CN104763778A - Eccentrically swinging reducer device - Google Patents
Eccentrically swinging reducer device Download PDFInfo
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- CN104763778A CN104763778A CN201410520850.4A CN201410520850A CN104763778A CN 104763778 A CN104763778 A CN 104763778A CN 201410520850 A CN201410520850 A CN 201410520850A CN 104763778 A CN104763778 A CN 104763778A
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- external gear
- cover
- gear
- protuberance
- eccentric
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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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—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)
- Retarders (AREA)
- General Details Of Gearings (AREA)
Abstract
The invention provides an eccentrically swinging reducer device. According to the invention, when a supplying port for lubricant is formed in a cover component,lubrcant can smoothly flow to the reducer from the supplying port, so lubricant supplying time can be further shortened; the eccentrically swinging reducer device comprises an internal gear, an external gear, an eccentric body axis, a flange component, an inner pin, namely a pin component (32) connected to the flange component and passing through a through hole (14A) formed in the external gear,an inner roller component, namely a roller component (38) externally embedded nto the inner pin, and a first cover, namely a cover component (53) configured to an axial load opposite side of the external gear. A supplying port (70C) for lubricant, namely lubricating oil is formed in the first cover; a gasket (80) is configured betweeen the first cover and the inner roller; a gap (Delta 5) is axially arranged between the gasket and the external gear; the first cover is provided with protruding parts (74) limiting axial movemnts of the external gear; and the protruding part is circumferentially ararnged at intervals.
Description
The application advocates the preference of No. 2014-001271, the Japanese patent application based on application on January 7th, 2014.The full content of this Japanese publication is by reference to being applied in this specification.
Technical field
The present invention relates to a kind of eccentric oscillating-type speed reducer.
Background technique
A kind of eccentric oscillating-type speed reducer is disclosed in patent documentation 1.
This speed reducer possesses: internal gear, with the external gear of this internal gear internal messing and eccentric shaft that this external gear eccentric swing is rotated.Vibrating part is configured with in the axial load side of external gear.Vibrating part is linked with the pin parts running through the penetration hole being arranged at external gear.The roller member as the slip promoting member with external gear is embedded with outside pin parts.
The cap assembly of a part for the shell forming this speed reducer is provided with at the axial load opposition side of external gear.Gasket part is configured with between hood and roller member.Gasket part abuts with the axial end of roller member, and also abuts with the axial end of external gear, and the axial position of restrict rollers parts and external gear.
In this speed reducer, in the assembling stage, each portion in reducing gear portion is in the enclosure coated with the lubricating grease as oiling agent in advance.
Patent documentation 1: Japanese Unexamined Patent Publication 2011-89542 publication (Fig. 1)
In this speed reducer, there are the following problems, that is, when being provided with the supplying mouth of oiling agent on cap assembly, due to the existence of gasket part, and the constricted flow of oiling agent, thus expend time in the supply of oiling agent.
Summary of the invention
The present invention completes to solve this problem in the past, its problem is when being provided with the supplying mouth of oiling agent on cap assembly, oiling agent can be made to become more smooth and easy from this supplying mouth to the flowing in reducing gear portion, thus shorten the service time of oiling agent.
The present invention solves above-mentioned problem by being set to following structure: a kind of eccentric oscillating-type speed reducer, and it possesses: internal gear; External gear, with this internal gear internal messing; Eccentric shaft, makes this external gear eccentric swing rotate; Vibrating part, is configured at the axial load side of described external gear; Pin parts, are linked to this vibrating part, and run through the penetration hole being arranged at described external gear; Roller member, is embedded in this pin parts outward; And cap assembly, be configured at the axial load opposition side of described external gear, wherein, described cap assembly is provided with the supplying mouth of oiling agent, gasket part is configured with between this cap assembly and described roller member, between this gasket part and described external gear, have gap vertically, described cap assembly is provided with the protuberance moved axially of the described external gear of restriction, and this protuberance is circumferentially set in distance.
In the present invention, between gasket part and external gear, guarantee there is gap vertically.On the other hand, cap assembly is provided with the protuberance moved axially of restriction external gear.This protuberance is circumferentially set in distance.
Its result, the oiling agent supplied from the supplying mouth of cap assembly can via gap the moving radially along external gear between described gasket part and external gear.In addition, because protuberance is circumferentially set in distance, therefore oiling agent can also be crossed this protuberance and radially moves.Therefore, it is possible to make from the oiling agent of supplying mouth supply inner throughout reducing gear portion swimmingly, thus the service time of oiling agent can be shortened.
According to the present invention, when being provided with the supplying mouth of oiling agent on cap assembly, oiling agent can be made to become more smooth and easy from this supplying mouth to the flowing in reducing gear portion, thus shorten the service time of oiling agent further.
Accompanying drawing explanation
Fig. 1 is the integrally-built sectional view of the eccentric oscillating-type speed reducer involved by an example representing embodiments of the present invention.
Fig. 2 is the amplification view of the major component of Fig. 1.
Fig. 3 is the plan view of the cap assembly of the speed reducer of Fig. 1
Fig. 4 is the sectional view of the arrow IV-IV line along Fig. 3.
Fig. 5 is by side, the reducing gear portion stereogram a little upward of above-mentioned cap assembly.
In figure: 10-speed reducer, 11-input shaft, 14-external gear, 14A-penetration hole, 14B-limiting unit, 14C-load reverse side end face, 14E-adjacent portion, 16-internal gear, 24-eccentric shaft, 32-domestic (pin parts), 32A-axial end, 34-vibrating part, 36-output shaft, roller (roller member) in 38-, 50-shell, 53-the 1st covers (cap assembly), 56-reducing gear portion, 70C-supplying mouth (supplying mouth of lubricant oil), 74-protuberance, 80-pad.
Embodiment
Below, with reference to the accompanying drawings the structure of the eccentric oscillating-type speed reducer involved by an example of embodiments of the present invention is described.
Fig. 1 is the integrally-built sectional view of the eccentric oscillating-type speed reducer involved by an example representing embodiments of the present invention.
This eccentric oscillating-type speed reducer 10 by 2 eccentric bodies 12,2 external gears 14 are swung while with internal gear 16 internal messing, and the relative rotation produced between internal gear 16 with external gear 14 to be exported as output.
The input shaft 11 of speed reducer 10 becomes to be integrated with the motor drive shaft 18A of motor 18.Input shaft 11 is linked with eccentric shaft 24 via key 22.Eccentric shaft 24 is integrally formed with described 2 eccentric bodies 12.External gear 14 is assembled with via the eccentric swing rotary of eccentric body bearing 26 in the periphery of eccentric body 12.External gear 14 swing while with internal gear 16 internal messing.
That is, speed reducer 10 is the eccentric oscillating-type speed reducer being called central crank-type that only there is 1 eccentric shaft 24 in the radial direction central authorities of internal gear 16.Possess side by side 2 external gears 14 be intended to guarantee required transfer capacity and by the eccentric phase that staggers to guarantee spin balancing.
The profile of tooth of external gear 14 is trochoid profile of tooth, and the profile of tooth of internal gear 16 is arc toothed.In this embodiment, internal gear 16 comprises: the internal gear main body 17 be integrated with the housing main body 51 one-tenth of shell 50, be configured at this internal gear main body 17 export trade support 17A multiple columned export trade 19, be embedded in the outer roller 20 of export trade 19 outward as slip promoting member.Outer roller 20 forms the internal tooth of internal gear 16.The quantity (quantity of export trade 19 or outer roller 20) of the internal tooth of internal gear 16 is a little more than the quantity (in this example only many 1) of the external tooth of external gear 14.
External gear 14 possesses multiple penetration hole 14A running through this external gear 14 in the position of the off-centring from this external gear 14.Domestic 32 (pin parts) run through each penetration hole 14A.Be embedded with outside the periphery of domestic 32 as roller 38 in slip promoting member.Between interior roller 38 and each penetration hole 14A, guarantee to have the gap of 2 times of the offset being equivalent to eccentric body 12.Vibrating part 34 is configured with in the axial load side of external gear 14.Domestic 32 are pressed into and are linked in the domestic retaining hole 34A of this vibrating part 34 and (also can be integrated with vibrating part 34 one-tenth as parts from the beginning).Vibrating part 34 is integrated with output shaft 36 one-tenth.Output shaft 36 is supported on a pair tapered roller bearing 37.
In addition, this speed reducer 10 shell 50 primarily of have concurrently described internal gear main body 17 function described housing main body 51, be configured at the load side of housing main body 51 carry-out part frame 52, be configured at housing main body 51 load reverse side the 1st cover (cap assembly) 53 and be configured at carry-out part frame 52 load side the 2nd cover 54 form.
In the present invention, as oiling agent, both can use lubricating grease, lubricant oil (oil) can be used again, but use lubricant oil (oil lubrication) in the present embodiment.At this, the structure relevant to the supply of the lubricant oil with the eccentric oscillating-type speed reducer 10 involved by present embodiment is described in detail.
Fig. 2 is the amplification view of the major component of eccentric oscillating-type speed reducer 10 involved by present embodiment, and Fig. 3 is the plan view of the 1st cover 53 monomers, and Fig. 4 is the sectional view of the arrow IV-IV line along Fig. 3.Further, Fig. 5 is with the stereogram being carried out towards the mode of upside a little describing in its side, axial reducing gear portion 56 by the 1st cover 53 monomers.
Illustrate from outline, as mentioned above, the eccentric oscillating-type speed reducer 10 involved by present embodiment possesses: internal gear 16, with the external gear 14 of this internal gear 16 internal messing and eccentric shaft 24 that this external gear 14 eccentric swing is rotated.Vibrating part 34 (Fig. 1) is configured with in the axial load side of external gear 14.Vibrating part 34 is linked with domestic (the pin parts) 32 running through the penetration hole 14A being arranged at external gear 14.Thus, vibrating part 34 carries out the motion synchronous with the rotation composition of external gear 14.Roller (roller member) 38 in slip promoting member between being embedded with outside domestic 32 as external gear 14.
The 1st cover (cap assembly) 53 of a part for the shell 50 forming this speed reducer 10 is provided with at the axial load opposition side of external gear 14.Pad (gasket part) 80 is configured with between the 1st cover 53 and interior roller 38.
Below, structure is more specifically described in detail.
In this embodiment, the 1st cover (cap assembly) 53 doubles as motor cover.Be provided with input side oil sealing 60 in the radial direction central authorities of the 1st cover 53, prevent the oil leak of side, reducing gear portion 56 to motor 18 side.Further, in the radial direction central authorities of the 1st cover 53, be provided with ball bearing 62 abreast with input side oil sealing 60, the supporting of this ball bearing 62 doubles as the input shaft 11 of motor drive shaft.This ball bearing 62 is so-called stuffing box bearing, and rolling element 62A is configured at by the lubricating place of inner ring 62B, outer ring 62C and sealed member 62D sealing.Therefore, even if be configured at the axially outside of input side oil sealing 60, also selflubricating can be carried out separately.
Further, as shown in Figure 3, the 1st cover 53 there is oil-feed port 64 from 1 of periphery towards radially inner side opening.Further, relief opening 66 is had towards radially inner side opening equally from another 1 of periphery.In addition, in this embodiment, although the opening portion depicted in the left side at Fig. 3 is used as oil-feed port 64, but the shape that oil-feed port 64 is substantially identical with relief opening 66, diameter d 68, the d69 of fuel supply line 68,69 are also identical, therefore can using wherein any one is as oil-feed port, another uses as relief opening.That is, one end of fuel supply line 68 is by oil-feed port 64 to reducing gear portion 56 opening, and the other end of fuel supply line 68 passes through the space openings of supplying mouth 70C to side, reducing gear portion 56 of lubricant oil (oiling agent).
In addition, " supplying mouth of oiling agent " in the present invention is equivalent to " part towards reducing gear portion opening ", that is, in present embodiment, be equivalent to the part instead of the oil-feed port 64 that mark symbol 70C.Namely, with regard to " supplying mouth of oiling agent " in the present invention, part to reducing gear portion opening is positioned at cap assembly (being the 1st cover 53 in this example embodiment), meaningful in this, can be such as following structure: externally opening in another frame (such as housing main body 51 or with the 1st motor cover etc. of covering 53 splits), and to be striden across in cap assembly that frame enters into speed reducer by pipe arrangement and to reducing gear portion opening.The supplying mouth of oiling agent involved in the present invention conversely speaking, also can in any position in reducing gear portion to cap assembly opening.
In addition, closure bolt 63,65 can be installed in oil-feed port 64 and relief opening 66, can after fuel feeding in closure 50.
The supplying mouth 70C of lubricant oil (oiling agent) with cover the 1st the circular arc oil circuit 70 that the surface of the side, axial reducing gear portion 56 of 53 is circumferentially formed and be communicated with.The radial width of circular arc oil circuit 70 is R.Circular arc oil circuit 70 radially inner side and in axial load side, be circumferentially formed with the 1st circumference oil circuit 71 of a circle and this circular arc oil circuit 70 continuous print ring-type.
Protuberance 74 is formed with (with reference to figure 1, Fig. 3 ~ Fig. 5 at the radial outside of the 1st circumference oil circuit 71 of the 1st cover 53.Not shown in Fig. 2).As shown in Figure 1, protuberance 74 and penetration hole 14A described in the ratio being arranged at external gear 14 more abut by the load reverse side end face 14C of the limiting unit 14B of radial outside, thus limit moving axially of this external gear 14.The load reverse side end face 14C of limiting unit 14B is in order to implement fine finishing with protuberance 74 sliding contact by surface grinding machine.
As depicted in figs. 3 and 5, the protuberance 74 of the 1st cover 53 is circumferentially set in distance.That is, result, the part not forming protuberance 74 is relatively formed with recess 76 relative to protuberance 74.Protuberance 74 and recess 76 be alternately configuration in the circumferential, in this embodiment, is formed with 4 place's protuberance 74,4 place's recesses 76 in one week respectively.The circumferential lengths of protuberance 74 is different from the circumferential lengths of recess 76.In this embodiment, the circumferential lengths of protuberance 74 is formed as the circumferential lengths of being longer than recess 76, thus the reduction of surface of contact pressure between the limiting unit 14B realizing protuberance 74 and external gear 14.Further, for each recess 76, respective circumferential lengths is different (length near the recess of fuel supply line 68,69 is longer) also.
At the radial outside of the 1st circumference oil circuit 71 of the 1st cover 53, and be circumferentially formed with ring-type at the radially inner side of protuberance 74 assemble face 78 with axially vertical pad.Pad (gasket part) 80 with the periphery 80A of this pad 80 be arranged at form that the 1st inner circumferential 74A covering the end difference of 53 abuts and be embedded in the 1st and cover 53, and assemble face 78 with this pad and abut.
In this embodiment, the annular plate parts that pad 80 by iron (steel) is are formed.Pad 80 with domestic 32 axial end 32A to keep the mode of gap delta 1 opposed, and with the axial end 38A of interior roller 38 to keep the mode of gap delta 3 opposed.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 size that the entirety of the axial end 38A of interior roller 38 abuts with load side end face (axial sides of side, the reducing gear portion 56) 80C of pad 80.In addition, necessarily may not require that the entirety of the axial end 38A of interior roller 38 abuts with the load side end face 80C of pad 80.
But the load side end face 80C of pad 80 is positioned at and more leans on axial load opposition side than the load side end face 74B (with reference to figure 1, Fig. 4) of protuberance 74.Namely, between the load side end face 80C of pad 80 and the load reverse side end face 14C of the limiting unit 14B of external gear 14, have gap delta 5 vertically, pad 80 does not contact with external gear 14 (pad 80 does not participate in the position limitation of the axis of external gear 14).This protuberance 74 moving axially through the 1st cover 53 of external gear 14 entirety, insert ring 15 and vibrating part 34 and be restricted.
In addition, in this embodiment, external gear 14 possesses the adjacent portion 14E adjacent with this limiting unit 14B at the radially inner side of limiting unit 14B.The axial width of limiting unit 14B is W14B, and the axial width of adjacent portion 14E is W14E.The axial width W14B of limiting unit 14B is greater than the axial width W14E (W14B > W14E) of adjacent portion 14E.Therefore, in this embodiment, between pad 80 and external gear 14, be formed with gap delta 5 at limiting unit 14B, in adjacent portion, 14E is formed with (being greater than this gap delta 5) gap delta 11.
In the present embodiment, the opening portion 70A (with reference to figure 1, Fig. 2) of the axial load side of the described circular arc oil circuit 70 of the 1st cover 53 closed by pad 80.That is, the lubricant oil being configured to flow into from supplying mouth 70C is not fed directly to side, reducing gear portion 56 from circular arc oil circuit 70, but the radially inner side crossing pad 80 flow into side, reducing gear portion 56.In other words, the lubricant oil being configured to flow into circular arc oil circuit 70 flow into side, reducing gear portion 56 via with radially inner side continuous print the 1st circumference oil circuit 71 of this circular arc oil circuit 70 near (needing most lubrication) eccentric body bearing 26.
The internal gear opposed portion 82 opposed with the export trade support 17A of internal gear main body 17 is provided with at the radial outside of the protuberance 74 of the 1st cover 53.The outside diameter d 82 of internal gear opposed portion 82 is greater than most internal diameter (2 times of the inner most size from the axle center O1 of input shaft 11 to the export trade 19) D19 of export trade 19.That is, prevent export trade 19 from coming off vertically from the export trade support 17A of internal gear main body 17 by this internal gear opposed portion 82.Be formed with gap delta 7 between the internal gear opposed portion 82 of covering 53 at the end face 17A1 and the 1st of axially the 1st cover side of the export trade support 17A of internal gear main body 17, between the axial end portion 19A and internal gear opposed portion 82 of export trade 19, be formed with gap delta 9.
The 2nd circumference oil circuit 84 is formed with in the mode along the circumferential direction around a week at the radial outside of the internal gear opposed portion 82 of the 1st cover 53.2nd circumference oil circuit 84 is configured to deeper wear to axial load opposition side than internal gear opposed portion 82, the lubricant oil entering into the 2nd circumference oil circuit 84 can be made circumferentially to flow swimmingly.
In addition, in FIG, symbol 86,87 is O type circle, and symbol 88 is cover between 54 via the outlet side oil sealing that ring-shaped member 55 configures at output shaft 36 and the 2nd.By these O type circles 86,87 and outlet side oil sealing 88 and described input side oil sealing 60, sealed in the shell 50 of speed reducer 10.
Then, the effect of this eccentric oscillating-type speed reducer 10 is described.
Refer again to Fig. 1, if the input shaft 11 of the speed reducer 10 becoming to be integrated with motor drive shaft 18A is rotated by the rotation of this motor drive shaft 18A of motor 18, then the eccentric shaft 24 linked via key 22 and input shaft 11 rotates.If eccentric shaft 24 rotates, then the eccentric body 12 formed as one with this eccentric shaft 24 rotates, and when input shaft 11 often rotates 1 circle, external gear 14 rotates 1 time via eccentric body bearing 26 eccentric swing.Its result, produce the phenomenon that external gear 14 departs from successively with the engaging position of internal gear 16, external gear 14 rotates (rotation) corresponding amount poor to the number of teeth of internal gear 16 relatively relative to the internal gear 16 being in stationary state, i.e. " 1 tooth amount ".This rotation composition is passed to the vibrating part 34 of the axial load side being configured at external gear 14 via domestic 32, thus rotates with the output shaft 36 that vibrating part 34 one-tenth is integrated.Its result, can realize the deceleration of the reduction speed ratio being equivalent to (internal gear 16 is poor with the number of teeth of external gear 14)/(number of teeth of external gear 14).
As the method for lubricating each portion of the eccentric oscillating-type speed reducer 10 involved by this structure, patent documentation 1 as the aforementioned, has following method, namely at the assembling stage in reducing gear portion 56, in advance to oiling agents such as each constitutive requirements coating lubricating grease.But, there is restriction in the amount of the oiling agent that the method can be guaranteed in shell 50, likely can not get sufficient greasy property according to purposes.
In contrast, as present embodiment, when lubricant oil (as mentioned above, also can be lubricating grease) is sent into the method in reducing gear portion 56 of speed reducer 10 from oil-feed port 64 via supplying mouth 70C by employing, the lubricant oil of q.s can be enclosed.But when adopting the method in " eccentric oscillating-type " speed reducer 10 in such as present embodiment, the allocation position of this supplying mouth 70C becomes problem.Such as, when adopt supplying mouth (70C) is set at housing main body 51 and supplies the structure of lubricant oil from this housing main body 51 to reducing gear portion 56 time, the positioning element inserting external gear such as ring 15 grade 14 hinders moving radially of lubricant oil, therefore in fact, to be positioned at this external gear 14 radially inner side (needing most lubrication) eccentric body bearing 26 near supply lubricant oil be very difficult.
Therefore, in the present embodiment, the 1st cover (cap assembly) 53 arranges supplying mouth 70C.Thus, by following effect, near eccentric body bearing 26, lubricant oil can be supplied well.That is, if supply lubricant oil by fuel supply line 68 via the supplying mouth 70C being arranged at the 1st cover 53 from oil-feed port 64, then first lubricant oil arrive circular arc oil circuit 70 (arrow A 1) from this supplying mouth 70C.The side, axial reducing gear portion 56 of circular arc oil circuit 70 is closed by pad 80.Therefore, the all lubricant oil arriving this circular arc oil circuit 70 enter into the 1st circumference oil circuit 71 formed continuously with the radially inner side of circular arc oil circuit 70, while throughout all-round, spread (arrow A 2, A3) near eccentric body bearing 26 to side, reducing gear portion 56 by the radially inner side of pad 80.Therefore, it is possible to make lubricant oil first near the eccentric body bearing 26 needing most lubrication.
In this embodiment, between pad 80 and external gear 14, be formed with gap delta 5 vertically at limiting unit 14B, be formed with (being greater than this gap delta 5) gap delta 11 vertically at the adjacent portion 14E of the radially inner side of limiting unit 14B.On the other hand, multiple interior roller 38 exists in interval in the circumferential.Therefore, namely the lubricant oil arriving the 1st circumference oil circuit 71 can be formed at this gap delta 5 between external gear 14 and pad 80 each other vertically by the interior roller 38 in circumference, gap delta 11 moves (arrow A 5) to radial outside.Now, especially in the 14E of adjacent portion, 53 can to guarantee the gap delta 11 of (being greater than the gap delta 5 in limiting unit 14B) relative to pad 80 or the 1st cover, therefore, it is possible to promote the movement of lubricant oil further.
And, gap delta 1 is formed between pad 80 and the axial end 32A of domestic 32, and gap delta 3 is formed between pad 80 and the axial end 38A of interior roller 38, therefore lubricant oil can also move (arrow A 4) to radial outside via this gap delta 1, gap delta 3.Its result, fully can supply lubricant oil between domestic 32 and interior roller 38 and between the penetration hole 14A of external gear 14 and interior roller 38.
Thus, because the protuberance 74 of the 1st cover 53 is circumferentially set in distance, the lubricant oil therefore arriving the radial outside of pad 80 can to move (arrow A 6) to radial outside further via (not being provided with this protuberance 74) recess 76.
Be formed with gap delta 7 between the internal gear opposed portion 82 of covering 53 at the end face 17A1 and the 1st of axially the 1st cover side of the export trade support 17A of internal gear main body 17, between the axial end portion 19A and internal gear opposed portion 82 of export trade 19, be formed with gap delta 9.Therefore, lubricant oil can arrive via this gap delta 7, gap delta 9 the 2nd circumference oil circuit 84 (arrow A 7, A8) being formed at the radial outside of internal gear opposed portion 82.2nd circumference oil circuit 84 circumferentially to be formed around the mode of a week, thereby, it is possible to between export trade 19 and export trade support 17A, supply lubricant oil well between export trade 19 and outer roller 20 and between outer roller 20 and external gear 14.
And, in the present embodiment, due to pad 80 periphery 80A be arranged at the 1st inner circumferential 74A covering the end difference of 53 and abut diametrically, therefore, it is possible to carry out the location of pad 80 relative to the 1st cover 53 simply, thus the gap delta 3 between the axial end 38A that can guarantee pad 80 and interior roller 38 all the time well.
Thus, such as, compared with the structure abutted with the axial end of gasket part in the past and interior roller or external gear, smoothly can carry out supply, the movement of lubricant oil, thus fuel feeding (supply of oiling agent) can be completed in shorter time.Especially, when motor configurations is configured at the longitudinal direction placement of vertical lower side in vertical upper side, output shaft, because gasket part becomes the state covering reducing gear portion, therefore this lubricating structure is more effective.
And the protuberance 74 that external gear 14 covers 53 at limiting unit 14B place and the 1st abuts, by reliably limiting moving axially of external gear 14 with abutting of this protuberance 74.The load reverse side end face 14C of limiting unit 14B implements fine finishing by surface grinding machine, and the slip resistance therefore and between protuberance 74 is less.And, the axial width W14B of limiting unit 14B is formed as the axial width W14E (the axial width W14E due to adjacent portion 14E is less than the axial width W14B of limiting unit 14B) of the adjacent portion 14E being greater than this limiting unit 14B, therefore adjacent portion 14E neither abuts with protuberance 74, does not abut again with pad 80.Therefore, for this adjacent portion 14E, the fine finishing utilizing surface grinding machine can be omitted, thus the shortening of the process time of external gear 14 and the reduction of processing cost can be realized.
In addition, in the above-described embodiment, the protuberance 74 of the 1st cover 53 and the limiting unit 14B of external gear 14 abutted with this protuberance 74 are arranged at the radial outside of pad (gasket part) 80, but in the present invention, the protuberance of cap assembly and the restriction site of external gear also can be made in the radially inner side of gasket part.That is, now, external gear is limited vertically in the radial position near eccentric body bearing, thus adjacent portion is positioned at the radial outside of limiting unit.In the structure shown here, because protuberance is circumferentially set in distance, therefore lubricant oil can move near eccentric body bearing via the recess between this protuberance.Further, lubricant oil via the gap between penetration hole 14A and interior roller 38 and by the axial clearance between external gear 14 and external gear 14, can also be supplied to eccentric body bearing 26 from the radially inner side inserting ring 15 from the 1st circumference oil circuit 71.
Further, the mode that gasket part also can abut with the inner circumferential of this gasket part and the periphery of cap assembly is diametrically assembled in cap assembly.Thus, in the same manner as above-mentioned mode of execution, the location of gasket part relative to cap assembly can be carried out simply, thus the gap (gap delta 3 in above-mentioned example) between gasket part and the axial end of roller member can be guaranteed all the time well.
Further, in the above-described embodiment, the circumferential lengths of protuberance 74 is formed as the circumferential lengths of being longer than recess 76, but protuberance 74 also can be identical with the circumferential lengths of recess 76.Further, such as, when paying the utmost attention to lubricant oil mobile, the circumferential lengths of recess 76 also can be made longer.Each protuberance 74 and the respective circumferential lengths of each recess 76 can be identical, as above-mentioned mode of execution, and also can be different.Further, the quantity of formation of protuberance 74 and recess 76 may not be 4 places (can greater or less than 4 places).
In addition, in the above-described embodiment, show the structure example being embedded with the outer roller 20 as slip promoting member outside the periphery of the export trade 19 of internal gear 16, but in the present invention, the assembling of the slip promoting member of this internal gear side not necessarily necessary.
Claims (3)
1. an eccentric oscillating-type speed reducer, it possesses: internal gear; External gear, with this internal gear internal messing; Eccentric shaft, makes this external gear eccentric swing rotate; Vibrating part, is configured at the axial load side of described external gear; Pin parts, are linked to this vibrating part, and run through the penetration hole be arranged on described external gear; Roller member, is embedded in this pin parts outward; And cap assembly, be configured at the axial load opposition side of described external gear, the feature of described eccentric oscillating-type speed reducer is,
The supplying mouth of oiling agent is provided with at described cap assembly,
Gasket part is configured with between this cap assembly and described roller member,
Between this gasket part and described external gear, vertically there is gap,
Described cap assembly is provided with the protuberance moved axially of the described external gear of restriction,
This protuberance is circumferentially set in distance.
2. eccentric oscillating-type speed reducer according to claim 1, is characterized in that,
Described gasket part and described cap assembly abut diametrically.
3. eccentric oscillating-type speed reducer according to claim 1 and 2, is characterized in that,
Described external gear possesses: the limiting unit abutted with described protuberance and the adjacent portion adjacent diametrically with this limiting unit,
The axial width of described limiting unit is greater than the axial width of described adjacent portion.
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 |
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| CN104763778A true CN104763778A (en) | 2015-07-08 |
| CN104763778B CN104763778B (en) | 2017-06-06 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201410520850.4A Active CN104763778B (en) | 2014-01-07 | 2014-09-30 | Eccentric oscillating-type deceleration device |
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| Country | Link |
|---|---|
| JP (1) | JP6109085B2 (en) |
| KR (1) | KR101612395B1 (en) |
| CN (1) | CN104763778B (en) |
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| CN107084229A (en) * | 2016-02-12 | 2017-08-22 | 住友重机械工业株式会社 | Eccentrically swinging gear device |
| CN108458056A (en) * | 2017-02-17 | 2018-08-28 | 住友重机械工业株式会社 | Eccentric oscillation gear device |
| CN111075890A (en) * | 2018-10-18 | 2020-04-28 | 住友重机械工业株式会社 | Eccentric oscillating type reduction gear |
| US11434978B1 (en) * | 2021-06-23 | 2022-09-06 | Tsun-Tien Yao | Roller-type speed reduction mechanism with lateral output |
| DE112019007809B4 (en) | 2019-11-18 | 2023-12-07 | Mitsubishi Electric Corporation | Gear reducer and industrial robot |
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| JP6563784B2 (en) * | 2015-11-06 | 2019-08-21 | 住友重機械工業株式会社 | Eccentric oscillation type speed reducer |
| JP6871283B2 (en) * | 2019-01-28 | 2021-05-12 | ファナック株式会社 | robot |
| JP7481106B2 (en) | 2019-12-03 | 2024-05-10 | ファナック株式会社 | Joint structure of industrial robots |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN104763778B (en) | 2017-06-06 |
| KR101612395B1 (en) | 2016-04-14 |
| JP6109085B2 (en) | 2017-04-05 |
| KR20150082069A (en) | 2015-07-15 |
| JP2015129553A (en) | 2015-07-16 |
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