CN105447295A - Planet gear system and method for determining structure parameter of planet gear system - Google Patents
Planet gear system and method for determining structure parameter of planet gear system Download PDFInfo
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- CN105447295A CN105447295A CN201410432644.8A CN201410432644A CN105447295A CN 105447295 A CN105447295 A CN 105447295A CN 201410432644 A CN201410432644 A CN 201410432644A CN 105447295 A CN105447295 A CN 105447295A
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Abstract
The invention discloses a planet gear system and a method for determining the structure parameter of the planet gear system. The planet gear system comprises a planet gear and a planet gear shaft, wherein a shaft hole is formed in the planet gear; the planet gear movably sleeves the planet gear shaft through the shaft hole; two ends of the planet gear shaft are mounted on one casing; both the inner wall of the shaft hole of the planet gear and the part on the outer surface of the planet gear shaft and in contact with the inner wall of the shaft hole are in the shape of a raised arc; the radius of the cross section of the shaft hole is increased progressively along the central axis of the shaft hole from the middle point to the two sides; the radius of the cross section of the part on the outer surface of the planet gear shaft and in contact with the inner wall of the shaft hole is decreased progressively along the central axis of the contact part from the middle point to the two sides. Through the scheme, the mesh unbalance loading of the planet gear and the eccentric wear of the planet gear and the planet gear shaft can be effectively avoided, the service lives of the planet gear and the planet gear shaft can be prolonged, the cost is low, and the planet gear system is environment-friendly and durable.
Description
Technical field
The present invention relates to field of automobile, particularly relate to the defining method of a kind of planetary gear system and structural parameters thereof.
Background technology
The basic training of car transmissions is with being that the power transmission that motor car engine produced is to wheel.Planet wheel and planet pin are the vitals in automotive transmission.
At present, planetary gear system is the important component part in the kinematic train of automobile, and wherein used planet wheel is located on planet pin by shaft hole sleeve.Wherein, planet pin is the cylindric of standard, and planetary axis hole is also the cylindric of standard, and the two ends of described planet pin are arranged on a housing.When by load, can there is corresponding distortion in planet wheel, planet pin and housing.Through after a period of time, planet wheel, planet pin and housing can produce the wearing and tearing and distortion that can not recover voluntarily.When planet pin, planet wheel and corresponding parts machining assembling are defective, easily occur that planet pin and planet wheel deflect in radial direction, thus cause planet wheel to engage the problems such as unbalance loading, planet wheel and planet pin eccentric wear.
Prior art, the main mode respectively plating one deck high-abrasive material or oil absorption material at the outside surface of planetary shaft hole inner wall and planet pin that adopts solves the problems referred to above.The high-abrasive material used in aforesaid way or oil absorption material be expensive but also contaminated environment not only, therefore, there is the problem that cost is high, the feature of environmental protection is poor.
Summary of the invention
What the embodiment of the present invention solved is how to effectively reduce planet wheel and planet wheel by wearing and tearing during load, reduces manufacturing cost, environmental and durable.
For solving the problem, embodiments provide a kind of planetary gear system, described planetary gear system comprises:
Planet wheel and planet pin, described planet wheel is provided with axis hole, described planet pin is movably set on described planet pin by described axis hole, the two ends of described planet pin are arranged on housing, the inwall of described planetary axis hole, the outside surface of described planet pin can contact part all in the arcuation of projection with the inwall of described axis hole, the radius of the xsect of described axis hole increases progressively along the mid point of the axis of axis hole to both sides, can the radius of xsect of contact portion can the mid point of axis of contact portion successively decreasing to both sides along described with described shaft hole inner wall of the outside surface of described planet pin.
Alternatively, the difference between the minimum cross-section of described axis hole and the radius of maximum cross section, and the outside surface of described planet pin with described shaft hole inner wall contact part maximum cross section equal with the difference between minimum cross-section.
Alternatively, the difference between the minimum cross-section of described axis hole and the radius of maximum cross section, and the difference between the maximum cross section of the part that contacts with described shaft hole inner wall of the outside surface of described planet pin and minimum cross-section meets following relation:
Difference between the minimum cross-section of described axis hole and the radius of maximum cross section, and the outside surface of described planet pin and described shaft hole inner wall can difference between the maximum cross section of contact portion and minimum cross-section, be difference corresponding when Max.contact stress is minimum between planet wheel and planet pin.
Alternatively, difference between the minimum cross-section of described axis hole and the radius of maximum cross section, with the outside surface of described planet pin and described shaft hole inner wall can differences between the maximum cross section of contact portion and the radius of minimum cross-section, for the wear extent between described planet wheel and described planet wheel minimum time corresponding difference.
The embodiment of the present invention additionally provides a kind of defining method of planetary gear system structural parameters, and described method comprises:
According to the structure of described planetary gear system, calculate the first convex value and described second convex value sum, described first convex value is the difference between the minimum cross-section of planetary axis hole in described planetary gear system and the radius of maximum cross section, and described second convex value is that the outside surface of planet pin in described planetary gear system and described shaft hole inner wall can differences between the maximum cross section of contact portion and minimum cross-section;
Calculate Max.contact stress between described planet wheel and planet pin, obtain the first convex value between described planet wheel and planet pin corresponding to Max.contact stress minimum value and the second convex value as the structural parameters in described planetary gear system.
Alternatively, the described structure according to described planetary gear system, calculates the first convex value and described second convex value sum, comprising:
Following formulae discovery is adopted to draw described first convex value and described second convex value sum:
D
crowned-ALL＝D
gear+D
shaft+D
case-d
Wherein, D
crowned-ALLfor described first convex value and the second convex value sum, D
gear, D
shaft, D
casebeing respectively axis hole is columned planet wheel, columned planet pin and the housing deflection when being subject to load, and d is the size in the gap coordinated between described cylindric planet pin and described planetary columned axis hole.
Alternatively, adopting Finite element arithmetic to obtain shaft outlet hole is columned planet wheel, columned planet pin and the housing deflection D when being subject to load
gear, D
shaft, D
case.
Alternatively, Max.contact stress between the described planet wheel of described calculating and planet pin, obtain the first convex value between described planet wheel and planet pin corresponding to Max.contact stress minimum value and the second convex value as the structural parameters in described planetary gear system, comprising:
According to hertz Max.contact stress formula, when described first convex value is equal with described second convex value, the Max.contact stress of described planet wheel and planet pin is minimum, and described first convex value and described second convex value meet following formula:
D
crowned-gear＝D
crowned-shaft＝0.5*D
crowned-ALL
Wherein, D
crowned-gearfor described first convex value, described D
crowned-shaftfor described second convex value, described D
crowned-ALLfor described first convex value and described second convex value sum.
Alternatively, described method also comprises:
Choose preliminary election convexity group more than two, described preliminary election convexity group comprises the first preliminary election convex value and the second preliminary election convex value, and described first preliminary election convexity and the second preliminary election convexity have default error with described first convex value and the second convex value respectively;
The first selected preliminary election convex value and the second preliminary election convex value are applied to described planet wheel and planet pin respectively;
The planet wheel and planet pin of applying described first preliminary election convex value and the second preliminary election convex value are respectively tested;
Choose the first preliminary election convex value and the second preliminary election convex value of the minimum described planet wheel of wear extent and planet pin, respectively as the first final convex value and the second convex value.
Alternatively, described first preliminary election convex value and the second preliminary election convex value have default error with described first convex value and the second convex value respectively, comprising:
Described first preliminary election convexity meets: 0 < D
crowned-gearN≤ D
crowned-gear;
Described second preliminary election convexity meets: 0 < D
crowned-shaftN≤ D
crowned-shaft;
Wherein, D
crowned-gearNfor described first preliminary election convex value, described D
crowned-shaftNfor described second preliminary election convex value, N represents N group preliminary election convexity group.
Compared with prior art, technical scheme of the present invention has following advantage:
All arcuation is set to the part that described shaft hole inner wall can contact by the outside surface by described planetary axis hole, planet pin, effectively can reduce the Max.contact stress between planet wheel and planet pin, thus the wearing and tearing that can effectively reduce between planet wheel and planet pin, planet wheel can be effectively avoided to engage unbalance loading and the eccentric wear between planet wheel and planet pin, improve the serviceable life of planet wheel and planet pin, with low cost, environmental and durable.
Further, by choosing the first preliminary election convex value with the first convex value and the second convex value with preset difference value and the second preliminary election convex value is tested, the first corresponding convex value and the second convex value when between the planet wheel obtain process test and planet pin, wear extent is minimum, as the first final convex value and the second convex value, by theory is combined with experimental verification, the structural parameters of described planetary gear system can be obtained further exactly, and be applied in described planetary gear system, thus the wearing and tearing that can more effectively reduce between planet wheel and planet pin, planet wheel can be effectively avoided to engage unbalance loading and the eccentric wear between planet wheel and planet pin, improve the serviceable life of planet wheel and planet pin.
Accompanying drawing explanation
Fig. 1 is the cross-sectional view of a kind of planetary gear system in the embodiment of the present invention;
Fig. 2 is the process flow diagram of the defining method of a kind of planetary gear system structural parameters in the embodiment of the present invention;
Fig. 3 determines the first final convex value and the process flow diagram of the second convex value in the defining method of planetary gear system structural parameters in the embodiment of the present invention.
Embodiment
For solving the above-mentioned problems in the prior art, the technical scheme that the embodiment of the present invention adopts is by being all set to arcuation by the outside surface of described planetary axis hole, planet pin with the part that described shaft hole inner wall can contact, effectively can reduce the friction between planet wheel and planet pin, improve the serviceable life of planetary gear system, with low cost, environmental and durable.
For enabling above-mentioned purpose of the present invention, feature and advantage more become apparent, and are described in detail specific embodiments of the invention below in conjunction with accompanying drawing.
Fig. 1 shows the structural representation of a kind of planetary gear system in the embodiment of the present invention.Planetary gear system as shown in Figure 1, can comprise:
Planet wheel 11 and planet pin 12, planet wheel 11 is provided with axis hole 11a, and planet wheel 11 is movably set on planet pin 12 by described axis hole 11a, and the two ends of planet pin 12 are arranged in a housing (not shown).
The inwall of axis hole 11a is in protruding arcuation, the xsect of axis hole 11a is circle, and along the direction, axis of axis hole 11a, axis hole 11a xsect radius of a circle is increased progressively to both sides by the mid point of axis, wherein, the radius of the maximum cross section of axis hole 11a can be equal with the radius of the xsect of the planetary axis hole in planetary gear system of the prior art.
With axis hole 11a similarly, the outside surface of planet pin 12 with the inwall of axis hole 11a can contact portion also in protruding arcuation.The outside surface of planet pin 12 and the inwall of axis hole 11a can the xsect of contact portion be circular, and along on the direction, axis of planet pin 12, the outside surface of planet pin 12 and the inwall of axis hole 11a can the radius of xsect of contact portion can the mid point of axis of contact portion successively decrease to both sides along described.Wherein, the outside surface of planet pin 12 and the non-of the inwall of axis hole 11a can contact portion can be cylindric, also namely the outside surface of planet pin 12 and the inwall of axis hole 11a non-can the radius of xsect of contact portion equal.
In concrete enforcement, according to hertz Max.contact stress formula, difference between the minimum cross-section and the radius of maximum cross section of described axis hole 11a, and the inwall of the outside surface of described planet pin 12 and described axis hole 11a can the maximum cross section of contact portion equal with the difference between minimum cross-section time, between planet wheel 11 and planet pin 12, Max.contact stress is minimum.
In concrete enforcement, can by the difference between the minimum cross-section of axis hole 11a and the radius of maximum cross section, as the first convex value.The outside surface of planet pin 12 and described axis hole 11a inwall can differences between the maximum cross section of contact portion and the radius of minimum cross-section, as the second convex value.
In order to determine finally to be applied in described planetary first convex value and the second convex value further, preliminary election convexity group more than two can be chosen, often organize in preliminary election convexity group and can comprise the first preliminary election convex value and the second preliminary election convex value respectively, the first preliminary election convex value in selected preliminary election convexity group and the second preliminary election convex value are applied in planetary gear system respectively and test.By test, the actual wear amount of planet wheel and planet pin just can be obtained, can using the first preliminary election convex value of applying in epicyclic train minimum for wear extent and the second preliminary election convex value as the first final convex value and the second convex value.
Fig. 2 shows the process flow diagram of the defining method of a kind of planetary gear system structural parameters in the embodiment of the present invention.The defining method of described planetary gear system structural parameters as shown in Figure 2, can comprise:
Step S21: according to the structure of described planetary gear system, calculates the first convex value and described second convex value sum.
In concrete enforcement, described first convex value is the difference between the minimum cross-section of planetary axis hole in described planetary gear system and the radius of maximum cross section, and described second convex value is that the outside surface of planet pin in described planetary gear system and described shaft hole inner wall can differences between the maximum cross section of contact portion and minimum cross-section.
In concrete enforcement, the planet wheel in planetary gear system and between planet pin, there is default gap, the first convex value and described second convex value sum can meet following formula:
D
crowned-ALL＝D
gear+D
shaft+D
case-d(1)
Wherein, D
crowned-ALLfor described first convex value and the second convex value sum, D
gear, D
shaft, D
casebeing respectively axis hole is columned planet wheel, columned planet pin and the housing deflection when being subject to load, and d is the size in the gap coordinated between described cylindric planet pin and described planetary columned axis hole.
In concrete enforcement, it is columned planet wheel, columned planet pin and the housing deflection D when being subject to load that Finite element arithmetic can be adopted to obtain shaft outlet hole
gear, D
shaft, D
case.
It is the assembly of one group of unit that continuous print is solved territory discrete by finite element method, the expression that the approximate function being used in hypothesis in each unit carrys out burst solves unknown field function to be asked on territory, approximate function is expressed at the numerical interpolation function of each node of unit by unknown field function and derivative thereof usually, thus makes a continuous print infinite degrees of freedom problem become discrete finite degrees of freedom problem.Finite element method can calculate columned planet wheel, columned planet pin and the housing deflection D when being subject to load efficiently, rapidly
gear, D
shaft, D
case.
Step S22: calculate Max.contact stress between described planet wheel and planet pin, obtains the first convex value between described planet wheel and planet pin corresponding to Max.contact stress minimum value and the second convex value as the structural parameters in described planetary gear system.
In order to reduce the contact stress between the inwall of axis hole and the outside surface of planet pin, according to hertz Max.contact stress derivation formula:
Wherein, q
maxrepresent Max.contact stress, the diameter of two spheroids at R1, R2 difference contact point place, P is outer normal vector, and K1, K2 are respectively two constants, and u1, u2 are respectively Poisson ratio, and E is elastic modulus.
From formula (2)-(4), when the inwall of axis hole and the outside surface of planet pin and axis hole inwall can curvature between contact portion everywhere equal time, the inwall of the inwall of axis hole and the outside surface of planet pin and axis hole can have minimum contact stress between contact portion.
Further, according to the structure of described planetary gear system, can obtain:
D
crowned-ALL＝D
gear+D
shaft+D
case-d(5)
Wherein, D
crowned-ALLfor the difference between the minimum cross-section of axis hole and the radius of maximum cross section, and the outside surface of described planet pin and described shaft hole inner wall can difference sums between the maximum cross section of contact portion and minimum cross-section, D
gear, D
shaft, D
casebeing respectively axis hole is columned planet wheel, columned planet pin and the housing deflection when being subject to load, and d is the size in the gap coordinated between described cylindric planet pin and described planetary columned axis hole.
In concrete enforcement, according to hertz Max.contact stress formula, when described first convex value is equal with described second convex value, the Max.contact stress of described planet wheel and planet pin is minimum, and described first convex value and described second convex value meet following formula:
D
crowned-gear＝D
crowned-shaft＝0.5*D
crowned-ALL(6)
Wherein, D
crowned-gearfor described first convex value, described D
crowned-shaftfor described second convex value, described D
crowned-ALLfor described first convex value and described second convex value sum.
In concrete enforcement, the factors such as the environment that planetary gear system is applied, when making to apply in the first convex value of being determined by step S21-S22 and the practice of the second convex value, may not obtain best effect.As shown in Figure 3, in order to determine to be applied to the first convex value in practice and the second convex value further, the defining method of described planetary gear system structural parameters, can also comprise:
Step S31: choose preliminary election convexity group more than two.
In concrete enforcement, described preliminary election convexity group comprises the first preliminary election convex value and the second preliminary election convex value, and described first preliminary election convexity and the second preliminary election convexity have default error with described first convex value and the second convex value respectively.Such as, described first preliminary election convexity and the second preliminary election convexity can meet with described first convex value and the second convex value respectively:
0＜D
crowned-gearN≤D
crowned-gear(7)
0＜D
crowned-shaftN≤D
crowned-shaft(8)
Wherein, D
crowned-gearNbe the first preliminary election convex value, described D
crowned-shaftNbe the second preliminary election convex value, described D
crowned-ALLbe the first convex value and the second convex value sum, N represents N group preliminary election convexity group.
Such as, can at the first convex value D
crowned-gearwith the second convex value D
crowned-shaftthe preliminary election convexity group that neighbouring selection is more than two: D
crowned-gear1, D
crowned-shaft1, D
crowned-gear2, D
crowned-shaft2, D
crowned-gear3, D
crowned-shaft3deng.
Step S32: the first selected preliminary election convex value and the second preliminary election convex value are applied to described planet wheel and planet pin respectively.
In concrete enforcement, selected preliminary election convexity group can be applied in planetary gear system respectively, manufacture a collection of planet pin with different convexity and planet wheel exemplar, to test.
Step S33: the planet wheel and planet pin of applying described first preliminary election convex value and the second preliminary election convex value are respectively tested.
In concrete enforcement, under same test specification, the planet pin of preliminary election convexity groups different for manufactured application and planet wheel exemplar are tested, to obtain the abrasion loss of each group of planet pin.
Step S34: the first preliminary election convex value and the second preliminary election convex value of choosing the minimum described planet wheel of wear extent and planet pin, respectively as the first final convex value and the second convex value.
In concrete enforcement, by the inspection of practice, obtain the wear extent of the planetary gear system tested under similarity condition, when wear extent is minimum, illustrate that the first preliminary election convexity of applying in described planetary gear system and the second preliminary election convexity can reduce the wearing and tearing of planetary gear system to greatest extent, therefore, just can by the first preliminary election convex value of applying in planetary gear system minimum for wear extent and the second preliminary election convex value, as the first final convex value and the second convex value, be applied in practice.
One of ordinary skill in the art will appreciate that all or part of step in the various methods of above-described embodiment is that the hardware that can carry out instruction relevant by program has come, this program can be stored in computer-readable recording medium, and storage medium can comprise: ROM, RAM, disk or CD etc.
Done detailed introduction to the method and system of the embodiment of the present invention above, the present invention is not limited to this.Any those skilled in the art, without departing from the spirit and scope of the present invention, all can make various changes or modifications, and therefore protection scope of the present invention should be as the criterion with claim limited range.
Claims (10)
1. a planetary gear system, it is characterized in that, comprise: planet wheel and planet pin, described planet wheel is provided with axis hole, described planet wheel is movably set on described planet pin by described axis hole, the two ends of described planet pin are arranged on a housing, described planetary shaft hole inner wall, the outside surface of described planet pin with described shaft hole inner wall can contact portion all in protruding arcuation, the radius of the xsect of described axis hole increases progressively along the mid point of axis hole axis to both sides, can the radius of xsect of contact portion can the mid point of axis of contact portion successively decreasing to both sides along described with described shaft hole inner wall of the outside surface of described planet pin.
2. planetary gear system according to claim 1, it is characterized in that, difference between the minimum cross-section of described axis hole and the radius of maximum cross section, and the outside surface of described planet pin with described shaft hole inner wall can difference between the maximum cross section of contact portion and the radius of minimum cross-section equal.
3. planetary gear system according to claim 2, it is characterized in that, difference between the minimum cross-section of described axis hole and the radius of maximum cross section, and the difference between the maximum cross section of the part that contacts with described shaft hole inner wall of the outside surface of described planet pin and the radius of minimum cross-section, meet following relation:
Difference between the minimum cross-section of described axis hole and the radius of maximum cross section, and the outside surface of described planet pin and described shaft hole inner wall can difference between the maximum cross section of contact portion and minimum cross-section, be difference corresponding when Max.contact stress is minimum between planet wheel and planet pin.
4. planetary gear system according to claim 2, its eigenwert is, difference between the minimum cross-section of described axis hole and the radius of maximum cross section, and the outside surface of described planet pin and described shaft hole inner wall can difference between the maximum cross section of contact portion and the radius of minimum cross-section, for the wear extent between described planet wheel and described planet wheel minimum time corresponding difference.
5. a defining method for planetary gear system structural parameters, is characterized in that, comprising:
According to the structure of described planetary gear system, calculate the first convex value and described second convex value sum, described first convex value is the difference between the minimum cross-section of planetary axis hole in described planetary gear system and the radius of maximum cross section, and described second convex value is that the outside surface of planet pin in described planetary gear system and described shaft hole inner wall can differences between the maximum cross section of contact portion and minimum cross-section; Calculate Max.contact stress between described planet wheel and planet pin, obtain the first convex value between described planet wheel and planet pin corresponding to Max.contact stress minimum value and the second convex value as the structural parameters in described planetary gear system.
6. very according to the defining method of planetary gear system structural parameters according to claim 5, it is characterized in that, the described structure according to described planetary gear system, calculate the first convex value and described second convex value sum, comprising:
Following formulae discovery is adopted to draw described first convex value and described second convex value sum:
D
crowned-ALL＝D
gear+D
shaft+D
case-d
Wherein, D
crowned-ALLfor described first convex value and the second convex value sum, D
gear, D
shaft, D
casebeing respectively axis hole is columned planet wheel, columned planet pin and the housing deflection when being subject to load, and d is the size in the gap coordinated between described cylindric planet pin and described planetary columned axis hole.
7. the defining method of planetary gear system structural parameters according to claim 6, is characterized in that, adopting Finite element arithmetic to obtain shaft outlet hole is columned planet wheel, columned planet pin and the housing deflection D when being subject to load
gear, D
shaft, D
case.
8. the defining method of planetary gear system structural parameters according to claim 6, it is characterized in that, Max.contact stress between the described planet wheel of described calculating and planet pin, obtain the first convex value between described planet wheel and planet pin corresponding to Max.contact stress minimum value and the second convex value as the structural parameters in described planetary gear system, comprising:
According to hertz Max.contact stress formula, when described first convex value is equal with described second convex value, the Max.contact stress of described planet wheel and planet pin is minimum, and described first convex value and described second convex value meet following formula:
D
crowned-gear＝D
crowned-shaft＝0.5*D
crowned-ALL
Wherein, D
crowned-gearfor described first convex value, described D
crowned-shaftfor described second convex value, described D
crowned-ALLfor described first convex value and described second convex value sum.
9. the defining method of planetary gear system structural parameters according to claim 8, is characterized in that, also comprise:
Choose preliminary election convexity group more than two, described preliminary election convexity group comprises the first preliminary election convex value and the second preliminary election convex value, and described first preliminary election convex value and the second preliminary election convex value have default difference with described first convex value and the second convex value respectively;
The first selected preliminary election convex value and the second preliminary election convex value are applied to described planet wheel and planet pin respectively;
The planet wheel and planet pin of applying described first preliminary election convex value and the second preliminary election convex value are respectively tested;
Choose the first preliminary election convex value and the second preliminary election convex value of the minimum described planet wheel of wear extent and planet pin, respectively as the first final convex value and the second convex value.
10. the defining method of planetary gear system structural parameters according to claim 9, is characterized in that, described first preliminary election convex value and the second preliminary election convex value have default difference with described first convex value and the second convex value respectively, comprising:
Described first preliminary election convex value meets: 0 < D
crowned-gearN≤ D
crowned-gear;
Described second preliminary election convex value meets: 0 < D
crowned-shaftN≤ D
crowned-shaft;
Wherein, D
crowned-gearNfor described first preliminary election convex value, described D
crowned-shaftfor described second preliminary election convex value, N represents N group preliminary election convexity group.
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106354975A (en) * | 2016-09-23 | 2017-01-25 | 清华大学 | Finite element method for acquiring misalignment quantity of planetary gear |
| DE102019209669A1 (en) * | 2019-07-02 | 2021-01-07 | Zf Friedrichshafen Ag | Planetary plain bearing with a convex sliding surface |
| DE102021122450A1 (en) | 2021-08-31 | 2023-03-02 | Rolls-Royce Deutschland Ltd & Co Kg | planetary gear |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106354975A (en) * | 2016-09-23 | 2017-01-25 | 清华大学 | Finite element method for acquiring misalignment quantity of planetary gear |
| DE102019209669A1 (en) * | 2019-07-02 | 2021-01-07 | Zf Friedrichshafen Ag | Planetary plain bearing with a convex sliding surface |
| DE102021122450A1 (en) | 2021-08-31 | 2023-03-02 | Rolls-Royce Deutschland Ltd & Co Kg | planetary gear |
| US11885410B2 (en) | 2021-08-31 | 2024-01-30 | Rolls-Royce Deutschland Ltd & Co Kg | Planetary gear box |
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| CN105447295B (en) | 2018-08-14 |
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