CN102996771B - Eccentric oscillating-type speed reducer - Google Patents

Eccentric oscillating-type speed reducer Download PDF

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Publication number
CN102996771B
CN102996771B CN201210344641.XA CN201210344641A CN102996771B CN 102996771 B CN102996771 B CN 102996771B CN 201210344641 A CN201210344641 A CN 201210344641A CN 102996771 B CN102996771 B CN 102996771B
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eccentric
lubrication channel
speed reducer
bearing
type speed
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CN201210344641.XA
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CN102996771A (en
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石川哲三
芳贺卓
志津庆刚
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Sumitomo Heavy Industries Ltd
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Sumitomo Heavy Industries Ltd
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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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • 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
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0469—Bearings or seals
    • F16H57/0471—Bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • F16H2001/323—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear comprising eccentric crankshafts driving or driven by a gearing

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Details Of Gearings (AREA)
  • Retarders (AREA)

Abstract

The invention provides a kind of eccentric oscillating-type speed reducer, it improves the lubricity of the bearing of supporting eccentric shaft relatively, and extends the life-span of this bearing further.Eccentric oscillating-type speed reducer of the present invention to possess in eccentric shaft (271) and is formed vertically and the 1st lubrication channel (222) that lubricant oil can be made to flow into and being communicated with the 1st lubrication channel (222) and the 2nd lubrication channel (224) radially extended to form, and the 2nd lubrication channel (224) is opening between the 1st, the 2nd roller bearing (278,279) and the 1st, the 2nd eccentric body (214,216).

Description

Eccentric oscillating-type speed reducer
Technical field
The present invention relates to a kind of eccentric oscillating-type speed reducer.
Background technique
Eccentric oscillating-type speed reducer is disclosed in patent documentation 1.
In this speed reducer, multiple external gear spread configuration vertically, and engage with internal gear while swinging each via the eccentric body being arranged on eccentric shaft.The number of teeth difference of the internal tooth of internal gear and the external tooth of external gear is set as " 1 ".And, be configured to when external gear during side oscillation, takes out the relative rotation of internal gear and the external gear produced according to this number of teeth difference in internal gear.
Eccentric shaft is supported on wheel carrier by bearing.
Patent documentation 1: Japanese Unexamined Patent Publication 2008-202764 publication (Fig. 1)
In order to ensure the life-span of the bearing of this eccentric shaft of supporting, fully supply oiling agent to this bearing and become important.
Summary of the invention
Problem of the present invention is to provide a kind of eccentric oscillating-type speed reducer, and it improves the lubricity of the bearing for supporting eccentric shaft, and extends the life-span of this bearing further.
The present invention solves above-mentioned problem by being set to following structure: a kind of eccentric oscillating-type speed reducer, it is possessed external gear, the internal gear engaged with this external gear, has the eccentric shaft of the eccentric body that described external gear is swung and supported the wheel support body of this eccentric shaft by bearing, this eccentric oscillating-type speed reducer possesses: the 1st lubrication channel, formed vertically in described eccentric shaft, and lubricant oil can be made to flow into; And the 2nd lubrication channel, be communicated with the 1st lubrication channel, and radially extend to form, the 2nd lubrication channel opening between described bearing and eccentric body.
In the present invention, in eccentric shaft, form the 1st lubrication channel vertically, radially form the 2nd lubrication channel.
Further, the 2nd lubrication channel opening between the bearing and eccentric body of supporting eccentric shaft is made.Therefore, it is possible to supply sufficient oiling agent to the bearing of supporting eccentric shaft, and the life-span of this bearing can be improved.Invention effect
According to the present invention, in eccentric oscillating-type speed reducer, sufficient oiling agent can be supplied to the bearing of supporting eccentric shaft, and the life-span of this bearing can be extended further.
Accompanying drawing explanation
Fig. 1 represents to understand the present invention and the global sections figure of an example of eccentric oscillating-type speed reducer as a reference.
Fig. 2 is the sectional view of the arrow II-II line along Fig. 1, and represents the sectional view of maximum load position when rotating forward.
Fig. 3 is the sectional view of the arrow III-III line along Fig. 1, and represents the sectional view of maximum load position when reversing.
Fig. 4 represents to understand the present invention and the global sections figure of another example of eccentric oscillating-type speed reducer as a reference.
Fig. 5 is the major component amplification sectional view of the eccentric oscillating-type speed reducer of Fig. 4.
Fig. 6 is the global sections figure of the eccentric oscillating-type speed reducer involved by an example of embodiments of the present invention.
Fig. 7 is the major component amplification sectional view of the eccentric oscillating-type speed reducer of Fig. 6.
In figure: 10,12-the 1st, the 2nd external gear, 14,16-the 1st, the 2nd eccentric body, 18-internal gear, 20-input shaft (eccentric shaft), 22-the 1st lubrication channel, 24-the 2nd lubrication channel, 24X-the 1st linear channel, 24Y-the 2nd linear channel, 28,30-the 1st, the 2nd eccentric body bearing, 36,38-the 1st, the 2nd ball bearing, 40,42-the 1st, the 2nd takes turns support body, 52,54-main bearing.
Embodiment
Below, first with reference to figure 1 ~ Fig. 5, to in order to understand the present invention and an example (hereinafter referred to as reference example) of eccentric oscillating-type speed reducer is as a reference described, on this basis, according to Fig. 6 and Fig. 7, one example of embodiments of the present invention is described in detail.
Fig. 1 is the global sections figure of the eccentric oscillating-type speed reducer involved by reference example, Fig. 2 is the sectional view of the arrow II-II line along Fig. 1, and representing the sectional view of maximum load position when rotating forward, Fig. 3 is the same sectional view representing maximum load position when reversing.
This speed reducer G1 is the 1st, the 2nd external gear 10,12 spread configuration vertically, and the eccentric oscillating-type speed reducer engaged with internal gear 18 while swinging each via the 1st, the 2nd eccentric body 14,16.Therefore, speed reducer G1 possesses the input shaft 20 being also used as " eccentric shaft " being formed with the 1st, the 2nd eccentric body 14,16 with the 1st, the 2nd external gear 10,12 accordingly.
Have the 1st lubrication channel 22 that formed vertically in input shaft 20 and be communicated with the 1st lubrication channel 22 and 4 article of the 2nd lubrication channel 24(24A ~ 24D radially extended to form).2nd lubrication channel 24 is opening between the 1st eccentric body 14 and the 2nd eccentric body 16.
Below, be described successively from the structure of this speed reducer G1.
With reference to figure 1, Fig. 2,2 the 1st, the 2nd eccentric body 14,16 is integrally formed on the input shaft (eccentric shaft) 20 of speed reducer G1.That is, input shaft 20 plays a role as the centre-crank formula " eccentric shaft " of the axle center O1 being configured at internal gear 18.
1st, in the 2nd eccentric body 14,16, its periphery is eccentric relative to the axle center (identical with O1) of input shaft 20.1st, the eccentric phase skew 180 degree of the 2nd eccentric body 14,16, the 1st, the 2nd eccentric body 14,16 respectively to the diametical direction bias Δ e(of radial direction with reference to figure 2).
1st, the 1st, the 2nd eccentric body bearing 28,30 is configured with respectively between the 2nd eccentric body the 14,16 and the 1st, the 2nd external gear 10,12.1st, the 2nd eccentric body bearing 28,30 is made up of the 1st, the 2nd roller (rolling element) 28A, 30A and the 1st, the 2nd retainer 28B, 30B of supporting the 1st, the 2nd roller 28A, 30A respectively, do not possess special Internal and external cycle (the 1st, the 2nd eccentric body 14,16 plays the effect of inner ring, and the 1st, the 2nd external gear 10,12 plays the effect of outer ring).
1st, in the 2nd retainer 28B, 30B, its axial end portion from during end on observation in the form of a ring.The ends contact of the opposed faces side that the 1st retainer 28B and the 2nd retainer 30B is mutually opposing, end and the 1st, the 2nd stopper 32,34 of opposed faces opposition side contact.1st, the 2nd stopper 32,34 is transfused to end difference 20A, 20B of axle 20 and (supporting input shaft 20) a pair ball bearing 36,38 clamps, and locate vertically.1st, the 2nd ball bearing 36,38 is pressed in this input shaft 20 with the state sandwiching the 1st, the 2nd stopper 32,34 between end difference 20A, 20B of its inner ring 36A, 38A and input shaft 20.The outer ring 36B of the 1st ball bearing 36 is by being arranged at the back-up ring 41 that the described later 1st takes turns support body 40, and the outer ring 38B of the 2nd ball bearing 38 carries out axial position limitation respectively by the end difference 42A that the 2nd takes turns support body 42.Thus, result, the axially locating of the 1st, the 2nd roller 28A, 30A is undertaken by the 1st, the 2nd stopper the 32,34 and the 1st, the 2nd retainer 28B, 30B.
1st, the internal gear 18 that the 2nd external gear 10,12 engages is made up of with the internal gear main body 18B with the cotter way 18B1 supporting this interior alligator 18A the cylindric interior alligator 18A forming internal tooth.Internal gear main body 18B is integrated with 44 one-tenth, shell.Shell 44 is fixed on outside fixed component (omitting diagram) by the not shown bolt being inserted through bolt hole 44A.
The interior number of teeth (quantity of interior alligator 18A) of internal gear 18 is only a little more than the outer number of teeth (being only 1 in this example) of the 1st, the 2nd external gear 10,12.1st, on the 2nd external gear 10,12, on the equidistant position of axle center O2, O3 of the 1st, the 2nd external gear 10,12, multiple (in this reference example being 10) the 1st, the 2nd penetration hole 10A, 12A is circumferentially being formed with respectively.1st, the 2nd penetration hole 10A, 12A separates movable fit on have the promotion body 48 that slides coated domestic 50.
Be configured with the 1st, the 2nd in the axial both sides of the 1st, the 2nd external gear 10,12 and take turns support body 40,42.As aforementioned, the 1st, the 2nd takes turns support body 40,42 supports input shaft 20 by the 1st, the 2nd ball bearing 36,38, and is supported on shell 44 by main bearing (angular contact ball bearing) 52,54.
Described domestic 50 and the 2nd take turns support body 42 one-tenth is integrated.2nd takes turns support body 42 takes turns support body 40 by domestic 50 and bolt 56 and the 1st and links.2nd takes turns support body 42 utilizes the driven member of bolt hole 42B and not shown object machinery to link.
At this, the structure of subtend the 1st, the 2nd eccentric body bearing 28,30 supply oiling agent is described in detail.
In input shaft (eccentric shaft) 20, the position by its axle center O1 is formed with the 1st lubrication channel 22 that can flow into lubricant oil vertically.Wherein, the 1st lubrication channel 22 runs through input shaft 20 vertically, and axial two end part 20C, 20D of this input shaft 20 has opening 22A, 22B.That is, become and from this input shaft 20, the structure of oiling agent can be flowed into by any end 20C, 20D opening 22A, 22B.
Further, in input shaft 20,4 articles of the 2nd lubrication channel 24(24A ~ 24D be communicated with the 1st lubrication channel 22 are radially extended to form).2nd lubrication channel 24 is opening (having opening 24A1 ~ 24D1 between the 1st eccentric body 14 and the 2nd eccentric body 16) between the 1st eccentric body 14 and the 2nd eccentric body 16.
As shown in Figures 2 and 3, in this reference example, the 2nd lubrication channel 24 is made up of the 1st and the 2nd linear channel 24X, 24Y.1st linear channel 24X is as lower channel, namely between the 1st eccentric body 14 and the 2nd eccentric body 16, separate the 2 place openings (there are 2 opening 24A1,24B1s in described 4 opening 24A1 ~ 24D1s) of 180 degree of phase differences at circumferencial direction, and 2 article of the 2nd lubrication channel 24A, 24B are continuous, thus result is formed as straight line shape passage.2nd linear channel 24Y is similarly as lower channel, namely between the 1st eccentric body 14 and the 2nd eccentric body 16, separate the 2 place openings (there are described 42 of opening in 24A1 ~ 24D1 open 24C1,24D1) of 180 degree of phase differences at circumferencial direction, and 2 article of the 2nd lubrication channel 24C, 24D are continuous, thus result is formed as 1 linear channel.
With reference to figure 2, in 1st linear channel 24X, when speed reducer G1 rotates to forward direction, namely, when input shaft 20 rotates to arrow A 1, result as the 2nd of output block take turns support body 42 rotate to arrow A 2 direction time, also identical to the 1st eccentric body bearing 28(the 2nd eccentric body bearing 30 side) apply the direction of maximum load F1 have described in open 24A1, open 24B1 described in having at its opposition side.In addition, this input shaft (eccentric shaft) 20 the 1st linear channel 24X by arranged by parts and by 1 drilling tool (omitting diagram) radially (diametric(al)) wear 2 article of the 2nd lubrication channel 24A, 24B continuously and formed.
Equally, with reference to figure 3, in 2nd linear channel 24Y, when speed reducer G1 rotates to reverse directions, that is, when input shaft 20 rotates to arrow B 1 direction, result as the 2nd of output block take turns support body 42 rotate to arrow B 2 direction time, also identical to the 1st eccentric body bearing 28(the 2nd eccentric body bearing 30 side) apply the direction of maximum load F2 have described in open 24C1, at its opposition side, there is described opening 24D1.2nd linear channel 24Y also by arranged by parts and by 1 drilling tool radially (diametric(al)) wear 2 article of the 2nd lubrication channel 24C, 24D continuously and formed.
Usually, in eccentric oscillating-type speed reducer, the position (eccentric direction) of the position (eccentric direction) applying the maximum load F1 of forward direction and the maximum load F2 applying reverse directions becomes the position determined by speed reducer.This position is according to the diameter of interior alligator or quantity, or the offset of eccentric body etc. is slightly different, but with maximum eccentric direction M1(or minimum eccentric direction M2) become general about 45 degree of offset phase angle α 1(for benchmark) position.
Then, the effect of this eccentric oscillating-type speed reducer G1 is described.
If input shaft 20 rotates, then the 1st, the 2nd eccentric body 14,16 rotates integrally, and swings while making the 1st, the 2nd external gear 10,12 mutually maintain the phase angle of 180 degree by the 1st, the 2nd eccentric body bearing 28,30.Thus, 1st, the engaging position of the 2nd external gear 10,12 and internal gear 18 offsets successively to circumferencial direction, when the 1st, the 2nd eccentric body 14,16 often rotates 1 time, the 1st, the 2nd external gear 10,12 only rotates relative to internal gear 18 amount that (rotation) be equivalent to number of teeth difference " 1 " relatively.
This rotation composition by domestic 50(and slide promote body 48) be passed to the 1st, the 2nd and take turns support body 40,42, be passed to the not shown driven member utilizing bolt hole 42B to link further.Thus, driven member rotates to the sense of rotation contrary with the sense of rotation of input shaft 20 with the speed be decelerated.
Wherein, the lubricant oil (oiling agent) in speed reducer G1 flows into the inside of input shaft 20 by the 1st lubrication channel 22.The lubricant oil flowed into utilizes the centrifugal force produced by the rotation of this input shaft 20 to guide to the space S P1 of the radial outside of this opening 24A1 ~ 24D1 from 4 opening 24A1 ~ 24D1 between the 1st eccentric body 14 and the 2nd eccentric body 16 through the 2nd lubrication channel 24 towards radial outside.The space S P1 of the radial outside of opening 24A1 ~ 24D1 is covered by the 1st retainer 28B and the 2nd retainer 30B, therefore the lubricant oil flowed in this space S P1 enters (arranging to circumferencial direction) the 1st roller 28A gap each other to axial change direction, or the 2nd roller 30A gap each other, and be dispersed throughout by the rotation of the 1st, the 2nd roller 28A, 30A the 1st, the 2nd roller 28A, 30A periphery, the 1st, the periphery of the 2nd eccentric body 14,16 and the inner circumferential of the 1st, the 2nd external gear 10,12.
Opening 24A1 ~ 24D1 total of the 2nd lubrication channel 24 is formed with 4.In the past, the opening due to the passage being equivalent to the radial direction of the 2nd lubrication channel 24 was formed at the rolling surface of eccentric body, therefore in order to prevent the damage of this rolling surface or roller as far as possible, was difficult to form multiple opening.But, in this reference example, the opening 24A1 ~ 24D1 of the 2nd lubrication channel 24 is formed between the 1st, the 2nd eccentric body 14,16 (but not rolling surface), therefore, there is not the problem of rolling surface damage and so on, therefore, it is possible to form multiple opening 24A1 ~ 24D1 without barrier.
Further, each opening 24A1 ~ 24D1 is all the time to the space S P1 opening (opening) between the 1st eccentric body 14 and the 2nd eccentric body 16.That is, can not because of the phenomenon of the 1st, the 2nd roller 28A, 30A generation " opening (part) frequent jams of the 2nd lubrication channel 24, now the flowing of lubricant oil is temporary weak " and so on.Therefore, along with the multiple opening 24A1 ~ 24D1 of formation, lubricant oil can be made to move very swimmingly with the order of the 1st lubrication channel the 22 → 2nd lubrication channel 24 → space S P1.
And, the 2nd lubrication channel 24 involved by this reference example is made up of the 1st linear channel 24X and the 2nd linear channel 24Y, described 1st linear channel 24X separates the phase difference of 180 degree at 2 place's openings (opening 24A1,24B1), result becomes continuous print 1 passage, described 2nd linear channel 24Y is the same separates the phase difference of 180 degree at 2 place's openings (opening 24C1,24D1), and result becomes continuous print 1 passage.Therefore, the 1st, the 2nd linear channel 24X, 24Y can be arranged by parts and by 1 drilling tool (omitting diagram) radially (diametric(al)) wear 2 article of the 2nd lubrication channel 24A, 24B or 24C, 24D and being formed continuously.Therefore, can not only process like a cork, residual cutting powder in the 1st, the 2nd lubrication channel 22,24, and the advantage that the situation because of the adjacent rolling surface of this cutting powder damage is prevented trouble before it happens can be obtained.Be difficult to arrange the passage that more than 2 articles are equivalent to the radial direction of the 2nd lubrication channel in the past, be therefore set to " having the end " (being formed to radiation direction from axle center O1) in the part being equivalent to the 1st lubrication channel.Therefore, cut powder and easily remain in the 1st, the 2nd lubrication channel 22,24, in order to do not make its residual must to carry out (due to for key shape or have the end so more difficult) clean in passage.But according to this reference example, (except the 1st lubrication channel 22 one-tenth penetration hole) especially the 2nd lubrication channel 24 is formed by " penetration hole " of the 1st and the 2nd linear channel, therefore almost do not cut the misgivings that powder is residual.
In addition, 1st linear channel 24X applies direction and its opposition side of maximum load F1 when being formed in rotating forward, 2nd linear channel 24Y applies direction and its opposition side of maximum load F2 when being formed in reversion, no matter therefore when rotating forward and when reversing, all fully lubricant oil can be supplied to the direction applying maximum load.About this point, in the past, in order to the impact of the lubrication channel to rolling surface opening is suppressed to inferior limit, have on the contrary to the direction opening of non-load application, but in this reference example, can all the time to the direction supply lubricant oil needing most lubricant oil.
According to the superposition of above multiple action effect, in speed reducer G1 involved by this reference example, the damage of the rolling surface (periphery of the 1st, the 2nd eccentric body 14,16 or the periphery of the 1st, the 2nd roller 28A, 30A) of the 1st, the 2nd eccentric body bearing 28,30 can be prevented, and fully supply oiling agent to this rolling surface, greatly can extend the life-span of the 1st, the 2nd eccentric body bearing 28,30.
In addition, about eccentric oscillating-type speed reducer G1, except centre-crank formula speed reducer G1 described above, such as, also there will be a known the speed reducer being called the structure of distributing type (sorting type).
The G2 of this speed reducer shown in Fig. 4 and Fig. 5.
In this speed reducer G2, the 1st, the 2nd external gear 110,112 also spread configuration vertically, with internal gear 118 engages while swinging each via the 1st, the 2nd eccentric body 114,116.
But, in above reference example, the input shaft 20 with the function of eccentric shaft is only configured with 1 in the position of the axle center O1 of internal gear 18, but in this reference example, the 1st eccentric shaft 171 wherein is only illustrated in 1st ~ 3rd eccentric shaft 171 ~ 173(Fig. 4) in the radial direction position offset from the axle center O4 of internal gear 118, to circumferencial direction to configure at equal intervals (3).
Be respectively arranged with the 1st, the 2nd eccentric body the 114,116, the 1st eccentric shaft 171 at the 1st ~ 3rd eccentric shaft 171 ~ 173 to drive through gear 174, thus the 1st, the 2nd external gear 110,112 carries out swing rotary.In addition, the 2nd eccentric shaft 172 and the 3rd eccentric shaft 173 at this moment in driven state, and support the 1st, the 2nd external gear 110,112, so that the 1st, the 2nd external gear 110,112 carries out swing rotary swimmingly.
1st, the 2nd the axial side that support body 140,142 is arranged on the 1st, the 2nd external gear 110,112 is taken turns, and by taking turns wheel carrier pin 182 and bolt 184 that support body 142 one-tenth is integrated with the 2nd and can integrally rotatably link.Described 1st ~ 3rd eccentric shaft 171 ~ 173 respectively by a pair the 1st, the 2nd tapered roller bearing 178,179 is supported on the 1st, the 2nd and takes turns support body 140,142.
In this speed reducer G2, the 1st, the 2nd external gear 110,112 as the revolution of the 1st ~ 3rd eccentric shaft 171 ~ 173 around the axle center O4 of internal gear 118 relative to the relative rotation of internal gear 118, and is taken turns support body 140,142 from the 1st, the 2nd and is taken out.
1st, the 2nd roller 128A, 130A utilizes that the 1st, the 2nd stopper 132,134 seizes its 1st, the 2nd retainer 128B, 130B on both sides by the arms from axial outside and restrictive axial moves.1st, the 2nd stopper 132,134 is connected to the 1st, the 2nd tapered roller bearing 178,179, and, be connected to the 1st, the 2nd retainer 128B, 130B.1st, the 2nd retainer 128B, 130B also abuts each other mutually.Therefore, in this speed reducer G2, lubricant oil is still difficult to arrive near the 1st, the 2nd eccentric body bearing 128,130.
In this speed reducer G2, also can be formed as lower channel with same structure: the 1st lubrication channel 122, is formed vertically, and can flow into lubricant oil in the 1st ~ 3rd eccentric shaft 171 ~ 173; And the 2nd lubrication channel 124, be communicated with the 1st lubrication channel 122, and radially extend to form.About the concrete structure (such as, aforesaid 1st, the 2nd linear channel 124X, 124Y etc.) of the 2nd lubrication channel 124, also can adopt the structure identical with above reference example, identical action effect can be obtained.
In addition, in this reference example, as enlarged icon in Figure 5, radial direction medial extremity 128B1,130B1 of the opening 124A1 ~ 124D1 side by the 2nd lubrication channel 124 of the 1st retainer 128B and the 2nd retainer 130B are respectively from the state tilt alpha 2 with parallel to an axis.Specifically, 1st retainer 128B(the 2nd retainer 130B) there is maintenance the 1st roller 128A(the 2nd roller 130A) holding part and the annulus that extends to radially inner side from the axial two ends of holding part, and by the radial direction medial extremity 128B1(130B1 that axial inboard portion is cut of the radially inner side end periphery that is set to this annulus), make it guide to the 1st roller 128A(the 2nd roller 130A with by from opening the lubricant oil that 124A1 ~ 124D1 flows out thus) inclination.Thereby, it is possible to by the flowing of opening the lubricant oil that 124A1 ~ 124D1 flows out towards radial outside from the 2nd lubrication channel 124 swimmingly to axial conversion, and guide to the 1st roller 128A(the 2nd roller 130A).In addition, in this reference example, the annulus both sides at axial two ends are with inclination, but the annulus at least opening 124A side has.
Namely, in eccentric oscillating-type speed reducer, if sufficient lubrication is configured in the eccentric body bearing between eccentric body and external gear, and improve the life-span, make the 2nd lubrication channel in the peripheral openings of eccentric body, then in order to not make the roller damaged of eccentric body bearing, fully must carry out fine finishing to opening portion periphery, thus cause process time, the increase of processing cost.Therefore, if arrange the opening 124A1 ~ 124D1 of the 2nd lubrication channel 124 between the 1st eccentric body 114 and the 2nd eccentric body 116, then there is no sliding contact between the 1st, the 2nd roller 128A, 130A of the 1st, the 2nd eccentric body bearing 128,130 and opening 124A1 ~ 124D1, therefore do not need the processing of opening portion periphery.
But, on the other hand, how the lubricant oil flowed out from opening 124A1 ~ 124D1 is supplied to the 1st, the 2nd roller 128A, 130A(of the 1st, the 2nd eccentric body bearing 128,130 and the slip surface of the 1st, the 2nd eccentric body 114,116) and become problem.According to this reference example, 2nd lubrication channel 124 is set between the 1st eccentric body 114 and the 2nd eccentric body 116, and the radially inner side end of the opening side of the 1st retainer 128 and the 2nd retainer 130B is set to radial direction medial extremity 128B1, the 130B1 with inclination, the lubricant oil flowed out from opening 124A1 ~ 124D1 is guided to the 1st, the 2nd roller 128A, 130A, therefore, do not need to carry out fine finishing to opening portion periphery, and sufficient lubrication the 1st, the 2nd eccentric body bearing 128,130, and the life-span can be improved.
About other structures, substantially the same with above reference example, therefore identical with above reference example to the additional in the drawings rear double figures in identical or functionally similar position symbol, and omit repeat specification.
One example of embodiments of the present invention shown in Fig. 6 and Fig. 7.
In preferably involved speed reducer G3,2 the 1st, the 2nd external gear 210,212 spread configuration vertically, and, have 3 eccentric shaft 271 ~ 273(being provided with the 1st, the 2nd eccentric body 214,216 and only illustrate eccentric shaft 271).But in the speed reducer G3 involved by this mode of execution, the eccentric shaft gear 274 being arranged on 3 eccentric shafts 271 ~ 273 engages with common central gear 176 respectively.That is, 3 eccentric shafts 271 ~ 273 all drive by central gear 176 is simultaneously synchronous.
In speed reducer G3, by a pair the 1st, the 2nd roller bearing (bearing of eccentric shaft) 278,279 supports eccentric shaft 271 ~ 273(and only illustrates eccentric shaft 271).1st, the 2nd roller bearing 278,279 is configured to not possess special inner ring, outer ring, and the outer circumferential face and the 1st, the 2nd that the 1st, the 2nd roller 278A, 279A is directly connected to eccentric shaft 271 ~ 273 takes turns support body 240,242.In this embodiment, to the 1st, the 2nd stopper 232,234 that the axial position of the 1st, the 2nd retainer 228B, 230B of the 1st, the 2nd eccentric body bearing 228,230 configured between the 1st, the 2nd eccentric body the 214,216 and the 1st, the 2nd external gear 210,212 limits, be connected to the 1st, the 2nd eccentric body 214,216 and double as main bearing (angular contact ball bearing) 250,252 inner ring the 1st, the 2nd take turns support body 240,242 to carry out position limitation.Described 1st, the 2nd roller bearing 278,279 of supporting eccentric shaft 271 ~ 273 is made up of the 1st, the 2nd roller 278A, 279A and the 1st, the 2nd retainer 278B, 279B.1st, the 2nd retainer 278B, 279B carrys out restrictive axial by the back-up ring 281,282 that is arranged on eccentric shaft 271 ~ 273 and the pad 283,284 of function that has both thrust plate and moves.Following situation is there is in the speed reducer G3 of this structure, namely be not only difficult to lubrication the 1st, the 2nd eccentric body bearing 228,230, and because there is the 1st, the 2nd stopper 232,234 and pad 283,284, supply lubricant oil be also difficult to the 1st, the 2nd roller bearing 278,279 of supporting eccentric shaft 271 ~ 273.
More specifically, the 1st, the 2nd stopper 232,234 is configured with respectively between the 1st, the 2nd roller bearing the 278,279 and the 1st, the 2nd eccentric body 214,216.Further, packing ring 231 is configured with between the 1st, the 2nd eccentric body bearing 228,230.1st roller bearing 278 moves by being clipped in back-up ring 281 and carrying out restrictive axial between pad 283 and the 1st stopper 232.2nd roller bearing 279 moves by being clipped in back-up ring 282 and carrying out restrictive axial between pad 284 and the 2nd stopper 234.1st eccentric body bearing 228 is clamped with packing ring 231 by the 1st stopper 232, and the 2nd eccentric body bearing 230 is clamped with packing ring 231 by the 2nd stopper 234, thus restrictive axial moves respectively.
Wherein, the internal diameter of the 1st, the 2nd stopper 232,234 is set to the external diameter of the eccentric shaft 271 of the part being greater than configuration the 1st, the 2nd stopper 232,234, is provided with gap between the 1st, the 2nd stopper 232,234 and eccentric shaft 271.Further, the internal diameter of packing ring 231 is set to the external diameter of the part be greater than between the 1st eccentric body 214 and the 2nd eccentric body 216, is provided with gap between packing ring 231 and eccentric shaft 271.
In present embodiment, as the 2nd lubrication channel 224, except (identical with above reference example) is arranged on the 1st, the 2nd linear channel 224X, 224Y between the 1st eccentric body 214 and the 2nd eccentric body 216, be also formed with lubrication channel 224K, 224L of opening between the 1st roller bearing 278 and the 1st eccentric body 214 and between the 2nd roller bearing 279 and the 2nd eccentric body 216 respectively.
The concrete structure of lubrication channel 224K, 224L can be set to the structure identical with the 2nd lubrication channel of above reference example.In present embodiment, except the 1st, the 2nd eccentric body bearing 228,230, fully can supply lubricant oil to the 1st of 3 eccentric shafts 271 ~ 273, the 2nd roller bearing 278,279 too.
That is, the lubricant oil flowed out from lubrication channel 224K, 224L to the outer circumferential side of eccentric shaft 271 is supplied to the 1st, the 2nd roller bearing 278,279 from the gap be arranged between the 1st, the 2nd stopper 232,234 and eccentric shaft 271.Further, the lubricant oil flowed out from the 1st, the 2nd linear channel 224X, 224Y to the outer circumferential side of eccentric shaft 271 is supplied to the 1st, the 2nd eccentric body bearing 228,230 from the gap be arranged between packing ring 231 and eccentric shaft 271.
In addition, in present embodiment, lubrication channel 224K, 224L separate 180 degree of phase differences to the maximum eccentric direction of adjoined eccentric body 214,216 and minimum eccentric direction and at 2 place's openings, become continuous print 1 linear channel, but the forming position of opening portion can be formed in any position of circumference, is also not particularly limited its number.
And, although omit description in the figure 7, but 1st, the radial direction medial extremity of lubrication channel 224K, 224L side of the 1st, the 2nd retainer 278B, 279B of the 2nd roller bearing 278,279 is identical with the 2nd retainer 130B with the 1st retainer 128B illustrated in fig. 5, be set to and tilt from the state with parallel to an axis, effectively the lubricant oil flowed out from lubrication channel 224K, 224L can be guided to the 1st, the 2nd roller bearing 278,279.
In addition, in above-mentioned reference example or mode of execution, shown with the example of 2 external gears speed reducer of spread configuration vertically, but the present invention can be applied to external gear is in the speed reducer of more than 1 or 3.
And, in above-mentioned reference example or mode of execution, structure about the 2nd lubrication channel is set to the 1st, the 2nd linear channel being formed and run through to diametric(al), but in the present invention, without the need to necessarily forming the 2nd lubrication channel by this linear channel, such as can for the lubrication channel extended to radial direction (radiation direction) with the state be communicated with the 1st lubrication channel.Further, its number is also not particularly limited.
In addition, in above-mentioned reference example or mode of execution, the maximum load direction be set in the forward direction and reverse direction forms the 2nd lubrication channel, but in the present invention, without the need to the 2nd lubrication channel must be formed in maximum load direction.Certainly, also the 2nd lubrication channel can be formed in the direction beyond maximum load direction.
In above-mentioned mode of execution, lubrication channel 224K, 224L are formed on the eccentric shaft of the eccentric oscillating-type speed reducer distributing type, but also can be applied in the eccentric oscillating-type speed reducer of centre-crank formula as shown in Figure 1.
In above-mentioned mode of execution, the example lubricant oil flowed out from lubrication channel 224K, 224L being mainly supplied to the 1st, the 2nd roller bearing 278,279 is illustrated, but be not limited thereto, such as, by forming radial slot etc. someway on the bearing surface of the 1st, the 2nd stopper the 232,234 and the 1st, the 2nd eccentric body 214,216, the lubricant oil flowed out also is supplied to the 1st, the 2nd eccentric body bearing 228,230 from lubrication channel 224K, 224L.
In above-mentioned mode of execution, the example that the 1st, the 2nd roller bearing 278,279 is made up of the roller being directly connected to eccentric shaft 271 is described, but is not limited thereto, also can be made up of the bearing possessing special inner ring.At this moment, by forming radial slot etc. at the bearing surface of inner ring and the 1st, the 2nd stopper 232,234 someway, the lubricant oil flowed out from lubrication channel 224K, 224L is supplied to rolling element.

Claims (7)

1. an eccentric oscillating-type speed reducer, it is possessed external gear, the internal gear engaged with this external gear, has the eccentric shaft of the eccentric body that described external gear is swung and supported the wheel support body of this eccentric shaft by bearing, the feature of described eccentric oscillating-type speed reducer is
Possess: the 1st lubrication channel, is formed vertically in described eccentric shaft, and lubricant oil can be made to flow into; 2nd lubrication channel, is communicated with described 1st lubrication channel, and radially extends to form,
2nd lubrication channel is opening between the bearing and eccentric body of described supporting eccentric shaft,
Eccentric body bearing is configured between the periphery and external gear of described eccentric body,
Between the bearing and eccentric body of described supporting eccentric shaft, configure stop component, this stop component limits moving axially of described eccentric body bearing,
Gap is provided with between the inner circumferential of this stop component and the periphery of described eccentric shaft,
Described 2nd lubrication channel is at the radially inner side opening of described stop component.
2. eccentric oscillating-type speed reducer as claimed in claim 1, is characterized in that,
The bearing of described supporting eccentric shaft is formed by with the roller that the outer circumferential face of described eccentric shaft directly abuts.
3. eccentric oscillating-type speed reducer as claimed in claim 1 or 2, is characterized in that,
Possess multiple described eccentric body and external gear,
Also possesses the 2nd lubrication channel of opening between the plurality of eccentric body.
4. eccentric oscillating-type speed reducer as claimed in claim 1 or 2, is characterized in that,
Described 2nd lubrication channel separates the phase difference of 180 degree and at 2 place's openings, and forms continuous print 1 linear channel.
5. eccentric oscillating-type speed reducer as claimed in claim 1 or 2, is characterized in that,
The opening of described 2nd lubrication channel is formed at the maximum eccentric direction of described eccentric body and minimum eccentric direction.
6. eccentric oscillating-type speed reducer as claimed in claim 5, is characterized in that,
The opening of described 2nd lubrication channel is formed at respectively: maximum load direction when maximum load direction during rotating forward and its opposition side and reversion and its opposition side.
7. eccentric oscillating-type speed reducer as claimed in claim 1 or 2, is characterized in that,
The radial direction medial extremity of the opening side by described 2nd lubrication channel of the retainer of the bearing of described supporting eccentric shaft tilts from the state with parallel to an axis.
CN201210344641.XA 2011-09-16 2012-09-17 Eccentric oscillating-type speed reducer Active CN102996771B (en)

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Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5922464B2 (en) * 2012-03-30 2016-05-24 ナブテスコ株式会社 Gear transmission
JP6181961B2 (en) * 2013-04-15 2017-08-16 ナブテスコ株式会社 Eccentric oscillating gear unit
JP6532386B2 (en) * 2015-11-18 2019-06-19 住友重機械工業株式会社 Eccentric rocking gear
JP6767804B2 (en) * 2016-07-29 2020-10-14 日本電産シンポ株式会社 Gear transmission
JP6736223B2 (en) * 2017-02-08 2020-08-05 住友重機械工業株式会社 Eccentric oscillating gear device
JP6878036B2 (en) * 2017-02-10 2021-05-26 住友重機械工業株式会社 Eccentric swing type gear device
JP6759124B2 (en) * 2017-02-17 2020-09-23 住友重機械工業株式会社 Eccentric swing type gear device

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4614123A (en) * 1985-01-11 1986-09-30 Global Manufacturing Co, Inc. Vertical vibrator
HUT50371A (en) * 1988-06-21 1990-01-29 Magyar Goerdueloecsapagy Mueve Mechanism for closed bearing particularly for bearing the wave disc of eccentric drive
JPH0988976A (en) * 1995-09-29 1997-03-31 Ntn Corp Oil feeder of rolling bearing
JP3891104B2 (en) * 2002-11-29 2007-03-14 アイシン・エィ・ダブリュ株式会社 Lubricating structure for belt type continuously variable transmission
JP4847892B2 (en) 2007-02-22 2011-12-28 住友重機械工業株式会社 Oscillating intermeshing planetary gear device and manufacturing method of eccentric shaft thereof
JP2007240003A (en) * 2007-04-26 2007-09-20 Nabtesco Corp Bearing part structure and eccentric oscillation type gear system with the bearing part structure
JP5158861B2 (en) * 2008-03-11 2013-03-06 Ｎｔｎ株式会社 In-wheel motor drive device
JP2010169247A (en) * 2008-12-26 2010-08-05 Ntn Corp Railroad vehicle drive unit
JP5388746B2 (en) * 2009-08-10 2014-01-15 ナブテスコ株式会社 Swing type reducer
JP5461263B2 (en) 2010-03-24 2014-04-02 株式会社日立システムズ Coordination system and method for cashier and depositing / dispensing machine
JP5068346B2 (en) * 2010-07-05 2012-11-07 ナブテスコ株式会社 Bearing structure

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