving force input to the input member and transmits the reduced rotational driving force to the inner member or the outer tube member; a sealing member interposed between the inner member and the outer cylindrical member; and a bearing interposed between the inner member and the outer cylindrical member so as to be juxtaposed to the seal member in an axial direction which is an extending direction of the relative rotation axes of the inner member and the outer cylindrical member. The bearing includes an inner ring disposed at a position adjacent to the inner member on the side of the sealed space in the axial direction of the seal holding surface. The inner ring includes a seal guide surface that is provided on an outer periphery of an end portion of the inner ring adjacent to the seal holding surface in the axial direction and is formed in a tapered shape. The outer diameter of the seal guide surface increases toward a position where the seal holding surface is disposed.
A rotating device according to an aspect of the present invention includes: an inner member; an outer cylinder member disposed on an outer peripheral side of the inner member so as to be rotatable relative to the inner member; a sealing mechanism for keeping a sealed space between the inner member and the outer tube member hermetically sealed; and a bearing interposed between the inner member and the outer cylindrical member. The bearing is provided with an inner ring. The sealing mechanism includes a 1 st sealing member for sealing between the outer peripheral surface of the inner ring and the outer cylindrical member.
A rotating device according to an aspect of the present invention includes: an inner member; an outer cylinder member disposed on an outer peripheral side of the inner member so as to be rotatable relative to the inner member; a sealing mechanism for keeping a sealed space between the inner member and the outer tube member hermetically sealed; and a bearing interposed between the inner member and the outer cylindrical member. The bearing is provided with an inner ring. The sealing mechanism is provided with: a 1 st sealing member that seals a space between an outer peripheral surface of the inner ring and the outer tube member; and a 2 nd sealing member that seals between the inner ring and the inner member.
In the rotating apparatus according to an aspect of the present invention, the inner ring may include: a seal holding surface that holds the 1 st seal member; and a seal guide surface formed in a tapered shape having an outer diameter that increases toward the seal holding surface in an axial direction, which is an extending direction of the relative rotation axes of the inner member and the outer cylinder member.
In the rotating apparatus according to one aspect of the present invention, the bearing may further include a rolling element. The inner ring is provided with a restricting wall that restricts displacement of the rolling elements at a position adjacent to the seal holding surface in the axial direction. The seal guide surface is formed on the restricting wall.
A speed reducer according to an aspect of the present invention includes: an inner member having a seal retaining surface; an outer cylinder member disposed on an outer peripheral side of the inner member so as to be rotatable relative to the inner member; an input member that inputs a rotational driving force; a speed reduction mechanism that reduces the speed of the rotational driving force input to the input member and transmits the reduced rotational driving force to the inner member or the outer tube member; a sealing mechanism for keeping a sealed space between the inner member and the outer tube member hermetically sealed; and a bearing interposed between the inner member and the outer cylindrical member. The bearing is provided with an inner ring. The sealing mechanism is provided with: a 1 st sealing member that seals a space between an outer peripheral surface of the inner ring and the outer tube member; and a 2 nd sealing member that seals between the inner ring and the inner member.
The bearing inner race according to one aspect of the present invention is used for a bearing, and the bearing and a seal member are interposed between an inner member and an outer cylinder member that are capable of relative rotation. The bearing inner race is disposed at a position adjacent to the seal holding surface on the inner member holding the seal member. The bearing inner race includes a seal guide surface for guiding the seal member to the seal holding surface.
ADVANTAGEOUS EFFECTS OF INVENTION
In the bearing inner race according to the above aspect, the seal guide surface is provided on the outer periphery of the end portion on the side adjacent to the seal holding surface in the axial direction, and therefore, the axial length of the inner member can be shortened as compared to a case where the seal guide surface is provided on the inner member at a position adjacent to the seal holding surface. Therefore, the rotary machine using the bearing inner race according to the above-described aspect can be downsized.
In addition, in each of the rotary devices according to the above-described embodiments, the seal guide surface is not provided at a position adjacent to the seal holding surface on the inner member, and therefore, the axial length of the inner member can be shortened. Therefore, the rotary machine can be miniaturized.
Drawings
Fig. 1 is a longitudinal sectional view showing a reduction gear unit according to embodiment 1.
Fig. 2 is an enlarged sectional view showing a section II of fig. 1.
Fig. 3 is a view corresponding to fig. 2, and is an enlarged cross-sectional view showing a structure of modification 1.
Fig. 4 is a view corresponding to fig. 2, and is an enlarged cross-sectional view showing a structure of a 2 nd modification.
Fig. 5 is a view corresponding to fig. 2, and is an enlarged sectional view showing a reduction gear according to embodiment 2.
Description of the reference numerals
10. 110, speed reducer (rotating device); 11. an outer cylinder member; 12A, 112A, bearings; 13A, 113A, 1 st gear rack module; 14. a crankshaft (input member); 15A, a 1 st oscillating gear (speed reduction mechanism portion); 15B, the 2 nd oscillating gear (speed reducing mechanism portion); 17. a pin groove (speed reduction mechanism portion); 20. an inner gear pin (speed reduction mechanism portion); 30A, 130A, an inner ring; 32. rollers (rolling bodies); 36. a sealing member; 37. a seal retention surface; 40. sealing the space; 47. 49, a limiting wall; 50b, a seal guide surface; 63. a 2 nd sealing member; 136. 1 st sealing member; 151. sealing the retaining surface.
Detailed Description
Next, embodiments of the present invention will be described with reference to the drawings. In the embodiments and modifications described below, the same reference numerals are given to common parts, and overlapping descriptions are partially omitted.
(embodiment 1)
First, embodiment 1 shown in fig. 1 and 2 will be described.
Fig. 1 is a sectional view of a rotary machine using a bearing inner race according to the present embodiment.
The rotating machine of the present embodiment is a speed reducer 10 used for an industrial robot, a machine tool, and the like. Power is transmitted from an electric motor (not shown) as a rotation drive source to an input portion (crankshaft 14) of the reduction gear 10.
The speed reducer 10 includes: an outer cylindrical member 11 serving also as a reducer case; a 1 st carrier module 13A and a 2 nd carrier module 13B rotatably held on an inner peripheral surface of the outer tube member 11; a plurality of (e.g., three) crankshafts 14 (input members) rotatably supported by the 1 st carrier module 13A and the 2 nd carrier module 13B; and a 1 st oscillating gear 15A and a 2 nd oscillating gear 15B that oscillate (revolve) together with the two eccentric portions (not shown) of the respective crankshafts 14. In the present embodiment, the 1 st carrier module 13A and the 2 nd carrier module 13B constitute an inner member.
Hereinafter, for convenience of description, a direction along the rotation central axis c1 (the relative rotation axis of the inner member and the outer cylinder member 11) of the 1 st carrier module 13A and the 2 nd carrier module 13B is referred to as an axial direction, and a direction extending in a radial direction with respect to the rotation central axis c1 is referred to as a radial direction. The center side of the 1 st and 2 nd carrier modules 13A and 13B in the axial direction is referred to as an axially inner side, and the side opposite to the axially inner side in the axial direction is referred to as an axially outer side. The side facing the rotation center axis c1 in the radial direction (the direction facing the rotation center axis c 1) is referred to as the radially inner side (the radially inner direction), and the side opposite to the radially inner side is referred to as the radially outer side (the radially outer direction).
The 1 st carrier module 13A includes: a perforated disc-shaped substrate portion 13 Aa; and a plurality of column portions 13Ab extending from an axially inner end surface of the base plate portion 13Aa in a direction toward the 2 nd carrier module 13B. The 1 st carrier module 13A is formed in a perforated disc shape. The end surfaces of the column portions 13Ab of the 1 st carrier module 13A abut against the end surfaces of the 2 nd carrier module 13B, and the column portions 13Ab are fastened and fixed to the 2 nd carrier module 13B with bolts 16.
A gap (space) in the axial direction is ensured between the base plate portion 13Aa of the 1 st carrier module 13A and the 2 nd carrier module 13B. The 1 st oscillating gear 15A and the 2 nd oscillating gear 15B are disposed in the gap.
Further, the 1 st swing gear 15A and the 2 nd swing gear 15B are formed with relief holes 19 through which the respective column portions 13Ab of the 1 st carrier module 13A are inserted. The escape hole 19 is formed to have a sufficiently large inner diameter with respect to the column part 13Ab so that the column part 13Ab does not interfere with the swing operation (turning operation) of the 1 st swing gear 15A and the 2 nd swing gear 15B.
The outer cylindrical member 11 is disposed across the outer peripheral surface of the substrate portion 13Aa of the 1 st gear frame module 13A and the outer peripheral surface of the 2 nd gear frame module 13B. The outer peripheral surface of the base plate portion 13Aa of the 1 st carrier block 13A and the outer peripheral surface of the 2 nd carrier block 13B are rotatably supported by bearings 12A and 12B at the inner peripheral portions on both sides of the outer tubular member 11 in the axial direction. Further, a plurality of pin grooves 17 extending in parallel with the rotation center axes c1 of the 1 st carrier block 13A and the 2 nd carrier block 13B are formed in the inner peripheral surface of the central region (the region facing the outer peripheral surface of the 1 st oscillating gear 15A and the outer peripheral surface of the 2 nd oscillating gear 15B) in the axial direction of the outer tubular member 11. A substantially cylindrical internal gear pin 20 is rotatably housed in each pin groove 17. The plurality of internal gear pins 20 attached to the inner peripheral surface of the outer cylindrical member 11 face the outer peripheral surfaces of the 1 st oscillating gear 15A and the 2 nd oscillating gear 15B, respectively.
The 1 st and 2 nd swing gears 15A and 15B are formed to have an outer diameter slightly smaller than the inner diameter of the outer cylindrical member 11. Outer teeth 15Aa and 15Ba that are in contact with a plurality of inner teeth pins 20 arranged on the inner circumferential surface of the outer cylindrical member 11 in a meshed state are formed on the outer circumferential surfaces of the 1 st oscillating gear 15A and the 2 nd oscillating gear 15B, respectively. The number of teeth of the external teeth 15Aa and 15Ba formed on the outer peripheral surfaces of the 1 st oscillating gear 15A and the 2 nd oscillating gear 15B is set to be slightly smaller (for example, one smaller) than the number of the internal pins 20.
The plurality of crankshafts 14 are arranged on the same circumference around the rotation center axis c1 of the 1 st carrier module 13A and the 2 nd carrier module 13B. Each crankshaft 14 is rotatably supported by the 1 st carrier module 13A and the 2 nd carrier module 13B via bearings, not shown. The two eccentric portions of each crankshaft 14 penetrate the 1 st oscillating gear 15A and the 2 nd oscillating gear 15B, respectively. Each eccentric portion is rotatably assembled to a support hole formed in each of the 1 st swing gear 15A and the 2 nd swing gear 15B via an eccentric portion bearing, not shown. Further, the two eccentric portions of each crankshaft 14 are eccentric so as to be shifted in phase from each other by 180 ° about the center axis of the crankshaft 14.
When the plurality of crankshafts 14 are rotated in one direction by power of an electric motor (not shown), the eccentric portions of the crankshafts 14 rotate in the same direction at a predetermined radius, and accordingly, the 1 st oscillating gear 15A and the 2 nd oscillating gear 15B rotate in the same direction (revolve) at the same radius. At this time, the external teeth 15Aa and 15Ba of the 1 st oscillating gear 15A and the 2 nd oscillating gear 15B contact the plurality of internal-tooth pins 20 held on the inner periphery of the outer cylindrical member 11 so as to mesh with the plurality of internal-tooth pins 20.
In fig. 1, reference numeral 28 denotes a crank gear which is attached to an end of each of the crankshafts 14 and receives power from the electric motor.
In the reduction gear 10 of the present embodiment, the number of teeth of the external teeth 15Aa and 15Ba of the 1 st oscillating gear 15A and the 2 nd oscillating gear 15B is set to be slightly smaller than the number of internal pins 20 on the outer cylindrical member 11 side. Therefore, while the 1 st and 2 nd oscillating gears 15A and 15B oscillate and rotate one rotation (one revolution), the 1 st and 2 nd oscillating gears 15A and 15B receive a reaction force in the rotation direction from the inner pins 20 on the outer cylindrical member 11 side, and rotate by a predetermined pitch in the direction opposite to the oscillation rotation direction. As a result, the 1 st and 2 nd carrier modules 13A and 13B coupled to the 1 st and 2 nd oscillating gears 15A and 15B via the crankshaft 14 rotate in the same direction at the same pitch together with the 1 st and 2 nd oscillating gears 15A and 15B. As a result, the rotation of the crankshaft 14 is decelerated and output as the rotation of the 1 st carrier module 13A and the 2 nd carrier module 13B. In the present embodiment, the outer cylindrical member 11 is fixed to an unillustrated mount base portion, and the 1 st carrier module 13A is coupled to an unillustrated rotation output member.
In the reduction gear 10 of the present embodiment, the reduction mechanism portion is configured by the 1 st and 2 nd oscillating gears 15A and 15B, the pin groove 17, the internal gear pin 20, and the like.
The bearing 12A interposed between the outer cylinder member 11 and the 1 st carrier module 13A and the bearing 12B interposed between the outer cylinder member 11 and the 2 nd carrier module 13B are roller bearings. Each of the bearings 12A, 12B has: an outer ring 31 fixed to the inner periphery of each end in the axial direction of the outer tube member 11; an inner ring 30 (bearing inner ring) fixed to the outer periphery of each of the 1 st and 2 nd carrier modules 13A and 13B; a plurality of rollers 32 (needle rollers) as rolling elements interposed between the outer ring 31 and the inner ring 30; and an annular retainer 33 that retains the plurality of rollers 32 so as to be rollable. The straight lines connecting the contact points of the inner ring 30, the rollers 32, and the outer ring 31 of the bearings 12A and 12B are inclined at a predetermined angle to the outside in the axial direction with respect to the plane orthogonal to the center axes of the bearings 12A and 12B. Each of the bearings 12A and 12B can support a radial load and an axial load in one direction.
The structure of the inner ring 30 (1 st inner ring) of the bearing 12A disposed on the 1 st carrier module 13A side is different from the structure of the inner ring 30 (2 nd inner ring) of the bearing 12B disposed on the 2 nd carrier module 13B side. Therefore, in order to distinguish the two inner rings, reference numeral 30A (30) is given to the inner ring (1 st inner ring) disposed on the 1 st carrier module 13A side, and reference numeral 30B (30) is given to the inner ring (2 nd inner ring) disposed on the 2 nd carrier module 13B side.
Fig. 2 is an enlarged sectional view of a portion II of the reduction gear 10 shown in fig. 1.
A bearing fixing surface 35 to which the inner ring 30A of the bearing 12A is press-fitted and fixed and a seal holding surface 37 to hold an annular seal member 36 are formed on the outer periphery of the base plate portion 13Aa of the 1 st carrier module 13A. The seal member 36 seals between the inner peripheral surface of the outer cylindrical member 11 and the 1 st carrier module 13A at a position axially outside the bearing 12A. That is, the seal member 36 is a member that keeps the sealed space 40 surrounded by the outer cylinder member 11, the 1 st carrier module 13A, and the 2 nd carrier module 13B sealed at a position axially outside the bearing 12A.
The sealing member 36 includes: an outer tube section 36a whose outer peripheral surface is in contact with the seal support surface 41 on the inner periphery of the end of the outer tube member 11; a 1 st lip 36b and a 2 nd lip 36c, the inner peripheral surfaces of which are in contact with the seal holding surface 37; and a connecting wall 36d extending radially inward from an axially outer end of the outer tube 36a to connect the outer tube 36a with the 1 st lip 36b and the 2 nd lip 36 c.
The seal holding surface 37 is disposed adjacent to the bearing fixing surface 35 on the axially outer side of the bearing fixing surface 35. The seal holding surface 37 and the bearing fixing surface 35 are concentric circular peripheral surfaces extending in the axial direction, and the outer diameter of the seal holding surface 37 is set larger than the outer diameter of the bearing fixing surface 35. A stepped surface 38 extending radially outward from an end of the bearing fixing surface 35 is formed between the bearing fixing surface 35 and the seal holding surface 37. The inner race 30A press-fitted into the bearing fixing surface 35 abuts against the stepped surface 38, and displacement outward in the axial direction is restricted. An end flange 39 extending radially outward is formed on the axially outer end of the seal holding surface 37. The outer peripheral surface of the end flange 39 is formed to have substantially the same outer diameter as that of the outer end portion of the outer cylindrical member 11 in the axial direction. The axially inner end surface of the end flange 39 faces the axially upper end surface of the outer cylindrical member 11 with a slight gap therebetween.
The above-described seal support surface 41 and the bearing fixing surface 42 to which the outer ring 31 of the bearing 12A is press-fitted and fixed are formed on the inner periphery of the end portion of the outer tubular member 11 on the 1 st carrier block 13A side. The seal support surface 41 and the bearing fixing surface 42 are concentric circular circumferential surfaces extending in the axial direction, and the seal support surface 41 is disposed on the axial outer side of the bearing fixing surface 42. The inner diameter of the seal support surface 41 is set larger than the inner diameter of the bearing fixing surface 42. A stepped surface 43 extending radially outward from an axially outer end of the bearing fixing surface 42 is formed between the bearing fixing surface 42 and the seal support surface 41. Further, a support surface 44 extending radially inward is formed at an axially inner end of the bearing fixing surface 42. The outer ring 31 press-fitted into the bearing fixing surface 42 abuts against the support surface 44, and displacement to the inside in the axial direction is restricted.
The inner race 30A of the bearing 12A is formed entirely of an annular metal block. The inner ring 30A includes: an inner peripheral surface 46 press-fitted and fixed to the bearing fixing surface 35 of the 1 st carrier module 13A; an outer surface 47 that abuts the stepped surface 38 of the 1 st carrier block 13A; and a rolling surface 48 against which the roller 32 as a rolling element rotatably abuts. The rolling surface 48 is formed in a tapered shape so as to have an outer diameter that decreases toward the axially inner side (the right side in fig. 2). A restricting wall 49 that abuts against one end surface of the roller 32 in the axial direction to restrict the axial displacement of the roller 32 is formed at a position radially outside the rolling surface 48 of the inner ring 30A. The restricting wall 49 is formed by an outer peripheral region of the inner race 30A bulging radially outward with respect to the rolling surface 48.
The restricting wall 49 has an annular overhang 50 bulging toward the axial inner side with respect to the rolling surface 48 at a position radially outside the rolling surface 48. A regulating surface 50a against which an end surface of the roller 32 in the axial direction can abut is formed on the inner peripheral side of the overhang portion 50. The restricting surface 50a is formed in a tapered shape so as to have an inner diameter that increases toward the axially inner side (the right side in fig. 2). Further, a tapered seal guide surface 50b is formed on the outer peripheral side of the overhang 50. The outer diameter of the seal guide surface 50b gradually increases toward the axial outside. An end outer peripheral surface 51 having a constant outer diameter is formed on the restricting wall 49 at a portion axially outward of the overhang portion 50. The end outer peripheral surface 51 is formed to have the same outer diameter as the maximum outer diameter portion (the end portion on the axial outside) of the seal guide surface 50b and also have the same outer diameter as the seal holding surface 37 of the 1 st carrier module 13A. Therefore, when the inner race 30A is assembled to the 1 st carrier block 13A so that the outer side surface 47 abuts against the stepped surface 38, the end outer peripheral surface 51 continues to the seal holding surface 37 of the 1 st carrier block 13A without a level difference.
In the present embodiment, the seal holding surface 37 and the end portion outer peripheral surface 51 formed so as to have the same outer diameter constitute a protection mechanism that prevents damage to the inner peripheral surface (the 1 st lip 36b and the 2 nd lip 36c) of the seal member 36. The seal guide surface 50b is disposed on the outer periphery of the end portion of the inner ring 30A on the side adjacent to the seal holding surface 37 in the axial direction. The outer diameter of the seal guide surface 50b gradually increases toward the side (axially outward) where the seal holding surface 37 is disposed. The shape of the seal guide surface 50b is not limited to a shape in which the outer diameter linearly increases toward the axial outside. A shape including a curved outer diameter changing portion in a part thereof may be adopted, such as a shape in which the outer diameter expands in a curved shape, or a shape in which the form of expansion of the outer diameter (inclination angle) changes in the middle of the outer diameter toward the outer side in the axial direction.
Next, a method of assembling the speed reducer 10 according to the present embodiment will be described.
When the reduction gear 10 is assembled, the inner race 30A of the bearing 12A is press-fitted and fixed to the bearing fixing surface 35 of the 1 st carrier block 13A in advance. The outer ring 31 of the bearing 12A and the rollers 32 held by the retainer 33 are mounted on the outer cylindrical member 11 side in advance. In this state, the seal member 36 is attached to the inclined seal guide surface 50b of the inner ring 30A, and the seal member 36 is press-fitted outward in the axial direction along the seal guide surface 50 b. Thereby, the seal member 36 moves onto the seal holding surface 37 of the 1 st carrier module 13A via the end outer peripheral surface 51 of the inner race 30A. At this time, the inner peripheral surface (the 1 st lip 36b and the 2 nd lip 36c) of the seal member 36 passes through a boundary portion between the end outer peripheral surface 51 of the inner ring 30A and the seal holding surface 37 of the 1 st carrier module 13A. However, since the position of the end outer peripheral surface 51 and the position of the seal holding surface 37 are continuous without a level difference, the inner peripheral surface of the seal member 36 is not damaged when it passes over the boundary portion between the end outer peripheral surface 51 and the seal holding surface 37.
After the seal member 36 is held on the seal holding surface 37 of the 1 st gear frame module 13A as described above, the outer cylindrical member 11 is assembled to the 1 st gear frame module 13A from the axially outer side. At this time, the plurality of rollers 32 mounted to the outer cylindrical member 11 together with the outer ring 31 and the cage 33 are rollably in contact with the rolling surface 48 of the inner ring 30A mounted on the 1 st carrier module 13A side. Thereafter, the 2 nd carrier module 13B is fastened and fixed to the column portion 13Ab of the 1 st carrier module 13A with the bolt 16.
The bearing 12B interposed between the outer cylinder member 11 and the 2 nd carrier module 13B has substantially the same configuration as the bearing 12A on the 1 st carrier module 13A side, except that the seal guide surface (50B) is not formed on the regulation wall (49) of the inner ring 30B. As shown in fig. 1, the inner race 30B is press-fitted and fixed to the bearing fixing surface 52 of the 2 nd carrier module 13B, and displacement in the axial direction is restricted by the end flange 53 of the 2 nd carrier module 13B. The bearings 12A and 12B are fixed by fastening the 1 st carrier module 13A and the 2 nd carrier module 13B with bolts 16, and preload is applied thereto. A spacer 54 for adjusting the preload is interposed between the inner ring 30B and the end flange 53 of the 2 nd carrier module 13B.
As described above, the seal guide surface 50b of the inner ring 30A of the bearing 12A employed in the speed reducer 10 (rotating equipment) of the present embodiment is formed on the outer periphery of the end portion of the inner ring 30A. The outer diameter of the seal guide surface 50b gradually increases toward the seal holding surface 37. Therefore, when the seal member 36 is attached to the seal holding surface 37, the seal member 36 can be smoothly moved to the seal holding surface 37 via the inclined seal guide surface 50 b.
Also, a seal guide surface 50b of the inner ring 30A for guiding the installation of the seal member 36 is formed on the end portion outer periphery of the inner ring 30A. Therefore, the axial length of the 1 st carrier module 13A (inner member) of the speed reducer 10 (rotating equipment) can be shortened as compared with the case where the same seal guide surface is provided at a position adjacent to the seal holding surface 37 on the 1 st carrier module 13A (inner member). Therefore, the reduction gear 10 (rotating machine) using the inner ring 30A of the present embodiment can be reduced in size as a whole.
In addition, the seal guide surface 50b of the speed reducer 10 (rotating device) of the present embodiment is formed on the restricting wall 49 of the inner race 30A for restricting the displacement of the rollers 32 (rolling elements) of the bearing 12A. Therefore, since a part of the regulating wall 49 of the inner ring 30A also serves as the seal guide surface 50b, the axial length of the inner ring 30A can be made shorter as compared with the case where the regulating wall and the seal guide surface are provided separately.
In the reduction gear 10 (rotating equipment) according to the present embodiment, the seal holding surface 37 of the 1 st carrier module 13A (inner member) and the end portion outer peripheral surface 51 of the inner race 30A are formed by circular outer peripheral surfaces having the same outer diameter and no level difference. That is, a protection mechanism is provided between the seal holding surface 37 and the seal guide surface 50 b. Therefore, when the seal member 36 is attached to the seal guide surface 50b of the inner ring 30A during assembly of the speed reducer 10, in this state, when the seal member 36 is moved in the direction of the seal holding surface 37 on the 1 st carrier module 13A side, the inner peripheral surface (the 1 st lip 36b and the 2 nd lip 36c) of the seal member 36 can be prevented from catching on the boundary portion between the end portion outer peripheral surface 51 and the seal holding surface 37.
(modification 1)
Fig. 3 is a view corresponding to fig. 2, and is an enlarged cross-sectional view showing the reduction gear 10 of modification 1.
The reduction gear 10 of the present modification is slightly different from the above-described basic form in the structure of the protection mechanism for preventing damage to the inner peripheral surface of the seal member 36. In the basic embodiment described above, the seal holding surface 37 of the 1 st carrier module 13A (inner member) and the end outer peripheral surface 51 of the inner ring 30A are formed in a circular shape having the same outer diameter without a height difference. In contrast, in the present modification, the seal holding surface 37 and the end portion outer peripheral surface 51 are formed in a circular shape having the same outer diameter, and a smoothly curved surface 58 is formed at an outer peripheral corner portion of the contact portion between the seal holding surface 37 and the end portion outer peripheral surface 51.
Therefore, in the protection mechanism of the present modification, even if a slight gap is formed between the seal holding surface 37 and the end portion outer peripheral surface 51, the inner peripheral surface of the seal member 36 can be prevented from catching on the boundary portion between the seal holding surface 37 and the end portion outer peripheral surface 51 when the seal member 36 is attached.
(modification 2)
Fig. 4 is a view corresponding to fig. 2, and is an enlarged cross-sectional view showing the reduction gear 10 of the 2 nd modification.
The speed reducer 10 of the present modification differs from the basic embodiment and modification 1 described above in the structure of the protection mechanism for preventing damage to the inner peripheral surface of the seal member 36. In the basic form and the 1 st modification, the seal holding surface 37 of the 1 st carrier module 13A (inner member) and the end outer peripheral surface 51 of the inner race 30A are formed to have the same outer diameter. In contrast, in the present modification, the outer diameter of the end outer peripheral surface 51 of the inner race 30A is formed smaller than the outer diameter of the seal holding surface 37 of the 1 st carrier module 13A. A chamfered portion 59 (tapered portion) is provided at an outer peripheral corner portion of the seal holding surface 37 on the inner ring 30A side.
Therefore, in the protection mechanism of the present modification, when the seal member 36 is moved from the end outer peripheral surface 51 of the inner ring 30A to the seal holding surface 37 at the time of mounting the seal member 36, the seal member 36 can be smoothly moved to the seal holding surface 37 via the chamfered portion 59. Therefore, when the protection mechanism of the present modification is employed, the inner peripheral surface of the seal member 36 can be more reliably prevented from catching on the boundary portion between the seal holding surface 37 and the end portion outer peripheral surface 51.
(embodiment 2)
Fig. 5 is a view corresponding to fig. 2, and is a sectional view showing a reduction gear (rotating device) according to embodiment 2.
The speed reducer 110 (rotating equipment) of the present embodiment is different from that of embodiment 1 in the point that the 1 st carrier module 113A and the inner race 130A of the bearing 112A fixed to the 1 st carrier module 113A are configured. The 1 st carrier module 113A is not provided with the seal holding surface (37) as in embodiment 1, but an outer peripheral surface of an end portion of the inner ring 130A is provided with the seal holding surface 151. The bearing fixing surface 135 of the 1 st carrier module 113A into which the inner race 130A is press-fitted and fixed extends to the root of the end flange 39. An annular seal accommodating groove 62 is formed in an end face 39a of the end flange 39 on the root side thereof, with which the outer surface 47 of the inner race 130A abuts.
The 1 st seal member 136 having the same structure as the seal member 36 used in the 1 st embodiment is interposed between the seal holding surface 151 fixed to the inner race 130A of the 1 st carrier module 113A and the seal support surface 41 on the inner periphery of the outer cylindrical member 11. Further, an annular 2 nd seal member 63 for sealing between the end flange 39 and the outer surface 47 of the inner ring 130A is accommodated in the seal accommodating groove 62 of the end flange 39. As the 2 nd seal member 63, for example, an annular elastic member having a substantially circular cross section can be used.
In the present embodiment, the 1 st sealing member 136 and the 2 nd sealing member 63 constitute a sealing mechanism that keeps the sealed space 40 between the 1 st carrier module 113A (inner member) and the outer cylindrical member 11 sealed. In the present embodiment, the 1 st seal member 136 and the 2 nd seal member 63 constitute the seal mechanism, but in the case where the 1 st carrier module 113A and the inner ring 130A can be hermetically sealed without using the 2 nd seal member 63, the seal mechanism may be constituted by only the 1 st seal member 136.
Next, a method of assembling the speed reducer 110 according to the present embodiment will be described.
When the reduction gear 110 is assembled, the inner race 130A of the bearing 112A is press-fitted and fixed to the bearing fixing surface 135 of the 1 st carrier module 113A. At this time, the 2 nd seal member 63 is housed in the seal housing groove 62 of the end face 39a of the 1 st carrier module 113A in advance. The space between the end surface 39a of the 1 st carrier module 113A and the outer surface 47 of the inner race 130A is sealed by the 2 nd seal member 63. On the other hand, the outer ring 31 of the bearing 112A and the rollers 32 held by the retainer 33 are mounted in advance on the outer tubular member 11 side.
In this state, the 1 st seal member 136 is attached to the inclined seal guide surface 50b of the inner ring 130A, and the 1 st seal member 136 is press-fitted outward in the axial direction along the seal guide surface 50 b. Thereby, the 1 st seal member 136 moves along the seal guide surface 50b of the inner ring 130A onto the seal holding surface 151.
Thereafter, the outer cylindrical member 11 is assembled to the 1 st carrier module 113A from the axially outer side, and the 2 nd carrier module is fastened to the pillar portion of the 1 st carrier module 113A by bolts. As a result, the plurality of rollers 32 of the bearing 112A are rollably in contact with the rolling surface 48 of the inner ring 130A attached to the 1 st carrier module 113A side. The sealed space 40 inside the outer cylindrical member 11 is sealed by the 1 st seal member 136 and the 2 nd seal member 63.
As described above, the reducer 110 (rotating device) according to the present embodiment is provided with the seal holding surface 151, with which the inner peripheral surface (the 1 st lip 36b and the 2 nd lip 36c) of the 1 st seal member 136 abuts, on the inner ring 130A press-fitted and fixed to the 1 st carrier module 113A. The seal holding surface 151 (outer peripheral surface) of the inner ring 130A and the outer cylindrical member 11 are sealed by the 1 st seal member 136. Therefore, the reduction gear 110 of the present embodiment can shorten the axial length of the 1 st carrier module 113A (inner member) as compared with the case where the sealing member is interposed between the outer peripheral surface of the 1 st carrier module 113A (inner member) and the outer cylindrical member 11. Therefore, when the reduction gear 110 of the present embodiment is used, the reduction gear 110 can be made smaller.
In addition, in the reduction gear 110 (rotating equipment) of the present embodiment, the 2 nd seal member 63 that seals between the end flange 39 and the inner ring 130A is also interposed between the end surface 39a of the end flange 39 of the 1 st carrier module 113A (inner member) and the outer surface 47 of the inner ring 130A. Therefore, when the speed reducer 110 (rotating equipment) of the present embodiment is used, it is possible to suppress foreign matter from entering the sealed space 40 through the gap between the inner ring 130A of the bearing 112A and the 1 st carrier module 113A (inner member).
Further, in the speed reducer 110 (rotating device) of the present embodiment, a seal holding surface 151 that holds the 1 st seal member 136 and a seal guide surface 50b whose outer diameter gradually widens in a tapered shape toward the seal holding surface 151 are formed on the outer peripheral surface of the inner ring 130A of the bearing 112A. Therefore, when the 1 st seal member 136 is attached to the seal holding surface 151 of the inner race 130A when the reduction gear 110 is assembled, the 1 st seal member 136 is first attached to the seal guide surface 50b, and from this state, the 1 st seal member 136 can be moved outward in the axial direction along the inclined shape of the seal guide surface 50 b. At this time, the 1 st seal member 136 moves onto the seal holding surface 151 while gradually expanding its inner peripheral surface by the seal guide surface 50 b. Therefore, when the speed reducer 110 (rotating device) of the present embodiment is used, the 1 st seal member 136 can be easily attached to the seal holding surface 151 of the inner ring 130A when the speed reducer 110 is assembled.
In addition, in the reduction gear 110 (rotating device) of the present embodiment, a restricting wall 49 for restricting displacement of the roller 32 as the rolling element is provided at a position adjacent to the seal holding surface 151 of the inner ring 130A. Further, a seal guide surface 50b having an outer diameter gradually expanding toward the axial outside is formed on the outer peripheral side of the restricting wall 49. Therefore, in the reduction gear 110 of the present embodiment, a part of the restricting wall 49 of the inner race 130A also serves as the seal guide surface 50 b. Therefore, the axial length of the inner ring 130A can be made shorter as compared with the case where the restricting wall and the seal guide surface are provided separately in the inner ring 130A. Therefore, when the reduction gear 110 of the present embodiment is used, the reduction gear 110 can be further downsized.
The present invention is not limited to the above-described embodiments, and various design changes can be made without departing from the scope of the invention. For example, in the above-described embodiment, the bearing inner race according to the present invention is used as a speed reducer, but the rotating machine used is not limited to the speed reducer, and may be a rotating machine without a speed reduction mechanism.

Claims (12)

1. A bearing inner race for a bearing interposed between an inner member and an outer cylindrical member which are relatively rotatable, and a seal member disposed at a position adjacent to a seal holding surface on the inner member which holds the seal member,
the bearing inner ring is provided with a seal guide surface which is provided on the outer periphery of an end portion of the bearing inner ring adjacent to the seal holding surface and is formed in a tapered shape,
the outer diameter of the seal guide surface increases toward a position where the seal holding surface is disposed.
2. The bearing inner race of claim 1, wherein,
the seal guide surface is formed on a restricting wall that restricts displacement of the rolling elements of the bearing at an end portion adjacent to the seal retaining surface in an axial direction along the relative rotation axes of the inner member and the outer cylindrical member.
3. A rotary apparatus, wherein,
the rotating device is provided with:
an inner member having a seal retaining surface;
an outer cylinder member disposed on an outer peripheral side of the inner member so as to be rotatable relative to the inner member;
a sealing member interposed between the inner member and the outer cylindrical member; and
a bearing interposed between the inner member and the outer cylindrical member so as to be juxtaposed to the seal member in an axial direction which is an extending direction of the relative rotation axes of the inner member and the outer cylindrical member,
the bearing includes an inner ring disposed at a position adjacent to the inner member on the side of the sealed space in the axial direction of the seal holding surface,
the inner ring includes a seal guide surface formed in a tapered shape and provided on an outer periphery of an end portion of the inner ring adjacent to the seal holding surface in the axial direction,
the outer diameter of the seal guide surface increases toward a position where the seal holding surface is disposed.
4. The rotary apparatus according to claim 3,
the bearing is further provided with a rolling element,
the inner race is provided with a restricting wall that restricts displacement of the rolling elements at an end portion adjacent to the seal retaining surface in the axial direction,
the seal guide surface is formed on the restricting wall.
5. The rotating apparatus according to claim 3 or 4,
a protection mechanism that prevents damage to the inner peripheral surface of the seal member is provided between the seal holding surface and the seal guide surface.
6. A speed reducer, wherein,
the speed reducer is provided with:
an inner member having a seal retaining surface;
an outer cylinder member disposed on an outer peripheral side of the inner member so as to be rotatable relative to the inner member;
an input member that inputs a rotational driving force;
a speed reduction mechanism that reduces the speed of the rotational driving force input to the input member and transmits the reduced rotational driving force to the inner member or the outer tube member;
a sealing member interposed between the inner member and the outer cylindrical member; and
a bearing interposed between the inner member and the outer cylindrical member so as to be juxtaposed to the seal member in an axial direction which is an extending direction of the relative rotation axes of the inner member and the outer cylindrical member,
the bearing includes an inner ring disposed at a position adjacent to the inner member on the side of the sealed space in the axial direction of the seal holding surface,
the inner ring includes a seal guide surface formed in a tapered shape and provided on an outer periphery of an end portion of the inner ring adjacent to the seal holding surface in the axial direction,
the outer diameter of the seal guide surface increases toward a position where the seal holding surface is disposed.
7. A rotary apparatus, wherein,
the rotating device is provided with:
an inner member;
an outer cylinder member disposed on an outer peripheral side of the inner member so as to be rotatable relative to the inner member;
a sealing mechanism for keeping a sealed space between the inner member and the outer tube member hermetically sealed; and
a bearing interposed between the inner member and the outer cylindrical member,
the bearing is provided with an inner ring which is provided with a bearing,
the sealing mechanism includes a 1 st sealing member for sealing between the outer peripheral surface of the inner ring and the outer cylindrical member.
8. A rotary apparatus, wherein,
the rotating device is provided with:
an inner member;
an outer cylinder member disposed on an outer peripheral side of the inner member so as to be rotatable relative to the inner member;
a sealing mechanism for keeping a sealed space between the inner member and the outer tube member hermetically sealed; and
a bearing interposed between the inner member and the outer cylindrical member,
the bearing is provided with an inner ring which is provided with a bearing,
the sealing mechanism is provided with:
a 1 st sealing member that seals a space between an outer peripheral surface of the inner ring and the outer tube member; and
and a 2 nd seal member that seals between the inner ring and the inner member.
9. The rotating apparatus according to claim 7 or 8,
the inner ring includes:
a seal holding surface that holds the 1 st seal member; and
and a seal guide surface formed in a tapered shape having an outer diameter that increases toward the seal holding surface in an axial direction that is an extending direction of the relative rotation axes of the inner member and the outer cylindrical member.
10. The rotary apparatus according to claim 9,
the bearing is further provided with a rolling element,
the inner race is provided with a restricting wall that restricts displacement of the rolling elements at a position adjacent to the seal retaining surface in the axial direction,
the seal guide surface is formed on the restricting wall.
11. A speed reducer, wherein,
the speed reducer is provided with:
an inner member having a seal retaining surface;
an outer cylinder member disposed on an outer peripheral side of the inner member so as to be rotatable relative to the inner member;
an input member that inputs a rotational driving force;
a speed reduction mechanism that reduces the speed of the rotational driving force input to the input member and transmits the reduced rotational driving force to the inner member or the outer tube member;
a sealing mechanism for keeping a sealed space between the inner member and the outer tube member hermetically sealed; and
a bearing interposed between the inner member and the outer cylindrical member,
the bearing is provided with an inner ring which is provided with a bearing,
the sealing mechanism is provided with:
a 1 st sealing member that seals a space between an outer peripheral surface of the inner ring and the outer tube member; and
and a 2 nd seal member that seals between the inner ring and the inner member.
12. A bearing inner race for a bearing interposed between an inner member and an outer cylindrical member which are relatively rotatable, and a seal member disposed at a position adjacent to a seal holding surface on the inner member which holds the seal member,
the bearing inner race includes a seal guide surface for guiding the seal member to the seal holding surface.
CN202110476124.7A 2020-05-08 2021-04-29 Bearing inner ring, rotating equipment and speed reducer Pending CN113623322A (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2020082492 2020-05-08
JP2020-082492 2020-05-08
JP2021065374A JP2021179252A (en) 2020-05-08 2021-04-07 Inner race of bearing, rotary machine, and speed reducer
JP2021-065374 2021-04-07

Publications (1)

Publication Number Publication Date
CN113623322A true CN113623322A (en) 2021-11-09

Family

ID=78231995

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202110476124.7A Pending CN113623322A (en) 2020-05-08 2021-04-29 Bearing inner ring, rotating equipment and speed reducer

Country Status (5)

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JP (1) JP2021179252A (en)
KR (1) KR20210136847A (en)
CN (1) CN113623322A (en)
DE (1) DE102021110590A1 (en)
TW (1) TW202204778A (en)

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5183998B2 (en) 2007-08-02 2013-04-17 Ｎｔｎ株式会社 Tapered roller bearing

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TW202204778A (en) 2022-02-01
JP2021179252A (en) 2021-11-18
DE102021110590A1 (en) 2021-11-11

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