CN102384221A - Swinging inner engaged planetary gear apparatus and manufacture method - Google Patents
Swinging inner engaged planetary gear apparatus and manufacture method Download PDFInfo
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- CN102384221A CN102384221A CN2011102332173A CN201110233217A CN102384221A CN 102384221 A CN102384221 A CN 102384221A CN 2011102332173 A CN2011102332173 A CN 2011102332173A CN 201110233217 A CN201110233217 A CN 201110233217A CN 102384221 A CN102384221 A CN 102384221A
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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
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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
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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
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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
- F16C43/00—Assembling bearings
- F16C43/04—Assembling rolling-contact 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
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/44—Needle bearings
- F16C19/46—Needle bearings with one row or needles
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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
- F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
- F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings 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
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
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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
- 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)
- Retarders (AREA)
- Rolling Contact Bearings (AREA)
- General Details Of Gearings (AREA)
Abstract
The present invention provides a singing inner engaged planetary gear apparatus and a manufacture method, easily equipped with an input shaft and especially capable of simply assembling a bearing for supporting the input shaft. The singing inner engaged planetary gear apparatus (50) is provided with an input shaft (52), a distribution gear (54) arranged on the input shaft (52), a decentration body shaft gear (crankshaft gear) (56A-56C) engaged with the distribution gear (54); a decentration body shaft (crankshaft) (58A-58C) assembled with the decentration body shaft gear (crankshaft gear) (56A-56C), wherein the gear (B3) of one side of a pair of gears (B3, B4) for supporting the input shaft (52) is a quill bearing (84), the bearing (B4) of the other side can be first and second corner contact ball bearings (86, 87) for bearing the push force load applied on the input shaft, and the outer diameter d1 of the inner ring (84B) of the quill bearing (84) is more than the gear top circle d2 of the distribution gear (54) and less than the inner diameters D1, D2 (D2=D1) of the outer ring (86C, 87C) of the first and second corner contact ball bearings (86, 87).
Description
Technical field
The application advocates the preference based on the Japanese patent application of on September 6th, 2010 application 2010-199190 number.All the elements of its application are applied in this specification through reference.
The invention particularly relates to a kind of swing internally meshed type planetary gear system and production method thereof that possesses a plurality of bent axles.
Background technique
Disclose swing internally meshed type planetary gear system in the patent documentation 1.Fig. 4 is the whole synoptic diagram of this swing internally meshed type planetary gear system, and Fig. 5 is the sectional view along the arrow V-V line of Fig. 4.
In this planetary gear system 10, the distribution gear 14 that is assembled in input shaft 12 meshes with 3 last 3 crankshaft gear 18A～18C (only illustrating 18A) of bent axle 16A～16C simultaneously.The last eccentric body 20,22 that is formed with respectively of each bent axle 16A～16C.The periphery of each eccentric body 20,22 is chimeric to have external gear 24,26.Be engaged in internal gear 30 in the external gear 24,26 with shell 28 being integral.Each bent axle 16A～16C is supported on the 1st, the 2nd flange 32,34 of mutual binding.
In this planetary gear system 10, if input shaft 12 rotations, then 3 bent axle 16A～16C rotate to equidirectional with identical speed through distribution gear 14 and 3 crankshaft gear 18A～18C.Be engaged in internal gear 30 in when thus, being embedded in external gear 24, the 26 swing rotation of each bent axle 16A～16C.The number of teeth of external gear 24,26 is less than the number of teeth of internal gear 30, so if be engaged in internal gear 30 in external gear 24,26 swing the time, then between each external gear 24,26 and internal gear 30, produce slowly and rotate relatively.In the disclosed example, take out rotation relatively as the output of slowing down from the 1st, the 2nd flange 32,34.
In the related planetary gear system 10 of this patent documentation 1, support input shaft 12 through pair of bearings B1, B2.A side bearing B1 is made up of roller bearing 36 among this pair of bearings B1, the B2, and the opposing party's bearing B2 is made up of (one group) the 1st, the 2nd tapered roller bearing 40,42 of bearing thrust load.In the patent documentation 1,, seek the expansion of the diameter of axle of this input shaft 12 simultaneously through this expansion that constitutes the radial dimension of the parts that suppress supporting input shaft 12.
Patent documentation 1: TOHKEMY 2009-287631 communique (Fig. 1, [0009] section, summary)
The part of the distribution gear 14 of disclosed swing internally meshed type planetary gear system 10 upwarps towards the end of input shaft 12 in the above-mentioned patent documentation 1; The size of the top circle of this distribution gear 14 is greater than the face that transfers of the roller 36A of roller bearing 36, so can only insert towards the left side and assembling input shaft 12 from the right side of Fig. 4.But; On the other hand; The most peripheral of the 1st tapered roller bearing 40 its roller 40A of the bearing B2 of another side of supporting input shaft 12 is greater than the face that transfers of the roller 36A of roller bearing 36; So (from the right side of Fig. 4 towards the left side) when inserting this input shaft 12, can't become the state that inner ring 40B and roller 40A with the 1st tapered roller bearing 40 are installed on input shaft 12.
Therefore, 40 assemblings of the 1st tapered roller bearing only are equipped with after the input shaft 12 of inner ring 40B, must 11 ground of roller 40A be assembled in this inner ring 40B from the left side of Fig. 3.
And; The 2nd tapered roller bearing 42 to bearing B2; When inserting input shaft 12, also can't become the state that inner ring 42B or roller 42A with the 2nd tapered roller bearing 42 are installed on input shaft 12, so; The result installs roller 40A, 42A one by one to any (at inner ring 40B, the 42B of assembled) in the 1st, the 2nd tapered roller bearing 40,42, so the assembling of input shaft 12 needs a lot of time and labors.
Summary of the invention
The present invention accomplishes in order to solve such problem in the past, and its problem is, provides a kind of and assembles input shaft like a cork, especially can assemble the swing internally meshed type planetary gear system and the production method thereof of the bearing of this input shaft of supporting simply.
The present invention solves above-mentioned problem through following structure: a kind of swing internally meshed type planetary gear system; Possess input shaft, be arranged at this input shaft distribution gear, with the crankshaft gear of this distribution gear engagement and the bent axle that is assembled with this crankshaft gear; Wherein, The pair of bearings that possesses the said input shaft of supporting; A side bearing is a needle bearing in this pair of bearings, and the opposing party's bearing be for also can bearing the thrust-bearing of the thrust load that puts on said input shaft, and the external diameter of the inner ring of said needle bearing is greater than the top circle of said distribution gear and less than the internal diameter of the outer ring of said thrust-bearing.
In addition, the notion that also comprises roller bearing in the notion of needle bearing of the present invention.
In the present invention, in the pair of bearings of supporting input shaft, a side bearing is set as (comprising this notion of roller bearing) needle bearing, and the opposing party's bearing also is set as the thrust-bearing that bears the thrust load that puts on input shaft.Thus, while the required basic bearing value of bearing that can keep as the supporting input shaft suppresses the whole radial direction size of planetary gear system lessly.
On this basis, among the present invention, the external diameter of the inner ring of needle bearing forms the top circle greater than distribution gear, and forms the internal diameter less than the outer ring of thrust-bearing.
Among the present invention, from opposite in the past direction promptly from the side assembling input shaft of a side direction needle bearing of thrust-bearing.At this moment; The external diameter of the inner ring of needle bearing is greater than the external diameter of the top circle of distribution gear; So the state that is assembled in the main body side of planetary gear system with outer ring and needle roller (rolling element) with needle bearing can be through the outer ring of this needle bearing and the inboard assembling of needle roller (install or the inner ring of integrally formed finish distribution gear and needle bearing) input shaft.
And; The external diameter of the inner ring of needle bearing forms the internal diameter less than the outer ring of thrust-bearing; So can be directly with state in the outer ring of the main body side installed thrust bearing of planetary gear system, (inner ring that makes needle bearing through the outer ring of this thrust-bearing inboard time) is from the side assembling input shaft of thrust-bearing.
Its result can enlarge the selection of thrust-bearing kind or the selection of its assembling, and all can carry out the work of needle bearing and thrust-bearing assembling easily.
The invention effect
According to the present invention, can be assembled input shaft like a cork, especially can be assembled swing internally meshed type planetary gear system or its production method of bearing of this input shaft of supporting simply.
Description of drawings
Fig. 1 is the whole synoptic diagram of the related swing internally meshed type planetary gear system of an example of mode of execution of the present invention.
Fig. 2 is the major component amplification sectional view of Fig. 1.
The major component amplification sectional view of the assembly process when Fig. 3 is expression assembling input shaft.
Fig. 4 is the whole synoptic diagram of swing internally meshed type planetary gear system in the past.
Fig. 5 is the sectional view along the arrow V-V line of Fig. 4.
Among the figure: 50-planetary gear system, 52-input shaft, 54-distribution gear, 56A～56C-eccentric body shaftgear (crankshaft gear); The eccentric axon (bent axle) of 58A～58C-, 70, the 71-external gear, 72-internal gear, 84-needle bearing; 84A-needle roller (rolling element), 84B-inner ring, 84C-outer ring, 86,87-the 1st, the 2nd angular contact ball bearing (thrust-bearing); 86A, 87A-ball (rolling element), 86B, 87B-inner ring, 86C, 87C-outer ring.
Embodiment
Below, specify an example of mode of execution of the present invention according to accompanying drawing.
Fig. 1 representes the related swing internally meshed type planetary gear system of an example of mode of execution of the present invention.
Fig. 2 is its major component amplification sectional view.
This planetary gear system 50 is assembled in the joint of mechanism hand (omitting diagram).In addition, identical with example in the past shown in Figure 4, in the end of the input shaft 52 of planetary gear system 50 through spline 53 assembling bevel gears (omitting diagram).This bevel gear is imported the rotation of just changeing, reversing, thereby produce the two-way thrust that meshes based on bevel gear at input shaft 52.A plurality of (in this example being 3) eccentric body shaftgear (crankshaft gear) 56A～56C that planetary gear system 50 possesses this input shaft 52, is arranged at the distribution gear 54 of this input shaft 52, mesh simultaneously with this distribution gear 54 and a plurality of (in this example being 3) eccentric axon (bent axle) 58A～58C that is assembled with each eccentric body shaftgear 56A～56C.In addition, not shown eccentric body shaftgear 56B, 56C and eccentric axon 58B, 58C.
Each eccentric body shaftgear 56A～56C is integrated in each eccentric axon 58A～58C to circumferencial direction through spline 60, and integrated to axially through brake hoop 62,63.Be formed with eccentric body 64,65 respectively at each eccentric axon 58A～58C.Periphery at eccentric body 64,65 disposes a plurality of rollers 66,67, external gear 70,71 is arranged in that the periphery of these a plurality of rollers 66,67 is chimeric.Be engaged in internal gear 72 in the external gear 70,71, the number of teeth only is less than internal gear 72 (it is individual to be merely " 1 " in this mode of execution) a little.The internal tooth 72A of internal gear 72 is made up of pin, main body 72B and shell 74 being integral.
Each eccentric axon 58A～58C is supported on the 1st, the 2nd flange 78,79 through tapered roller bearing 76,77.The 1st flange 78 and the 2nd flange 79 are through from the outstanding wheel support body 79A of the 2nd flange 79 one and bolt 80 and by integrated.Be supported on said shell 74 through the 1st, the 2nd angular contact ball bearing 82,83 respectively by incorporate the 1st, the 2nd flange 78,79.
Main reference Fig. 2, input shaft 52 is by pair of bearings B3, B4 supporting.In this mode of execution, the bearing B3 of load opposition side among pair of bearings B3, the B4 (distribution gear 54 sides) is a needle bearing 84, and the bearing B4 of load side (distribution gear 54 opposition sides) is the 1st, the 2nd angular contact ball bearing (thrust-bearing) 86,87.
The needle bearing 84 that constitutes the bearing B3 of load opposition side mainly is made up of needle roller (rolling element) 84A, inner ring 84B, outer ring 84C and retainer 84D.Inner ring 84B and input shaft were opened formation in 52 minutes, were pressed into or the mode of shrink fit is assemblied in input shaft 52 with (in advance).Needle roller 84A is kept by retainer 84D.Outer ring 84C has claw 84C1, the 84C2 that is used for fixing retainer 84D, is pressed in said the 1st flange (main body side of planetary gear system 50) 78.Stretch into the part of said distribution gear 54 in the inboard of the inner ring 84B of needle bearing 84.
The outside diameter d 1 of the inner ring 84B of said needle bearing 84 is greater than the top circle d2 of said distribution gear 54 (d1＞d2).And, the outer ring 86C that the external diameter of this inner ring 84B (inscribed circle diameter of needle roller 84A) d1 states after less than the 1st, the 2nd angular contact ball bearing 86,87, the inside diameter D 1 of 87C, D2 (D2=D1) (d1＜D1=D2).
In addition, the inner ring 84B of needle bearing 84 also can be the structure of input shaft 52 dual-purposes.At this moment, to transfer the external diameter of part of face identical for the external diameter of the inner ring of needle bearing and the formation of input shaft 52.
On the other hand, among the pair of bearings B3 of supporting input shaft 52, the B4, the bearing B4 of load side is set as the 1st, the 2nd angular contact ball bearing (thrust-bearing) 86,87 that also bears the thrust load that puts on input shaft 52.1st, the structure of the bearing of the 2nd angular contact ball bearing 86,87 itself is identical, but with the face-to-face duplex assembling of the opposite mutually mode of the direction of bearing thrust load.
1st, the 2nd angular contact ball bearing 86,87 mainly is made up of ball (rolling element) 86A, 87A, inner ring 86B, 87B and outer ring 86C, 87C respectively.1st, the outer ring 86C of the 2nd angular contact ball bearing 86,87,87C fix in the 2nd flange (main body side of planetary gear system 50) 79 through clamping each pad 91 by the brake hoop 88,89 of the groove 79A that is embedded in the 2nd flange 79,79B.And the inner ring 86B of the 1st, the 2nd angular contact ball bearing 86,87,87B fix in this input shaft 52 through clamping each pad 92 by the end difference 52A of input shaft 52 and the brake hoop 90 that is embedded in the groove 52B that is located in input shaft 52.Through the axial width of the pad 91,92 selecting to be inserted, can adjust the precompressed of the 1st, the 2nd angular contact ball bearing 86,87.As previously mentioned, the inside diameter D 1 of the outer ring 86C of the 1st, the 2nd angular contact ball bearing 86,87,87C, D2 (D2=D1) are greater than the outside diameter d 1 of the inner ring 84B of needle bearing 84 (D1=D2＞d1).
Then, the effect of this planetary gear system 50 is described, the production method of this planetary gear system 50 of double as especially comprises the explanation of the production method that the assembling of input shaft 52 is related.
In the lump with reference to figure 3, with following operation assembling input shaft 52.
At first, through brake hoop 62,63 (assembled) eccentric axon 58A～58C fixedly eccentric body shaftgear 56A (～56C).And, shown in Fig. 3 (A), be pressed into the outer ring 84C of needle bearing 84, the needle roller 84A (the 1st operation) that assembling keeps with retainer 84D between the claw 84C1 of this outer ring 84C, 84C2 at the 1st flange (main body side of planetary gear system 50) 78.
The outer ring 86C of then, assembling on the 2nd flange (main body side of planetary gear system 50) 79 (axially inboard) the 1st angular contact ball bearing 86 until with brake hoop 88 butts (the 2nd operation).
In addition; In this mode of execution; The bearing of load opposition side (thrust-bearing) B4 is by 1 group the 1st of assembling of opposite mode, the 2nd angular contact ball bearing 86,87 constitute mutually with the direction of bearing thrust load; So, the outer ring 86C of only assembling (axial inboard) the 1st angular contact ball bearing 86 in the 2nd operation.
(perhaps parallel) afterwards with the 1st, the 2nd operation; Become on the input shaft 52 of distribution gear 54 except the inner ring 86B and ball 86A of assembled shaft the 1st angular contact ball bearing 86 to the inside at prior cutting tooth form, also together the inner ring 87B of assembled shaft the 2nd angular contact ball bearing 87 laterally and ball 87A (the 3rd operation～the 5th operation).In addition, the inner ring 86B of the 1st, the 2nd angular contact ball bearing 86,87,87B are at the end difference 52A of input shaft 52 and be embedded in and together clamped with pad 92 between the brake hoop 90 of groove 52B of input shaft 52 and be fixed in input shaft 52.Because it is last to be installed on ball 86A, inner ring 86B, the 87B before the 87A of assembling the 1st, the 2nd angular contact ball bearing 86,87 in advance; So with compare when assembling on the inner ring after assembling, can especially easily ball 86A, 87A be installed on inner ring 86B, 87B.
In addition, even changing their operation, the 1st～the 5th operation also has not big harm.Therefore, which type of carrying out the 1st～the 5th operation with in proper order also is used as and is contained in the present invention.
Afterwards, towards the assembling of needle bearing 84 sides inner ring 86B, 87B and the ball 86A of distribution gear 54 and the 1st, the 2nd angular contact ball bearing 86,87, the input shaft 52 (the 6th operation) of 87A are installed from the 1st, the 2nd angular contact ball bearing 86,87 sides.
Shown in Fig. 3 (A)～(B); The outside diameter d 1 of the inner ring 84B of needle bearing 84 forms dimension D 1, the D2 less than the internal diameter of the outer ring 86C of the 1st, the 2nd angular contact ball bearing 86,87,87C, so input shaft 52 can directly pass the outer ring 86C of the 1st, the 2nd angular contact ball bearing 86,87, the inboard of 87C with the state of inner ring 84B that needle bearing 84 is installed.And the outside diameter d 1 of the inner ring 84B of needle bearing 84 forms the top circle d2 greater than distribution gear 54, so shown in Fig. 3 (B)～(C), (being formed on the input shaft 52) distribution gear 54 can directly pass the inboard of the needle roller 84A of needle bearing 84.
Afterwards; The outer ring 87C of the 2nd angular contact ball bearing 87 that will (be positioned at the axial outside) is assemblied in the 2nd flange (main body side of planetary gear system 50) 79, while the groove 79B that uses pad 91 adjustment precompressed that brake hoop 89 is embedded in the 2nd flange 79 finishes the assembling of input shaft 52.
In addition, the decelerating effect to the swing internally meshed type planetary gear system 50 of manufacturing like this describes simply.
If input shaft 52 rotations, then 3 eccentric axon 58A～58C rotate to identical direction with identical speed through distribution gear 54 and 3 eccentric body shaftgear 56A～56C.Be engaged in internal gear 72 in when thus, being embedded in 70, the 71 swing rotations of the last external gear of each eccentric axon 58A～58C.The number of teeth of external gear 70,71 only is less than the number of teeth of internal gear 72 a little, so if be engaged in internal gear 72 in external gear 70,71 swing the time, then between each external gear 70,71 and internal gear 72, produce slowly and rotate relatively.
At this, during fixed annulus 72 (and shell 74), the rotation composition of eccentric axon 58A～58C and external gear 70,71 revolves round the sun around the axle center O1 of planetary gear system 50 synchronously.Thus, can take out the output of slowing down from the 1st, the 2nd flange 78,79 of following this revolution.On the contrary, if the rotation of external gear 70,71 (revolution of eccentric axon 58A～58C) is when being limited, internal gear 72 sideway swivels are so can take out so-called frame rotation output from the shell 74 with these internal gear 72 being integral.
In addition; In the above-mentioned mode of execution; Directly cutting tooth form becomes distribution gear 54 on input shaft 52; And a part that is set to distribution gear 54 stretches into the inboard of the inner ring 84B of needle bearing 84 and seeks the reduction of part number of packages and axial cripetura, but the distribution gear among the present invention directly cutting tooth form be formed in input shaft, also can the distribution gear of making in addition be assemblied in input shaft.
In addition, this operation is equivalent to the 3rd operation, but because so its not restriction of front and back order of the 1st～the 5th operation as previously mentioned in fact, can be carried out this operation in arbitrary operation of the 1st～the 5th operation.Distribution gear among the present invention is set to the external diameter of its top circle less than the inner ring of needle bearing; So; Even with input shaft distribution gear independently, also can be with the direct ground same as described above of the state that this distribution gear is assembled in input shaft (from the thrust-bearing side) assembling input shaft.
In addition, in the above-mentioned mode of execution, adopt with one group the 1st of the face-to-face duplex assembling of the opposite mutually mode of the direction of bearing thrust load, the 2nd angular contact ball bearing 86,87 as thrust-bearing.But thrust-bearing involved in the present invention may not necessarily be defined in the thrust-bearing of this structure.For example; Can be one group of tapered roller bearing with same form assembling; Even can also be determined thrust load also only from the purposes that a side applies the time for for example being used in sense of rotation in qualification, only dispose 1 structure that only can bear the thrust-bearing (for example for being equivalent to the thrust-bearing of the 1st angular contact ball bearing 86 in the above-mentioned mode of execution) of the thrust load of this direction.And, can also be as intersect roller, self-aligning roller bearing or the self-aligning ball bearing, monomer available bears the bearing of two-way thrust load and so on.When this only assembling " 1 " monomer available is born the sort of bearing of two-way thrust load; When perhaps back-to-back duplex is assembled one group of thrust-bearing; (structure of patent documentation 1 different from the past) also can be from the side assembling input shaft of a side direction needle bearing of angular contact bearing among the present invention; So can be in advance through be pressed into or " rear end " that general such as shrink fit (being assembled with rolling element in the Internal and external cycle) angular contact bearing (remaining untouched) is installed on the input shaft that inserts (in addition; When installing, after cooling off, insert input shaft) with the shrink fit mode.
By the way, even common ball bearing or deep trouth ball bearing also can bear some thrust loads through suitably limiting outer ring and inner ring in the axial direction.In the present invention, these bearings are not also to apply flexibly as the thrust-bearing among the present invention.But; For example for example be used for the situation in the purposes that joint as mechanism hand is applied in stronger thrust load driving sometimes if consider swing internally meshed type planetary gear system involved in the present invention more, then more preferably as can be further (aforesaid) bearing the bearing thrust load reliably.
In addition, in the above-described embodiment, show and crankshaft gear, each bent axle are set on all a plurality of bent axles, still, may not all will have crankshaft gear by all bent axles in the present invention through driven swing internally meshed type planetary gear system of distribution gear while.For example, can be following structure: crankshaft gear (having only 1 bent axle to drive through distribution gear) only is set on 1 in a plurality of bent axles, and other bent axle does not drive through distribution gear, but follows the action of external gear driven yet.
Claims (6)
1. swing internally meshed type planetary gear system possesses input shaft, is arranged at the distribution gear of this input shaft, with the crankshaft gear of this distribution gear engagement and be assembled with the bent axle of this crankshaft gear, it is characterized in that,
The pair of bearings that possesses the said input shaft of supporting,
A side bearing is a needle bearing in this pair of bearings, and the opposing party's bearing is the thrust-bearing that also can bear the thrust load that puts on said input shaft,
The external diameter of the inner ring of said needle bearing is greater than the top circle of said distribution gear, and less than the internal diameter of the outer ring of said thrust-bearing.
2. swing internally meshed type planetary gear system as claimed in claim 1 is characterized in that,
The inner ring of said needle bearing separates formation with said input shaft, and the part of said distribution gear stretches into the inboard of the inner ring of this needle bearing.
3. according to claim 1 or claim 2 swing internally meshed type planetary gear system is characterized in that,
Said thrust-bearing is made up of 1 group of angular contact bearing, the direction mutually opposite mode face-to-face duplex assembling of said angular contact bearing to bear said thrust load.
4. production method of swinging the internally meshed type planetary gear system; This swing internally meshed type planetary gear system possesses input shaft, is arranged at the distribution gear of this input shaft, with the crankshaft gear of this distribution gear engagement and be assembled with the bent axle of this crankshaft gear; It is characterized in that, comprise:
The 1st operation is at the outer ring and the needle roller of one of the said input shaft of the main body side of said planetary gear system assembling supporting distolateral needle bearing;
The 2nd operation is in the outer ring that another distolateral thrust-bearing of said input shaft is supported in the main body side assembling of said planetary gear system;
The 3rd operation is at said input shaft assembling or integrally formed said distribution gear;
The 4th operation is at the inner ring of said input shaft assembling or integrally formed said thrust-bearing;
The 5th operation is assembled the rolling element of said thrust-bearing at said input shaft; And
The 6th operation, from the side assembling input shaft of the said needle bearing of a side direction of this thrust-bearing, said input shaft forms or the inner ring and the rolling element of integrated said distribution gear and thrust-bearing.
5. the production method of swing internally meshed type planetary gear system as claimed in claim 4 is characterized in that,
In said the 3rd operation, come integrated in this input shaft through said distribution gear cutting tooth form being formed in said input shaft.
6. like the production method of claim 4 or 5 described swing internally meshed type planetary gear system, it is characterized in that,
Said thrust-bearing is the bearing that 1 group of different angular contact bearing of the direction of said thrust load is born in the configuration of face-to-face duplex,
In said the 2nd operation, the outer ring that is positioned at the angular contact bearing of axial inboard in this group of angular contact bearing is installed on the main body side of planetary gear system,
In said the 3rd～the 5th operation, except said distribution gear and be positioned at this axially the inner ring and rolling element of inboard angular contact bearing, the inner ring and the rolling element that are positioned at the angular contact bearing in the axial outside also are assembled in or are integrally formed at said input shaft,
After said the 6th operation, the outer ring that will be positioned at the said thrust-bearing in the axial outside is assemblied in the main body side of said planetary gear system.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010199190A JP5603717B2 (en) | 2010-09-06 | 2010-09-06 | Oscillating intermeshing planetary gear device and manufacturing method thereof |
| JP2010-199190 | 2010-09-06 |
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| Publication Number | Publication Date |
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| CN102384221A true CN102384221A (en) | 2012-03-21 |
| CN102384221B CN102384221B (en) | 2015-03-11 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201110233217.3A Active CN102384221B (en) | 2010-09-06 | 2011-08-15 | Swinging inner engaged planetary gear apparatus and manufacture method |
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| Country | Link |
|---|---|
| JP (1) | JP5603717B2 (en) |
| CN (1) | CN102384221B (en) |
| DE (1) | DE102011112177B4 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
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| JP2014169736A (en) * | 2013-03-01 | 2014-09-18 | Sumitomo Heavy Ind Ltd | Epicyclic reduction gear |
| CN104769318A (en) * | 2012-11-06 | 2015-07-08 | 纳博特斯克有限公司 | Gear device |
| CN105134888A (en) * | 2015-10-16 | 2015-12-09 | 宋志安 | Precise reduction transmission mechanism |
| CN105526314A (en) * | 2016-02-01 | 2016-04-27 | 武汉市精华减速机制造有限公司 | Direct-connected offset reducer |
| CN108679206A (en) * | 2018-06-03 | 2018-10-19 | 今峰精密机电（上海）有限公司 | A method of reducing speed reducer oil leak, enhancing frictional force |
| CN112427941A (en) * | 2020-03-26 | 2021-03-02 | 宁波市海曙必伟工业自动化有限公司 | Automatic assembly equipment for gear assembly and assembly method thereof |
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Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004270846A (en) * | 2003-03-10 | 2004-09-30 | Ts Corporation | Eccentrically swinging reduction gear, rotary drive device provided therewith and container provided with the rotary drive device |
| JP2008101726A (en) * | 2006-10-20 | 2008-05-01 | Nabtesco Corp | Reduction gear device |
| CN101251166A (en) * | 2007-02-22 | 2008-08-27 | 住友重机械工业株式会社 | Oscillating internally meshing planetary gear system and method for manufacturing eccentric body shaft |
| JP2009287631A (en) * | 2008-05-28 | 2009-12-10 | Nabtesco Corp | Eccentric oscillation type gear device |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3574273B2 (en) * | 1996-06-18 | 2004-10-06 | 株式会社クボタ | Axle drive for traveling vehicles |
| JP3916855B2 (en) * | 2000-07-07 | 2007-05-23 | 住友重機械工業株式会社 | Pinion mounting structure |
| JP2002046077A (en) * | 2000-08-03 | 2002-02-12 | Ryobi Ltd | Impact tool |
| JP2010199190A (en) | 2009-02-24 | 2010-09-09 | Panasonic Corp | Bonding method and device manufacturing method |
-
2010
- 2010-09-06 JP JP2010199190A patent/JP5603717B2/en active Active
-
2011
- 2011-08-15 CN CN201110233217.3A patent/CN102384221B/en active Active
- 2011-09-01 DE DE102011112177.7A patent/DE102011112177B4/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004270846A (en) * | 2003-03-10 | 2004-09-30 | Ts Corporation | Eccentrically swinging reduction gear, rotary drive device provided therewith and container provided with the rotary drive device |
| JP2008101726A (en) * | 2006-10-20 | 2008-05-01 | Nabtesco Corp | Reduction gear device |
| CN101251166A (en) * | 2007-02-22 | 2008-08-27 | 住友重机械工业株式会社 | Oscillating internally meshing planetary gear system and method for manufacturing eccentric body shaft |
| JP2009287631A (en) * | 2008-05-28 | 2009-12-10 | Nabtesco Corp | Eccentric oscillation type gear device |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104769318A (en) * | 2012-11-06 | 2015-07-08 | 纳博特斯克有限公司 | Gear device |
| JP2014169736A (en) * | 2013-03-01 | 2014-09-18 | Sumitomo Heavy Ind Ltd | Epicyclic reduction gear |
| CN105134888A (en) * | 2015-10-16 | 2015-12-09 | 宋志安 | Precise reduction transmission mechanism |
| CN105134888B (en) * | 2015-10-16 | 2018-02-06 | 宋志安 | A kind of accurate reduction gearing mechanism |
| CN105526314A (en) * | 2016-02-01 | 2016-04-27 | 武汉市精华减速机制造有限公司 | Direct-connected offset reducer |
| CN108679206A (en) * | 2018-06-03 | 2018-10-19 | 今峰精密机电（上海）有限公司 | A method of reducing speed reducer oil leak, enhancing frictional force |
| CN112427941A (en) * | 2020-03-26 | 2021-03-02 | 宁波市海曙必伟工业自动化有限公司 | Automatic assembly equipment for gear assembly and assembly method thereof |
| CN112427941B (en) * | 2020-03-26 | 2022-09-06 | 宁波市海曙必伟工业自动化有限公司 | Automatic assembly equipment for gear assembly and assembly method thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102011112177B4 (en) | 2017-02-02 |
| CN102384221B (en) | 2015-03-11 |
| JP5603717B2 (en) | 2014-10-08 |
| DE102011112177A1 (en) | 2012-04-19 |
| JP2012057661A (en) | 2012-03-22 |
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