CN112901727A - Variable-rigidity flexible pin shaft load balancing structure for reducing axial inclination angle of planet wheel - Google Patents
Variable-rigidity flexible pin shaft load balancing structure for reducing axial inclination angle of planet wheel Download PDFInfo
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- CN112901727A CN112901727A CN202110255227.0A CN202110255227A CN112901727A CN 112901727 A CN112901727 A CN 112901727A CN 202110255227 A CN202110255227 A CN 202110255227A CN 112901727 A CN112901727 A CN 112901727A
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- 238000009826 distribution Methods 0.000 claims abstract description 20
- 238000004519 manufacturing process Methods 0.000 claims abstract description 13
- 230000000694 effects Effects 0.000 claims description 9
- 230000005489 elastic deformation Effects 0.000 claims description 7
- 238000010008 shearing Methods 0.000 claims description 5
- 238000000034 method Methods 0.000 claims description 3
- 239000007787 solid Substances 0.000 claims description 3
- 238000010586 diagram Methods 0.000 description 15
- 230000005540 biological transmission Effects 0.000 description 4
- 241001397809 Hakea leucoptera Species 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 3
- 238000009434 installation Methods 0.000 description 3
- 238000009825 accumulation Methods 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
- F16H2001/325—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear comprising a carrier with pins guiding at least one orbital gear with circular holes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- 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
- F16H2001/328—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 balancing means
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Abstract
The invention discloses a variable-rigidity flexible pin shaft uniform load structure for reducing the axial inclination angle of a planet wheel, wherein the excircle of a novel pin shaft sleeve (6) of the flexible pin shaft uniform load structure is a cylinder with a shaft shoulder at one end, the interior of the novel pin shaft sleeve is a stepped shaft and is divided into three sections according to the aperture, the inner aperture is reduced in sequence from the end close to a planet carrier (1), and an annular groove is processed at the end, away from the planet carrier (1), of the novel pin shaft sleeve (6). Meanwhile, the pin shaft (5) is hollow, an opening is formed in one side of the pin shaft, the hollow volume, the opening degree and the interference assembling amount of the two ends of the pin shaft are required to be calculated, and the pin shaft (5) is fixed in a pin hole of the planet carrier (1) through a fastening screw (13); the axial inclination angle of the gear with the uniform loading structure of the existing flexible pin shaft is reduced, the problem of local failure of gear teeth caused by uneven distribution of tooth-direction contact loads is avoided, meanwhile, the rigidity-variable design increases the flexibility of the pin shaft, the manufacturing and mounting errors of larger parts can be offset, and the problem of serious uneven load distribution among the planet gears is solved.
Description
Technical Field
The invention relates to the field of planetary gear transmission, in particular to a variable-rigidity flexible pin shaft load balancing structure for reducing the axial inclination angle of a planetary gear.
Background
The planetary transmission device has the characteristics of large coaxial output speed ratio, small volume, high bearing capacity and the like, and is widely applied to the industries of aerospace, ships, wind power and the like. The planetary gear train consists of a sun gear, an inner gear ring, a planet carrier and a plurality of planet gears, and the plurality of planet gears carry out load splitting, so that the planetary gear train can realize large transmission ratio in a smaller volume. When the strength of the gear train is calculated, the bearing of each planet wheel is assumed to be the same, but due to the existence of manufacturing and installing errors, the load distribution among a plurality of planet gears is uneven, so that a single planet gear fails due to overlarge load, and therefore load balancing measures are required to be taken, and the bearing of each planet wheel is the same. The flexible pin shaft structure is one of the load balancing measures, the weight of the planet carrier can be reduced, and the error is offset through the flexible deformation of the pin shaft, so that the uniform load distribution of the planet wheel is realized.
The existing flexible pin shaft patent CN205715578U (a wind power gear box flexible shaft), the flexible pin shaft structure mainly comprises a planet carrier, a planet wheel, a bearing, an elastic check ring, a pin shaft and a pin shaft sleeve, the pin shaft extends out from the cantilever end of the planet carrier, the pin shaft sleeve extends out from a cantilever at one end far away from the planet carrier, the pin shaft and the pin shaft sleeve form a double-cantilever structure, the pin shaft sleeve is internally provided with a single-step ladder, the minimum diameter part is in interference fit with the pin shaft, the axial positioning is carried out through a shaft shoulder structure at the tail end of the pin shaft, the pin shaft sleeve is processed out of the shaft shoulder structure near one end of the planet carrier, the other end of the. By adopting the existing flexible pin shaft load balancing structure, when the load borne by a single planet wheel is larger than the average value, the manufacturing and mounting errors can be counteracted through the double-cantilever deformation of the pin shaft and the pin shaft sleeve, and the uniform distribution of the load among the planet wheels in the planetary gear train is realized.
However, there are also studies (Shyi-Jeng Tsai, Siang-Yu Ye, Yuan-Yi Yu, et al. design and analysis of the planar gear drive with flexible pins for with turbines [ C ]// European with energy conference & understanding 2012.volume 2of 3.2013:706-715.) that show: the flexible pin shaft is stressed and bent to deform, and the planet wheel arranged on the pin shaft sleeve generates a corresponding inclination angle along the axial direction, so that loads at the meshing positions of the planet wheel and the inner gear ring and the planet wheel and the sun wheel are unevenly distributed along the tooth direction of the gear teeth, and the local load of the gear teeth is overlarge to generate plastic deformation or gluing to fail. And when the manufacturing and mounting errors accumulated by parts are large, the existing solid pin shaft has small deformation and small offset error, so that the load distribution among the gear train planet wheels is seriously uneven, the load shared by a single planet wheel is large, and the failure of the gear teeth is easily caused, thereby reducing the reliability of a transmission system.
Therefore, need design a novel flexible pin axle load balancing structure who reduces planet wheel axial inclination, can reduce planet wheel axial inclination, the serious uneven problem of planet wheel teeth of a cogwheel load distribution, when solving the manufacturing installation error of accumulation again, load distribution is uneven between each planet wheel.
Disclosure of Invention
The invention aims to overcome the defects in the prior art, and provides a novel variable-rigidity flexible pin shaft load balancing structure for reducing the axial inclination angle of a planet wheel, which can effectively solve the problem of uneven distribution of the tooth-direction load of the planet gear caused by the inclination angle of the existing flexible pin shaft and solve the problem of serious uneven distribution of the load between the planet wheels of a gear train when the accumulated manufacturing and mounting errors of parts are larger.
The invention is completed by the following technical scheme: the utility model provides a reduce novel flexible pin axle load balancing structure at planet wheel axial inclination, mainly comprises planet carrier, planet wheel, bearing, circlip, round pin axle sleeve, fastening screw, and the one end cantilever that the planet carrier was kept away from to the round pin axle sleeve stretches out, minimum diameter portion and round pin axle interference fit in the round pin axle sleeve. The invention is characterized in that: the excircle of the pin shaft sleeve is a cylinder with a shaft shoulder at one end, the inner part of the pin shaft sleeve is stepped, the pin shaft sleeve is divided into three sections according to the aperture, the inner aperture is reduced in sequence from the end close to the planet carrier, an annular groove is processed at the end, far away from the planet carrier, of the pin shaft sleeve, the outer diameter of the annular groove is the same as the maximum aperture of the end, close to the planet carrier, of the stepped hole of the pin shaft sleeve, the depth of the annular groove hole is the same as the depth of the hole close to the section of the planet carrier, the maximum aperture on the left side of. The pin shaft sleeve is used for axial positioning at the part with the largest diameter close to the shaft shoulder at one end of the planet carrier. The pin shaft is internally designed with a hollow opening, the hollow volume is smaller, the opening is formed in one side of the circumference, the opening angle is also smaller, the plane formed by the symmetrical center lines of the two sides of the opening and the center line of the pin shaft is perpendicular to the plane formed by the center line of the pin shaft and the center line of the sun gear, the pin shaft after interference assembly meets the requirements of shear strength and torsional strength, and one end of the pin shaft is fixed in the pin hole of the planet carrier by a fastening screw.
Preferably, the method comprises the following steps: the pin shaft sleeve is in interference connection with the pin shaft and is axially positioned through a shaft shoulder on the pin shaft, the pin shaft sleeve is close to a shaft shoulder structure at one end of the planet carrier and an elastic check ring at the other end of the planet carrier to axially position the bearing, and the bearing is fixed on the pin shaft sleeve.
Preferably, the method comprises the following steps: the pin shaft is hollow and opened, one end of the pin shaft is fixed with a fastening screw through interference fit, the other end of the pin shaft is installed in a corresponding pin shaft sleeve hole in an interference fit mode, the hollow volume is small, the hollow volume and the assembling interference magnitude need to be calculated to guarantee the shearing strength and the torsion strength of the pin shaft, the opening angle is small, the size of the fastening screw tightening torque is determined according to needs, and the size of the fastening screw tightening torque is determined according to actual conditions.
The principle of the invention is as follows: when the load borne by a single planet wheel is larger than the average value, the flexible pin shaft is stressed, deformed and bent, and the planet wheel arranged on the pin shaft sleeve generates an axial inclination angle, so that the load of the gear teeth meshed with the inner gear ring is unevenly distributed along the tooth direction. By adopting the pin shaft sleeve structure, at the end with large tooth axial load of the tooth at the meshing position of the planet wheel and the inner gear ring, the meshing radial force enables the outer ring at the same side of the pin shaft sleeve to be pressed and deformed through the planet wheel bearing, and the axial inclination angle of the planet wheel is reduced at the moment. The side of the planetary gear, which has large tooth-direction bearing capacity with the meshing gear of the sun gear, is opposite to the inner gear ring, the radial force of the meshing of the sun gear and the planetary gear enables the other side of the pin shaft sleeve to be pressed, bent and deformed, and the axial inclination angle of the planetary gear is further reduced.
The circular ring holes on the two sides of the pin shaft sleeve are symmetrical to the middle section, so that the two sides can elastically deform along the middle section. When the planet wheel is respectively meshed with the inner gear ring and the sun wheel, no matter the meshing force is far away from or close to the planet carrier end is large, the two ends of the pin shaft sleeve can correspondingly generate elastic deformation, so that the inclination angle generated after the pin shaft is loaded can be offset by the elastic deformation of the pin shaft sleeve. The pin shaft sleeve can change the planet wheel into translation, thereby not only offsetting errors and achieving the load balancing effect, but also not generating an inclination angle, and reducing the inclination angle caused by the load balancing effect of the prior flexible pin shaft load balancing structure, thereby reducing the phenomenon of partial failure of the wheel teeth caused by uneven distribution of tooth-direction contact load.
The pin shaft is hollow and is provided with an opening at one side of the circumference, the plane formed by the symmetrical center line at the two sides of the opening and the center line of the pin shaft is vertical to the plane formed by the center line of the pin shaft and the center line of the sun gear, the pin shaft after interference assembly meets the requirements of shearing strength and torsional strength, and the pin shaft is fixed in the pin hole of the planet carrier by a fastening screw; when the accumulated manufacturing and mounting errors of all parts are large, so that the load distribution among the gear train planet wheels is seriously uneven, the load shared by a single planet wheel is larger, the rigidity of a pin shaft with a hollow opening structure is smaller than that of a solid pin shaft, the deformation is larger, larger manufacturing and mounting errors can be offset, the load balancing effect is better, the deformation direction is vertical to symmetrical center lines at two sides of the opening, and the opening tends to be closed; meanwhile, in order to prevent the pin shaft from deforming too much to cause other changes of the wheel train, the opening angle is smaller, the opening is closed after the pin shaft deforms to a certain degree, the rigidity of the pin shaft is increased, and the flexible pin shaft can be prevented from deforming too much integrally.
Compared with the prior art, the invention has the following effects: the flexibility of the pin shaft is increased, the manufacturing and mounting errors of parts are offset, and the problem of uneven load distribution among the planet wheels is solved; meanwhile, the axial inclination angle of the planet wheel caused by the realization of the load balancing effect of the existing flexible pin shaft load balancing structure can be reduced, and the phenomenon of local failure of the wheel teeth caused by uneven distribution of the tooth-direction contact load is avoided.
Compared with the prior art, the invention has the following effects: the axial inclination angle of the planet wheel of the existing flexible pin shaft load balancing structure is reduced through the flexible deformation of the pin shaft sleeve, the phenomenon that the load is distributed unevenly along a contact line is effectively improved, and the phenomenon that the wheel teeth are partially failed due to uneven distribution of the tooth-direction contact load is avoided; meanwhile, the rigidity of the pin shaft is reduced, the overall flexibility of the flexible pin shaft structure is increased, larger manufacturing and mounting errors accumulated by parts can be offset, the loading among the planet gears can be more balanced, the problem that the loads among the planet gears are seriously unevenly distributed can be solved, the weight of the planet gear box is reduced, the requirements of different flexibility of different planet gear systems are met by conveniently and quickly adjusting the opening angle of the pin shaft, and experimental statistics can be conveniently carried out, so that the flexible pin shaft structure can be widely applied.
Drawings
FIG. 1 is a variable-rigidity flexible pin shaft load balancing structure for reducing the axial inclination angle of a planet wheel.
Fig. 2 is a schematic view of an existing flexible pin shaft load balancing structure.
Fig. 3 shows the result of gear tilt caused by prior art flexpin deformation. (taken from the literature: Shyi-Jeng Tsai, Siang-Yu Ye, Yuan-Yi Yu, et al. design and analysis of the planar gear drive with flexible pins for with turbines [ C ]// European with energy conference & preference 2012.volume 2of 3.2013:706-715.)
Figure 4 shows the prior flexpin deformation and tooth load distribution diagram.
Fig. 5 is a small rigidity deformation diagram of the variable rigidity flexible pin shaft for reducing the axial inclination angle of the planet wheel.
FIG. 6 is a large rigidity deformation diagram of a variable rigidity flexible pin shaft for reducing the axial inclination angle of a planet wheel.
Figure 7 is a graph of stiffness as a function of deformation.
Fig. 8 is a schematic view of a two-dimensional configuration of the pin bosses.
Fig. 9 is a schematic view of the left side three-dimensional structure of the pin boss.
Fig. 10 is a schematic view of the three dimensional structure of the right side of the pin boss.
Fig. 11 is a schematic view of a pin structure.
FIG. 12 is a finite element deformation diagram of a simplified model hollow opening shaft opening state of a variable-rigidity flexible pin shaft load balancing structure for reducing the axial inclination angle of a planet wheel.
FIG. 13 is a finite element deformation diagram of a simplified model hollow opening shaft closed state of a variable-rigidity flexible pin shaft load balancing structure for reducing the axial inclination angle of a planet wheel.
Fig. 14 shows the existing load balancing structure of the flexible pin shaft, the load balancing structure of the variable-stiffness flexible pin shaft, the novel load balancing structure of the flexible pin shaft for reducing the axial inclination angle of the planet wheel, and the displacement of the top bus of the planet wheel of the variable-stiffness flexible pin shaft for reducing the axial inclination angle of the planet wheel.
In the figure, 1-planet carrier, 2-planet wheel, 3-bearing, 4-elastic retainer ring (pin shaft sleeve positioning), 5-pin shaft, 6-novel pin shaft sleeve, 7-elastic retainer ring (bearing positioning), 8-maximum diameter part, 9-middle section of pin shaft sleeve, 10-circular groove hole outer ring part, 11-existing pin shaft, 12-existing pin shaft sleeve, and 13-fastening screw.
Detailed Description
The invention will be further described with reference to the accompanying drawings.
Fig. 2, 3 and 4 show a schematic diagram of an existing flexpin shaft load balancing structure, a gear inclination result caused by deformation of an existing flexpin shaft, and a distribution diagram of deformation of an existing flexpin shaft and a tooth direction load. The existing flexible pin shaft can improve the phenomenon of uneven load distribution among planet gears to a certain extent through elastic deformation, but as shown in fig. 4, the flexible pin shaft has a very high limitation, the flexible pin shaft is stressed to bend and deform, a planet gear installed on a pin shaft sleeve generates a corresponding inclination angle along the axial direction, one side of the existing pin shaft sleeve deforms to offset uneven load on one side, the other side of the existing pin shaft sleeve cannot deform to offset uneven load on the other side due to the structural limitation of the existing pin shaft sleeve, so that the meshing positions of the planet gear and an inner gear ring on the one side and the planet gear and a sun gear are unevenly distributed along the tooth direction load of the gear teeth, and the local load of the gear teeth is overlarge to generate plastic.
As shown in fig. 1, fig. 5, and fig. 6, a variable-stiffness flexible pin shaft load balancing structure for reducing an axial tilt angle of a planet wheel, a small-stiffness deformation diagram of a variable-stiffness flexible pin shaft for reducing an axial tilt angle of a planet wheel, and a large-stiffness deformation diagram of a variable-stiffness flexible pin shaft for reducing an axial tilt angle of a planet wheel are shown. The invention relates to a variable-rigidity flexible pin shaft load balancing structure for reducing the axial inclination angle of a planet wheel, which mainly comprises a planet carrier (1), the planet wheel (2), a bearing (3), an elastic retainer ring (4), a pin shaft (5), a novel pin shaft sleeve (6), the elastic retainer ring (7) and a fastening screw (13). The pin shaft (5) is hollow and is provided with an opening at one side of the circumference, the plane formed by the symmetrical center lines at the two sides of the opening and the center line of the pin shaft (5) is perpendicular to the plane formed by the center line of the pin shaft (5) and the center line of the sun gear, one end of the pin shaft is fixed by interference fit and a fastening screw, the other end of the pin shaft is arranged in a corresponding pin shaft sleeve hole in an interference fit manner, and the pin shaft after interference fit meets the requirements of shear strength and torsional strength. The hollow volume is small, the hollow volume and the assembling interference magnitude need to be calculated so as to ensure the shearing strength and the torsional strength of the pin shaft, and the opening angle is small and is determined according to the requirement. The rigidity is small when the opening shaft is opened, the deformation of the pin shaft (5) is large, the offset error is large, and the load balancing effect is better; rigidity is increased after closing, and the deformation that the round pin axle (5) continuously increased reduces, can guarantee that whole deformation can not be too big to avoid arousing other problems of train.
As shown in fig. 7, the graph of the change in stiffness is shown, the ordinate representing the stiffness and the abscissa representing the degree of deformation. The small rigidity corresponds to the rigidity of the opening state of the pin shaft (5), the large rigidity corresponds to the rigidity of the closing state of the pin shaft (5), and the sudden change point of the rigidity corresponds to the moment when the opening of the pin shaft (5) is closed.
The installation process of the invention is as follows: insert the axle collar until round pin axle (5) from the no collar end of round pin axle (5) with the aperture diameter end of novel round pin axle sleeve (6) and contact completely of the novel round pin axle sleeve (6) with the aperture diameter end of round pin axle sleeve (6) earlier, insert planet carrier (1) with the novel round pin axle sleeve (6) of installing and the non-collar end of round pin axle (5), round pin axle (5) are fixed to installation fastening screw (13), then install bearing (3) on novel round pin axle sleeve (6), and installation circlip (4) make bearing (3) carry out axial positioning on novel round pin axle sleeve (6), adorn planet wheel (2) on well fixed bearing (3) at last.
Fig. 8, 9, 10 and 11 show a two-dimensional structure diagram of the pin bush, a left-side three-dimensional structure diagram of the pin bush, a right-side three-dimensional structure diagram of the pin bush, and a pin structure diagram, respectively. The deformation gear of the flexible pin shaft is inclined when the planet wheel (2) is subjected to the meshing force, the load of the gear teeth is unevenly distributed along the axis direction, and the circular holes on the two sides of the novel pin shaft sleeve (6) are symmetrical to the middle section, so that the two sides can elastically deform along the middle section (8). When meshing with ring gear and sun gear respectively, no matter keep away from or be close to the meshing force of planet carrier end big, novel round pin axle sleeve (6) both ends all can corresponding take place elastic deformation for the inclination that produces after round pin axle (5) are loaded can be offset by the elastic deformation of novel round pin axle sleeve (6).
Fig. 12 shows a deformation diagram of the opening state of the hollow opening shaft of the simplified model of the variable-stiffness flexible pin shaft load balancing structure for reducing the axial inclination angle of the planet wheel. A concentrated load of 1000N was applied to the top of the planet wheel and the scaling factor was set to 200 for clarity of deformation.
Fig. 13 is a deformation diagram of a closed state of a hollow open shaft of a simplified model of a variable-stiffness flexible pin shaft load balancing structure for reducing an axial inclination angle of a planet wheel. The concentrated load 50000N is applied to the top middle point of the planet wheel, the hollow opening shaft is opened and closed, the adjustment scaling factor is set to be 1.5 for the purpose of clearly seeing the deformation condition, and the deformation of the hollow opening shaft in the closed condition can be seen.
Fig. 14 shows the planet wheel top bus displacement of the existing flexible pin shaft load balancing structure, the variable stiffness flexible pin shaft load balancing structure, the novel flexible pin shaft load balancing structure for reducing the planet wheel axial inclination angle, and the variable stiffness flexible pin shaft load balancing structure for reducing the planet wheel axial inclination angle. Under the condition that the load is loaded to 3000N, the nodes at the top side generatrix of the planet wheel in the finite element model are respectively selected and drawn into point graphs, the abscissa is the position of the node, the ordinate is the longitudinal displacement value of the node, the variable-rigidity flexible pin shaft load balancing structure for reducing the axial inclination angle of the planet wheel has higher flexibility, the axial inclination angle of the planet wheel can be effectively reduced, and the uniform load performance is more superior.
Claims (3)
1. A variable-rigidity flexible pin shaft load balancing structure for reducing the axial inclination angle of a planet wheel mainly comprises a planet carrier (1), the planet wheel (2), a bearing (3), an elastic retainer ring (4), a pin shaft (5), a pin shaft sleeve (6), the elastic retainer ring (bearing positioning) (7) and a fastening screw (13); one end of the pin shaft (5) is firstly assembled in a pin hole of the planet carrier (1) in an interference fit mode, then the pin shaft (5) is assembled with a fastening screw (13), the other cantilever end extends out, the pin shaft sleeve (6) extends out from one cantilever end, far away from the planet carrier (1), of the pin shaft (5), the minimum diameter part in the pin shaft sleeve (6) is in interference fit with the other end of the pin shaft (5), the pin shaft (5) and the pin shaft sleeve (6) form a double-cantilever structure, the pin shaft sleeve (6) is close to a shaft shoulder structure at one end of the planet carrier (1) and an elastic check ring (4) at the other end, the bearing (3) is axially positioned, and the bearing (3) is fixed on; the method is characterized in that: the outer circle of the pin shaft sleeve (6) is a cylinder with a shaft shoulder at one end, the inside of the pin shaft sleeve is stepped, the pin shaft sleeve is divided into three sections according to the aperture, and the inner aperture is reduced in sequence from the end close to the planet carrier (1); an annular groove is processed at one end, far away from the planet carrier (1), of the pin shaft sleeve (6), the outer diameter of the annular groove is the same as the maximum aperture of one end, close to the planet carrier (1), of the pin shaft sleeve (6), the depth of the circular annular groove hole is the same as the depth of an end hole, close to the planet carrier (1), of the pin shaft sleeve (6), the diameters of a left side maximum hole (7) and a right side maximum hole (9) of the annular groove are the same, the pin shaft sleeve (6) is symmetrical relative to the middle section of the pin shaft sleeve (8), and the abrupt change positions of the sectional area of; the pin shaft (5) is hollow and opened, the hollow volume is small, the hollow volume and the assembling interference magnitude need to be calculated so as to ensure the shearing strength and the torsional strength of the pin shaft, and the opening angle is small and needs to be determined according to the requirement; one end of the pin shaft (5) is fixed with a fastening screw (13) through interference fit, and the tightening torque of the fastening screw (13) is determined by actual conditions.
2. The pin bushing of claim 1 wherein: when a single planet wheel (2) bears a load larger than the average value, the flexible pin shaft is stressed, deformed and bent, and the planet wheel (2) arranged on the pin shaft sleeve (6) generates a corresponding inclination angle along the axial direction, so that the tooth-direction load distribution of the planet wheel (2) and the gear teeth meshed with the sun wheel and the inner gear ring is uneven; by adopting the pin shaft sleeve (6) structure, the radial force of the meshing at the end with large tooth load at the meshing position of the planet wheel (2) and the inner gear ring can make the outer ring at the same side of the pin shaft sleeve (6) deform under pressure through the planet wheel bearing (3), so that the axial inclination angle of the planet wheel (2) is reduced; the side with large tooth direction bearing of the meshing gear teeth of the planet gear (2) and the sun gear is opposite to the inner gear ring, the radial force of the meshing of the sun gear and the planet gear (2) enables the other side of the pin shaft sleeve to be pressed, bent and deformed, and the axial inclination angle of the planet gear (2) is further reduced; the circular ring holes on the two sides of the pin shaft sleeve are of a structure symmetrical to the middle section, so that the two sides can elastically deform along the middle section (8); when the planetary gear is respectively meshed with the inner gear ring and the sun gear, no matter the meshing force is far away from or close to the planet carrier end is large, two ends of the pin shaft sleeve (6) can correspondingly generate elastic deformation, so that the inclination angle generated after the pin shaft (5) is loaded is offset by the elastic deformation of the pin shaft sleeve (6), and the planetary gear (2) is changed into translation; the manufacturing and mounting errors are offset, the uniform load effect is achieved, the inclination angle is not generated, the distribution nonuniformity of the axial inclination angle and the tooth direction contact load of the planet wheel with the flexible pin shaft uniform load structure is reduced, and the local failure of the wheel teeth is avoided.
3. The pin of claim 1, wherein: the pin shaft (5) is hollow and is provided with an opening at one side of the circumference, the plane formed by the symmetrical center lines at the two sides of the opening and the center line of the pin shaft (5) is vertical to the plane formed by the center line of the pin shaft (5) and the center line of the sun gear, and the pin shaft after interference assembly meets the requirements of shearing strength and torsional strength; when the accumulated manufacturing and mounting errors of all parts are large, so that the load distribution among the planet wheels is seriously uneven, the load shared by a single planet wheel is larger, the rigidity of a pin shaft with a hollow opening structure is smaller than that of a solid pin shaft, the flexibility of the pin shaft is increased, the deformation is larger, larger manufacturing and mounting errors can be offset, the load balancing effect is better, the deformation direction is vertical to symmetrical center lines at two sides of the opening, and the opening tends to be closed; meanwhile, in order to prevent the pin shaft from deforming excessively to cause other changes of the gear train, the opening angle is smaller, the opening is closed after the pin shaft deforms to a certain degree, the rigidity of the pin shaft is increased, and the flexible pin shaft can be prevented from deforming excessively.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110255227.0A CN112901727A (en) | 2021-03-09 | 2021-03-09 | Variable-rigidity flexible pin shaft load balancing structure for reducing axial inclination angle of planet wheel |
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| CN202110255227.0A CN112901727A (en) | 2021-03-09 | 2021-03-09 | Variable-rigidity flexible pin shaft load balancing structure for reducing axial inclination angle of planet wheel |
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Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111022615A (en) * | 2019-12-23 | 2020-04-17 | 湘潭大学 | Novel flexible pin shaft load balancing structure for eliminating planet wheel axial inclination angle |
| CN111059262A (en) * | 2019-12-23 | 2020-04-24 | 湘潭大学 | Planetary gear transmission variable-rigidity flexible pin shaft load balancing structure |
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2021
- 2021-03-09 CN CN202110255227.0A patent/CN112901727A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111022615A (en) * | 2019-12-23 | 2020-04-17 | 湘潭大学 | Novel flexible pin shaft load balancing structure for eliminating planet wheel axial inclination angle |
| CN111059262A (en) * | 2019-12-23 | 2020-04-24 | 湘潭大学 | Planetary gear transmission variable-rigidity flexible pin shaft load balancing structure |
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Application publication date: 20210604 |