CN110425256A - Gear assembly - Google Patents
Gear assembly Download PDFInfo
- Publication number
- CN110425256A CN110425256A CN201910754253.0A CN201910754253A CN110425256A CN 110425256 A CN110425256 A CN 110425256A CN 201910754253 A CN201910754253 A CN 201910754253A CN 110425256 A CN110425256 A CN 110425256A
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- China
- Prior art keywords
- gear
- external gear
- cylindrical element
- insertion groove
- internal
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- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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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
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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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/10—Constructively simple tooth shapes, e.g. shaped as pins, as balls
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
- F16H2001/323—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear comprising eccentric crankshafts driving or driven by a gearing
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
The present invention gear assembly excellent for realizing the transmission efficiency of torque.Gear assembly (100) includes internal gear (10) and external gear (28).External gear (28) is eccentrically rotated relative to internal gear (10).Internal gear (10) has internal tooth component (6) and cylindrical element (8).Cylindrical element (8) is inserted in the slot (9) being arranged on the inner peripheral surface of internal tooth component (6).External gear (28) is meshed and being in contact with cylindrical element (8) with internal gear (10).In gear assembly (100), the direction of the texture of the circumferential surface of cylindrical element (8) is different from the direction of texture on surface of slot (9).
Description
The application be the applying date be on April 30th, 2015, application No. is 201510218547.3, invention and created names are as follows:
The divisional application of the Chinese patent application of " gear assembly ".
Technical field
This disclosure one kind technology related with gear assembly.
Background technique
It include that internal gear and internal gear of relativeing to while being meshed with internal gear are eccentrically rotated there is known one kind
External gear gear assembly.In such gear assembly, including cylindrical element is inserted into
Internal gear is formed in the slot being arranged on the inner peripheral surface of tooth component.Under being disclosed in Japanese Unexamined Patent Publication 2013-185619 bulletin
It states gear assembly: the surface roughness of the circumferential surface of cylindrical element (export trade) in the axial direction being made to be less than its table in the circumferential
Surface roughness, to reduce the friction between cylindrical element and slot (outer cotter way).In the following description, by Japanese Unexamined Patent Publication
2013-185619 bulletin is referred to as patent document 1.In addition, in patent document 1, also recording following content: by making slot
Surface surface roughness in the axial direction be less than its surface roughness in the circumferential, can reduce cylindrical element and slot it
Between friction.
Summary of the invention
Problems to be solved by the invention
In the gear assembly of patent document 1, reduce the friction between the cylindrical element and slot that constitute internal gear,
To reduce loss caused by friction.However, in the presence of when reducing the friction between cylindrical element and slot, cylindrical element
The case where friction between (tooth of internal gear) and external gear becomes smaller.As a result, being generated between internal gear and external gear sometimes
Sliding.If generating sliding between internal gear and external gear, the transmission efficiency of torque can be reduced.This disclosure solves
The above problem and the technology for realizing the excellent gear assembly of the transmission efficiency of torque.
The solution to the problem
Technology disclosed in this specification is related to a kind of gear assembly, which includes: internal gear；With
And external gear, it is eccentrically rotated relative to internal gear.In the gear assembly, internal gear have internal tooth component and by
The cylindrical element being inserted into the slot being arranged on the inner peripheral surface of internal tooth component.In addition, external gear by with cylindrical element
It is in contact and is meshed with internal gear.In gear assembly disclosed in this specification, cylindrical element and external gear it
Between coefficient of friction be greater than coefficient of friction between cylindrical element and slot.
In said gear transmission device, cylindrical element (tooth of internal gear) can be rotated in slot.It is specific and
Speech, external gear relative to while being meshed with internal gear internal gear be eccentrically rotated when, cylindrical element relative to
Slot is rotated.Coefficient of friction between cylindrical element and external gear is greater than the coefficient of friction between cylindrical element and slot.
Therefore, cylindrical element can be rolled and being rotated in slot relative to external gear.That is, cylindrical element is opposite
It is functioned in external gear as rolling bearing.Due to the sliding being able to suppress between cylindrical element and external gear, energy
Enough reduce the torque transmission loss of gear assembly.In addition, cylindrical element is played relative to above-mentioned slot as sliding bearing
Function.
Above-mentioned " external gear being eccentrically rotated relative to internal gear " is simultaneously not only external gear relative to gear drive
The mode that the axis of device is eccentrically rotated also includes that internal gear is eccentrically rotated relative to the axis of gear assembly
Mode.That is, " external gear being eccentrically rotated relative to internal gear " refers to that one of internal gear and external gear are opposite
It is eccentrically rotated in the axis of gear assembly, and internal gear and external gear are relatively eccentrically rotated.
Detailed description of the invention
Fig. 1 is the cross-sectional view of the gear assembly of the 1st embodiment.
Fig. 2 is the II-II line cross-sectional view of Fig. 1.
Fig. 3 is by the enlarged drawing of the part surrounded the dotted line III of Fig. 2.
Description of symbols
6, internal tooth component；8, cylindrical element；9, slot；10, internal gear；28, external gear；100, gear assembly
Specific embodiment
Hereinafter, illustrating several technical characteristics of gear assembly disclosed in this specification.In addition, thing described below
Item individually has technical practicability.
Gear assembly may include internal gear and external gear.It is also possible to internal gear and external gear is nibbled mutually on one side
Unification side is relatively eccentrically rotated.I.e., it is possible to be, external gear is eccentrically rotated while being meshed with internal gear.
It is eccentrically rotated while being meshed with external gear alternatively, being also possible to internal gear.Internal gear may include internal tooth component
Be inserted in internal tooth component inner peripheral surface on cylindrical element in the slot that is arranged.In other words, internal gear can be by forming
It is formed in the slot of the inner peripheral surface of internal tooth component with the cylindrical element being inserted into the slot.Hereinafter, in the present specification, sometimes
The slot formed on the inner peripheral surface of internal tooth component is referred to as insertion groove.
It, can also be by the shell of gear assembly as being in the case where the type being eccentrically rotated for external gear
Internal tooth component.I.e., it is possible to be that internal gear is formed in the inner circumferential of shell.In this case, it can also be configured in the inside of shell
Tooth rest, crankshaft and external gear.Crankshaft can be supported on tooth rest in a manner of it can rotate.Crankshaft can have bias
Body.It can be, the eccentric body of external gear and crankshaft fastens and as the rotation of crankshaft is eccentrically rotated.It can be, internal tooth
Wheel has the number of teeth different from the number of teeth of external gear.
It is also possible to be inserted into the cylindrical element in insertion groove to function as the tooth of internal gear.In this case,
The tooth socket for being also possible to inner peripheral surface in the inner peripheral surface of internal tooth component, between adjacent insertion groove as internal gear is sent out
Wave function.It can be, each insertion groove is being arc-shaped with the shape on the section of the axis vertical take-off of gear assembly.It can be with
It is that multiple insertion grooves extend along the axis of gear assembly.In such a case it is possible to be, each insertion groove is along internal tooth structure
Part it is equally circumferentially spaced.
It in the case where insertion groove is arc-shaped, can be, the center of the imaginary circle where the surface of insertion groove is located at circle
On the rotation axis of cylindrical component, and keep the diameter of imaginary diameter of a circle and cylindrical element roughly equal.It is also possible to cylinder
Shape component exists while being in contact with external gear to be rotated in insertion groove.That is, being also possible in external gear one side and internal tooth
Wheel is meshed on one side when being relatively eccentrically rotated, and cylindrical element is rotated in insertion groove.
It is also possible to the coefficient of friction when driving gear assembly, between cylindrical element and external gear and is greater than circle
Coefficient of friction between cylindrical component and insertion groove.More specifically, it is also possible to tooth of the cylindrical element relative to external gear
Coefficient of friction (coefficient of rolling friction) when face starts sliding is greater than rubbing when cylindrical element starts sliding relative to insertion groove
It wipes coefficient (coefficient of rolling friction).Furthermore it is possible to be, the surface roughness on the surface of insertion groove is less than the table of the flank of tooth of external gear
Surface roughness.In this case, it is also possible to by being processed using different cutters, to realize the surface of different value
Roughness.Alternatively, being also possible to after having processed insertion groove and external gear, the surface for removing insertion groove is carried out
The processing of texture.
The surface roughness of the flank of tooth of external gear can be Ra0.2 μm~Ra0.5 μm.It is less than Ra0.2 μ in surface roughness
In the case where m, adequately friction cannot be obtained between cylindrical element and the flank of tooth of external gear, may cause cylindrical element
The flank of tooth relative to external gear slides.In addition, being easy to send out when being driven if surface roughness is greater than Ra0.5 μm
Heat etc., so as to cause external gear durability (service life) reduction.In addition, the surface roughness in the flank of tooth of external gear is
In the case where Ra0.2 μm~Ra0.5 μm, the surface roughness of insertion groove can be less than Ra0.2 μm.
The surface roughness of insertion groove can be less than Ra0.3 μm.Furthermore, it is possible to be, the surface roughness of insertion groove is preferred
For Ra0.2 μm hereinafter, particularly preferably Ra0.1 μm or less.In addition, in order to avoid the manufacturing procedure of insertion groove become it is complicated plus
Increase between working hour, the surface roughness of insertion groove can be 0.01 μm or more.In addition, the surface roughness in insertion groove is less than
In the case where Ra0.3 μm, the surface roughness of the flank of tooth of external gear can be Ra0.3 μm~Ra0.5 μm.
It can be, the direction of texture of the flank of tooth in direction and external gear of the texture of the circumferential surface of cylindrical element is identical.It is logical
Crossing keeps the direction of texture identical, the coefficient of friction being capable of increasing between cylindrical element and external gear, so as to inhibit cylinder
Shape component is slided relative to the flank of tooth of external gear.Alternatively, it is also possible to be, the direction of the texture of the circumferential surface of cylindrical element and insertion
The direction of the texture on the surface of slot is different.Coefficient of friction when the direction difference of texture, between cylindrical element and insertion groove
Become smaller, cylindrical element is easy to slide relative to insertion groove.It, can by making cylindrical element be easy to slide relative to insertion groove
Relatively increase the coefficient of friction between cylindrical element and external gear.It is also possible to the texture of the circumferential surface of cylindrical element
Direction is orthogonal with the direction of the texture on the surface of insertion groove.It is produced when processing part on the surface of part in addition, texture is referred to
Raw cutter trade.
Covering part can also be set on the surface of insertion groove.In this case, between covering part and cylindrical element
Coefficient of friction can be less than the coefficient of friction between the surface and cylindrical element of insertion groove.That is, and not having by setting covering part
It is compared when having setting covering part, cylindrical element can be easy sliding relative to insertion groove.Covering part can be formed at insertion
The carbon on the surface of slot, fluororesin, molybdenum overlay film.It is also possible to slotting to reduce by the way that covering part is arranged on the surface of insertion groove
Enter the surface roughness of rooved face.
Embodiment
1st embodiment
Illustrate the essential structure of gear assembly 100 referring to Figures 1 and 2.Fig. 1 shows gear assembly 100
Longitudinal section view (cross-sectional view along axis 12 of gear assembly 100).Fig. 2 shows the cross of gear assembly 100
Cross-sectional view (cross-sectional view along the line orthogonal with axis 12 of gear assembly 100).Gear assembly 100 includes internal tooth
Wheel 10, tooth rest 4, crankshaft 14 and external gear 28.
Internal gear 10 has shell 6 and interior alligator 8.In being formed and multiple interior alligators 8 are configured at the inner circumferential of shell 6
Gear 10.Interior alligator 8 is cylindric and is inserted in the insertion groove 9 formed on the inner peripheral surface 7 of shell 6.Insertion groove 9 is along week
To the inner circumferential being equally spaced in shell 6.In addition, insertion groove 9 is in a manner of the axis 12 for being parallel to gear assembly 100
Extend.That is, interior alligator 8 is circumferentially, equally spaced arranged in the inner circumferential of shell 6 and is extended in a manner of being parallel to axis 12.Shell
6 be an example of internal tooth component, and interior alligator 8 is an example of cylindrical element.
Tooth rest 4 is supported on shell in a manner of it can rotate a pair of bearings 22 (hereinafter, sometimes referred to as base bearing 22)
Body 6.Base bearing 22 axially limits tooth rest 4 relative to shell 6 with the movement of radial direction.It is passed in gear
In dynamic device 100, use angular contact ball bearing as base bearing 22.Tooth rest 4 has the first plate 4a and the second plate 4c.First plate
4a has columnar part 4b.Columnar part 4b extends towards the second plate 4c from the first plate 4a and is fixed on the second plate 4c using bolt 34.
Bolt 34 passes through the second plate 4c and is fastened onto the bolt slot 34a being located on columnar part 4b.
In addition, (saving sketch map inserted with the positioning pin for carrying out the positioning in circumferential direction on columnar part 4b and the second plate 4c
Show).The pin hole 36 set on columnar part 4b is shown in FIG. 2.Pin hole (illustration omitted) also is provided on the second plate 4c.Positioning pin
Across the second plate 4c pin hole and be inserted into pin hole 36.In addition, being configured with oil sealing 18 between shell 6 and the first plate 4a.
Crankshaft 14 is supported on tooth rest 4 by a pair of bearings 20 in a manner of it can rotate.A pair of bearings 20 is to crankshaft 14
It is limited relative to the movement axially of tooth rest 4 and the movement of radial direction.In gear assembly 100,
Use tapered roller bearing as a pair of bearings 20.Crankshaft 14 has input gear 32 and two eccentric bodies 30.Eccentric body 30 is matched
It sets between a pair of bearings 22.Eccentric body 30 is sticked in external gear 28 by cylinder roller bearing 26.External gear 28 is by crankshaft
14 are supported on tooth rest 4.In addition, the configuration of input gear 32 is in the outside of a pair of bearings 20.
In gear assembly 100, the torque of motor (illustration omitted) is passed to input gear 32.When turning for motor
When square is transferred to input gear 32, crankshaft 14 is rotated, and eccentric body 30 is eccentrically rotated therewith.It is inclined with eccentric body 30
Heart rotation, external gear 28 are eccentrically rotated while being meshed with internal gear 10.External gear 28 carries out bias around axis 12
Rotation.Two eccentric bodies 30 are eccentric in mutually symmetrical with mode.Therefore, two external gears 28 are opposite to each other in axis 12 to phase
It is eccentrically rotated in the state that anti-direction is eccentric around axis 12.The number of teeth of external gear 28 and the number of teeth (internal tooth of internal gear 10
The quantity of pin 8) it is different (referring to Fig. 2).Therefore, when external gear 28 is eccentrically rotated, carry the tooth of external gear 28
Wheel carrier 4 is rotated corresponding to the teeth number difference between external gear 28 and internal gear 10 relative to shell 6.It can also be by axis 12
The referred to as rotation axis of tooth rest 4.
Illustrate the feature of gear assembly 100 referring to Fig. 3.As described above, 28 one side of external gear is nibbled with 10 phase of internal gear
Unification side is eccentrically rotated.More specifically, external gear 28 is wound while being in contact with its flank of tooth with the circumferential surface of interior alligator 8
Axis 12 is eccentrically rotated.When external gear 28 is rotated along the direction arrow R1, interior alligator 8 is in insertion groove 9 along the arrow side R2
To rotation.Interior alligator 8 exists while sliding relative to insertion groove 9 to be rotated in insertion groove 9.
In gear assembly 100, the coefficient of friction between the flank of tooth of external gear 28 and the circumferential surface of interior alligator 8, which is greater than, to be inserted
Enter the coefficient of friction between the surface of slot 9 and the circumferential surface of interior alligator 8.Therefore, compared between insertion groove 9 and interior alligator 8, external gear
It is difficult to slide between 28 and interior alligator 8.Interior alligator 8 is in the power smaller than its power when starting sliding on the flank of tooth of external gear 28
It is slided under effect relative to insertion groove 9.Therefore, when external gear 28 is rotated along the direction arrow R1, interior 8 one side of alligator is outside
An edge direction arrow R2 is rolled on the flank of tooth of gear 28 to rotate.Interior alligator 8 is played relative to external gear 28 as rolling bearing
Function, and functioned relative to insertion groove 9 as sliding bearing.In addition, in gear assembly 100, for external gear
28, interior alligator 8 and insertion groove 9 have carried out at least one of processing below (1)~processing (3) processing.
Processing (1): the surface roughness Ra on the surface of insertion groove 9 is made to be less than the surface roughness of the flank of tooth of external gear 28
Ra。
Processing (2): the direction of the texture of the flank of tooth of external gear 28 is adjusted to the direction with the texture of the circumferential surface of interior alligator 8
It is identical, also, the direction of the texture on the surface of insertion groove 9 is adjusted to different from the direction of texture of circumferential surface of interior alligator 8.
Processing (3): covering the surface of insertion groove 9, the friction between insertion groove 9 and interior alligator 8 after making covering
Coefficient is lower than the coefficient of friction between the insertion groove 9 and interior alligator 8 before covering.
By being handled (1), can make coefficient of friction between external gear 28 and interior alligator 8 be greater than insertion groove 9 with it is interior
Coefficient of friction between alligator 8 is particularly handled without internal alligator 8.External gear 28 is via interior alligator 8 and insertion groove
9 (shells 6) are in contact.That is, being configured with interior alligator 8 between external gear 28 and insertion groove 9.By carrying out the processing of above-mentioned (1),
Compared between insertion groove 9 and interior alligator 8, opposite slide is not easy between external gear 28 and interior alligator 8.More specifically, outside
Before gear 28 starts sliding relative to interior alligator 8, interior alligator 8 rotates while sliding relative to insertion groove 9.
In addition, the surface roughness of the flank of tooth of external gear 28 is adjusted to Ra0.2 μm~Ra0.5 μm.By the way that surface is thick
Rugosity is adjusted to Ra0.2 μm or more, and external gear 28 can more reliably be inhibited to slide relative to interior alligator 8.In addition, by by table
Surface roughness is adjusted to Ra0.5 μm hereinafter, being able to suppress the abrasion of the flank of tooth of external gear 28.By by the flank of tooth of external gear 28
Surface roughness is adjusted to Ra0.2 μm~Ra0.5 μm, is able to suppress the deterioration of external gear 28 and inhibits interior alligator 8 relative to outer
Gear 28 slides.In addition, can be avoided by the way that the surface roughness Ra on the surface of insertion groove 9 is adjusted to 0.01 μm~0.1 μm
The processing of insertion groove 9 becomes miscellaneous and interior alligator 8 is made to be easy to slide relative to insertion groove 9.
By being handled (2), can make coefficient of friction between external gear 28 and interior alligator 8 be greater than insertion groove 9 with it is interior
Coefficient of friction between alligator 8, without adjusting the surface roughness Ra of external gear 28 and insertion groove 9.For example, columned
The direction of the texture formed on the surface of part (cylindrical element) is different from the direction of the texture formed on the surface of plate
In the case where, in cylindrical element when rolling on the surface of plate, the contact area between cylindrical element and plate is reduced,
To be easy to generate sliding therebetween.In contrast, the direction of the texture formed on the surface of cylindrical element with
In the identical situation in the direction of the texture formed on the surface of plate, texture hooks each other, is not easy to generate sliding therebetween.
In processing (2), the direction of the texture on the surface by making insertion groove 9 is orthogonal with the direction of texture of circumferential surface of interior alligator 8, energy
It is enough that interior alligator 8 is more reliably made to be easy to slide relative to insertion groove 9.
Specifically describe the direction of the texture of external gear 28, interior alligator 8 and insertion groove 9.As described above, external gear 28 around
Axis 12 is eccentrically rotated.When processing external gear 28, in general, so that the texture of the flank of tooth is parallel with axis 12 or make the flank of tooth
The texture mode orthogonal with axis 12 is processed.Similarly, in processing when the circumferential surface and insertion groove 9 of alligator 8, in general,
It is processed in the mode for keeping texture parallel with axis 12 or keeping texture orthogonal with axis 12.
Therefore, in the case where processing external gear 28 in such a way that grain parallel is formed in axis 12, with grain parallel
Interior alligator 8 is processed in the mode that axis 12 is formed, and is processed in a manner of the direction orthogonal with axis 12 by texture edge is formed slotting
Enter slot 9.In the case where processing external gear 28 in such a way that texture is formed along the direction orthogonal with axis 12, with grain parallel in
Axis 12 and the mode formed processes interior alligator 8, and insertion groove 9 is processed in such a way that axis 12 is formed by grain parallel.This
Outside, the direction of texture can be adjusted by changing the moving direction of process tool.
By being handled (3), can make coefficient of friction between external gear 28 and interior alligator 8 be greater than insertion groove 9 with it is interior
Coefficient of friction between alligator 8 is particularly handled without internal alligator 8 and external gear 28.Specifically, handling
(3) in, reduce the coefficient of friction between interior alligator 8 and insertion groove 9, be equivalent to and increase rubbing between external gear 28 and interior alligator 8
Wipe coefficient.That is, reducing interior alligator 8 and insertion groove in the case where not changing the coefficient of friction between external gear 28 and interior alligator 8
Coefficient of friction between 9 is greater than the coefficient of friction between external gear 28 and interior alligator 8 between insertion groove 9 and interior alligator 8
Coefficient of friction.In addition, by the overlay film that carbon, fluororesin, molybdenum etc. are coated on the surface of insertion groove 9 to, are formed these materials,
The surface of insertion groove 9 can be covered.Overlay film (covering part) is so as to form rubbing between insertion groove 9 and interior alligator 8 coated with film
The mode that coefficient is 0.01 μm~0.1 μm is wiped to be formed.
The advantages of illustrating gear assembly 100.As described above, between the flank of tooth of external gear 28 and the circumferential surface of interior alligator 8
Coefficient of friction be greater than insertion groove 9 surface and interior alligator 8 circumferential surface between coefficient of friction.Therefore, in driving gear drive
When device 100, it is not easy to generate sliding between external gear 28 and interior alligator 8, interior alligator 8 is used as the axis of rolling relative to external gear 28
It holds and functions.It is able to suppress transmitting loss of the torque between external gear 28 and internal gear 10.
More than, it is described in detail by concrete example of the invention, but these concrete examples only illustrate, is not used to limit
Determine the protection scope of claims.Technology documented by claims includes to carry out various changes to the concrete example illustrated above
The scheme obtained after shape, change.The technical characteristic illustrated in this specification or attached drawing be it is independent or by it is various combination come
Technical practicability is played, combination documented by claim when being not limited to application.In addition, this specification or attached drawing
Illustrated by technology be used for and meanwhile realize multiple purposes, it is technical practical to realize that technology of purpose of one of them itself has
Property.
Claims (6)
1. a kind of gear assembly comprising: internal gear；And external gear, it is eccentrically rotated relative to internal gear,
In,
The cylindrical element that internal gear has internal tooth component and is inserted in the slot being arranged on the inner peripheral surface of internal tooth component,
External gear is meshed and being in contact with cylindrical element with internal gear,
The direction of the texture of the circumferential surface of cylindrical element is different from the direction of the texture on the surface of the slot.
2. gear assembly according to claim 1, wherein
Coefficient of friction between cylindrical element and external gear is greater than the coefficient of friction between cylindrical element and slot.
3. gear assembly according to claim 1, wherein
The surface roughness on the surface of the slot is less than the surface roughness of the flank of tooth of external gear.
4. gear assembly according to claim 3, wherein
The surface roughness of the flank of tooth of external gear is 0.2 μm~0.5 μm,
The surface roughness on the surface of the slot is less than 0.3 μm.
5. gear assembly according to claim 1, wherein
The direction of texture of the flank of tooth in direction and external gear of the texture of the circumferential surface of cylindrical element is identical.
6. gear assembly according to any one of claim 1 to 5, wherein
Covering part is equipped on the surface of the slot,
Coefficient of friction between covering part and cylindrical element is less than the friction system between the surface and cylindrical element of the slot
Number.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014-093773 | 2014-04-30 | ||
| JP2014093773A JP6310764B2 (en) | 2014-04-30 | 2014-04-30 | Gear transmission |
| CN201510218547.3A CN105041981B (en) | 2014-04-30 | 2015-04-30 | Gear assembly |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510218547.3A Division CN105041981B (en) | 2014-04-30 | 2015-04-30 | Gear assembly |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110425256A true CN110425256A (en) | 2019-11-08 |
| CN110425256B CN110425256B (en) | 2023-02-28 |
Family
ID=54326193
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910754253.0A Active CN110425256B (en) | 2014-04-30 | 2015-04-30 | Gear transmission device |
| CN201510218547.3A Active CN105041981B (en) | 2014-04-30 | 2015-04-30 | Gear assembly |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510218547.3A Active CN105041981B (en) | 2014-04-30 | 2015-04-30 | Gear assembly |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP6310764B2 (en) |
| KR (1) | KR102337724B1 (en) |
| CN (2) | CN110425256B (en) |
| DE (1) | DE102015207762A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112112940B (en) * | 2019-06-21 | 2022-03-29 | 宁波瀚晟传动技术有限公司 | Transmission mechanism |
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| JP2594602Y2 (en) * | 1993-10-01 | 1999-05-10 | 帝人製機株式会社 | Pin gear type reducer |
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| JP4278816B2 (en) * | 2000-02-22 | 2009-06-17 | 住友重機械工業株式会社 | Reduction method of angular backlash of swinging intermeshing planetary gear transmission |
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| JP2009115274A (en) * | 2007-11-09 | 2009-05-28 | Nabtesco Corp | Eccentric oscillating gear device and industrial robot joint structure having the same |
| JP5797131B2 (en) * | 2012-03-06 | 2015-10-21 | 住友重機械工業株式会社 | Planetary gear reducer |
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2014
- 2014-04-30 JP JP2014093773A patent/JP6310764B2/en active Active
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2015
- 2015-04-13 KR KR1020150051646A patent/KR102337724B1/en active IP Right Grant
- 2015-04-28 DE DE102015207762.4A patent/DE102015207762A1/en active Pending
- 2015-04-30 CN CN201910754253.0A patent/CN110425256B/en active Active
- 2015-04-30 CN CN201510218547.3A patent/CN105041981B/en active Active
Patent Citations (5)
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| JPH02261943A (en) * | 1989-03-30 | 1990-10-24 | Teijin Seiki Co Ltd | Planetary gearing speed reduction machine |
| CN102667238A (en) * | 2009-12-02 | 2012-09-12 | 住友重机械工业株式会社 | Gear device |
| CN102713347A (en) * | 2010-01-07 | 2012-10-03 | 纳博特斯克株式会社 | Gear transmission |
| CN103291851A (en) * | 2012-02-28 | 2013-09-11 | 住友重机械工业株式会社 | Bending engagement type toothed wheel device |
| CN103670586A (en) * | 2012-09-12 | 2014-03-26 | 住友重机械工业株式会社 | Reduction gear |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102015207762A1 (en) | 2015-11-05 |
| JP6310764B2 (en) | 2018-04-11 |
| KR102337724B1 (en) | 2021-12-10 |
| JP2015209956A (en) | 2015-11-24 |
| CN110425256B (en) | 2023-02-28 |
| KR20150125570A (en) | 2015-11-09 |
| CN105041981A (en) | 2015-11-11 |
| CN105041981B (en) | 2019-09-03 |
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