CN112013029B - Bearing assembly structure of rotary equipment - Google Patents

Bearing assembly structure of rotary equipment Download PDF

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Publication number
CN112013029B
CN112013029B CN202010334166.2A CN202010334166A CN112013029B CN 112013029 B CN112013029 B CN 112013029B CN 202010334166 A CN202010334166 A CN 202010334166A CN 112013029 B CN112013029 B CN 112013029B
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CN
China
Prior art keywords
spacer
peripheral surface
shaft portion
carrier module
outer peripheral
Prior art date
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Active
Application number
CN202010334166.2A
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Chinese (zh)
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CN112013029A (en
Inventor
下出祐司
古田和哉
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Nabtesco Corp
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Nabtesco Corp
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Publication of CN112013029A publication Critical patent/CN112013029A/en
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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
    • 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
    • F16C19/16—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 a single row of balls
    • F16C19/163—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 a single row of balls with angular contact
    • 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
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings 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
    • 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
    • F16C33/58—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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063—Fixing them on the shaft
    • 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
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F16H57/022—Adjustment of gear shafts or 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
    • F16C2229/00—Setting preload
    • 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
    • F16C2361/65—Gear shifting, change speed gear, gear box
    • 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element
    • F16C35/073—Fixing them on the shaft or housing with interposition of an element between shaft and inner race ring
    • 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
    • F16H57/022—Adjustment of gear shafts or bearings
    • F16H2057/0221—Axial adjustment

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)
  • Retarders (AREA)
  • Support Of The Bearing (AREA)

Abstract

The invention provides a bearing assembly structure of a rotating device. The bearing assembly structure of the rotating equipment of the invention comprises: an outer member; a bearing fixed to the outer member; an inner member having a shaft portion inserted into the bearing, a flange portion radially extending from a position of the shaft portion axially outward of the bearing, and an enlarged diameter portion formed between the shaft portion and the flange portion so as to be larger than an outer diameter of the shaft portion; and an annular spacer disposed between the bearing and the flange portion, the spacer being disposed so as to avoid interference with the enlarged diameter portion.

Description

Bearing assembly structure of rotary equipment
Technical Field
The present invention relates to a bearing assembly structure of a rotary device such as a speed reducer.
Background
For industrial robots, machine tools, and the like, a decelerator is used to decelerate the rotation of a rotation driving source such as a motor (for example, refer to patent document 1).
The speed reducer (rotating device) described in patent document 1 includes: an outer tube (outer member); a carrier module (inner member) rotatably supported on the inner side of the outer tube; a crankshaft rotatably supported at a position deviated from a rotation center of the carrier module in a radial direction; and a final drive mechanism that reduces the rotation of the crankshaft to rotate the carrier module itself. The final drive mechanism includes a rotation gear that rotates integrally with an eccentric portion of the crankshaft, and a plurality of inner teeth pins that are held on an inner peripheral surface of the outer cylinder. The swing gear has external teeth engaged with the internal tooth pins in an engaged state. The number of teeth of the external teeth is set to be slightly smaller than the number of the internal tooth pins. Therefore, when the revolving gear rotates one revolution together with the crankshaft, the carrier module rotates a predetermined pitch in a direction opposite to the revolving direction due to the engagement between the external teeth and the internal tooth pins. The outer cylinder is attached to a base block of an industrial robot, a machine tool, or the like, and the carrier module rotates as an output rotary body.
In the above-described reduction gear, the carrier module is supported by the outer tube via an angular ball bearing and the like. The outer ring of the bearing is press-fitted and fixed to the inner periphery of the end portion of the outer tube while restricting axial displacement, and the inner ring of the bearing is fitted to the outer periphery of the cylindrical body portion (shaft portion) of the carrier module. A flange portion extending radially outward from the main body portion is provided at one end side in the axial direction of the main body portion of the carrier module. An annular spacer for imparting axial preload to the inner ring is interposed between the flange portion and the inner ring of the bearing. When the carrier module is assembled to the outer tube, the flange portion of the carrier module presses the spacer in the axial direction, and the spacer applies preload to the inner ring of the bearing.
Further, a curved corner portion, in which the outer diameter of the outer peripheral surface of the main body portion increases as the main body portion (shaft portion) is curved toward the flange portion, is provided at an end portion in the axial direction of the main body portion (shaft portion) of the carrier module. Thereby, the strength between the main body portion and the flange portion is improved.
Prior art literature
Patent literature
Patent document 1: japanese patent No. 5917421
Disclosure of Invention
Problems to be solved by the invention
The speed reducer (rotating device) described in patent document 1 is provided with a curved corner portion having an outer diameter larger than that of other portions of a main body portion at an end portion in an axial direction of the main body portion of a carrier module (inner member). Therefore, when the outer tube (outer member) is assembled with the carrier module (inner member), there is a concern that the spacers interfere with the bent corners on the carrier module side, and the preload applied to the bearing via the spacers becomes unstable.
The invention provides a bearing assembly structure of a rotating device, which can stabilize pre-compression applied to a bearing by a spacer.
Solution for solving the problem
The bearing assembly structure of a rotary device according to an aspect of the present invention includes: an outer member; a bearing fixed to the outer member; an inner member having a shaft portion inserted into the bearing, a flange portion radially enlarged from a position of the shaft portion axially outward of the bearing, and an enlarged diameter portion formed between the shaft portion and the flange portion so as to have an outer diameter larger than an outer diameter of the shaft portion; and an annular spacer disposed between the bearing and the flange portion, the spacer being disposed so as to avoid interference with the enlarged diameter portion.
The inner peripheral surface of the spacer may be formed to have an inner diameter larger than an outer diameter of the enlarged diameter portion.
In addition, a bearing assembly structure of a rotary device according to an aspect of the present invention includes: a bearing having an inner race and an outer race; an outer member to which the outer ring is fixed; an inner member having a shaft portion to which the inner ring is fixed, a flange portion that expands in a radial direction from a position of the shaft portion axially outward of the inner ring, and an expanded diameter portion formed between the shaft portion and the flange portion so as to have an outer diameter larger than an outer diameter of the shaft portion; an annular spacer disposed between the inner ring and the flange portion on an outer peripheral side of the shaft portion and the enlarged diameter portion; an interference avoiding portion formed on the spacer to avoid interference between the spacer and the expanded diameter portion; and a positioning portion provided on either one of an inner peripheral surface and an outer peripheral surface of the spacer, the positioning portion being capable of positioning a relative position in a radial direction between the spacer and the inner member.
According to the above configuration, when the spacer is assembled together with the bearing to the outer member and the inner member, the pressing load of the flange portion acts on the inner ring of the bearing via the spacer. At this time, since the interference avoiding portion is provided in the spacer, the spacer does not interfere with the enlarged diameter portion of the inner member. Further, since any one of the inner peripheral surface and the outer peripheral surface of the spacer is provided as a positioning portion in the radial direction with the inner member, the spacer is positioned with respect to the inner member in the radial direction by any one of the inner peripheral surface and the outer peripheral surface of the spacer at the time of assembly, and therefore, the position of the spacer can be suppressed from being deviated in the radial direction with respect to the inner member. As a result, the spacer stabilizes the supporting position (preload applying position) of the inner ring.
The interference avoiding portion may be formed by forming an annular gap between an inner peripheral surface of the spacer and outer peripheral surfaces of the shaft portion and the diameter-enlarged portion, and the outer peripheral surface of the spacer may be formed to have an outer diameter equal to or smaller than an outer diameter of the flange portion, and may be formed to define the positioning portion.
In this case, for example, when the spacer is attached to the shaft portion of the inner member, the position of the spacer in the radial direction is adjusted so that the outer peripheral surface of the spacer coincides with the outer peripheral surface of the flange portion in the radial direction, or so that the outer peripheral surface of the spacer is positioned radially inward of the outer peripheral surface of the flange portion. In this case, since an annular gap is secured between the inner peripheral surface of the spacer and the shaft portion of the inner member, the inner peripheral surface of the spacer does not interfere with the enlarged diameter portion of the inner member.
Desirably, the outer peripheral surface of the spacer is formed to have the same outer diameter as the flange portion.
In this case, when the spacer is attached to and fixed to the shaft portion of the inner member, the position of the spacer in the radial direction is adjusted so that the outer peripheral surface of the spacer coincides with the outer peripheral surface of the flange portion in the radial direction. Thereby, the spacer is positioned radially with respect to the inner member.
The spacer may have a positioning portion that restricts movement of the spacer in the radial direction by an outer peripheral surface of the shaft portion in a region of an inner peripheral surface of the spacer that does not face the enlarged diameter portion, and the interference avoiding portion may have an inner diameter larger than an outer diameter of the enlarged diameter portion in a region of the inner peripheral surface of the spacer that faces the enlarged diameter portion.
In this case, when the spacer is attached and fixed to the shaft portion of the inner member, the positioning portion of the inner peripheral surface of the spacer is restricted from moving in the radial direction by the outer peripheral surface of the shaft portion. In addition, since the interference avoiding portion is provided in the region of the inner peripheral surface of the spacer, which is opposed to the expanded diameter portion, the spacer does not interfere with the expanded diameter portion of the inner member.
The interference avoiding portion may be formed by a chamfer portion formed in a region of the inner peripheral surface of the spacer, the region being opposite to the enlarged diameter portion.
The diameter-enlarged portion may be a bent corner portion in which the outer diameter of the outer peripheral surface increases as the portion is bent from the end portion of the shaft portion toward the flange portion.
In this case, the strength of the connection portion between the shaft portion and the flange portion can be improved by the bent corner portion, and interference between the inner peripheral surface of the spacer and the bent corner portion can be avoided.
In addition, a bearing assembly structure of a rotary device according to an aspect of the present invention includes: a bearing having an inner race and an outer race; an outer member to which the outer ring is fixed; an inner member having a shaft portion to which the inner ring is fixed, a flange portion that expands in a radial direction from a position of the shaft portion axially outward of the inner ring, and a bent corner portion whose outer diameter increases as the outer peripheral surface is bent from an end portion of the shaft portion toward the flange portion; a spacer disposed between the inner ring and the flange portion on an outer peripheral side of the shaft portion and the bent corner portion; an interference avoiding portion that avoids interference between the spacer and the curved corner portion; and a positioning portion capable of positioning a relative position in a radial direction between the spacer and the inner member, wherein an annular recess is provided at an end portion of the shaft portion, the annular recess is recessed radially inward and is connected to the bent corner portion inside the recess, the annular recess constitutes the interference avoiding portion, and a portion in a region adjacent to the annular recess of an outer peripheral surface of the shaft portion constitutes the positioning portion that restricts movement of the spacer in the radial direction.
In this case, when the spacer is attached and fixed to the shaft portion of the inner member, the spacer is restricted from moving in the radial direction by a portion of the outer peripheral surface of the shaft portion adjacent to the annular recess. Further, since the bent corner portion of the end portion of the shaft portion is formed so as to be continuous with the annular recess inside the annular recess, the inner peripheral surface of the spacer does not interfere with the bent corner portion.
ADVANTAGEOUS EFFECTS OF INVENTION
Since the spacer is disposed so as to avoid interference with the enlarged diameter portion of the inner member, the bearing assembly structure of the rotating apparatus described above can stabilize the preload applied to the bearing by the spacer.
Drawings
Fig. 1 is a longitudinal sectional view of a rotary apparatus of embodiment 1.
Fig. 2 is a partially enlarged cross-sectional view of the rotary device of embodiment 1 in fig. 1.
Fig. 3 is a cross-sectional view similar to fig. 2 showing an assembled state of the rotary device according to embodiment 1.
Fig. 4 is a partial cross-sectional view of the rotary apparatus of embodiment 2.
Fig. 5 is an enlarged view of the V part of fig. 4 of the rotating device of embodiment 2.
Fig. 6 is a partial cross-sectional view of the rotary apparatus of embodiment 3.
Fig. 7 is an enlarged view of part VII of fig. 6 of the rotating device of embodiment 3.
Description of the reference numerals
10. A speed reducer; 11. an outer tube (outer member); 12A, 12B, bearings; 12Ai, inner ring; 12Ao, outer ring; 12Ar, balls (rolling elements); 13A, 1 st carrier module (inner member); 13B, 2 nd carrier module (inner member); 13Aa, shaft portion; 13Ab, flange portion; 13Aa-1, an outer peripheral surface; 30. 130, 230, spacers; 30a, an outer peripheral surface (positioning portion); 30b, an inner peripheral surface (interference avoidance portion); 35. bending corner (expanded diameter portion); 37. chamfer (interference avoidance part); 38. a positioning part; 47. annular concave portions (interference avoidance portions); 48. and a positioning part.
Detailed Description
Next, embodiments of the present invention will be described based on the drawings. In the embodiments described below, common parts are denoted by the same reference numerals, and overlapping description is partially omitted.
(Embodiment 1)
First, embodiment 1 shown in fig. 1 to 3 will be described.
Fig. 1 is a cross-sectional view of a rotary device employing the bearing assembly structure of the present embodiment.
The rotating device of the present embodiment is a decelerator 10 used for industrial robots, machine tools, and the like. An electric motor, not shown, as a rotation driving source is connected to an input portion of the speed reducer 10.
The speed reducer 10 includes: an outer cylinder 11 which doubles as a speed reducer case; a1 st carrier module 13A and a2 nd carrier module 13B rotatably held on the inner peripheral surface of the outer tube 11; a plurality of (e.g., three) crankshafts 14 rotatably supported by the 1 st carrier module 13A and the 2 nd carrier module 13B; and a1 st rotation gear 15A and a2 nd rotation gear 15B which rotate together with the two eccentric portions 14a, 14B of each crankshaft 14.
In the present embodiment, the outer tube 11 constitutes an outer member, and the 1st carrier module 13A and the 2nd carrier module 13B constitute an inner member.
The 1 st carrier module 13A is formed in a disk shape with holes. The 2 nd carrier module 13B has a disk-shaped base plate portion 13Ba with holes and a plurality of pillar portions 13Bb extending from end surfaces of the base plate portion 13Ba in the direction of the 1 st carrier module 13A. The end surfaces of the post portions 13Bb of the 2 nd carrier module 13B abut against the end surfaces of the 1 st carrier module 13A, and the post portions 13Bb are fastened and fixed to the 1 st carrier module 13A by bolts 16. The 1 st carrier module 13A is formed with a bolt penetration hole 17 through which the bolt 16 penetrates. A screw hole 18 for screw-coupling the shaft portion of the bolt 16 is formed in a position of the 2 nd carrier module 13B corresponding to the bolt through hole 17.
An axial gap is secured between the 1 st carrier module 13A and the 2 nd carrier module 13B at the base plate portion 13 Ba. The 1 st rotary gear 15A and the 2 nd rotary gear 15B are disposed in the gap.
Further, the 1 st rotation gear 15A and the 2 nd rotation gear 15B are formed with escape holes 19 through which the respective strut portions 13Bb of the 2 nd carrier module 13B pass. The escape hole 19 is formed to have an inner diameter sufficiently large relative to the strut portions 13Bb so that the strut portions 13Bb do not interfere with the turning operation of the 1 st turning gear 15A and the 2 nd turning gear 15B.
The outer tube 11 is disposed so as to straddle the outer peripheral surface of the 1 st carrier module 13A and the outer peripheral surface of the base plate portion 13Ba of the 2 nd carrier module 13B. Both end sides of the outer tube 11 in the axial direction are supported by the base plate portions 13Ba of the 1 st carrier block 13A and the 2 nd carrier block 13B via bearings 12A and 12B so as to be rotatable relative to each other. Further, a plurality of pin grooves (not shown) extending parallel to the rotation center axis c1 are formed in the inner peripheral surface of the central region (region facing the outer peripheral surfaces of the 1 st rotation gear 15A and the 2 nd rotation gear 15B) in the axial direction of the outer cylinder 11. Each pin groove rotatably accommodates a substantially cylindrical internal tooth pin 20. The plurality of inner teeth pins 20 attached to the inner peripheral surface of the outer tube 11 face the outer peripheral surfaces of the 1 st rotary gear 15A and the 2 nd rotary gear 15B.
The 1 st rotation gear 15A and the 2 nd rotation gear 15B are formed to have an outer diameter slightly smaller than the inner diameter of the outer tube 11. External teeth 15Aa, 15Ba are formed on the outer peripheral surfaces of the 1 st rotary gear 15A and the 2 nd rotary gear 15B, respectively, and are in contact with a plurality of inner teeth pins 20 arranged on the inner peripheral surface of the outer cylinder 11 in an engaged state. The number of teeth of the external teeth 15Aa, 15Ba formed on the outer peripheral surfaces of the 1 st and 2 nd rotary gears 15A, 15B is set to be slightly smaller (for example, one less) than the number of the internal tooth pins 20.
The plurality of crankshafts 14 are disposed on the same circumference centering on the rotation center axis c1 of the 1 st carrier module 13A and the 2 nd carrier module 13B. The crankshafts 14 are rotatably supported by the 1 st carrier module 13A and the 2 nd carrier module 13B via bearings 21. Eccentric portions 14a and 14B of the crankshafts 14 penetrate through the 1 st rotary gear 15A and the 2 nd rotary gear 15B, respectively. The eccentric portions 14a and 14B are rotatably fitted in support holes 22 formed in the 1 st and 2 nd rotary gears 15A and 15B, respectively, via eccentric portion bearings 23. The two eccentric portions 14a and 14b of each crankshaft 14 are eccentric so that the phases are offset 180 ° about the axis of the crankshaft 14.
When the plurality of crankshafts 14 are rotated in one direction by an external force, the eccentric portions 14A and 14B of the crankshafts 14 rotate in the same direction with a predetermined radius, and accordingly the 1 st rotation gear 14A and the 2 nd rotation gear 14B rotate in the same direction with the same radius. At this time, the external teeth 14Aa, 14Ba of the 1 st and 2 nd slewing gears 14A, 14B are in contact with the plurality of inner teeth pins 20 held on the inner periphery of the outer tube 11 so as to mesh with the plurality of inner teeth pins 20.
One end of each crankshaft 14 penetrates the 1 st carrier module 13A and protrudes outward in the axial direction of the 1 st carrier module 13A. A crank gear 28 is attached to an end of each crankshaft 14 protruding from the 1 st carrier module 13A. Each crank gear 28 meshes with an input gear, not shown. The input gear is rotated by a driving force of an electric motor, not shown.
In the reduction gear 10 of the present embodiment, the number of teeth of the external teeth 14Aa, 14Ba of the 1 st swing gear 14A and the 2 nd swing gear 14B is set to be slightly smaller than the number of the internal tooth pins 20 on the outer cylinder 11 side. Therefore, during the period in which the 1 st rotation gear 14A and the 2 nd rotation gear 14B rotate once, the 1 st rotation gear 14A and the 2 nd rotation gear 14B receive the reaction force in the rotation direction from the inner pin 20 on the outer cylinder 11 side and rotate in the direction opposite to the rotation direction by an amount corresponding to the predetermined pitch. As a result, the 1 st carrier module 13A and the 2 nd carrier module 13B, which are engaged with the 1 st rotary gear 14A and the 2 nd rotary gear 14B via the crankshaft 14, rotate together with the 1 st rotary gear 14A and the 2 nd rotary gear 14B in the same pitch in the same direction. As a result, the rotation of the crankshaft 14 is decelerated and outputted as the rotation of the 1 st carrier module 13A and the 2 nd carrier module 13B. In the present embodiment, since the eccentric portions 14A and 14B of the crankshafts 14 are eccentric so as to be offset 180 ° about the axis, the rotational phases of the 1 st and 2 nd rotation gears 14A and 14B are offset 180 °.
Fig. 2 is a partially enlarged sectional view showing the reduction gear 10 of fig. 1.
The bearing 12A interposed between the outer tube 11 and the 1 st carrier module 13A and the bearing 12B interposed between the outer tube 11 and the 2 nd carrier module 13B are constituted by, for example, angular contact ball bearings. The bearings 12A, 12B have: an outer ring 12Ao fixed to an end inner periphery of the outer tube 11; an inner ring 12Ai fixed to outer peripheral portions of the 1 st and 2 nd carrier modules 13A and 13B; and balls 12Ar as rolling elements interposed between the outer ring 12Ao and the inner ring 12 Ai. The straight line connecting the contact points of the inner ring 12Ai, the ball 12Ar, and the outer ring 12Ao of the bearings 12A, 12B is inclined at a predetermined angle with respect to a plane orthogonal to the axis of the bearings 12A, 12B. The bearings 12A, 12B are capable of supporting both radial loads and axial loads in one direction. In the case of the present embodiment, the bearing 12A supporting the 1 st carrier module 13A on the right side in fig. 2 receives an initial load axially inward (leftward in the drawing), and thus preload is given to the inner race 12 Ai.
The 1 st carrier module 13A has: a shaft portion 13Aa fitted and fixed to the inner ring 12Ai of the bearing 12A; and a flange portion 13Ab extending radially outward from one axial end (an end opposite to the 2 nd carrier module 13B) of the shaft portion 13 Aa. In the present embodiment, the outer peripheral surfaces of the shaft portion 13Aa and the flange portion 13Ab are each formed in a circular shape. The outer peripheral surface of the flange portion 13Ab is formed so that the outer diameter thereof is substantially the same as the maximum outer diameter portion of the inner ring 12Ai on the outer side in the axial direction.
An annular spacer 30 is interposed between the flange 13Ab and the axially outer end surface of the inner ring 12Ai, and is supported by pressing the inner ring 12Ai axially inward. The spacer 30 is formed of, for example, a metal plate material into a rectangular cross-sectional shape. The outer peripheral surface 30a of the spacer 30 is formed so that its outer diameter is equal to or smaller than the outer diameter of the flange portion 13Ab, and desirably is formed so that its outer diameter is equal to the outer diameter of the flange portion 13 Ab. In the present embodiment, the outer peripheral surface 30a of the spacer 30 is formed to have the same outer diameter as the flange portion 13 Ab. In addition, the inner peripheral surface 30b of the spacer 30 is formed to have an inner diameter sufficiently larger than the outer diameter of the shaft portion 13Aa of the 1 st carrier module 13A. An annular gap 40 is secured between the inner peripheral surface 30b of the spacer 30 and the outer peripheral surface 13Aa-1 of the shaft portion 13 Aa.
A curved corner portion 35 (a diameter-enlarged portion) in which the outer diameter of the outer peripheral surface of the shaft portion 13Aa increases as the shaft portion 13Aa is curved toward the flange portion 13Ab is formed at an end portion of the shaft portion 13Aa of the 1 st carrier module 13A on the flange portion 13Ab side. The bent corner 35 is formed between the shaft portion 13Aa and the flange portion 13Ab so that its outer diameter is larger than that of the shaft portion 13 Aa. The bent corner 35 improves the strength of the connection portion between the end of the shaft portion 13Aa and the flange portion 13 Ab.
The inner diameter of the inner peripheral surface 30b of the spacer 30 is set larger than the maximum outer diameter of the bent corner 35. The annular gap 40 secured between the inner peripheral surface 30b of the spacer 30 and the outer peripheral surface of the shaft portion 13Aa can prevent the inner peripheral surface 30b of the spacer 30 from interfering with the bent corner portion 35. In the present embodiment, the inner peripheral surface of the spacer 30 forming the annular gap 40 constitutes an interference avoiding portion. In addition, the outer peripheral surface 30a of the spacer 30 can be positioned with respect to the flange portion 13Ab in the radial direction at the time of assembly of the bearing 12A as will be discussed later. In the present embodiment, the outer peripheral surface 30a of the spacer 30 constitutes a positioning portion.
Fig. 3 is a cross-sectional view similar to fig. 2 showing an assembled state of the reduction gear 10. In fig. 3, the following states are shown: the spacer 30 is positioned on the 1 st carrier module 13A, and in this state, the spacer 30 is assembled together with the 1 st carrier module 13A to the inner race 12Ai of the bearing 12A. In fig. 3, the bearing 12A is fitted and fixed in advance to the inner periphery of the end portion of the outer tube 11.
As shown in fig. 3, when the spacer 30 and the 1 st carrier module 13A are assembled to the inner ring 12Ai of the bearing 12A, the annular spacer 30 is fitted over the shaft portion 13Aa of the 1 st carrier module 13A, and the spacer 30 is positioned at the end portion of the bearing 12A near the flange portion 13 Ab. In this state, the spacer 30 is positioned with respect to the flange portion 13Ab in the radial direction so that the outer peripheral surface of the spacer 30 coincides with the outer peripheral surface of the flange portion 13Ab in the radial direction.
The shaft portion 13Aa is fitted into the inner ring 12Ai of the bearing 12A in this state. The 1 st carrier module 13A is fastened and fixed to the 2 nd carrier module 13B by bolts 16 in this state. At this time, one end surface in the axial direction of the spacer 30 abuts against the end surface in the axial direction of the flange portion 13Ab, and the inner peripheral surface 30b is located radially outward of the bent corner portion 35.
In this way, when the 1 st carrier module 13A is assembled, the flange portion 13Ab of the 1 st carrier module 13A applies axial preload to the inner race 12Ai of the bearing 12A via the spacer 30. At this time, the spacer 30 is accurately positioned in the radial direction with respect to the 1 st carrier module 13A. Therefore, the preload acts equally on the inner race 12Ai in the radial direction.
As described above, in the bearing assembly structure of the present embodiment, the inner peripheral side of the spacer 30 constitutes the interference avoiding portion (annular gap 40) that avoids interference with the curved corner portion 35 (expanded diameter portion), and the outer peripheral surface of the spacer 30 is provided as a positioning portion that can position the relative position in the radial direction between the spacer and the 1 st carrier module 13A (inner member). Therefore, the spacer 30 can be positioned in the radial direction at the 1 st carrier module 13A without causing interference with the bent corner 35 of the 1 st carrier module 13A. Therefore, in the case of the bearing assembly structure according to the present embodiment, the position of the spacer 30 can be restrained from being displaced in the radial direction with respect to the 1 st carrier module 13A, and the support position (preload applying position) of the spacer 30 to the inner race 12Ai can be stabilized.
In the bearing assembly structure of the present embodiment, an annular gap 40 is secured between the inner peripheral surface 30b of the spacer 30 and the outer peripheral surface 13Aa-1 of the shaft portion 13Aa of the 1 st carrier module 13A, interference between the spacer 30 and the bent corner 35 is avoided by the gap 40, and the outer peripheral surface 30a of the spacer 30 is set as a positioning portion having an outer diameter equal to or smaller than the outer diameter of the flange portion 13 Ab. Therefore, when the 1 st carrier module 13A is assembled, the outer peripheral surface 30a of the spacer 30 and the outer peripheral surface of the flange portion 13Ab are aligned in the radial direction, so that the spacer 30 can be easily positioned in the 1 st carrier module 13A in the radial direction.
The outer diameter of the spacer 30 is not necessarily the same as the outer diameter of the flange portion 13Ab, but may be slightly smaller than the flange portion 13 Ab. In this case, when the 1 st carrier module 13A is assembled, the position of the spacer 30 can be prevented from being greatly deviated in the radial direction by restricting the position of the outer peripheral surface 30a of the spacer 30 to be positioned inside the outer peripheral surface of the flange portion 13 Ab. However, in the case where the outer diameter of the spacer 30 is formed to be the same as the outer diameter of the flange portion 13Ab as in the present embodiment, the spacer 30 can be easily and accurately positioned on the 1 st carrier module 13A.
(Embodiment 2)
Fig. 4 is a cross-sectional view of the reduction gear (rotating device) of the present embodiment, which is similar to fig. 2, and fig. 5 is an enlarged view of the V portion of fig. 4.
The structure of the spacer 130 of the bearing assembly structure of the present embodiment is different from that of embodiment 1. The spacer 130 has a chamfer 37 formed at an inner peripheral corner of the 1 st carrier module 13A near the flange 13 Ab. The chamfer 37 is formed of an annular tapered surface inclined radially outward from a substantially central position in the axial direction of the inner peripheral surface 130b of the spacer 130 toward the axially outer side. The chamfer portion 37 can avoid interference of the spacer 130 with the bent corner portion 35 of the 1 st carrier module 13A when the spacer 130 is sandwiched between the inner race 12Ai and the flange portion 13Ab of the bearing 12A. In the present embodiment, the chamfer portion 37 constitutes an interference avoiding portion.
Further, a positioning portion 38 that abuts against the outer peripheral surface 13Aa-1 of the shaft portion 13Aa of the 1 st carrier module 13A (the displacement in the radial direction is restricted by the outer peripheral surface 13Aa-1 of the shaft portion 13 Aa) is formed in a portion of the inner peripheral surface 130b of the spacer 130 adjacent to the chamfer portion 37 (a portion adjacent to the inner side in the axial direction of the chamfer portion 37). The positioning portion 38 has an inner diameter substantially equal to an outer diameter of the shaft portion 13 Aa. The positioning portion 38 is fitted to the outer peripheral surface of the shaft portion 13 Aa. The positioning portion 38 may be in point contact with the outer peripheral surface of the shaft portion 13Aa at three or more points. In the case of the present embodiment, the outer diameter of the outer peripheral surface 130a of the spacer 130 may be equal to or smaller than the outer diameter of the flange portion 13Ab or may be larger than the outer diameter of the flange portion 13 Ab.
As described above, in the bearing assembly structure of the present embodiment, when the spacer 130 is attached and fixed to the shaft portion 13Aa of the 1 st carrier module 13A, the positioning portion 38 of the inner peripheral surface of the spacer 130 abuts against the outer peripheral surface 13Aa-1 of the shaft portion 13 Aa. Thereby, the spacer 130 is positioned radially with respect to the 1 st carrier module 13A. On the other hand, since the chamfer 37 is provided at the inner peripheral corner of the spacer 130 near the flange portion 13Ab, the spacer 130 does not interfere with the bent corner 35 of the 1 st carrier module 13A.
Therefore, even when the bearing assembly structure of the present embodiment is employed, the position of the spacer 130 can be suppressed from being displaced in the radial direction with respect to the 1 st carrier module 13A, and the support position (preload applying position) of the spacer 130 to the inner race 12Ai can be stabilized.
(Embodiment 3)
Fig. 6 is a cross-sectional view of the decelerator (rotating device) of the present embodiment, which is similar to fig. 2 and 4, and fig. 7 is an enlarged view of a VII part of fig. 6.
The shape of the outer periphery of the end of the shaft portion 13Aa of the 1 st carrier module 13A in the bearing assembly structure of the present embodiment is different from those of embodiment 1 and embodiment 2. An annular recess 47 is formed in an end portion of the shaft portion 13a on the flange portion 13Ab side, and the annular recess 47 is recessed radially inward and connected to the bent corner 35 on the inner side of the recessed portion. In the present embodiment, the bent corner 35 is located in the annular recess 47, and the annular recess 47 constitutes an interference avoiding portion.
In addition, a positioning portion 48 that abuts against the inner peripheral surface 230b of the spacer 230 is formed in a portion adjacent to the annular recess 47 (a portion adjacent to the inner side in the axial direction of the annular recess 47) of the outer peripheral surface 13Aa-1 of the shaft portion 13Aa of the 1 st carrier module 13A. The inner diameter of the inner peripheral surface 230b of the spacer 230 is formed to be substantially the same as the outer diameter of the positioning portion 48 of the shaft portion 13 Aa. The spacer 230 is fitted to the positioning portion 48 of the shaft portion 13 Aa. The positioning portion 48 and the inner peripheral surface of the spacer 230 may be in point contact with each other at three or more points. In the case of the present embodiment, the outer diameter of the outer peripheral surface 230a of the spacer 230 may be equal to or smaller than the outer diameter of the flange portion 13Ab or may be larger than the outer diameter of the flange portion 13 Ab.
As described above, in the bearing assembly structure of the present embodiment, when the spacer 230 is attached and fixed to the shaft portion 13Aa of the 1 st carrier module 13A, the inner peripheral surface 230b of the spacer 230 abuts against the positioning portion 48 of the shaft portion 13 Aa. Thereby, the spacer 230 is positioned radially with respect to the 1 st carrier module 13A. Further, since the bent corner 35 of the shaft portion 13Aa is disposed inside the annular recess 47, the spacer 230 does not interfere with the bent corner 35.
Therefore, even when the bearing assembly structure of the present embodiment is employed, the position of the spacer 230 can be restrained from being displaced in the radial direction with respect to the 1 st carrier module 13A, and the support position (preload applying position) of the spacer 230 to the inner race 12Ai can be stabilized.
The present invention is not limited to the above-described embodiments, and various design changes may be made without departing from the spirit and scope of the present invention. For example, in the above-described embodiment, the bearing assembly structure of the present invention is used for the reduction gear, but the rotation equipment used is not limited to the reduction gear, and may be rotation equipment not provided with a reduction mechanism.

Claims (2)

1. A bearing assembly structure of a rotary apparatus, wherein,
The bearing assembly structure of the rotating equipment comprises:
A bearing having an inner race and an outer race;
An outer member to which the outer ring is fixed;
an inner member having a shaft portion to which the inner ring is fixed, a flange portion that expands in a radial direction from a position of the shaft portion axially outward of the inner ring, and a bent corner portion whose outer diameter increases as the outer peripheral surface is bent from an end portion of the shaft portion toward the flange portion;
A spacer disposed between the inner ring and the flange portion on an outer peripheral side of the shaft portion and the bent corner portion; and
An interference avoiding portion that avoids interference between the spacer and the bent corner portion,
An annular recess is provided at an end of the shaft portion, the annular recess being recessed radially inward and connected to the curved corner portion inside the recess,
The annular recess constitutes the interference avoiding portion,
The curved corner is formed inside the annular recess and is continuous with the annular recess.
2. The bearing assembly configuration of a rotary apparatus according to claim 1, wherein,
The bearing assembly structure of the rotating device further comprises a positioning part capable of positioning the relative position between the spacer and the inner member in the radial direction,
A portion of the outer peripheral surface of the shaft portion in a region adjacent to the annular recess constitutes the positioning portion that restricts movement of the spacer in the radial direction.
CN202010334166.2A 2019-05-31 2020-04-24 Bearing assembly structure of rotary equipment Active CN112013029B (en)

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JP2020197232A (en) 2020-12-10
TW202045838A (en) 2020-12-16

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