CN112013029A - Bearing assembling part structure of rotary equipment - Google Patents
Bearing assembling part structure of rotary equipment Download PDFInfo
- Publication number
- CN112013029A CN112013029A CN202010334166.2A CN202010334166A CN112013029A CN 112013029 A CN112013029 A CN 112013029A CN 202010334166 A CN202010334166 A CN 202010334166A CN 112013029 A CN112013029 A CN 112013029A
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- China
- Prior art keywords
- spacer
- peripheral surface
- bearing
- shaft portion
- outer peripheral
- Prior art date
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- 125000006850 spacer group Chemical group 0.000 claims abstract description 141
- 230000002093 peripheral effect Effects 0.000 claims description 108
- 239000003638 chemical reducing agent Substances 0.000 description 11
- 230000036316 preload Effects 0.000 description 11
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000005096 rolling process Methods 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 239000000758 substrate Substances 0.000 description 1
Images
Classifications
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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
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
- F16C25/06—Ball or roller bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- 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
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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
- F16H57/02—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2229/00—Setting preload
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/65—Gear shifting, change speed gear, gear box
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- 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
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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
- F16H57/02—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
Abstract
The invention provides a bearing assembly structure of a rotary device. The bearing assembly structure of a rotary machine according to 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 expanded from a position on the shaft portion axially outward of the bearing, and an expanded diameter portion formed between the shaft portion and the flange portion 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
Technical Field
The present invention relates to a bearing assembly structure for a rotary device such as 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 (see, for example, patent document 1).
The speed reducer (rotating device) described in patent document 1 includes: an outer cylinder (outer member); a carrier module (inner member) rotatably supported inside the outer tube; a crankshaft rotatably supported at a position radially offset from a rotation center of the carrier module; and a main speed reduction mechanism for reducing the rotation speed of the crankshaft to rotate the carrier module itself. The main speed reduction mechanism includes a rotation gear that rotates integrally with the eccentric portion of the crankshaft, and a plurality of inner pins held on the inner circumferential surface of the outer cylinder. The rotary gear has external teeth that are engaged with the internal gear pins in a meshed 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 rotary gear makes one rotation together with the crankshaft, the carrier module rotates by a predetermined pitch in the direction opposite to the rotation 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 rotating body.
In the above-described reduction gear, the carrier module is supported by the outer cylinder via a bearing such as an angular ball bearing. The outer ring of the bearing is press-fitted and fixed to the inner periphery of the end of the outer cylinder while restricting the 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 that protrudes radially outward from the main body portion is provided at one axial end side of the main body portion of the carrier module. An annular spacer that applies an 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 cylinder, the flange portion of the carrier module presses the spacer in the axial direction, and the spacer applies a preload to the inner ring of the bearing.
Further, a bent 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) of the carrier module is bent toward the flange portion is provided at an end portion in the axial direction. This improves the strength between the body portion and the flange portion.
Documents of the prior art
Patent document
Patent document 1: japanese patent No. 5917421
Disclosure of Invention
Problems to be solved by the invention
In the reduction gear (rotating device) described in patent document 1, a bent corner portion having an outer diameter larger than that of the other portion of the main body portion is provided at an end portion of the main body portion of the carrier module (inner member) in the axial direction. Therefore, when the outer cylinder (outer member) and the carrier module (inner member) are assembled, the spacer interferes with the curved corner portion on the carrier module side, and the preload applied to the bearing by the spacer may become unstable.
The invention provides a bearing assembly structure of a rotating device, which can stabilize the pre-pressure applied to a bearing by a spacer.
Means for solving the problems
The bearing assembly structure of a rotary machine 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 expanded from a position on the shaft portion axially outward of the bearing, 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; 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 machine 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 race is fixed; an inner member having a shaft portion to which the inner ring is fixed, a flange portion that is radially enlarged from a position on the shaft portion axially outward of the inner ring, and an enlarged diameter portion formed between the shaft portion and the flange portion so that an outer diameter is 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 in the spacer and avoiding interference between the spacer and the enlarged 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 to the outer member and the inner member together with the bearing, the pressing load of the flange portion acts on the inner ring of the bearing via the spacer. In this case, since the spacer has the interference avoiding portion, the spacer does not interfere with the enlarged diameter portion of the inner member. Further, since either the inner peripheral surface or the outer peripheral surface of the spacer is provided as the positioning portion in the radial direction with respect to the inner member, the spacer is positioned in the radial direction with respect to the inner member by either the inner peripheral surface or the outer peripheral surface of the spacer at the time of assembly, and the position of the spacer can be suppressed from being displaced in the radial direction with respect to the inner member. As a result, the spacer stabilizes the support position (preload application position) of the inner ring.
The interference avoiding portion may be formed by an annular gap formed between an inner peripheral surface of the spacer and outer peripheral surfaces of the shaft portion and the enlarged diameter 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 to constitute the positioning portion.
In this case, for example, when the spacer is 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 and the outer peripheral surface of the flange portion are aligned 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. At this time, 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 that of the flange portion.
In this case, when the spacer is 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 and the outer peripheral surface of the flange portion are aligned in the radial direction. Thereby, the spacer is positioned in the radial direction with respect to the inner member.
The positioning portion may be provided in a region of the inner peripheral surface of the spacer that does not face the enlarged diameter portion, the positioning portion being configured to restrict movement of the spacer in the radial direction by the outer peripheral surface of the shaft portion, and the interference avoiding portion may be provided in a region of the inner peripheral surface of the spacer that faces the enlarged diameter portion, the interference avoiding portion having an inner diameter larger than an outer diameter of 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. Further, since the interference avoiding portion is present in the region of the inner peripheral surface of the spacer that faces the enlarged diameter portion, the spacer does not interfere with the enlarged diameter portion of the inner member.
The interference avoiding portion may be formed by a chamfered portion formed in a region of the inner peripheral surface of the spacer facing the enlarged diameter portion.
The enlarged diameter portion may be a curved corner portion whose outer peripheral surface increases in outer diameter as it curves from an end portion of the shaft portion toward the flange portion.
In this case, the strength of the connecting portion between the shaft portion and the flange portion can be increased by the curved corner portion, and interference between the inner peripheral surface of the spacer and the curved corner portion can be avoided.
In addition, a bearing assembly structure of a rotary machine 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 race 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 on the shaft portion axially outward of the inner ring, and a curved corner portion in which an outer diameter of an outer peripheral surface increases as the outer peripheral surface curves from an end 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 curved corner portion; an interference avoiding portion that avoids interference between the spacer and the bent 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 recessed portion that is recessed inward in the radial direction and is continuous with the curved corner portion inside the recess is present at an end portion of the shaft portion, the annular recessed portion constitutes the interference avoiding portion, and a portion of an outer peripheral surface of the shaft portion in a region adjacent to the annular recessed 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 recessed portion. Further, since the curved corner portion of the end portion of the shaft portion is formed so as to be continuous with the annular recessed portion inside the annular recessed portion, the inner peripheral surface of the spacer does not interfere with the curved 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 rotary machine described above can stabilize the preload applied to the bearing by the spacer.
Drawings
Fig. 1 is a longitudinal sectional view of the rotating apparatus of embodiment 1.
Fig. 2 is a partially enlarged cross-sectional view of fig. 1 of the rotating apparatus according to embodiment 1.
Fig. 3 is a sectional view similar to fig. 2 showing an assembled state of the rotating apparatus according to embodiment 1.
Fig. 4 is a partial sectional view of the rotating apparatus of embodiment 2.
Fig. 5 is an enlarged view of a V portion of fig. 4 of the rotating apparatus of embodiment 2.
Fig. 6 is a partial sectional view of the rotating apparatus of embodiment 3.
Fig. 7 is an enlarged view of a section VII of fig. 6 of the rotating apparatus of embodiment 3.
Description of the reference numerals
10. A speed reducer; 11. an outer cylinder (outer member); 12A, 12B, bearings; 12Ai, inner ring; 12Ao, an outer ring; 12Ar, balls (rolling elements); 13A, 1 st gear rack module (inner member); 13B, 2 nd carrier module (inner member); 13Aa, a shaft portion; 13Ab, flange portion; 13Aa-1, outer peripheral surface; 30. 130, 230, spacers; 30a, an outer peripheral surface (positioning portion); 30b, an inner peripheral surface (interference avoiding portion); 35. a curved corner portion (diameter-enlarged portion); 37. chamfered portions (interference avoiding portions); 38. a positioning part; 47. an annular recess (interference avoidance portion); 48. a positioning part.
Detailed Description
Next, embodiments of the present invention will be described with reference to the drawings. In the embodiments 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 to 3 will be described.
Fig. 1 is a sectional view of a rotary machine that employs a bearing assembly structure of the present embodiment.
The rotary machine of the present embodiment is a speed reducer 10 used for industrial robots, machine tools, and the like. An electric motor, not shown, is connected to the input portion of the reduction gear 10 as a rotation drive source.
The speed reducer 10 includes: an outer cylinder 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 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 a 1 st slewing gear 15A and a 2 nd slewing gear 15B that revolve together with the two eccentric portions 14a, 14B of each crankshaft 14.
In the present embodiment, the outer cylinder 11 constitutes an outer member, and the 1 st carrier module 13A and the 2 nd carrier module 13B constitute an inner member.
The 1 st carrier module 13A is formed in a perforated disc shape. The 2 nd carrier module 13B includes a perforated disc-shaped base plate portion 13Ba and a plurality of column portions 13Bb extending from an end surface of the base plate portion 13Ba in a direction toward the 1 st carrier module 13A. An end surface of the column portion 13Bb of the 2 nd carrier module 13B abuts on an end surface of the 1 st gear frame module 13A, and each column portion 13Bb is fastened and fixed to the 1 st gear frame module 13A by a bolt 16. A bolt insertion hole 17 through which the bolt 16 is inserted is formed in the 1 st gear frame module 13A. A screw hole 18 to which the shaft portion of the bolt 16 is screwed is formed in the 2 nd carrier module 13B at a position corresponding to the bolt through hole 17.
An axial gap is secured between the base plate portions 13Ba of the 1 st and 2 nd carrier modules 13A and 13B. The 1 st slewing gear 15A and the 2 nd slewing gear 15B are disposed in the gap.
Further, relief holes 19 through which the respective column portions 13Bb of the 2 nd carrier module 13B pass are formed in the 1 st slewing gear 15A and the 2 nd slewing gear 15B. The relief hole 19 is formed with an inner diameter sufficiently large for the column portion 13Bb so that each column portion 13Bb does not interfere with the turning operation of the 1 st turning gear 15A and the 2 nd turning gear 15B.
The outer cylinder 11 is disposed across the outer peripheral surface of the 1 st carrier module 13A and the outer peripheral surface of the substrate portion 13Ba of the 2 nd carrier module 13B. Both end sides in the axial direction of the outer cylinder 11 are relatively rotatably 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. 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 in the axial direction of the outer tube 11 (the region facing the outer peripheral surfaces of the 1 st and 2 nd rotary gears 15A, 15B). A substantially cylindrical internal gear pin 20 is rotatably housed in each pin groove. The plurality of internal gear pins 20 attached to the inner peripheral surface of the outer cylinder 11 face the outer peripheral surfaces of the 1 st slewing gear 15A and the 2 nd slewing gear 15B, respectively.
The 1 st slewing gear 15A and the 2 nd slewing gear 15B are formed to have an outer diameter slightly smaller than the inner diameter of the outer cylinder 11. Outer teeth 15Aa and 15Ba that are in contact with a plurality of inner-tooth pins 20 arranged on the inner circumferential surface of the outer cylinder 11 in a meshed state are formed on the outer circumferential surfaces of the 1 st slewing gear 15A and the 2 nd slewing gear 15B, respectively. The number of teeth of the external teeth 15Aa and 15Ba formed on the outer peripheral surfaces of the 1 st and 2 nd rotary gears 15A and 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 a bearing 21. The eccentric portions 14a and 14B of the crankshafts 14 penetrate the 1 st and 2 nd rotary gears 15A and 15B, respectively. The eccentric portions 14a and 14B are rotatably fitted into support holes 22 formed in the 1 st and 2 nd rotary gears 15A and 15B via eccentric portion bearings 23. The two eccentric portions 14a and 14b of each crankshaft 14 are eccentric so as to be out of phase by 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 at a predetermined radius, and accordingly, the 1 st slewing gear 14A and the 2 nd slewing gear 14B rotate in the same direction at the same radius. At this time, the external teeth 14Aa and 14Ba of the 1 st and 2 nd rotating gears 14A and 14B respectively contact the plurality of internal-tooth pins 20 held on the inner periphery of the outer cylinder 11 so as to mesh with the plurality of internal-tooth pins 20.
One end of each crankshaft 14 penetrates the 1 st carrier block 13A and protrudes outward in the axial direction of the 1 st carrier block 13A. A crank gear 28 is attached to an end of each crankshaft 14 protruding from the 1 st carrier block 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 and 14Ba of the 1 st slewing gear 14A and the 2 nd slewing gear 14B is set to be slightly smaller than the number of internal pins 20 on the outer cylinder 11 side. Therefore, during one rotation of the 1 st slewing gear 14A and the 2 nd slewing gear 14B, the 1 st slewing gear 14A and the 2 nd slewing gear 14B receive a reaction force in the rotation direction from the internal gear pins 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 block 13A and the 2 nd carrier block 13B, which are engaged with the 1 st slewing gear 14A and the 2 nd slewing gear 14B via the crankshaft 14, rotate in the same direction at the same pitch as the 1 st slewing gear 14A and the 2 nd slewing gear 14B. 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, since the eccentric portions 14A and 14B of the crankshafts 14 are eccentric so as to be offset by 180 ° about the axis, the rotational phases of the 1 st and 2 nd slewing gears 14A and 14B are offset by 180 °.
Fig. 2 is an enlarged sectional view of a part of the reduction gear 10 of fig. 1.
The bearing 12A interposed between the outer cylinder 11 and the 1 st carrier module 13A and the bearing 12B interposed between the outer cylinder 11 and the 2 nd carrier module 13B are formed of, for example, angular ball bearings. The bearings 12A, 12B have: an outer ring 12Ao fixed to the inner periphery of the end of the outer tube 11; an inner ring 12Ai fixed to outer peripheral portions of the 1 st carrier module 13A and the 2 nd carrier module 13B; and balls 12Ar as rolling elements interposed between the outer race 12Ao and the inner race 12 Ai. The straight line connecting the contact points of the inner ring 12Ai, the balls 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 axes 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 block 13A on the right side in fig. 2 receives an initial load in the axial direction inward (leftward in the drawing), and applies a preload to the inner ring 12 Ai.
The 1 st carrier module 13A includes: a shaft portion 13Aa fitted and fixed to the inner ring 12Ai of the bearing 12A; and a flange portion 13Ab that extends radially outward from one end (an end portion on the opposite side from the 2 nd carrier module 13B) in the axial direction 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 formed in a circular shape. The outer peripheral surface of the flange portion 13Ab is formed to have an outer diameter substantially equal to the maximum outer diameter portion on the outside in the axial direction of the inner ring 12 Ai.
An annular spacer 30 for pressing and supporting the inner ring 12Ai inward in the axial direction is interposed between the flange portion 13Ab and the axially outer end surface of the inner ring 12 Ai. The spacer 30 is formed of a plate material made of, for example, metal in a rectangular shape in cross section. The outer peripheral surface 30a of the spacer 30 is formed to have an outer diameter equal to or smaller than the outer diameter of the flange portion 13Ab, and is desirably formed to have an outer diameter 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 that of the flange portion 13 Ab. 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 bent corner portion 35 (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 bent toward the flange portion 13Ab is formed at the end portion of the shaft portion 13Aa of the 1 st carrier module 13A on the flange portion 13Ab side. The bent corner portion 35 is formed between the shaft portion 13Aa and the flange portion 13Ab so as to have an outer diameter larger than that of the shaft portion 13 Aa. The bent corner portion 35 increases the strength of the connection portion between the end portion 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 curved corner portion 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 avoid interference between the inner peripheral surface 30b of the spacer 30 and the curved 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 radially with respect to the flange portion 13Ab when the bearing 12A is assembled, 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 sectional view similar to fig. 2 showing an assembled state of the speed reducer 10. The following states are shown in fig. 3: the spacer 30 is positioned at the 1 st carrier block 13A, and in this state, the spacer 30 is assembled together with the 1 st carrier block 13A to the inner ring 12Ai of the bearing 12A. In fig. 3, a bearing 12A is fitted and fixed to the inner periphery of the end of the outer tube 11 in advance.
As shown in fig. 3, when the spacer 30 and the 1 st carrier block 13A are assembled to the inner ring 12Ai of the bearing 12A, the annular spacer 30 is externally fitted to the shaft portion 13Aa of the 1 st carrier block 13A, and the spacer 30 is positioned at the end of the bearing 12A near the flange portion 13 Ab. In this state, the spacer 30 is positioned radially with respect to the flange portion 13Ab such that the outer peripheral surface of the spacer 30 and the outer peripheral surface of the flange portion 13Ab radially coincide.
The shaft portion 13Aa is fitted into the inner race 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 the bolts 16 in this state. At this time, one end surface in the axial direction of the spacer 30 abuts on an end surface in the axial direction of the flange portion 13Ab, and the inner peripheral surface 30b is positioned radially outward of the bent corner portion 35.
When the 1 st carrier block 13A is assembled in this way, the flange portion 13Ab of the 1 st carrier block 13A applies an 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 block 13A. Therefore, the preload acts on the inner ring 12Ai equally 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 (enlarged diameter portion), and the outer peripheral surface of the spacer 30 is provided as the positioning portion that can position the relative position in the radial direction between the spacer and the 1 st carrier block 13A (inner member). Therefore, the spacer 30 can be positioned in the 1 st carrier block 13A in the radial direction without causing interference with the curved corner portion 35 of the 1 st carrier block 13A. Therefore, when the bearing assembly structure of the present embodiment is employed, the position of the spacer 30 can be suppressed from being displaced in the radial direction with respect to the 1 st carrier block 13A, and the support position (preload application position) of the spacer 30 with respect to the inner ring 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 block 13A, interference between the spacer 30 and the bent corner portion 35 is avoided by the gap 40, and the outer peripheral surface 30a of the spacer 30 is 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 block 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, whereby the spacer 30 can be easily positioned in the radial direction on the 1 st carrier block 13A.
The outer diameter of the spacer 30 is not necessarily the same as the outer diameter of the flange portion 13Ab, and 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 is restricted so that the outer peripheral surface 30a of the spacer 30 is positioned inside the outer peripheral surface of the flange portion 13Ab, and the assembly can be performed so that the position of the spacer 30 is prevented from being largely deviated in the radial direction. However, when the outer diameter of the spacer 30 is set 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 in the 1 st carrier block 13A.
(embodiment 2)
Fig. 4 is a cross-sectional view of the speed reducer (rotating device) of the present embodiment similar to fig. 2, and fig. 5 is an enlarged view of a 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 chamfered portion 37 formed at an inner peripheral corner portion of the 1 st carrier block 13A near the flange portion 13 Ab. The chamfered portion 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 axial outer side. The chamfered portion 37 can avoid interference between the spacer 130 and the bent corner portion 35 of the 1 st carrier block 13A when the spacer 130 is interposed between the inner ring 12Ai and the flange portion 13Ab of the bearing 12A. In the present embodiment, the chamfered portion 37 constitutes an interference avoiding portion.
Further, a positioning portion 38 (radially restricted from displacement by the outer peripheral surface 13Aa-1 of the shaft portion 13 Aa) that abuts against the outer peripheral surface 13Aa-1 of the shaft portion 13Aa of the 1 st carrier module 13A is formed in a portion of the inner peripheral surface 130b of the spacer 130 adjacent to the chamfered portion 37 (a portion adjacent to the inside in the axial direction of the chamfered portion 37). The inner diameter of the positioning portion 38 is formed to be substantially the same as the 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 present embodiment, the outer peripheral surface 130a of the spacer 130 may have an outer diameter equal to or smaller than the outer diameter of the flange portion 13Ab, or may have an outer diameter 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 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 in the radial direction with respect to the 1 st carrier module 13A. On the other hand, since there is a chamfered portion 37 at the inner peripheral corner portion of the spacer 130 near the flange portion 13Ab, the spacer 130 does not interfere with the curved corner portion 35 of the 1 st carrier block 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 block 13A, and the support position (preload application position) of the spacer 130 with respect to the inner ring 12Ai can be stabilized.
(embodiment 3)
Fig. 6 is a cross-sectional view of the speed reducer (rotating device) of the present embodiment similar to fig. 2 and 4, and fig. 7 is an enlarged view of a VII portion of fig. 6.
The shape of the outer periphery of the end portion of the shaft portion 13Aa of the 1 st gear frame module 13A of the bearing assembly portion structure of the present embodiment is different from those of the 1 st and 2 nd embodiments. 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 is connected to the curved corner portion 35 inside the recessed portion. In the present embodiment, the curved corner portion 35 is located inside the annular recessed portion 47, and the annular recessed portion 47 constitutes an interference avoiding portion.
Further, a positioning portion 48 that abuts against the inner peripheral surface 230b of the spacer 230 is formed in a portion of the outer peripheral surface 13Aa-1 of the shaft portion 13Aa of the 1 st carrier module 13A that is adjacent to the annular recessed portion 47 (a portion that is adjacent to the inside in the axial direction of the annular recessed portion 47). The inner peripheral surface 230b of the spacer 230 has an inner diameter substantially equal to 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 circumferential surface of the spacer 230 may be in point contact at three or more points. In the present embodiment, the outer peripheral surface 230a of the spacer 230 may have an outer diameter equal to or smaller than the outer diameter of the flange portion 13Ab, or may have an outer diameter 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 fixed to the shaft portion 13Aa of the 1 st carrier module 13A, the inner peripheral surface 230b of the spacer 230 abuts on the positioning portion 48 of the shaft portion 13 Aa. Thereby, the spacer 230 is positioned in the radial direction with respect to the 1 st carrier block 13A. Further, since the bent corner portion 35 of the shaft portion 13Aa is disposed inside the annular recess 47, the spacer 230 does not interfere with the bent corner portion 35.
Therefore, even when the bearing assembly structure of the present embodiment is employed, the position of the spacer 230 can be suppressed from being displaced in the radial direction with respect to the 1 st carrier block 13A, and the support position (preload application position) of the spacer 230 with respect to the inner ring 12Ai can be stabilized.
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 present invention. For example, in the above-described embodiment, the bearing assembly structure of the present invention is applied to the speed reducer, but the rotating machine to be used is not limited to the speed reducer, and may be a rotating machine without a speed reduction mechanism.
Claims (9)
1. A bearing assembling portion structure of a rotary apparatus, wherein,
the bearing assembly structure of the rotary equipment 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 expanded from a position on the shaft portion axially outward of the bearing, 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; and
an annular spacer disposed between the bearing and the flange portion,
the spacer is disposed so as to avoid interference with the enlarged diameter portion.
2. The bearing assembly configuration of a rotary apparatus according to claim 1,
the inner peripheral surface of the spacer is formed to have an inner diameter larger than an outer diameter of the enlarged diameter portion.
3. A bearing assembling portion structure of a rotary apparatus, wherein,
the bearing assembly structure of the rotary equipment comprises:
a bearing having an inner race and an outer race;
an outer member to which the outer race is fixed;
an inner member having a shaft portion to which the inner ring is fixed, a flange portion that is radially enlarged from a position on the shaft portion axially outward of the inner ring, and an enlarged diameter portion formed between the shaft portion and the flange portion so that an outer diameter is 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 in the spacer and avoiding interference between the spacer and the enlarged diameter portion; and
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.
4. The bearing assembly configuration of a rotary apparatus according to claim 3,
an annular gap is formed between an inner peripheral surface of the spacer and outer peripheral surfaces of the shaft portion and the enlarged diameter portion to constitute the interference avoiding portion,
the outer peripheral surface of the spacer is formed so that the outer diameter thereof is equal to or smaller than the outer diameter of the flange portion, and constitutes the positioning portion.
5. The bearing assembly configuration of a rotary apparatus according to claim 4,
the outer peripheral surface of the spacer is formed to have the same outer diameter as that of the flange portion.
6. The bearing assembly configuration of a rotary apparatus according to claim 3,
the spacer has a positioning portion in a region of an inner peripheral surface of the spacer not opposed to the enlarged diameter portion, the positioning portion being configured to restrict movement of the spacer in a radial direction by an outer peripheral surface of the shaft portion,
the interference avoiding portion has an inner diameter larger than an outer diameter of the enlarged diameter portion in a region of the inner peripheral surface of the spacer facing the enlarged diameter portion.
7. The bearing assembly configuration of a rotary apparatus according to claim 6,
the interference avoiding portion is formed of a chamfered portion formed in a region of an inner peripheral surface of the spacer that faces the enlarged diameter portion.
8. The bearing assembly structure of a rotary apparatus according to any one of claims 1 to 7,
the enlarged diameter portion is a curved corner portion whose outer peripheral surface increases in outer diameter as it curves from an end portion of the shaft portion toward the flange portion.
9. A bearing assembling portion structure of a rotary apparatus, wherein,
the bearing assembly structure of the rotary equipment comprises:
a bearing having an inner race and an outer race;
an outer member to which the outer race 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 on the shaft portion axially outward of the inner ring, and a curved corner portion in which an outer diameter of an outer peripheral surface increases as the outer peripheral surface curves from an end 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 curved corner portion;
an interference avoiding portion that avoids interference between the spacer and the bent corner portion; and
a positioning portion capable of positioning a relative position in a radial direction between the spacer and the inner member,
an annular recessed portion that is recessed radially inward and is continuous with the curved corner portion inside the recess is provided at an end of the shaft portion,
the annular recessed portion constitutes the interference avoiding portion,
a portion of the outer peripheral surface of the shaft portion in a region adjacent to the annular recessed portion constitutes the positioning portion that restricts movement of the spacer in the radial direction.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2019102686A JP7444551B2 (en) | 2019-05-31 | 2019-05-31 | Bearing assembly structure of rotating equipment |
| JP2019-102686 | 2019-05-31 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112013029A true CN112013029A (en) | 2020-12-01 |
Family
ID=73264971
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010334166.2A Pending CN112013029A (en) | 2019-05-31 | 2020-04-24 | Bearing assembling part structure of rotary equipment |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP7444551B2 (en) |
| CN (1) | CN112013029A (en) |
| DE (1) | DE102020205366A1 (en) |
| TW (1) | TW202045838A (en) |
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| JP2002013539A (en) * | 2000-06-29 | 2002-01-18 | Koyo Seiko Co Ltd | Rolling bearing and assembly of the same with stepped shaft |
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| JP6550947B2 (en) * | 2015-06-11 | 2019-07-31 | 株式会社Ihi | Rotating machine |
| DE112016002607B4 (en) * | 2015-06-11 | 2022-03-31 | Ihi Corporation | turbocharger |
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2019
- 2019-05-31 JP JP2019102686A patent/JP7444551B2/en active Active
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2020
- 2020-04-21 TW TW109113298A patent/TW202045838A/en unknown
- 2020-04-24 CN CN202010334166.2A patent/CN112013029A/en active Pending
- 2020-04-28 DE DE102020205366.9A patent/DE102020205366A1/en active Pending
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|---|---|---|---|---|
| JP2000229501A (en) * | 1999-02-10 | 2000-08-22 | Nsk Ltd | Wheel supporting hub unit |
| JP2001065584A (en) * | 1999-08-25 | 2001-03-16 | Showa Corp | Bearing structure |
| JP2002161948A (en) * | 2000-11-24 | 2002-06-07 | Tsubakimoto Chain Co | Inner pin supporting structure for planetary gear |
| CA2384532A1 (en) * | 2001-05-03 | 2002-11-03 | Merlyn Duane Bass | Arrangement for clamping inner bearing race to non-circular section shaft and for preventing axial load in the bearing, axial creep and rotational knock |
| JP2003194038A (en) * | 2001-12-26 | 2003-07-09 | Musashi Seimitsu Ind Co Ltd | Ball joint |
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| JP2015175388A (en) * | 2014-03-13 | 2015-10-05 | ナブテスコ株式会社 | Bearing pre-load mechanism of reduction gear |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2020197232A (en) | 2020-12-10 |
| TW202045838A (en) | 2020-12-16 |
| DE102020205366A1 (en) | 2020-12-03 |
| JP7444551B2 (en) | 2024-03-06 |
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