CN104763778B - Eccentric oscillating-type deceleration device - Google Patents
Eccentric oscillating-type deceleration device Download PDFInfo
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- CN104763778B CN104763778B CN201410520850.4A CN201410520850A CN104763778B CN 104763778 B CN104763778 B CN 104763778B CN 201410520850 A CN201410520850 A CN 201410520850A CN 104763778 B CN104763778 B CN 104763778B
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- external gear
- protuberance
- gear
- deceleration device
- eccentric
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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
- 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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/34—Toothed gearings for conveying rotary motion with gears having orbital motion involving gears essentially having intermeshing elements other than involute or cycloidal teeth
-
- 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
- F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
-
- 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
- F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
- F16H57/0445—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control for supply of different gearbox casings or sections
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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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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
- F16H2001/325—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear comprising a carrier with pins guiding at least one orbital gear with circular holes
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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
- F16H2700/00—Transmission housings and mounting of transmission components therein; Cooling; Lubrication; Flexible suspensions, e.g. floating frames
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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 present invention provides a kind of eccentric oscillating-type deceleration device.According to the present invention, when the supply mouth of lubricant is provided with cap assembly, can make lubricant from the supply mouth to reducing gear portion in flowing become more smoothly so that further shorten lubricant service time.Eccentric oscillating-type deceleration device of the invention possesses：Internal gear, external gear, eccentric shaft, vibrating part, it is linked to the vibrating part and is disposed through the domestic i.e. pin member (32) of the through hole (14A) of external gear, the domestic interior roller i.e. roller member (38) is embedded in outward, it is configured at the 1st cover i.e. cap assembly (53) of the axial load opposition side of external gear, wherein, the lubricating oil i.e. supply mouth of lubricant (70C) is covered with the 1st, pad (80) is configured between the 1st cover and interior roller, there is gap (δ 5) vertically between the pad and external gear, in the protuberance (74) of the 1st axial movement for being covered with limitation external gear, the protuberance is circumferentially set in distance.
Description
The application advocates the priority based on Japanese patent application filed in 7 days January in 2014 2014-001271.Should
The full content of Japanese publication is by reference to being applied in this specification.
Technical field
The present invention relates to a kind of eccentric oscillating-type deceleration device.
Background technology
There is a kind of eccentric oscillating-type deceleration device disclosed in patent document 1.
The deceleration device possesses：The external gear of internal gear and the internal gear internal messing and revolve the external gear eccentric swing
The eccentric shaft for turning.Vibrating part is configured with the axial load side of external gear.It is linked with vibrating part and is disposed through
The pin member of the through hole of external gear.It is embedded with outside pin member as the roller member with the slip promoting member of external gear.
The cap assembly of a part for the shell for constituting the deceleration device is provided with the axial load opposition side of external gear.In cover
Gasket part is configured between part and roller member.Gasket part is abutted with the axial end of roller member, and also with the axle of external gear
Abutted to end face, and limit the axial location of roller member and external gear.
In the deceleration device, in the assembling stage, each portion in the reducing gear portion in shell is pre-coated with as lubricant
Lubricating grease.
Patent document 1：Japanese Unexamined Patent Publication 2011-89542 publications (Fig. 1)
There are the following problems in this deceleration device, i.e. when the supply mouth of lubricant is provided with cap assembly, due to pad
The presence of chip part, the constricted flow of lubricant, so as to expend the time in the supply of lubricant.
The content of the invention
The present invention is completed to solve the problems, such as this conventional, and its problem is to work as to be provided with lubrication on cap assembly
During the supply mouth of agent, can make lubricant from the supply mouth to reducing gear portion in flowing become more smoothly, so as to shorten
The service time of lubricant.
The present invention solves above-mentioned problem by being set to following structure：A kind of eccentric oscillating-type deceleration device, it possesses：It is interior
Gear；External gear, with the internal gear internal messing；Eccentric shaft, rotates the external gear eccentric swing；Vibrating part, is configured at
The axial load side of the external gear；Pin member, is linked to the vibrating part, and be disposed through running through for the external gear
Hole；Roller member, is embedded in outward the pin member；And cap assembly, the axial load opposition side of the external gear is configured at, wherein, in institute
The supply mouth that cap assembly is provided with lubricant is stated, gasket part is configured between the cap assembly and the roller member, in the pad
There is gap vertically between chip part and the external gear, the axial direction shifting of the limitation external gear is provided with the cap assembly
Dynamic protuberance, the protuberance is circumferentially set in distance.
In the present invention, ensure there is gap vertically between gasket part and external gear.On the other hand, set on cap assembly
The protuberance of the axial movement of restricted external gear.The protuberance is circumferentially set in distance.
As a result, the lubricant supplied from the supply mouth of cap assembly can be between the gasket part and external gear
Gap moves radially along external gear.Further, since protuberance is circumferentially set in distance, therefore lubricant can also be crossed
The protuberance is moved radially.Therefore, it is possible to make the lubricant from supply mouth supply swimmingly inside reducing gear portion, from
And the service time of lubricant can be shortened.
According to the present invention, when the supply mouth of lubricant is provided with cap assembly, can make lubricant from the supply mouth to
Flowing in reducing gear portion becomes more smoothly, so as to further shorten the service time of lubricant.
Brief description of the drawings
Fig. 1 is represent eccentric oscillating-type deceleration device involved by one of embodiments of the present invention integrally-built
Sectional view.
Fig. 2 is the amplification view of the major part of Fig. 1.
Fig. 3 is the front view of the cap assembly of the deceleration device of Fig. 1
Fig. 4 is the sectional view along the arrow IV-IV lines of Fig. 3.
Fig. 5 is the stereogram by the reducing gear portion side of above-mentioned cap assembly somewhat upwardly.
In figure：10- deceleration devices, 11- input shafts, 14- external gears, 14A- through holes, 14B- limiting units, 14C- load phases
Toss about end face, 14E- adjacency sections, 16- internal gears, 24- eccentric shafts, 32- domestic (pin member), 32A- axial ends, 34- is convex
Edge part, 36- output shafts, roller (roller member) in 38-, 50- shells, the covers of 53- the 1st (cap assembly), 56- reducing gears portion, 70C-
Supply mouth (supply mouth of lubricating oil), 74- protuberances, 80- pads.
Specific embodiment
Hereinafter, with reference to the accompanying drawings to the structure of the eccentric oscillating-type deceleration device involved by of embodiments of the present invention
Illustrate.
Fig. 1 is represent eccentric oscillating-type deceleration device involved by one of embodiments of the present invention integrally-built
Sectional view.
The eccentric oscillating-type deceleration device 10 makes 2 external gears 14 swing while and internal tooth by 2 eccentric bodies 12
16 internal messings are taken turns, and rotating against as output for being produced between internal gear 16 and external gear 14 is exported.
The input shaft 11 of deceleration device 10 is integrally formed with the motor drive shaft 18A of motor 18.Via key 22 on input shaft 11
It is linked with eccentric shaft 24.2 eccentric bodies 12 are integrally formed with eccentric shaft 24.Passed through in the periphery of eccentric body 12
External gear 14 is assembled with by the eccentric swing rotary of eccentric body bearing 26.External gear 14 swing while with internal gear 16 in
Engagement.
That is, deceleration device 10 is to only exist 1 referred to as central crank of eccentric shaft 24 in the radial direction center of internal gear 16
The eccentric oscillating-type deceleration device of formula.Possesses transfer capacity required for 2 external gears 14 are intended to ensure side by side and by staggering
Eccentric phase is ensuring spin balancing.
The tooth form of external gear 14 is trochoid tooth form, and the tooth form of internal gear 16 is arc toothed.In this embodiment, it is interior
Gear 16 includes：The internal tooth wheel body 17 that is integrally formed with the housing main body 51 of shell 50, it is configured at the internal tooth wheel body 17
The multiple columned export trade 19 of export trade support 17A, the outer roller 20 for being embedded in export trade 19 outward as promoting member is slided.Outer roller
20 internal tooths for constituting internal gear 16.The quantity (quantity of export trade 19 or outer roller 20) of the internal tooth of internal gear 16 is slightly more than external gear
The quantity (only many 1 in the example) of 14 external tooth.
External gear 14 possesses multiple through holes through the external gear 14 in the position of the off-centring from the external gear 14
14A.Domestic 32 (pin members) run through each through hole 14A.It is embedded with outside domestic 32 periphery as the interior roller for sliding promoting member
38.2 times of the offset for having equivalent to eccentric body 12 of gap is ensured between interior roller 38 and each through hole 14A.In external gear
14 axial load side is configured with vibrating part 34.Domestic 32 are pressed into and are linked to the domestic retaining hole 34A of the vibrating part 34
In (can also be integrally formed as a part and vibrating part 34 from the beginning).Vibrating part 34 turns into output shaft 36
Integrally.Output shaft 36 is supported on a pair of taper roll bearings 37.
In addition, the main shell master by having the function of the internal tooth wheel body 17 concurrently of the shell 50 of the deceleration device 10
Body 51, be configured at housing main body 51 load-side output section shell body 52, be configured at the load reverse side of housing main body 51
2nd cover 54 of the 1st cover (cap assembly) 53 and the load-side for being configured at output section shell body 52 is constituted.
In the present invention, as lubricant, lubricating grease can be both used, lubricating oil (oil) can be used again, but in this implementation
Lubricating oil (oil lubrication) is used in mode.Here, the profit pair with the eccentric oscillating-type deceleration device 10 involved by present embodiment
The structure that the supply of lubricating oil is relevant is described in detail.
Fig. 2 is the amplification view of the major part of the eccentric oscillating-type deceleration device 10 involved by present embodiment, Fig. 3
It is the front view of the 1st 53 monomers of cover, Fig. 4 is the sectional view along the arrow IV-IV lines of Fig. 3.Also, Fig. 5 is to cover 53 monomers by the 1st
The stereogram described in the way of so that its axial side of reducing gear portion 56 to be slightly toward upside.
Illustrated since outline, as described above, the eccentric oscillating-type deceleration device 10 involved by present embodiment possesses：It is interior
The external gear 14 of gear 16 and the internal messing of internal gear 16 and make the eccentric shaft 24 that the eccentric swing of external gear 14 rotates.
The axial load side of external gear 14 is configured with vibrating part 34 (Fig. 1).It is linked with vibrating part 34 and is disposed through external tooth
Domestic (pin member) 32 of the through hole 14A of wheel 14.Thus, vibrating part 34 carries out synchronous with the rotation composition of external gear 14
Motion.It is embedded with outside domestic 32 as the interior roller (roller member) 38 of the slip promoting member between external gear 14.
The 1st cover of a part for the shell 50 for constituting the deceleration device 10 is provided with the axial load opposition side of external gear 14
(cap assembly) 53.Pad (gasket part) 80 is configured between the 1st cover 53 and interior roller 38.
Hereinafter, more specifically structure is described in detail.
In this embodiment, the 1st cover (cap assembly) 53 doubles as motor cover.Input is provided with the radial direction center of the 1st cover 53
Side seal 60, prevents the oil leak of the side of reducing gear portion 56 to the side of motor 18.Also, it is central in the radial direction of the 1st cover 53, with
Input side seal 60 is abreast provided with ball bearing 62, input shaft 11 of the ball bearing 62 supporting as motor drive shaft.The ball bearing 62
It is so-called sealed bearings, rolling element 62A is configured at the lubricating place sealed by inner ring 62B, outer ring 62C and seal member 62D
It is interior.Therefore, even if being configured at the axially external of input side seal 60, it is also possible to individually carry out self-lubricating.
Also, as shown in figure 3, interior side opening is radially oriented from the 1 of periphery on the 1st cover 53 oil-feed port 64.Also,
Equally being radially oriented interior side opening from another the 1 of periphery has exhaust outlet 66.In addition, in this embodiment, although by Fig. 3's
The opening portion that left side is depicted is used as oil-feed port 64, but oil-feed port 64 and exhaust outlet 66 are in essentially identical shape, fuel feed pump 68,
69 diameter d68, d69 is also identical, therefore can be using any of which as oil-feed port, and another is used as exhaust outlet.That is, supply
One end of oil pipe 68 is open by oil-feed port 64 to reducing gear portion 56, and the other end of fuel feed pump 68 passes through lubricating oil (lubricant)
Space openings from supply mouth 70C to the side of reducing gear portion 56.
In addition, " supply mouth of lubricant " in the present invention is equivalent to " towards the part of reducing gear portion opening ", i.e. this
In implementation method, equivalent to being labeled with the part of symbol 70C rather than oil-feed port 64." the confession of lubricant i.e., just in the present invention
To mouth " for, it is located in cap assembly (being in this example embodiment the 1st cover 53) to the part of reducing gear portion opening, in this
It is meaningful, for example can be following structure：Another shell body (for example housing main body 51 or with the 1st cover 53 splits motor cover
Deng) in outside opening, and entered into the cap assembly of deceleration device across shell body and opened to reducing gear portion by pipe arrangement
Mouthful.The supply mouth of lubricant involved in the present invention can also be opened in any position in reducing gear portion to cap assembly conversely speaking,
Mouthful.
In addition, closure bolt 63,65 can be installed in oil-feed port 64 and exhaust outlet 66, can be finished outside rear enclosed in fuel feeding
In shell 50.
The supply mouth 70C of lubricating oil (lubricant) with the 1st cover 53 the axial side of reducing gear portion 56 surface on along week
Connected to the circular arc oil circuit 70 for being formed.The radial width of circular arc oil circuit 70 is R.Circular arc oil circuit 70 radially inner side and in axial direction
Load-side, is circumferentially formed with the 1st circumference oil circuit 71 of a circle and the continuous ring-type of circular arc oil circuit 70.
Protuberance 74 is formed with the radial outside of the 1st circumference oil circuit 71 of the 1st cover 53 (refer to Fig. 1, Fig. 3~Fig. 5.Fig. 2
Not shown in).As shown in figure 1, protuberance 74 be arranged at through hole 14A described in the ratio of external gear 14 more by the limit of radial outside
The load reverse side end face 14C of portion 14B processed is abutted, so as to limit the axial movement of the external gear 14.The load phase of limiting unit 14B
Toss about end face 14C in order to the sliding contact of protuberance 74 and by surface grinding machine implement finish.
As depicted in figs. 3 and 5, the protuberance 74 of the 1st cover 53 is circumferentially set in distance.I.e., as a result, do not form protuberance
74 part is relatively formed with recess 76 relative to protuberance 74.Protuberance 74 and recess 76 are alternately arranged in the circumferential,
In the implementation method, recess 76 protuberance 74,4 at was respectively formed with 4 in one week.The circumferential lengths and recess of protuberance 74
76 circumferential lengths are different.In this embodiment, the circumferential lengths of protuberance 74 are formed as being longer than the circumferential lengths of recess 76,
So as to realize the reduction of the contact face pressure between limiting unit 14B of the protuberance 74 with external gear 14.Also, for each recess 76,
Respective circumferential lengths are also different (more long near the length of the recess of fuel feed pump 68,69).
Circumferentially it is formed with the radial outside of the 1st circumference oil circuit 71 of the 1st cover 53, and radially inner side in protuberance 74
Ring-type with axially vertical pad assem-bly faces 78.Pad (gasket part) 80 with the periphery 80A of the pad 80 be arranged at the 1st
The form that the inner circumferential 74A of the end difference of cover 53 is abutted is embedded in the 1st cover 53, and assem-bly faces 78 with the pad and abut.
In this embodiment, pad 80 is made up of the annular plate part of iron (steel) system.Axial direction of the pad 80 with domestic 32
End face 32A to keep gap delta 1 in the way of it is opposed, and also with the axial end 38A of interior roller 38 to keep gap delta 3 in the way of pair
Put.In the present embodiment, the radial width W (outside diameter d 80 of periphery 80A and the internal diameter D80 of inner circumferential 80B) of pad 80 is set as
The entirety of the axial end 38A of interior roller 38 is supported with load-side end face (axial sides of the side of reducing gear portion 56) 80C of pad 80
The size for connecing.In addition, the entirety of axial end 38A of roller 38 is supported with the load-side end face 80C of pad 80 in not necessarily requiring
Connect.
But, the load-side end face 80C of pad 80 is located at the load-side end face 74B (referring to Fig. 1, Fig. 4) than protuberance 74
More lean on axial load opposition side.That is, it is opposite with the load of the limiting unit 14B of external gear 14 in the load-side end face 80C of pad 80
There is gap delta 5 vertically, pad 80 and external gear 14 are not in contact with (pad 80 is not involved in external gear 14 between the 14C of side end face
The position limitation of axial direction).The protuberance 74, insertion ring 15 and the flange that move axially through the 1st cover 53 of the entirety of external gear 14
Part 34 is restricted.
In addition, in this embodiment, external gear 14 possesses and limiting unit 14B phases in the radially inner side of limiting unit 14B
Adjacent adjacency section 14E.The axial width of limiting unit 14B is W14B, and the axial width of adjacency section 14E is W14E.Limiting unit 14B's
Axial width W14Es (W14B ＞ W14E) of the axial width W14B more than adjacency section 14E.Therefore, in this embodiment, in pad
Between piece 80 and external gear 14, gap delta 5 is formed with limiting unit 14B, 14E is formed with (more than the gap delta 5) in adjacency section
Gap delta 11.
In the present embodiment, the opening portion of the axial load side of the circular arc oil circuit 70 of the cover 53 of the closing of pad 80 the 1st
70A (refers to Fig. 1, Fig. 2).That is, the lubricating oil for being configured to be flowed into from supply mouth 70C is not fed directly to deceleration from circular arc oil circuit 70
The side of mechanism part 56, but the radially inner side for crossing pad 80 is flowed into the side of reducing gear portion 56.In other words, it is configured to be flowed into circle
The lubricating oil of arc oil circuit 70 via with the continuous 1st circumference oil circuit 71 of the radially inner side of the circular arc oil circuit 70 from (needing most lubrication
) eccentric body bearing 26 nearby be flowed into the side of reducing gear portion 56.
It is provided with opposed with the export trade support 17A of internal tooth wheel body 17 in the radial outside of the protuberance 74 of the 1st cover 53
Internal gear opposed portion 82.The outside diameter d 82 of internal gear opposed portion 82 more than export trade 19 innermost diameter (from the axle center O1 of input shaft 11 to
2 times of the inner most size of export trade 19) D19.That is, export trade 19 from internal tooth wheel body 17 is prevented by the internal gear opposed portion 82
Export trade support 17A come off vertically.In the end face of axially the 1st cover side of the export trade support 17A of internal tooth wheel body 17
Gap delta 7 is formed between the internal gear opposed portion 82 of the covers of 17A1 and the 1st 53, in axial end portion 19A and the internal gear pair of export trade 19
Put and be formed with gap delta 9 between portion 82.
The 2nd is formed with the way of one week by along the circumferential direction in the radial outside of the internal gear opposed portion 82 of the 1st cover 53
Circumference oil circuit 84.2nd circumference oil circuit 84 is configured to deeper be worn to axial load opposition side than internal gear opposed portion 82, so as to
The lubricating oil entered into the 2nd circumference oil circuit 84 can be made circumferentially swimmingly to flow.
In addition, in Fig. 1, symbol 86,87 is O-ring, also, symbol 88 is to be passed through between the cover of output shaft 36 and the 2nd 54
The output side seal configured by endless member 55.By these O-rings 86,87 and output side seal 88 and the input side seal
60, sealed in the shell 50 of deceleration device 10.
Then, the effect to the eccentric oscillating-type deceleration device 10 is illustrated.
Fig. 1 is referred again to, if the input shaft 11 of the deceleration device 10 being integrally formed with motor drive shaft 18A being somebody's turn to do by motor 18
The rotation of motor drive shaft 18A and rotate, then the eccentric shaft 24 for linking with input shaft 11 via key 22 rotates.If eccentric shaft 24 revolves
Turn, then the eccentric body 12 for being formed as one with the eccentric shaft 24 rotates, input shaft 11 often rotate 1 enclose when, external gear 14 via
The eccentric swing of eccentric body bearing 26 rotates 1 time.As a result, what the position of engagement of generation external gear 14 and internal gear 16 was deviateed successively
Phenomenon, it is poor to the number of teeth of internal gear 16 corresponding that external gear 14 rotates against (rotation) relative to the internal gear 16 in stationary state
Amount, i.e., " 1 tooth amount ".The rotation composition via the domestic 32 axial load sides for being transferred to be configured at external gear 14 vibrating part
34, so as to the output shaft 36 being integrally formed with vibrating part 34 rotates.As a result, can realize equivalent to (internal gear 16 with it is outer
The number of teeth of gear 14 is poor) the deceleration of/speed reducing ratio of (number of teeth of external gear 14).
Method as being lubricated for each portion to the eccentric oscillating-type deceleration device 10 involved by this structure, such as
Foregoing patent document 1, there are as below methods, i.e., in the assembling stage in reducing gear portion 56, each constitutive requirements are coated with moisten in advance
The lubricants such as consistent lubricant.But, be present limitation in the aspect of the amount of the lubricant that the method can ensure that in shell 50, had according to purposes
Sufficient greasy property may be cannot get.
In contrast, such as present embodiment, when using from oil-feed port 64 via supply mouth 70C by lubricating oil (as described above,
Or lubricating grease) feeding deceleration device 10 reducing gear portion 56 method when, the lubricating oil of q.s can be enclosed.But
It is, when the method is used in " eccentric oscillating-type " deceleration device 10 of such as present embodiment, the configuration bit of supply mouth 70C
It is problem to be set to.For example, setting supply mouth (70C) and from the housing main body 51 to reducing gear portion in housing main body 51 when using
During the structure of 56 supply lubricating oil, the positioning element of the grade of insertion ring 15 external gear 14 hinders moving radially for lubricating oil, therefore real
On border, lubricating oil right and wrong are nearby supplied to (needing most lubrication) the eccentric body bearing 26 of the radially inner side positioned at the external gear 14
Often difficult.
Therefore, in the present embodiment, supply mouth 70C is set on the 1st cover (cap assembly) 53.Thus, by following work
With can well supply lubricating oil to the vicinity of eccentric body bearing 26.That is, if from oil-feed port 64 by fuel feed pump 68 via setting
The supply mouth 70C supply lubricating oil of the 1st cover 53 is placed in, then lubricating oil arrives first at the (arrow of circular arc oil circuit 70 from supply mouth 70C
A1).Closed by pad 80 the axial side of reducing gear portion 56 of circular arc oil circuit 70.Therefore, all profits of the circular arc oil circuit 70 are reached
Lubricating oil enters into the 1st circumference oil circuit 71 being continuously formed with the radially inner side of circular arc oil circuit 70, while throughout all-round, while logical
The radially inner side for crossing pad 80 nearby spreads (arrow A2, A3) from eccentric body bearing 26 to the side of reducing gear portion 56.Therefore, it is possible to
Make lubricating oil first near the eccentric body bearing 26 for needing most lubrication.
In this embodiment, between pad 80 and external gear 14, gap delta 5 has been axially formed in limiting unit 14B,
(more than the gap delta 5) gap delta 11 is axially formed in the adjacency section 14E of the radially inner side of limiting unit 14B.On the other hand,
Roller 38 exists in interval in the circumferential in multiple.Therefore, the lubricating oil for reaching the 1st circumference oil circuit 71 can be by circumference
The gap delta 5, gap delta 11 that roller 38 is axially formed between external gear 14 and pad 80 each other is moved to radial outside
Dynamic (arrow A5).Now, especially in the 14E of adjacency section, it is able to ensure that (more than limiting unit 14B relative to the cover of pad 80 or the 1st 53
In gap delta 5) gap delta 11, therefore, it is possible to further promote the movement of lubricating oil.
Also, gap delta 1 is formed between pad 80 and domestic 32 axial end 32A, and in pad 80 and interior roller 38
Axial end 38A between be formed with gap delta 3, therefore lubricating oil can also be moved via the gap delta 1, gap delta 3 to radial outside
Dynamic (arrow A4).As a result, can be between domestic 32 and interior roller 38 and between the through hole 14A and interior roller 38 of external gear 14
It is sufficiently fed lubricating oil.
Consequently, it is possible to because the protuberance 74 of the 1st cover 53 is circumferentially set in distance, therefore it is outside to reach the footpath of pad 80
The lubricating oil of side further can move (arrow A6) via (being not provided with the protuberance 74) recess 76 to radial outside.
53 internal gear is covered in axially the 1st end face 17A1 and the 1st for covering side of the export trade support 17A of internal tooth wheel body 17
Gap delta 7 is formed between opposed portion 82, gap delta is formed between the axial end portion 19A and internal gear opposed portion 82 of export trade 19
9.Therefore, lubricating oil can reach the 2nd circle of the radial outside for being formed at internal gear opposed portion 82 via the gap delta 7, gap delta 9
All oil circuits 84 (arrow A7, A8).2nd circumference oil circuit 84 is formed in the way of circumferentially around one week, thereby, it is possible to export trade 19 with
Lubricating oil is supplied well between export trade support 17A, between export trade 19 and outer roller 20 and between outer roller 20 and external gear 14.
Also, in the present embodiment, due to pad 80 periphery 80A be arranged at the 1st cover 53 end difference inner circumferential
74A is diametrically abutted, therefore, it is possible to simply carry out positioning of the pad 80 relative to the 1st cover 53 such that it is able to good all the time
Ground ensures the gap delta 3 between pad 80 and the axial end 38A of interior roller 38.
Thus, for example with conventional gasket part compared with the structure that the axial end of interior roller or external gear is abutted, can
Smoothly it is lubricated supply, the movement of oil such that it is able to fuel feeding (supply of lubricant) is completed in shorter time.Especially
Its by motor configurations in vertical upper side, output shaft be configured at vertical lower side it is placed longitudinally in the case of, because gasket part into
To cover the state in reducing gear portion, therefore the lubrication system is more effectively.
And, external gear 14 at limiting unit 14B with the 1st cover 53 protuberance 74 abut, by with the protuberance 74
Abut the axial movement for reliably limiting external gear 14.The load reverse side end face 14C of limiting unit 14B is implemented by surface grinding machine
Finishing, thus it is smaller with resistance to sliding between protuberance 74.And, the axial width W14B of limiting unit 14B is formed as
Axial width W14E more than the adjacency section 14E of limiting unit 14B is (because the axial width W14E of adjacency section 14E is less than limitation
The axial width W14B of portion 14B), therefore adjacency section 14E neither abuts with protuberance 74, and do not abut with pad 80.Therefore, it is right
In adjacency section 14E, can omit using the finishing of surface grinding machine such that it is able to realize the contracting of the process time of external gear 14
Short and processing cost reduction.
In addition, in the above-described embodiment, the protuberance 74 of the 1st cover 53 and the external gear 14 that is abutted with the protuberance 74
Limiting unit 14B is arranged at the radial outside of pad (gasket part) 80, but in the present invention, can also make the protuberance of cap assembly and
The restriction site of external gear is in the radially inner side of gasket part.I.e., now, external gear is in the radial position near eccentric body bearing
It is limited vertically, so that adjacency section is located at the radial outside of limiting unit.In the structure shown here, because protuberance is circumferentially in interval
Set, therefore lubricating oil can be moved about via the recess between the protuberance to eccentric body bearing.Also, lubricating oil is from
Gap of the 1 circumference oil circuit 71 between through hole 14A and interior roller 38 and by the axial direction between external gear 14 and external gear 14
Gap, additionally it is possible to supplied to eccentric body bearing 26 from the radially inner side of insertion ring 15.
Also, gasket part can also be in the way of the inner circumferential of the gasket part be diametrically abutted with the periphery of cap assembly
It is assembled in cap assembly.Thus, in the same manner as above-mentioned implementation method, gasket part determining relative to cap assembly can simply be carried out
Position such that it is able to consistently well ensure the gap between gasket part and the axial end of roller member (between in above-mentioned example
Gap δ 3).
Also, in the above-described embodiment, the circumferential lengths of protuberance 74 are formed as being longer than the circumferential lengths of recess 76, but
The circumferential lengths of protuberance 74 and recess 76 can also be identical.Also, for example, when pay the utmost attention to lubricating oil it is mobile when, also may be used
So that the circumferential lengths of recess 76 are longer.Each protuberance 74 and the respective circumferential lengths of each recess 76 can be real as described above with identical
Apply mode, it is also possible to different.Also, the quantity of formation of protuberance 74 and recess 76 may not be at 4 (can be more or less than 4
Place).
In addition, in the above-described embodiment, showing and being embedded with outside the periphery of the export trade 19 of internal gear 16 as slip rush
Enter the configuration example of the outer roller 20 of part, but in the present invention, the assembling of the slip promoting member of this internal gear side is not necessarily
It is necessary.
Claims (3)
1. a kind of eccentric oscillating-type deceleration device, it possesses：Internal gear；External gear, with the internal gear internal messing；Eccentric shaft,
Rotate the external gear eccentric swing；Vibrating part, is configured at the axial load side of the external gear；Pin member, is linked to this
Vibrating part, and it is disposed through the through hole on the external gear；Roller member, is embedded in outward the pin member；And cap assembly, match somebody with somebody
The axial load opposition side of the external gear is placed in, the eccentric oscillating-type deceleration device is characterised by,
The supply mouth of lubricant is provided with the cap assembly,
Gasket part is configured between the cap assembly and the roller member,
There is gap vertically between the gasket part and the external gear,
The protuberance of the axial movement for abutting and limiting the external gear with the external gear is provided with the cap assembly,
The protuberance is circumferentially set in distance,
The load-side end face of the gasket part is located at and more leans on axial load opposition side than the load-side end face of the protuberance.
2. eccentric oscillating-type deceleration device according to claim 1, it is characterised in that
The gasket part and the cap assembly are diametrically abutted.
3. eccentric oscillating-type deceleration device according to claim 1 and 2, it is characterised in that
The external gear possesses：The limiting unit abutted with the protuberance and the adjacency section diametrically adjacent with the limiting unit,
Axial width of the axial width of the limiting unit more than the adjacency section.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014001271A JP6109085B2 (en) | 2014-01-07 | 2014-01-07 | Eccentric oscillation type speed reducer |
| JP2014-001271 | 2014-01-07 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104763778A CN104763778A (en) | 2015-07-08 |
| CN104763778B true CN104763778B (en) | 2017-06-06 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410520850.4A Active CN104763778B (en) | 2014-01-07 | 2014-09-30 | Eccentric oscillating-type deceleration device |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6109085B2 (en) |
| KR (1) | KR101612395B1 (en) |
| CN (1) | CN104763778B (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6563784B2 (en) * | 2015-11-06 | 2019-08-21 | 住友重機械工業株式会社 | Eccentric oscillation type speed reducer |
| JP6758845B2 (en) * | 2016-02-12 | 2020-09-23 | 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 |
| JP7193976B2 (en) * | 2018-10-18 | 2022-12-21 | 住友重機械工業株式会社 | Eccentric oscillating reduction gear |
| JP6871283B2 (en) * | 2019-01-28 | 2021-05-12 | ファナック株式会社 | robot |
| CN114729678B (en) | 2019-11-18 | 2023-01-13 | 三菱电机株式会社 | Reduction gear and industrial robot |
| JP7481106B2 (en) | 2019-12-03 | 2024-05-10 | ファナック株式会社 | Joint structure of industrial robots |
| US11434978B1 (en) * | 2021-06-23 | 2022-09-06 | Tsun-Tien Yao | Roller-type speed reduction mechanism with lateral output |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001108039A (en) | 1999-10-07 | 2001-04-20 | Sumitomo Heavy Ind Ltd | Planetary roller type friction gearing |
| KR100771666B1 (en) * | 2006-09-11 | 2007-11-01 | 주식회사 해성산전 | Oil pump assembly for reducer |
| DE112008003469B4 (en) * | 2007-12-21 | 2012-10-04 | Sumitomo Heavy Industries, Ltd. | Reduction gear |
| JP5060969B2 (en) * | 2008-01-15 | 2012-10-31 | 住友重機械工業株式会社 | Robot joint drive device |
| JP5006838B2 (en) * | 2008-01-30 | 2012-08-22 | 住友重機械工業株式会社 | Reduction gear |
| JP5158861B2 (en) * | 2008-03-11 | 2013-03-06 | Ｎｔｎ株式会社 | In-wheel motor drive device |
| JP2011089542A (en) * | 2009-10-20 | 2011-05-06 | Sumitomo Heavy Ind Ltd | Planetary gear device |
| JP5474577B2 (en) * | 2010-01-08 | 2014-04-16 | 住友重機械工業株式会社 | Swing intermeshing planetary gear unit |
| CN201651111U (en) * | 2010-02-10 | 2010-11-24 | 山东科技大学 | Liquid viscosity speed regulating device |
| JP5822392B2 (en) * | 2011-12-15 | 2015-11-24 | 住友重機械工業株式会社 | Eccentric rocking speed reducer |
| JP5779120B2 (en) * | 2012-02-24 | 2015-09-16 | 住友重機械工業株式会社 | Eccentric oscillation type speed reducer |
| JP5816582B2 (en) * | 2012-03-21 | 2015-11-18 | 住友重機械工業株式会社 | Eccentric oscillation type speed reducer and manufacturing method of external gear |
-
2014
- 2014-01-07 JP JP2014001271A patent/JP6109085B2/en active Active
- 2014-09-30 CN CN201410520850.4A patent/CN104763778B/en active Active
- 2014-10-02 KR KR1020140133117A patent/KR101612395B1/en active IP Right Grant
Also Published As
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| JP2015129553A (en) | 2015-07-16 |
| KR101612395B1 (en) | 2016-04-14 |
| JP6109085B2 (en) | 2017-04-05 |
| KR20150082069A (en) | 2015-07-15 |
| CN104763778A (en) | 2015-07-08 |
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