CN110234907A - Differential speed reducer - Google Patents
Differential speed reducer Download PDFInfo
- Publication number
- CN110234907A CN110234907A CN201880009531.3A CN201880009531A CN110234907A CN 110234907 A CN110234907 A CN 110234907A CN 201880009531 A CN201880009531 A CN 201880009531A CN 110234907 A CN110234907 A CN 110234907A
- Authority
- CN
- China
- Prior art keywords
- input shaft
- bearing
- external gear
- eccentric part
- speed reducer
- Prior art date
- 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.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/44—Needle bearings
- F16C19/46—Needle bearings with one row or needles
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Problem of the present invention is that increasing the outer diameter of roller also even if using roller bearing in the axis support of external gear to realize strength enhancing.For this purpose, differential speed reducer (1A~1C) includes: the internal gear (4) being set in shell (2)；Coaxially penetrate through the input shaft (12) of internal gear (4)；Via eccentric part bearing outside loaded on the eccentric part (14A~14C) for being set to input shaft (12), with internal gear (4) the inscribed external gear (17A~17C) engaged；And has the pin (22 for being loosely inserted into external gear (17A~17C), 22 ...) and make ball bearing (10, 11) output shaft (9) between it between input shaft (12), by the rotation of input shaft (12) to which external gear (17A~17C) is relative to internal gear (4) eccentric motion, thus rotate output shaft (9) by pin (22) with given reduction ratio, eccentric part is wherein set as to the needle bearing (15) of full roller with bearing, and the outer diameter (D2) of the eccentric part (14A~14C) in input shaft (12) is made to be less than setting ball bearing (10, 11) outer diameter (D1) of shaft supporting part (13).
Description
Technical field
The present invention relates to include internal gear and be inscribed shuttle-type differential subtract with the inscribed external gear engaged of internal gear
Fast device.
Background technique
Differential speed reducer includes internal gear and the external gear engaged is inscribed with internal gear, passes through the rotation from input shaft
It inputs and external gear is made to carry out eccentric motion in internal gear, relative rotation is thus generated between two gears, based on eccentric fortune
The dynamic reduction ratio with the rotational speed difference of relative rotation is exported to output shaft to be rotated.Such as Patent Document 1 discloses a kind of power
Transfer device, the power transmission are that hollow input shaft axis is supported in a pair of of the support lug in front and back via a pair of bearings,
What the periphery in input shaft via roller bearing by two external gears respectively with different phase configurations between bearing was arranged
Front and back a pair of eccentric body, and to power transmission made of domestic set up between support lug, wherein it is domestic loosely
It is inserted in the inner pinhole of each external gear setting.That is, swinging external gear in internal gear via eccentric body if input shaft is rotated
(eccentric motion) is exported by taking out the relative rotation component of number of teeth difference of internal tooth and external tooth to support lug, especially
Here, inputting the outer diameter of input shaft towards power in order to which the input links such as pulley, gear are firmly fixed at input shaft
Side is amplified by stages according to each part corresponding with bearing.
Citation
Patent document
Patent document 1: International Publication No. 2006/085536
Summary of the invention
(subject to be solved by the invention)
In order to improve the intensity of differential speed reducer, it is effective for increasing external gear wheel to carry out the outer diameter of the roller of axis support.
But in the invention of above patent document 1, since the outer diameter of input shaft periodically amplifies, the internal diameter of roller bearing
Greater than the internal diameter of the bearing of input shaft, the outer diameter of roller is restricted, and strength enhancing is more difficult.
Therefore, roller bearing is used in the axis support of external gear even if the object of the present invention is to provide one kind, also can
Increase the outer diameter of roller enough to realize the differential speed reducer of strength enhancing.
(a technical solution to solve project)
In order to achieve the above objectives, the invention that technical solution 1 is recorded is a kind of differential speed reducer comprising: internal gear,
Setting is inside the shell；Input shaft coaxially penetrates through internal gear；External gear is loaded on outside via eccentric part bearing and sets
It is placed in the eccentric part of input shaft, and is inscribed and engages with internal gear；And output section, have the pin for being loosely inserted into external gear,
And make input shaft bearing between it between input shaft, external gear is carried out relative to internal gear by the rotation of input shaft
Eccentric motion, thus reduction ratio determined by the difference of the number of teeth and the number of teeth of external gear with the number of teeth and external gear based on internal gear
By pin rotate output section,
Eccentric part is set as full roller with bearing by the differential speed reducer, and the outer diameter of the eccentric part in input shaft is set as comparing
The outer diameter that the part of input shaft bearing is arranged is small.
The invention that technical solution 2 is recorded is characterized in that, in the structure of technical solution 1, in input shaft bearing and eccentric part
Anti-delinking part is set in the periphery of input shaft between bearing, which abuts with the side of input shaft bearing to limit input
Movement in the axial direction of axis, eccentric part form lower than anti-delinking part throughout complete cycle.
Technical solution 3 record invention be characterized in that, in the structure of technical solution 2, anti-delinking part be in input shaft it is coaxial and
Integrally formed circular plate shape.
Technical solution 4 record invention be characterized in that, in the structure of any one of technical solution 1 to 3, eccentric part and
Eccentric part bearing, external gear are provided with multiple groups, and the outer diameter of each eccentric part is all equal.
The invention that technical solution 5 is recorded is characterized in that in the structure of technical solution 4, the shape of each external gear is identical, and each
The shape of eccentric part bearing is identical.
(invention effect)
According to the invention that technical solution 1 is recorded, by the way that eccentric part is set as full roller with bearing, and will be in input shaft
The outer diameter that the outer diameter of eccentric part is set as the part than input shaft bearing is arranged is small, so as to increase the outer diameter of roller, helps
In strength enhancing.
According to technical solution 2 record invention, other than the effect of technical solution 1, by the periphery of input shaft setting with
The side of input shaft bearing abuts the anti-delinking part of the movement in the axial direction to limit input shaft, and eccentric part is spread complete cycle
Formed lower than anti-delinking part, thus even if being set as full roller, also can throughout eccentric part complete cycle limitation roller in the axial direction
It is mobile.Furthermore it is possible to which anti-delinking part to be common to the anticreep of both input shaft bearing and roller.
According to the invention that technical solution 3 is recorded, other than the effect of technical solution 2, since anti-delinking part being set as and input shaft
Coaxial and integrally formed circular plate shape, therefore anti-delinking part can be easily processed by lathe etc..
According to the invention that technical solution 4 is recorded, other than the effect of any one of technical solution 1 to 3, since setting multiple groups are inclined
Center portion and eccentric part bearing, external gear, and the outer diameter of each eccentric part is set as all equal, therefore can be in each eccentric part
Identical eccentric part bearing is configured, the outer diameter of the roller of each eccentric part bearing is capable of increasing.
According to the invention that technical solution 5 is recorded, other than the effect of technical solution 4, due to by each external gear and each bias
The shape of portion's bearing is set as identical respectively, therefore can expect to further reduce the cost.
Detailed description of the invention
Fig. 1 is the central longitudinal section view of the series of differential speed reducer.
The cross-sectional view of differential speed reducer 1A~1C at the line A-A of Fig. 1 is shown respectively in (A) of Fig. 2~(C).
Fig. 3 is the portion the F enlarged drawing of Fig. 1.
Fig. 4 is the curve graph for being compared efficiency of the modification coefficient of internal gear 4 in the case where different.
Specific embodiment
Hereinafter, based on attached drawing, embodiments of the present invention will be described.
Fig. 1,2 show the serial S being made of three kinds of differential speed reducers 1A, 1B, 1C.Wherein, the construction of differential speed reducer 1A~1C
It is roughly the same, therefore as the central longitudinal section view for representing and showing differential speed reducer 1A in Fig. 1, in (A)~(C) of Fig. 2
In, respectively illustrate the cross-sectional view of differential speed reducer 1A~1C at the line A-A of Fig. 1.In addition, when by differential speed reducer 1A~
When 1C distinguishes constituting portion respectively, English alphabet is marked as 14A~14C.
In differential speed reducer 1A (1B, 1C), 2 be shell, and the shell 2 is by being provided integrally with the cylinder of internal gear 4 in inside
The middle shell 3 of shape, the axial end face (input side, the right side of Fig. 1) being configured in middle shell 3 discoid case lid
It 5 and is configured at the cylindric outer housing 6 of another end face (outlet side, the left side of Fig. 1) and constitutes.Shell 3 and case lid in this
5 and outer housing 6 in conjunction with from shell 3 in the perforation of 5 side of case lid and and multiple bolts 7,7 ... screwed togather with outer housing 6
It is integrated.
In the inside of outer housing 6, via the crossed roller bearing 8 as outboard bearing, the rotatable earth's axis is supported by disk
The output shaft 9 of shape.In addition, via the ball bearing 10,11 for becoming input shaft bearing, coaxially and can be revolved in the inside of shell 2
Turn the input shaft 12 that the earth's axis is supported by hollow tube-shape.Wherein, about the ball bearing 10 of the inboard bearing as input side, outer ring
The axial input side half of 10a is supported in case lid 5, and the axial outlet side half of outer ring 10a is supported in aftermentioned carrying
Part 24.
In the input shaft 12, between the shaft supporting part 13,13 of configuration ball bearing 10,11, it is adjacent to be formed in the axial direction
Have outer diameter be equal to each other and maximum eccentric side become each other differ 180 degree phase a pair of of eccentric part 14A, 14A (14B, 14B
And 14C, 14C).At each eccentric part 14A, 14A (14B, 14B and 14C, 14C), be provided with as eccentric part bearing by
The needle bearing 15 of the full roller of the multiple needle rollers 16 of cross section round, 16 ... compositions that are arranged throughout complete cycle, via rolling
Needle bearing 15 can respectively rotatably be equipped with external gear 17A, 17A (17B, 17B and 17C, 17C) of identical appearance outside.Cause
This, each needle roller 16 is directly abutted with external gear 17A~17C of eccentric part 14A~14C of inside and outside.
Here, configuring the outer diameter D 1 and setting needle bearing of the shaft supporting part 13 of ball bearing 10,11 in input shaft 12
The outer diameter D 2 of 15 eccentric part 14A (14B, 14C) is formed as, the relationship in D1 > D2.Reduce eccentric part 14A in this way
The outer diameter D 2 of (14B, 14C) is capable of increasing the size (outer diameter) for being set to each needle roller 16 of its periphery.In addition, in shaft supporting part
Between 13 and eccentric part 14A (14B, 14C), circumferentially it is provided with higher to outer peripheral side than eccentric part 14A (14B, 14C) throughout complete cycle
Ground disk-shaped anti-delinking part 18 outstanding.It, can be throughout the shifting in complete cycle limitation needle roller 16 outside in the axial direction by the anti-delinking part 18
The movement of dynamic and ball bearing 10,11 inside in the axial direction.As a result, the movement in the axial direction of input shaft 12 is also limited.Ball
The movement of bearing 10 outward is limited by the inner peripheral and the covering part 19 Chong Die with outer ring 10a from outside for being set to case lid 5,
The movement of ball bearing 11 outward is limited by the stepped part 20 for being set to output shaft 9.
As shown in Fig. 2, external gear 17A~17C has the number of teeth fewer than the number of teeth of internal gear 4, and at eccentric position
It is inscribed with internal gear 4.Here, in differential speed reducer 1A~1C, each internal gear 4, which has used, sets the number of teeth as 120 similar shape
Internal gear.In contrast, for each external gear 17A~17C, external gear 17A sets the number of teeth as 114 thus with internal gear 4
Teeth number difference is 6, and reduction ratio becomes 1/19, and external gear 17B sets the number of teeth as 116 to be 4 with the teeth number difference of internal gear 4, reduction ratio
As 1/29, external gear 17C sets the number of teeth as 118 to which the teeth number difference with internal gear 4 is 2, and reduction ratio becomes 1/59.Therefore, outside
Center O1 (the axis of input shaft 12 of the respective center O2 of gear 17A~17C (center of eccentric part 14A~14C) from internal gear 4
The heart) eccentricity δ 1, δ 2, δ 3 become 1 > δ of δ, 2 > δ 3 relationship.
Here, the internal tooth of internal gear 4 and the external tooth of external gear 17 are respectively involute tooth type, the modification coefficient setting of internal gear 4
More than between 1 and 1.9 or less.
In addition, being spaced apart from each other in the circumferential direction ground on the concentric circles centered on the O2 of center in each external gear 17A~17C
Eight circular pin hole 21A~21C are formed with, in pin hole 21A~21C, have been loosely inserted into pin 22,22 ... respectively.
The pin 22 is between output shaft 9 and the discoid load-bearing part 24 for the inside for being configured at case lid 5, with the axis of internal gear 4
The axis body set up in parallel on concentric circles centered on line with the axis, the periphery of pin 22 external gear 17A~17C it is loose
Insertion portion is integrally equipped with the metalwork 23 of tubular outside.Load-bearing part 24 case lid 5 inside rotating bearing ball bearing 10 it is outer
The inside half for enclosing 10a, can integrally be rotated by pin 22 with output shaft 9.Here, pin 22 and via pin 22 link it is defeated
Shaft 9 becomes output section.
Each pin 22 makes the pin hole of the periphery of metalwork 23 and external gear 17A, 17A (17B, 17B and 17C, 17C) of front and back
The inner circumferential of 21A~21C is inscribed with the phase for differing 180 degree each other, and the aperture of pin hole 21A~21C of external gear 17A~17C is pressed
Each differential speed reducer 1A~1C is set.It is being wrapped that is, the diameter of pin hole 21A~21C in external gear 17A~17C becomes
Size obtained from 2 times of the 1~δ of eccentricity δ 3 for being diametrically added external gear 17A~17C of pin 22 containing metalwork 23, pin
The aperture of hole 21A~21C is different according to each differential speed reducer 1A~1C.But even if aperture is different, each external gear 17A
The center of pin hole 21A~21C of~17C is also all consistent.
On the other hand, 10 movable fit of ball bearing is in the inner peripheral surface of case lid 5 and load-bearing part 24, in supporting outer ring 10a
Case lid 5 and load-bearing part 24 between, as also showed that in Fig. 3, the axis of input shaft 12 be upwardly formed gap A and with it is outer
Connection in shell 2.In addition, being respectively formed with cricoid grease trough throughout complete cycle in the inner peripheral surface of case lid 5 and load-bearing part 24
25、25。
In turn, the cricoid ridge 26 being provided projectingly as the oil sealing of containment member 27 between the front surface of case lid 5 with it is defeated
Between the outer peripheral surface for entering axis 12.In addition, being also folded between outer housing 6 and output shaft 9 in the outlet side of crossed roller bearing 8
Oil sealing 28.In addition, being also folded with oil sealing 29 in the outlet side of ball bearing 11 between output shaft 9 and input shaft 12.
In differential speed reducer 1A~1C as constructed as above, if rotating input to input shaft 12 and rotating input shaft 12,
Then front and back eccentric part 14A~14C respectively symmetrically carry out eccentric motion, make each external gear 17A~17C with internal gear 4 in
Eccentric and spinning motion is carried out in the state of connecing.Therefore, although each pin hole 21A~21C also carries out eccentric and spinning motion,
But since to be formed as the diameter compared with the pin 22 comprising metalwork 23 bigger by each pin hole 21A~21C, thus each pin 22 with pin
In the state that hole 21A~21C is inscribed relatively eccentric motion and absorb eccentricity component, only take out rotation component from each pin 22.Cause
This, output shaft 9 and load-bearing part 24 synchronous rotary via pin 22, output shaft 9 is in the state of with above-mentioned reduction ratio deceleration
It is rotated.Here, differential speed reducer 1A becomes low deceleration, and differential speed reducer 1B becomes middle deceleration, differential to subtract in serial S
Fast device 1C becomes high and slows down.
At this point, the lubricating grease filled into shell 2 passes through the inner peripheral surface and load-bearing part of outer ring 10a and case lid 5 from gap A
It is supplied to grease trough 25,25 between 24 inner peripheral surface, guarantee to lubricate and reduces friction.In addition, even if supply lubricates in this way
Rouge, because between case lid 5 and input shaft 12, lubricating grease leakage will not occur for oil sealing 27.
(invention effect involved in the series of differential speed reducer)
In this way, according to the serial S of differential speed reducer 1A~1C of aforesaid way, as long as by by the pin of each external gear 17A~17C
Hole 21A~21C according to the number of teeth of external tooth respectively to be formed by each external gear 17A~17C different diameters, make internal gear 4,
23 commonization of pin 22 and metalwork, to only form the pin in aperture corresponding with a reduction ratio in external gear 17A~17C
Just it is enough by hole 21A~21C.Therefore, component can be shared under the premise of the intensity of external gear 17A~17C will not be made to decline
Change to inhibit manufacturing cost.
Especially herein, since the center of pin hole 21A~21C is consistent with each other between each external gear 17A~17C, because
This also can be realized commonization of output shaft 9 and load-bearing part 24.
In addition, the flute profile of internal gear 4 and external gear 17A~17C are involute tooth type.
According to the JGMA (Japanese Gear industry meeting standard) (JGMA 611-01) of the standards for gears as Japanese Gear industry meeting
" the displacement mode for following iso standard cylinder gear ", it is contemplated that the meshing efficiency of gear, the modification coefficient of involute internal gear and
The aggregate value of the modification coefficient of involute external gear recommends design below 1.
But in this mode, by being set in the modification coefficient of internal gear 4 more than between 1 and 1.9 or less, so as to
Increase the root diameter of the external gear 17A~17C engaged, it can be ensured that the tooth root and pin hole of external gear 17A~17C
The wall thickness of 21A~21C.
In addition, Fig. 4 is to compare that the modification coefficient of internal gear 4 is set as 1.9 and 0.2 and makes input torque when inputting 2000rpm
The curve graph of the variation of efficiency (transmission efficiency) when changing to 1Nm, the solid line of No.1 show modification coefficient 1.9 (number of teeth 76,
Teeth number difference 1, reduction ratio 1/75) the case where, the dotted line of No.2 shows modification coefficient 0.2 (number of teeth 60, teeth number difference 1, reduction ratio 1/
59) the case where.
Here, maximal efficiency is substantially 68% in modification coefficient 1.9, it is substantially 70% in modification coefficient 0.2, it is known that even if
Modification coefficient becomes 1.9, also and less big to the disturbance degree of efficiency.
In turn, since the quantity of the pin 22 of output section is set as eight, it can be improved differential speed reducer 1A~1C's
Rigidity.Especially because pin hole 21A~21C corresponding with a reduction ratio is only formed with regard to enough in external gear 17A~17C, because
The quantity of pin 22 is set as eight or more by this also can easily be done.
In addition, being effective by 22 thickening of pin to improve the rigidity of differential speed reducer 1A~1C.If the background enumerated as before
Technology forms multiple interior roller holes by each reduction ratio in external gear like that, then interior roller holes are close to each other, is by pin thickening
Highly difficult, but in the above method, it is corresponding with a reduction ratio due to only being formed for external gear 17A~17C
Pin hole 21A~21C, therefore can ensure the distance of pin hole 21A~21C to each other.Therefore, by 22 thickening of pin so that rigidity becomes
It is higher also to can easily be done.
Further, since only formation pin hole 21A~21C corresponding with a reduction ratio is for external gear 17A~17C
Can, therefore even if it is set as three kinds different of series of reduction ratio, external gear 17A~17C in each differential speed reducer 1A~1C
Intensity will not reduce.Therefore, it is able to maintain that internal gear 4, pin 22,24 commonization of metalwork 23, output shaft 9 and load-bearing part
State and constitute three kinds or more of series.
Also, by the way that input shaft 12 is set as hollow, it can be realized lightweight.In addition, even if input shaft 12 is set as hollow, outside
The intensity of gear 17A~17C is also able to maintain that.
In addition, though the series of three kinds of differential speed reducers is instantiated in the above method, but reduction ratio, differential speed reducer
Quantity be not limited to this, even if for the series of different two kinds or four kinds or more of the differential speed reducer of reduction ratio, also can be same
Carry out to sample commonization of internal gear, output section.Each reduction ratio is also not limited to aforesaid way.It is arranged in each differential speed reducer
The quantity of external gear can also increase and decrease.
Although, can also be with rotors such as exterior rollers in addition, make that metalwork is housed outside pin in the above method, or be set as
The not independent pin of other components as exterior.
(invention effect of differential speed reducer involved in the outer diameter of eccentric part bearing and eccentric part)
Like this, according to differential speed reducer 1A~1C of aforesaid way, by the needle roller that eccentric part is set as to full roller with bearing
Bearing 15, and the outer diameter D 2 of eccentric part 14A~14C in input shaft 12 is set as the axis branch than ball bearing 10,11 is arranged
The outer diameter D 1 of support part 13 is small, so as to increase the outer diameter of needle roller 16, facilitates strength enhancing.
Especially herein, due to, in the periphery of input shaft 12, being arranged and rolling between ball bearing 10,11 and needle bearing 15
The side of pearl bearing 10,11 abuts the anti-delinking part 18,18 of the movement in the axial direction to limit input shaft 12, and eccentric part 14A
~14C forms lower than anti-delinking part 18 throughout complete cycle, therefore even if being set as full roller, also can be throughout eccentric part 14A~14C's
Complete cycle limits the movement in the axial direction of needle roller 16.Furthermore it is possible to by anti-delinking part 18 be common to ball bearing 10,11 and needle roller 16 this
The anticreep of two sides.Moreover, anti-delinking part 18 also serves as the anticreep of input shaft 12 itself.
Further, since anti-delinking part 18 is set as the circular plate shape coaxial and integrally formed with input shaft 12, therefore can lead to
It crosses lathe etc. and easily processes anti-delinking part 18.
In turn, due to setting multiple groups eccentric part 14A~14C and needle bearing 15, external gear 17A~17C, and by each bias
The outer diameter of portion 14A~14C is set as all equal, therefore can configure identical needle bearing 15 in each eccentric part 14A~14C,
It is capable of increasing the outer diameter of the needle roller 16 of each needle bearing 15.
Further, since the shape of each external gear 17A~17C and each needle bearing 15 are set as identical respectively, therefore being capable of the phase
Wait further reduce the cost.
Also, due to configuring the needle roller 16 of needle bearing 15 the center O1's (axle center of input shaft 12) close to internal gear 4
Position, it is thus possible to increase the diameter of the pin 22 for taking out spinning motion from external gear 17A~17C.Therefore, can make differential
The strength enhancing of retarder 1A~1C.
In addition, the shape of anti-delinking part not necessarily circular plate shape, as long as the movement of needle roller can be limited, or outside
It is formed with the gear shape of multiple protrusions week, can also be the component seperated with input shaft.
(invention effect of differential speed reducer involved in the bearing of ball bearing)
Like this, according to differential speed reducer 1A~1C of aforesaid way, by making the outer ring 10a of ball bearing 10 by shell 2
Case lid 5 and load-bearing part 24 support, and so as to improve the concentricity of input shaft 12 Yu shell 2, can accurately assemble
Input shaft 12.
Especially herein, embedding since the outer ring 10a of ball bearing 10 is carried out gap relative to case lid 5 and load-bearing part 24
It closes, therefore can be slided by sliding surface, rotational resistance reduces.
Further, since being formed with profit on the outer ring 10a and case lid 5 of movable fit and the sliding surface of load-bearing part 24
Grease way 25,25, therefore lubricating grease can be held in sliding surface and be slided with low friction.
In turn, since grease trough 25 is formed in case lid 5 and load-bearing part 24, the ball bearing of standard can be used
10, it is able to suppress cost increase.
In addition, grease trough 25 can easily process profit by lathe etc. since the complete cycle throughout sliding surface is formed
Grease way 25.
Also, since, in the outside of ball bearing 10, being configured with will be between shell 2 and input shaft 12 in the axial direction of input shaft 12
The oil sealing 27 being sealed, therefore oil sealing 27 and input shaft 12 can be kept high between concentricity high shell 2 and input shaft 12
It contacts to precision, can reduce the risk of lubricating grease leakage.
In addition, though carrying out the outer ring of ball bearing relative to both case lid and load-bearing part
Movable fit, but can also movable fit only be carried out with any one.Therefore, grease trough is also only arranged at movable fit
The sliding surface of one side side.
In addition, other than throughout the setting of the complete cycle of sliding surface, can also break in the circumferential in the case where grease trough is arranged
It is arranged continuously.
In addition, same in each mode, the construction of shell be not limited to middle shell as aforesaid way and case lid and
The combination of outer housing can also increase and decrease the quantity of component, or form shell by a component.
In addition, outboard bearing is not limited to crossed roller bearing, can also also be increased using other bearings such as ball bearings
The quantity of bearing.
In turn, input shaft, output shaft construction be also not necessarily limited to aforesaid way, can suitably be designed change, such as will input
Axis is set as solid and simultaneously non-hollow etc..
Symbol description
1A~1C differential speed reducer, 2 shells, shell in 3,4 internal gears, 5 case lids, 6 outer housings, 7 bolts, 8
Crossed roller bearing, 9 output shafts, 10 ball bearings, the outer ring 10a, 11 ball bearings, 12 input shafts, 13 shaft supporting parts,
14 eccentric parts, 15 needle bearings, 16 needle rollers, 17A~17C external gear, 18 anti-delinking parts, 21A~21C pin hole, 22 pins,
23 metalworks, 24 load-bearing parts, 25 grease troughs, 27,28,29 oil sealings, S is serial, the gap A, outside D1 shaft supporting part
Diameter, the outer diameter of D2 eccentric part, the center of O1 internal gear, the center of O2 external gear, 1~δ of δ, 3 eccentricity.
Claims (5)
1. a kind of differential speed reducer characterized by comprising
Internal gear, setting is inside the shell；
Input shaft coaxially penetrates through the internal gear；
External gear, via eccentric part bearing outside loaded on being set to the eccentric part of the input shaft, and with the internal gear
Inscribed engagement；And
Output section has the pin for being loosely inserted into the external gear, and makes input shaft bearing between the output section and institute
It states between input shaft,
The external gear is set to carry out eccentric motion relative to the internal gear by the rotation of the input shaft, thus to be based on
Reduction ratio determined by the number of teeth of the difference and the external gear of the number of teeth of the internal gear and the number of teeth of the external gear passes through
The pin rotates the output section,
The eccentric part is set as full roller with bearing by the differential speed reducer, and by the eccentric part in the input shaft
Outer diameter be set as the part than the input shaft bearing is arranged outer diameter it is small.
2. differential speed reducer according to claim 1, which is characterized in that
Anti-delinking part is set in the periphery of the input shaft between the input shaft bearing and the eccentric part bearing, it is described
Anti-delinking part is abutted with the side of input shaft bearing to limit the movement in the axial direction of the input shaft, the eccentric part time
And complete cycle forms lower than the anti-delinking part.
3. differential speed reducer according to claim 2, which is characterized in that
The anti-delinking part is in the circular plate shape coaxial and integrally formed with the input shaft.
4. differential speed reducer according to any one of claims 1 to 3, which is characterized in that
The eccentric part and eccentric part bearing, the external gear are provided with multiple groups, and the outer diameter of each eccentric part is complete
Portion is equal.
5. differential speed reducer according to claim 4, which is characterized in that
The shape of each external gear is identical, and the shape of each eccentric part bearing is identical.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2017050241A JP6803273B2 (en) | 2017-03-15 | 2017-03-15 | Differential reducer |
| JP2017-050241 | 2017-03-15 | ||
| PCT/JP2018/009492 WO2018168763A1 (en) | 2017-03-15 | 2018-03-12 | Differential reduction gear |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110234907A true CN110234907A (en) | 2019-09-13 |
| CN110234907B CN110234907B (en) | 2023-03-10 |
Family
ID=63523637
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201880009531.3A Active CN110234907B (en) | 2017-03-15 | 2018-03-12 | Differential speed reducer |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6803273B2 (en) |
| CN (1) | CN110234907B (en) |
| WO (1) | WO2018168763A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110748611A (en) * | 2019-10-25 | 2020-02-04 | 青岛郑洋机器人有限公司 | Speed reducer driven by rigid gear of eccentric input shaft with large hollow structure |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2023015745A (en) | 2021-07-20 | 2023-02-01 | 住友重機械工業株式会社 | Eccentric oscillation type gear device |
Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0287037A2 (en) * | 1987-04-13 | 1988-10-19 | Sumitomo Heavy Industries, Ltd | Planetary gear apparatus |
| CN2591333Y (en) * | 2002-11-29 | 2003-12-10 | 夏正权 | Cyclo gear speed reducer |
| US20040218844A1 (en) * | 2003-03-31 | 2004-11-04 | Ts Corporation | Needle bearing and speed reducer using the needle bearing |
| WO2006085536A1 (en) * | 2005-02-09 | 2006-08-17 | Sumitomo Heavy Industries, Ltd. | Power transmission device |
| US20070243967A1 (en) * | 2006-04-17 | 2007-10-18 | Sumitomo Heavy Industries, Ltd. | Oscillating internally meshing planetary gear system |
| JP2011047457A (en) * | 2009-08-26 | 2011-03-10 | Sumitomo Heavy Ind Ltd | Bearing structure and bearing |
| CN102345680A (en) * | 2010-07-30 | 2012-02-08 | 住友重机械工业株式会社 | Roller keeper and swing inner gearing type geared apparatus |
| JP2014122681A (en) * | 2012-12-21 | 2014-07-03 | Jtekt Corp | Reducer of wind power generation device, and manufacturing method of reducer of wind power generation device |
| CN104565261A (en) * | 2014-12-26 | 2015-04-29 | 浙江恒丰泰减速机制造有限公司 | Precision rotational transmission mechanism |
| WO2015141387A1 (en) * | 2014-03-18 | 2015-09-24 | Ntn株式会社 | In-wheel motor drive device |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6727034B2 (en) * | 2016-05-30 | 2020-07-22 | 日本電産シンポ株式会社 | Gear reducer |
-
2017
- 2017-03-15 JP JP2017050241A patent/JP6803273B2/en active Active
-
2018
- 2018-03-12 CN CN201880009531.3A patent/CN110234907B/en active Active
- 2018-03-12 WO PCT/JP2018/009492 patent/WO2018168763A1/en active Application Filing
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0287037A2 (en) * | 1987-04-13 | 1988-10-19 | Sumitomo Heavy Industries, Ltd | Planetary gear apparatus |
| CN2591333Y (en) * | 2002-11-29 | 2003-12-10 | 夏正权 | Cyclo gear speed reducer |
| US20040218844A1 (en) * | 2003-03-31 | 2004-11-04 | Ts Corporation | Needle bearing and speed reducer using the needle bearing |
| WO2006085536A1 (en) * | 2005-02-09 | 2006-08-17 | Sumitomo Heavy Industries, Ltd. | Power transmission device |
| US20070243967A1 (en) * | 2006-04-17 | 2007-10-18 | Sumitomo Heavy Industries, Ltd. | Oscillating internally meshing planetary gear system |
| JP2011047457A (en) * | 2009-08-26 | 2011-03-10 | Sumitomo Heavy Ind Ltd | Bearing structure and bearing |
| CN102345680A (en) * | 2010-07-30 | 2012-02-08 | 住友重机械工业株式会社 | Roller keeper and swing inner gearing type geared apparatus |
| JP2014122681A (en) * | 2012-12-21 | 2014-07-03 | Jtekt Corp | Reducer of wind power generation device, and manufacturing method of reducer of wind power generation device |
| WO2015141387A1 (en) * | 2014-03-18 | 2015-09-24 | Ntn株式会社 | In-wheel motor drive device |
| CN104565261A (en) * | 2014-12-26 | 2015-04-29 | 浙江恒丰泰减速机制造有限公司 | Precision rotational transmission mechanism |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110748611A (en) * | 2019-10-25 | 2020-02-04 | 青岛郑洋机器人有限公司 | Speed reducer driven by rigid gear of eccentric input shaft with large hollow structure |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2018155264A (en) | 2018-10-04 |
| JP6803273B2 (en) | 2020-12-23 |
| CN110234907B (en) | 2023-03-10 |
| WO2018168763A1 (en) | 2018-09-20 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP5822392B2 (en) | Eccentric rocking speed reducer | |
| JP5941863B2 (en) | Deceleration device having an eccentric oscillation type deceleration mechanism | |
| EP2386780B1 (en) | Gear power transmitting device | |
| JP5283591B2 (en) | Series of simple planetary gear reducers | |
| CN107664178A (en) | Gear-shift mechanism | |
| WO2018147200A1 (en) | Planetary gear device | |
| TWI656287B (en) | Planetary gear reducer | |
| JP5844628B2 (en) | Planetary gear device and method of manufacturing planetary gear device | |
| KR20150012043A (en) | Differential speed reducer with conjugate dual cycloid tooth profile | |
| CN110234907A (en) | Differential speed reducer | |
| JP2017015206A (en) | Bearing and reduction gear | |
| CN110234906A (en) | Differential speed reducer | |
| JP6769897B2 (en) | How to manufacture a series of differential reducers | |
| JP6257683B2 (en) | Deceleration device having an eccentric oscillation type deceleration mechanism | |
| CN108730427A (en) | A kind of planet-gear transmission device and retarder | |
| JP6890563B2 (en) | Eccentric swing type speed reducer | |
| JP6025642B2 (en) | Planetary gear reducer and its series | |
| CN207975194U (en) | Speed changer | |
| JP7442364B2 (en) | Differential reducer with improved lubrication performance | |
| WO2019181965A1 (en) | Reduction gear and method for manufacturing reduction gear series | |
| CN105020348A (en) | Inner-connection meshing type gear device | |
| JP2020020409A (en) | Differential reducer | |
| JP2012246946A (en) | Rocking difference reduction gear | |
| CN109281995B (en) | Rolling cycloid planetary speed change mechanism | |
| KR20170070986A (en) | Bearing with gear tooth and reducer using the bearing |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |