CN104373520A - Eccentrically swinging reducer device - Google Patents
Eccentrically swinging reducer device Download PDFInfo
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- CN104373520A CN104373520A CN201410167858.7A CN201410167858A CN104373520A CN 104373520 A CN104373520 A CN 104373520A CN 201410167858 A CN201410167858 A CN 201410167858A CN 104373520 A CN104373520 A CN 104373520A
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- China
- Prior art keywords
- external gear
- liner
- speed reducer
- roller member
- eccentric
- Prior art date
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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
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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
- F16H13/00—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members
- F16H13/06—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members with members having orbital motion
- F16H13/08—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members with members having orbital motion with balls or with rollers acting in a similar manner
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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
- F16H57/08—General details of gearing of gearings with members having orbital motion
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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
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
- F16H25/20—Screw mechanisms
- F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
- F16H25/2247—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with rollers
- F16H2025/2276—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with rollers using roller spacers, i.e. spacers separating the rollers, e.g. by forming a complete chain
Abstract
The invention provides an eccentrically swinging reducer device. The reducer device restrains a liner part disposed between a roller part and a cover part from being worn. The reducer device (12) is provided with an inner gear (14), an outer gear (16), an input shaft (an eccentric body shaft) (18), a flange part (36), a pin part (38) penetrating through a penetrating hole (16A) of the outer gear, a roller part (40) externally embedded in the pin part (38) and a cover (54) disposed on the other side part in the axial direction of the outer gear. A liner (70) is disposed between the roller part (40) and the cover (54). The outer gear (16) is provided with a recessed part (16D) storing the liner (70). The inner circumferential face (70B) and the outer circumferential face (70A) of the liner (70) contact with the outer gear (16).
Description
The application advocates the preference of No. 2013-168750th, the Japanese patent application based on application on August 14th, 2013.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
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.
An axially sidepiece of external gear is configured with vibrating part.Vibrating part is linked with the pin parts running through the penetration hole being arranged on external gear.The upper outside roller member being embedded with slip for promoting these pin parts and external gear of pin parts.
Axial the other side of external gear is configured with the cap assembly of the axial side covering speed reducer.Accompany positioning plate (liner component) between this cap assembly and described roller member, carried out the axial limiting of roller member by this positioning plate.
The speed reducer of patent documentation 1 passes through this structure, as the output of this speed reducer, via described roller member and the relative rotation of pin parts output inner gear with external gear.
Patent documentation 1: Japanese Unexamined Patent Publication 2009-204156 publication
But, in the eccentric oscillating-type speed reducer of this structure, there is the problem that the liner component be configured between roller member with cap assembly causes because abutting with this roller member easily wearing and tearing.
Summary of the invention
The present invention completes to solve this problem in the past, and its problem is to provide a kind of eccentric oscillating-type speed reducer, and it can suppress the liner component advanced wear be configured between roller member and cap assembly.
The present invention is the mechanism of investigation liner component advanced wear, and makes according to the result of study obtained by this result.Carry out aftermentioned about this result of study.
The present invention solves above-mentioned problem by 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 in an axially sidepiece of described external gear; Pin parts, link with this vibrating part, and run through the penetration hole be arranged on described external gear; Roller member, fitted on these pin parts; Cap assembly, be configured in axial the other side of described external gear, wherein, between described roller member and described cap assembly, be configured with liner component, described external gear has the recess holding described liner component, and the inner circumferential of described liner component and at least side of periphery contact with this external gear.
According to this structure, liner component can be made almost synchronous with the action (rotation and swing) of external gear, therefore, it is possible to suppress the advanced wear of liner component further.
Further, the present invention solves above-mentioned problem equally by 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 in an axially sidepiece of described external gear; Pin parts, link with this vibrating part, and run through the penetration hole be arranged on described external gear; Roller member, fitted on these pin parts; Cap assembly, is configured in axial the other side of described external gear, wherein, between described roller member and described cap assembly, is configured with liner component, and described external gear and described liner component rotate integrally.
According to this structure, the action Complete Synchronization of liner component and external gear, therefore can suppress the advanced wear of liner component equally further.
Further, the present invention solves above-mentioned problem equally by 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 in an axially sidepiece of described external gear; Pin parts, link with this vibrating part, and run through the penetration hole be arranged on described external gear; Roller member, fitted on these pin parts; Cap assembly, is configured in axial the other side of described external gear, and wherein, between described roller member and described cap assembly, the circumference along described external gear is arranged at intervals with liner, and the revolution of this liner component and described pin parts is integrally revolved round the sun.
According to this structure, the revolution of liner component and pin parts can be made synchronously to revolve round the sun, therefore can suppress the advanced wear of liner component equally further.
According to the present invention, the liner component advanced wear be configured between roller member and cap assembly can be suppressed.
Accompanying drawing explanation
Fig. 1 is the sectional view of the structure of the eccentric oscillating-type speed reducer involved by an example representing embodiments of the present invention, comprises major component amplification view.
Fig. 2 is the sectional view of the arrow II-II line along Fig. 1.
Fig. 3 illustrates the eccentric oscillating-type speed reducer involved by an example of another embodiment of the present invention, wherein, (A) be the sectional view being equivalent to Fig. 2, (B) be the partial sectional view of IIIB-IIIB line along (A) in Fig. 3, (C) is the partial sectional view of the IIIC-IIIC line along (A) in Fig. 3.
Fig. 4 is the partial perspective view of the liner of the speed reducer shown in Fig. 3.
Fig. 5 illustrates the eccentric oscillating-type speed reducer involved by an example of another embodiment of the invention, and wherein, (A) is the sectional view being equivalent to Fig. 2, and (B) is the partial sectional view of the VB-VB line along (A) in Fig. 5.
Fig. 6 illustrates the eccentric oscillating-type speed reducer involved by an example of another embodiment of the invention, and wherein, (A) is the sectional view being equivalent to Fig. 2, and (B) is the partial sectional view of the VIB-VIB line along (A) in Fig. 6.
In figure: 12-speed reducer, 14-internal gear, 14A-internal gear main body, 16-external gear, 16A-penetration hole, 16D-recess, 16E-covers side end face, 18-eccentric shaft (input shaft), 28-eccentric body, 32-eccentric body bearing, 34-housing, 36-vibrating part, the end face of the axial external gear side of 36B-, 38-sells parts, 40-roller member, and 40A-covers side end face, 54-covers (cap assembly), 54A-protuberance, 70-liner (liner component).
Embodiment
Below, with reference to the accompanying drawings an example of embodiments of the present invention is described in detail.
Fig. 1 is the sectional view of the structure of the eccentric oscillating-type speed reducer 12 involved by an example representing embodiments of the present invention.Fig. 2 is the sectional view of the arrow II-II line along Fig. 1.
This speed reducer 12 possesses: internal gear 14, with the external gear 16 of this internal gear 14 internal messing and (forming eccentric shaft) input shaft 18 that this external gear 16 eccentric swing is rotated, as output, export the relative rotation produced between internal gear 14 with external gear 16.Speed reducer 12 is the eccentric oscillating-type speed reducer that only there is the what is called " central crank-type " of an eccentric shaft in the radial direction central authorities of internal gear 14.
Below, successively structure is described from input side.
Input shaft 18 is integrated with the motor drive shaft 24 one-tenth of motor 22 (motor drive shaft 24 doubles as the input shaft of speed reducer 12).Input shaft 18 is linked with the starting of oscillation parts 30 possessing two eccentric bodies 28 via key 26.The periphery of each eccentric body 28 is eccentric relative to the axle center O1 of input shaft 18.The periphery of eccentric body 28 can be assembled with external gear 16 by eccentric swing rotatably via eccentric body bearing 32.That is, input shaft 18 and starting of oscillation parts 30 pass through into the eccentric shaft being integrated and forming and external gear 16 eccentric swing is rotated.External gear 16 and internal gear 14 internal messing.
In this mode of execution, internal gear 14 is formed primarily of with lower component: internal gear main body 14A, is integrated with housing 34 one-tenth; Cylindric rest pin 14B, is bearing in this internal gear main body 14A; Outer roller 14C, is rotatably assembled in the periphery of this rest pin 14B, forms the internal tooth of internal gear 14.The interior number of teeth (quantity of outer roller 14C) of internal gear 14 is slightly more than the outer number of teeth (only having more 1 in this example) of external gear 16.
An axially sidepiece of external gear 16 is configured with vibrating part 36.Vibrating part 36 is formed with press-in hole 36A, and pin parts 38 be fitted together to/are attached at by being pressed in this press-in hole 36A.These pin parts 38 run through the penetration hole 16A be arranged on external gear 16.On the periphery of pin parts 38, chimeric (outer) has roller member 40 slidably.The gap of 2 times being equivalent to eccentric body 28 offset is guaranteed between the penetration hole 16A of roller member 40 and external gear 16.
The intermediate portion 42 that vibrating part 36 reduces further via the diameter of axle, is integrated with the output shaft 44 one-tenth that the diameter of axle more reduces.Roller member 40, pin parts 38, vibrating part 36, intermediate portion 42 and output shaft 44 are integrally formed the larger output block 46 of rotation.Output block 46, in described intermediate portion 42 and output shaft 44, is rotatably bearing on housing 34 via two output bearings 48,50.
Housing 34 is formed primarily of with lower component: housing body 34A, is positioned at axial central authorities; Cover (cap assembly) 54, supports described motor drive shaft 24 (input shaft 18) at the load opposition side of housing body 34A; End shield 56, output block 46 described in the load side bearing of this housing body 34A.
Cover 54 is configured in a sidepiece of external gear 16, forms a part for the housing 34 of speed reducer 12, and doubles as a part for motor casing.In addition, motor drive shaft 24 (input shaft 18) is supported on the input shaft bearing 60,62 being configured in this cover 54 and vibrating part 36 respectively.
At this, in the lump with reference to amplification cross section and Fig. 2 of Fig. 1, the structure relevant to roller member 40 axially locating is described in detail.Fig. 2 represents the cross section of the arrow II-II line along Fig. 1, wherein, when (A) represents external gear 16 bias to the top side of Fig. 1, Fig. 2, (B) represent eccentric to lower side time.
As previously mentioned, roller member 40 fitted in run through external gear 16 penetration hole 16A pin parts 38 periphery on.Roller member 40 is not fixed with pin parts 38, circumferentially can slide, and also can move vertically relative to pin parts 38.
Roller member 40 is limited with abutting of vibrating part 36 to the movement of axial ledge parts 36 side by this roller member 40.
On the other hand, roller member 40 is limited to the movement of axial shroud 54 side by following structure.
That is, between roller member 40 and cover 54, be configured with the liner (liner component) 70 of the axial position limiting this roller member 40.External gear 16 has the recess 16D holding this liner 70.The periphery (outer circumferential face 70A) of liner 70 contacts with the periphery wall 16D1 of recess 16D, and the inner circumferential (inner peripheral surface 70B) of liner 70 contacts with the inner circle wall 16D2 of recess 16D.
More specifically, the recess 16D of external gear 16 is formed as ring-type at the side 16E of cover 54 side of this external gear 16, and the diameter of the periphery wall 16D1 of this ring is D16D1, and the diameter of inner circle wall 16D2 is d16D2, and radial dimension is R16, and axial depth is H16D.
In the present embodiment, liner 70 is made up of the flat board of ring-type.Liner 70 possesses the 1st side 70C abutted with the protuberance 54A of this cover 54 in cover 54 side of this flat board, possess the 2nd side 70D abutted with the cover side end face 40A of this roller member 40 in roller member 40 side of this flat board.The thickness of liner 70 is W70, and external diameter is d70A, and internal diameter is D70B, and radial dimension is R70.
The outside diameter d 70A of liner 70 corresponds to the diameter D16D1 of the periphery wall 16D1 of the recess 16D of external gear 16, the diameter D70B of the inner peripheral surface 70B of liner 70 corresponds to the diameter d 16D2 of the inner circle wall 16D2 of recess 16D, and the radial dimension R70 of liner 70 corresponds to the radial dimension R16 of recess 16D.That is, liner 70 is formed with the size being just in time fitted together to recess 16D/contacting.In addition, in present embodiment, liner 70 is formed by the plate of iron class, is undertaken being fitted together to/contacting by " Spielpassung " mode be fitted together to/contacting of recess 16D.In other words, the diameter D16D1 of the periphery wall 16D1 of recess 16D is less times greater than the outside diameter d 70A of liner 70, and the diameter D70B of the inner peripheral surface 70B of liner 70 is less times greater than the diameter d 16D2 of the inner circle wall 16D2 of recess 16D.
In addition, in this embodiment, liner 70 is configured to both its outer circumferential face 70A and inner peripheral surface 70B and all contacts with the periphery wall 16D1 of recess 16D and inner circle wall 16D2, but liner contacts with recess 16D and also can only contact with any one of outer circumferential face 70A and inner peripheral surface 70B.Further, about the way of contact, also can make wherein that one or both contacts in " interference fit " mode.About this point, be described later.
Further, in present embodiment, the axial depth H16D of the recess 16D of external gear 16 is less than the thickness W70 of liner 70 (H16D < W70).That is, only have an axial part for liner 70 to be contained in recess 16D, another part is more outstanding to cover 54 side than the side 16E of the axial shroud side of external gear 16.While this is the intensity in order to ensure liner 70, reduce the axial depth H16D of the recess 16D be formed on external gear 16 as far as possible, thus suppress the intensity of external gear 16 to decline.
In addition, between the cover side end face 38E and the 2nd side 70D of liner 70 of pin parts 38, guarantee have gap delta 1.That is, sell parts 38 (even if having foozle) to contact with the 2nd side 70D of liner 70.
From Fig. 2 clearly, be in any swing position even if the radial dimension R70 of liner 70 is set to external gear 16, the certain size abutted with the cover side end face 40A of roller member 40 of a part of the 2nd side 70D of liner 70.On the other hand, the radial dimension R70 of this liner 70 is slightly less than the outside diameter d 40 (d40 > R70) of roller member 40.That is, liner 70 all can not contact with whole of the cover side end face 40A of roller member 40 in any swing position.Its object is to, spacing as roller member 40, as long as liner 70 abuts just enough with a part of the cover side end face 40A of this roller member 40, therefore in order to suppress the slip resistance of two parts 40,70 as far as possible.In addition, inner circumferential bight 70F1, the 70F2 of cover 54 side of liner 70, bight, periphery 70K1,70K2 are all in roughly 45 degree chamferings.
On the other hand, cover 54 is provided with to the outstanding protuberance 54A of axial roller member 40 side ring shape, and the 1st side 70C of liner 70 contacts with this protuberance 54A.Specifically, the front end of protuberance 54A is square with the axis planar surface portion 54A1, and the 1st side 70C abuts with this planar surface portion 54A1.
The protuberance 54A of cover 54 does not all contact with inner circumferential bight 70F1, bight, the periphery 70K1 of cover cap 54 side of liner 70.
Then, the effect of the eccentric oscillating-type speed reducer 12 involved by present embodiment is described.
By the rotation of the motor drive shaft 24 of motor 22, the input shaft 18 of the speed reducer 12 be integrated with this motor drive shaft 24 one-tenth rotates, then the starting of oscillation parts 30 linked via key 26 and input shaft 18 rotate.If starting of oscillation parts 30 rotate, then the eccentric body 28 be integrally formed with these starting of oscillation parts 30 rotates, and input shaft (eccentric shaft) 18 often rotates once, and external gear 16 rotates once via eccentric swing while eccentric body bearing 32 and internal gear 14 internal messing., there is the phenomenon that external gear 16 misplaces successively with the engaging position of internal gear 14 in its result, external gear 16 rotates the poor amount of the number of teeth of (rotation) itself and internal gear 14 relatively relative to the internal gear 14 of stationary state, i.e. only dislocation " tooth ".This rotation composition is delivered to the vibrating part 36 of the axial side being configured at external gear 16 via roller member 40 and pin parts 38, and the output shaft 44 be integrated with vibrating part 36 one-tenth is rotated.Its result, can realize the deceleration of the reduction speed ratio being equivalent to (internal gear 14 is poor with the number of teeth of external gear 16: be 1 in this example)/(number of teeth of external gear 16).
From the clear mechanism of this transmission of power, when external gear 16 is delivered to pin parts 38 relative to the relative rotation composition of internal gear 14, roller member 40 rotates in the periphery (relative to these pin parts 38) of pin parts 38 and together revolves round the sun around the axle center O1 of input shaft 18 with pin parts 38.Therefore, there are the following problems in the past: on the parts positioned roller member 40, form continuous print in circumference " scratch " (the actual generation confirming scratch) along the revolution track of this roller member 40.Especially, can think: as this mode of execution, the structure that pin parts 38 are outstanding with cantilever position from vibrating part 36, if because of the load applied when running, moment of flexure is applied on pin parts 38, axle center O2 then fitted in the roller member 40 of these pin parts 38 also tilts, therefore the cover side end face 40A of roller member 40 also tilts, therefore the comparatively strong formation affecting on business transduce " scratch " that cause.
Further, larger secondary problem can also be produced, such as, because the rolling surface etc. of slip surface between pin parts 38 and roller member 40 or eccentric body bearing 32 should be entered by " scratch " abrasion powder of producing, to the slip of those parts or rotate and produce harmful effect.
But according to the present embodiment, be configured to as follows: external gear 16 has and holds the recess 16D of liner 70, the outer circumferential face 70A of liner 70 and inner peripheral surface 70B contacts with the periphery wall 16D1 of the recess 16D of this external gear 16 and inner circle wall 16D2 respectively.According to this structure, the action (rotation and swing) " almost synchronous rotary " of liner 70 and external gear 16 can be made, its result, also almost synchronous with the revolution of roller member 40, therefore, it is possible to suppress the wearing and tearing of liner 70, the wearing and tearing produced because of continuous print in circumference " scratch " especially can be suppressed.
At this, carry out more specifically bright to the effect of " almost synchronous rotary ".In present embodiment, the periphery wall 16D1 of the recess 16D of the external gear 16 and outer circumferential face 70A of liner 70, and the inner circle wall 16D2 of recess 16D is all contacted by " Spielpassung " mode with the inner peripheral surface 70B of liner 70.Therefore, although the gap degree difference to some extent of " Spielpassung ", liner 70 sometimes not necessarily completely and the rotation synchronous rotary of external gear 16.Such as, the load being applied to roller member 40 is comparatively light and axle center O2 tilts hardly, liner 70 and roller member 40 with less face press slide sleekly when, liner 70 sometimes not with the rotation synchronous rotary of external gear 16.But, now, carry out because the rotation between liner 70 and roller member 40 itself is round and smooth, therefore produce the wearing and tearing of roller member 40 hardly, almost also do not form the upper continuous print " scratch " of circumference.
On the other hand, such as, when the load of connected driven member is larger etc., under the state that the axle center O2 of roller member 40 tilts, liner 70 and roller member 40 compress into line slip with higher face, become the reason forming circumferentially continuous print " scratch ".
But in present embodiment, when liner 70 compresses into line slip with roller member 40 with higher face, liner 70 is synchronous with the rotation of external gear 16 and easily rotate, therefore, it is possible to prevent from forming the upper continuous print " scratch " of circumference.
As a result, according to the present embodiment, no matter the state of carrying out sleekly is pressed with lower face at liner 70 and the slip of roller member 40, or the state of carrying out under being pressed in high-drag with higher face, all effectively prevent the wearing and tearing of liner 70.
On the other hand, the contact of " Spielpassung " has the following advantage that cannot obtain in " interference fit ": a) easily liner 70 is assembled into recess 16D; B) because external gear 16 must be heat-treated, be therefore difficult to without fine finishing the dimensional accuracy guaranteeing interference fit, but if Spielpassung, then also there is no special relationship without the need to carrying out fine finishing.Therefore, from the viewpoint of the fasibility structure of also cost consideration being entered, the structure contacted by the mode of Spielpassung is comparatively reasonable.
Further, in present embodiment, inner circumferential bight 70F1,70F2 of liner 70 and bight, periphery 70K1,70K2 are configured to the chamfered of all carrying out roughly 45 degree.Further, the protuberance 54A covering 54 does not all contact with inner circumferential bight 70F1, bight, the periphery 70K1 of cover cap 54 side of liner 70.Thus, prevent the inner circumferential bight 70F1 of cover 54 side of the liner 70 formed by hard raw material or bight, periphery 70K1 from damaging the generation of the phenomenon (so-called " blocking " phenomenon) of the planar surface portion 54A1 of the protuberance 54A of cover 54, liner 70 can be made to slide sleekly on the planar surface portion 54A1 of the protuberance 54A of cover 54.And, by carrying out chamfered to the inner circumferential bight 70F2 of liner 70 and bight, periphery 70K2, prevent from producing " blocking " etc. between the cover side end face 40A of the roller member 40 and inner circumferential bight 70F2 of liner 70 and bight, periphery 70K2, liner 70 can be made to slide sleekly on the cover side end face 40A of roller member 40.
Further, liner 70 only has an axial part to be contained in recess 16D, and another part is more outstanding to cover 54 side than the side 16E of the axial shroud side of external gear 16.Thereby, it is possible to guarantee the intensity of liner 70, and reduce the axial depth H16D of the recess 16D be formed on external gear 16 as far as possible, and the axial contact length of external gear 16 and roller member 40 can be guaranteed longlyer.Its result, compared with the structure all entering the recess 16D of external gear 16, can prevent the intensity of external gear 16 from declining with liner 70 further, and can carry out the transmission of power of external gear 16 and roller member 40 more reliably.
In addition, as previously mentioned, one or two that can also make in the outer circumferential face 70A of liner 70 and inner peripheral surface 70B are contacted with the recess 16D of external gear 16 by " interference fit " mode.In this case, liner 70 rotates integrally (rotation and swing) with external gear 16 all the time, therefore based on its structure, can not produce the upper continuous print " scratch " of circumference in liner 70.Therefore, when making external gear 16 and liner 70 fully integrated rotation, liner 70 can be configured to and be contacted with recess 16D by interference fit.
One example of another embodiment of the present invention shown in Fig. 3, Fig. 4.
The structure of external gear and the fully integrated rotation of liner component is made to be not limited to above-mentioned " interference fit " structure.Such as, the structure shown in Fig. 3, Fig. 4 also can make external gear and the fully integrated rotation of liner component.
In structure shown in Fig. 3, Fig. 4, liner 76 has ringed liner main body 76A and multiple jut 76B.Each jut 76B, with the gap-forming corresponding with penetration hole 16A, is formed as the shape (shape of a part for excision circle) be just in time contained in (pin parts 38 run through) penetration hole 16A of external gear 16 in the scope of the radial dimension R76A of gasket body 76A.Penetration hole 16A also can be contacted by interference fit (gap fiting mode cost is low by contrast) by gap fiting mode with jut 76B.
In addition, in present embodiment, be formed with recess 76C at the back side of the position corresponding with jut 76B of gasket body 76A, but also can not form this recess 76C.
The axial sides 16E of cover 54 side of external gear 16 is formed with recess 16D, and an axial part of the gasket body 76A of liner 76 is contained in this recess 16D.Further, the periphery wall 16D1 of the outer circumferential face 76A1 of the gasket body 76A of liner 76 and inner peripheral surface 76A2 and the recess 16D of external gear 16 and inner circle wall 16D2 contacts.In addition, the outer circumferential face 76A1 of this gasket body 76A and the contact of inner peripheral surface 76A2 also can adopt gap fiting mode or interference fit.
According to this structure, by the Qian He of the penetration hole 16A of external gear 16 with the jut 76B of liner 76, external gear 16 and liner 76 can be made " to rotate integrally " not slidably.That is, liner 76 integrally swings with the swing of external gear 16, and with the rotation synchronous rotary of external gear 16.Therefore, liner 76 also with the revolution synchronous rotary of roller member 40, therefore the wearing and tearing of this liner 76 are inhibited, and especially based on its structure, the upper continuous print " scratch " of circumference can not occur.
Other structures are identical with mode of execution before, therefore mark identical bis to part identical or similar in accompanying drawing, omit repeat specification.
In addition, in the mode of execution of Fig. 3, Fig. 4, liner 76 has the jut 76B of the penetration hole 16A being embedded in external gear 16.Therefore, by the engaging of this jut 76B with penetration hole 16A, even if liner 76 does not contact with the recess 16D of external gear 16, also can rotate integrally with external gear 16.Therefore, in the structure of Fig. 3, Fig. 4, the formation of recess 16D can be omitted about external gear 16.
Thereby, it is possible to reduce the processing cost of external gear 16 further.Further, can suppress to form recess 16D and the decline of the intensity of external gear 16 that causes.And, the size (depth H 16D) that jut 76B enters from the side 16E of the axial shroud side of external gear 16 can be reduced further, therefore, correspondingly, roller member 40 and the axial contact length of the penetration hole 16A of external gear 16 can be guaranteed significantly, the transmission of power of external gear 16 and roller member 40 (and selling parts 38) can also be carried out more reliably.
Fig. 5 illustrates another embodiment of the invention.
In mode of execution shown in Fig. 5, liner 90 interval in the circumference of external gear 82 is arranged.Specifically, liner 90 has round base portion 90A and the jut 90B coaxial with this base portion 90A, is provided with altogether 8.Each liner 90 is contained in respectively and is formed in 8 penetration hole 82A of external gear 82.Specifically, jut 90B is entrenched in penetration hole 82A by Spielpassung or interference fit.That is, the liner 90 (not unifying spacing to multiple roller member 40) involved by present embodiment individually carries out spacing to each roller member 40.
In present embodiment, external gear 82 is also formed with recess 82D, an axial part of the base portion 90A of liner 90 is contained in this recess 82D.Wherein, periphery (outer circumferential face) 90A1 of liner 90 does not contact with the recess 82D of this external gear 82.As an alternative, periphery (outer circumferential face) 90B1 of the jut 90B of liner 90 contacts with the inner peripheral surface 80A1 of penetration hole 82A.
According to this structure, by the Qian He of the penetration hole 82A of external gear 82 with the jut 90B of liner 90, external gear 82 and liner 90 also can be made " to rotate integrally " not slidably.That is, liner 90 integrally swings with the swing of external gear 82, and, with the rotation synchronous rotary of external gear 82.
In addition, in the structure of this Fig. 5, also can omit the recess 82D forming external gear 82, the base portion 90A of liner 90 is abutted with the cover side end 82E of external gear 82.Thereby, it is possible to the action effect that the situation obtaining omitting in the structure with Fig. 3, Fig. 4 the recess 16D forming external gear 16 is identical.
In addition, in the structure example of Fig. 3 ~ Fig. 5, by forming the jut chimeric with the penetration hole of external gear on liner component, external gear and liner component are rotated integrally, but the structure making external gear and liner component rotate integrally is not limited to the structure of Fig. 3 ~ Fig. 5, it can be arbitrary structures.Such as, also can bond liner component on external gear.
Further, in above-mentioned mode of execution, the action being configured to liner component (liner 70,76,90) and external gear almost or Complete Synchronization, especially, makes on liner component, do not form continuous print in circumference " scratch ".But, continuous print " scratch " in the circumference that the structure that also revolution of liner component (not rotating integrally with external gear) and pin parts can be made to rotate integrally (revolution) by employing avoids the formation of liner component.
This structure example shown in Fig. 6.
In structure example shown in Fig. 6, the liner 94 allowing to the lid shape engaged with the periphery, end of pin parts 92 (outer circumferential face 92A) covers this periphery.That is, in this example, liner 94 is also interval setting in the circumference of external gear 98.Abutted with the cover side end face 96A of roller member 96 by the end face 94B of roller member 96 side of cylindrical part (part contacted with the pin parts 92 outer circumferential face 92A) 94A of liner 94, carry out axially to roller member 96 spacing.The pin outer circumferential face 92A of parts 92 also can be contacted by interference fit (gap fiting mode cost is low) by Spielpassung with the inner circumferential (inner peripheral surface 94C) of the cylindrical part 94A of liner 94.Liner 94 is configured between roller member 96 and cover 54 (omit in Fig. 6 and illustrate).Therefore, even if adopt Spielpassung, also can not depart from from pin parts 92.
The outside diameter d 94 of the cylindrical part 94A of liner 94 is less than the outside diameter d 96 (d94 < d96) of roller member 96.Therefore, liner 94 does not contact with the penetration hole 98A of external gear 98.But by this result, liner 94 completely and (the axle center O1 around input shaft 18) revolution synchronous rotary of pin parts 92.Therefore, even if the axle center O2 of pin parts 92 tilts, the end face 94B of roller member 96 side of the cylindrical part 94A of liner 94 does not tilt mutually with the cover side end face 96A of roller member 96 and coaxially abuts, and very effectively suppresses the wearing and tearing of liner 94.
In addition, in the structure example of Fig. 6, the liner 94 allowing to the lid shape of the periphery, end (outer circumferential face 92A) being sticked in pin parts 92 covers this periphery, thus makes liner component synchronous with the revolution of pin parts.But as long as liner component and pin parts one revolve round the sun, being then not limited to the structure example of above-mentioned Fig. 6, can be arbitrary structures.Such as, also can by pin parts and liner component bonding.
In addition, in above-mentioned mode of execution, the raw material of liner component adopt iron class raw material, but in present embodiment, owing to structure can suppress wearing and tearing, and therefore also can be comparatively cheap and lightweight raw material form liner by resin etc.
Claims (8)
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 in an axially sidepiece of described external gear; Pin parts, link with this vibrating part, and run through the penetration hole be arranged on described external gear; Roller member, fitted on these pin parts; Cap assembly, be configured in axial the other side of described external gear, the feature of this eccentric oscillating-type speed reducer is,
Liner component is configured with between described roller member and described cap assembly,
Described external gear has the recess holding described liner component,
The inner circumferential of described liner component and at least side of periphery contact with described external gear.
2. eccentric oscillating-type speed reducer according to claim 1, is characterized in that,
The contact of the inner circumferential of described external gear and described liner component and at least side of periphery is the contact by gap fiting mode.
3. 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 in an axially sidepiece of described external gear; Pin parts, link with this vibrating part, and run through the penetration hole be arranged on described external gear; Roller member, fitted on these pin parts; Cap assembly, be configured in axial the other side of described external gear, the feature of this eccentric oscillating-type speed reducer is,
Liner component is configured with between described roller member and described cap assembly,
Described external gear and described liner component rotate integrally.
4. eccentric oscillating-type speed reducer according to claim 3, is characterized in that,
Described liner component has jut,
Described jut is entrenched in the penetration hole of described external gear.
5. 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 in an axially sidepiece of described external gear; Pin parts, link with this vibrating part, and run through the penetration hole be arranged on described external gear; Roller member, fitted on these pin parts; Cap assembly, be configured in axial the other side of described external gear, the feature of this eccentric oscillating-type speed reducer is,
Between described roller member and described cap assembly, the circumference along described external gear is arranged at intervals with liner component, and,
The revolution of this liner component and described pin parts is integrally revolved round the sun.
6. eccentric oscillating-type speed reducer according to claim 5, is characterized in that,
Described liner component is fitted in the front end of described pin parts.
7. the eccentric oscillating-type speed reducer according to any one in claim 1 ~ 6, is characterized in that,
Described cap assembly has the protuberance abutted with described liner component,
This protuberance does not contact with the inner circumferential bight of described liner component and bight, periphery.
8. the eccentric oscillating-type speed reducer according to any one in claim 1 ~ 7, is characterized in that,
A described liner component part is given prominence in the axial direction from the axial sides of described external gear.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
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| JP2013168750A JP6144996B2 (en) | 2013-08-14 | 2013-08-14 | Eccentric oscillation type speed reducer |
| JP2013-168750 | 2013-08-14 |
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| CN104373520A true CN104373520A (en) | 2015-02-25 |
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| CN201410167858.7A Active CN104373520B (en) | 2013-08-14 | 2014-04-24 | Eccentrically swinging reducer device |
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| JP (1) | JP6144996B2 (en) |
| KR (1) | KR101568164B1 (en) |
| CN (1) | CN104373520B (en) |
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|---|---|---|---|---|
| CN106949196A (en) * | 2015-11-06 | 2017-07-14 | 住友重机械工业株式会社 | Eccentric oscillating-type deceleration device |
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| JP6976787B2 (en) * | 2017-09-22 | 2021-12-08 | 株式会社ニッセイ | Differential reducer |
| JP7444551B2 (en) * | 2019-05-31 | 2024-03-06 | ナブテスコ株式会社 | Bearing assembly structure of rotating equipment |
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| JPH04111946U (en) * | 1991-03-15 | 1992-09-29 | アイセル株式会社 | Eccentric swing type reducer |
| DE20023013U1 (en) * | 1999-03-20 | 2002-11-21 | Asec Gmbh | Primary gearbox on high-speed engines for auxiliary drive units |
| JP2001205377A (en) * | 2000-01-20 | 2001-07-31 | Sumitomo Heavy Ind Ltd | Method for manufacturing rotary roller body, rotary roller body obtained by the method and inrevolvable planetary gear structure with internal rotary roller body |
| JP5160756B2 (en) * | 2006-08-17 | 2013-03-13 | Ｎｔｎ株式会社 | In-wheel motor drive device |
| JP5006838B2 (en) * | 2008-01-30 | 2012-08-22 | 住友重機械工業株式会社 | Reduction gear |
| JP5520247B2 (en) * | 2011-03-02 | 2014-06-11 | 住友重機械工業株式会社 | Reduction device for wind power generation equipment and reduction device with output pinion |
| JP5822383B2 (en) * | 2011-07-08 | 2015-11-24 | 住友重機械工業株式会社 | Reduction gear |
| CN102359555B (en) * | 2011-08-29 | 2013-11-06 | 浙江恒丰泰减速机制造有限公司 | Precise cycloidal movable tooth transmission speed reducer |
| JP5727331B2 (en) * | 2011-08-29 | 2015-06-03 | 住友重機械工業株式会社 | Yaw reduction device and yaw drive system used for yaw drive system of wind power generation equipment |
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| CN106949196A (en) * | 2015-11-06 | 2017-07-14 | 住友重机械工业株式会社 | Eccentric oscillating-type deceleration device |
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| Publication number | Publication date |
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| JP6144996B2 (en) | 2017-06-07 |
| JP2015036581A (en) | 2015-02-23 |
| CN104373520B (en) | 2017-04-12 |
| KR101568164B1 (en) | 2015-11-11 |
| KR20150020028A (en) | 2015-02-25 |
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