WO2017050159A1 - Differential, power transmission system and vehicle - Google Patents

Differential, power transmission system and vehicle Download PDF

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Publication number
WO2017050159A1
WO2017050159A1 PCT/CN2016/098897 CN2016098897W WO2017050159A1 WO 2017050159 A1 WO2017050159 A1 WO 2017050159A1 CN 2016098897 W CN2016098897 W CN 2016098897W WO 2017050159 A1 WO2017050159 A1 WO 2017050159A1
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WO
WIPO (PCT)
Prior art keywords
planetary
gear
carrier
gear ring
differential
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Application number
PCT/CN2016/098897
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English (en)
French (fr)
Inventor
Dongsheng Yang
Yubo Lian
Jintao Zhang
Hongbin Luo
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Byd Company Limited
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Publication date
Application filed by Byd Company Limited filed Critical Byd Company Limited
Publication of WO2017050159A1 publication Critical patent/WO2017050159A1/en

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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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H48/11—Differential gearings with gears having orbital motion with orbital spur gears having intermeshing planet gears
    • 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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H2048/104—Differential gearings with gears having orbital motion with orbital spur gears characterised by two ring gears

Definitions

  • Embodiments of the present disclosure relates to a differential, a power transmission system having the differential, and a vehicle having the power transmission system.
  • a differential in a differential technology, includes a driven gear of a final drive, a planetary gear, a center gear, and the like.
  • the planetary gear is mounted on a secondary plate of the driven gear through a square shaft and a shaft sleeve and is meshed with the center gear, so as to implement revolution and moving functions thereof by a revolution pair and a planar moving pair.
  • the center gear is connected to two half shafts, namely left and right half shafts, through an angular alignment pin and a cylindrical pair or through a spline to achieve an objective of outputting torque.
  • Original components such as left and right housings and a planetary gear shaft of the differential, are omitted from such a differential, and instead, the planetary gear is directly mounted on the secondary plate of the driven gear of the final drive by using the square shaft and the shaft sleeve, thereby effectively reducing a number of parts of the differential, simplifying the structure thereof, and reducing the weight thereof.
  • such a differential implements an inter-wheel speed differential by using a symmetrical angle gear structure, which is only a partial innovation for a conventional symmetrical angle gear differential and cannot really overcome disadvantages thereof.
  • an axial dimension of such a differential structure is excessively large, masses of the housing and the angle gear therein are heavy, and reliability thereof is relatively poor.
  • Embodiments of the present disclosure aims at solving at least one of the foregoing technical problems in the prior art to some extent.
  • embodiments of the present disclosure provide a differential, which implements a speed differential function by using a planetary differential principle, and has a compact and simple structure, and can at least reduce an axial dimension thereof.
  • Embodiments of the present disclosure further provide a power transmission system having the differential above.
  • Embodiments of the present disclosure further provide a vehicle having the power transmission system above.
  • a differential includes: a first planetary carrier, a first planetary gear, and a first gear ring, in which the first planetary gear is connected to the first planetary carrier, and the first planetary gear is meshed with the first gear ring; and a second planetary carrier, a second planetary gear, and a second gear ring, in which the second planetary gear is connected to the second planetary carrier, the second planetary gear is meshed with the second gear ring and the first planetary gear, and the first gear ring and the second gear ring are configured as two power output ends of the differential; and an input unit, in which the input unit, the first planetary carrier and the second planetary carrier are arranged coaxially, and the input unit is linked with the first planetary carrier and the second planetary carrier.
  • the differential according to an embodiment of the present disclosure implements a speed differential function by using a planetary differential principle, has a high space utilization ratio in terms of structure and connection form, provides a small axial dimension, and also have much advantages in production and assembly.
  • a power transmission system includes the differential according to the foregoing embodiments of the present dislcosure.
  • a vehicle according to an embodiment of the present disclosure includes the power transmission system according to the foregoing embodiment of the present dislcosure.
  • FIG. 1 is an exploded view of a differential according to an embodiment of the present disclosure from a perspective;
  • FIG. 2 is another exploded view of a differential according to an embodiment of the present disclosure from another perspective;
  • FIG. 3 is a perspective view of a differential according to an embodiment of the present disclosure.
  • FIG. 4 is a planar schematic diagram showing a principle of a differential according to an embodiment of the present disclosure
  • FIG. 5 is a perspective view of a differential according to an embodiment of the present disclosure, in which a second gear ring and a second plantery carrier are not shown;
  • FIG. 6 is a schematic view illustrating a meshing between a first planetary gear and a second planetary gear according to an embodiment of the present disclosure
  • FIG. 7 is a brief diagram illustrating a meshing principle between a first planetary gear and a second planetary gear accordinging to an embodiment of the present disclosure
  • FIG. 8 is a perspective view of a first gear ring or a second gear ring according to another embodiment of the present disclosure.
  • FIG. 9 is a perspective view of a first gear ring or a second gear ring according to still another embodiment of the present disclosure.
  • FIG. 10 is a schematic diagram of a power transmission system according to an embodiment of the present disclosure.
  • FIG. 11 is a schematic diagram of a vehicle according to an embodiment of the present disclosure.
  • first and second are used merely for the purpose of description, but shall not be construed as indicating or implying relative importance or implicitly indicating a number of the indicated technical feature.
  • the feature defined with “first” and “second” may explicitly or implicitly include one or more of features.
  • a plurality of means at least two, for example, two or three.
  • connection may be a fixed connection, or may be a detachable connection or an integral connection; a connection may be a mechanical connection, or may be an electrical connection; a connection may be a mechanical connection, or may be an electrical connection, or may be used for intercommunication; a connection may be a direct connection, or may be an indirect connection via an intermediate medium, or may be communication between interiors of two elements or an interaction relationship between two elements. It may be appreciated by those of ordinary skill in the art that the specific meanings of the aforementioned terms in the present disclosure can be understood depending on specific situations.
  • a first feature being “above” or “under” a second feature may include that the first and second features are in direct contact and may also include that the first and second features are not in direct contact but are in contact by means of another feature therebetween.
  • the first feature being “over” , “above” or “on the top of” a second feature may include that the first feature is over or above the second feature or merely indicates that the horizontal height of the firs feature is higher than that of the second feature.
  • the first feature being “underneath” , “below” or “on the bottom of” a second feature may include that the first feature is underneath or below the second feature or merely indicates that the horizontal height of the first feature is lower than that of the second feature.
  • a differential 100 according to an embodiment of the present disclosure is described in detail by referring to FIG. 1 to FIG. 7, and the differential 100 may be used for an inter-wheel speed differential or an inter-shaft speed differential.
  • the differential 100 can enable left and right driving wheels to roll at different angular velocities when a vehicle is turning or traveling on an uneven road, so as to ensure pure rolling movements between the driving wheels on two sides and the ground.
  • the differential 100 may include a first planetary carrier 11, a first planetary gear 12, and a first gear ring 13 as well as a second planetary carrier 21, a second planetary gear 22, and a second gear ring 23.
  • both the first planetary carrier 11 and the second planetary carrier 21 may be configured as circular plate-shaped structures, so as to reduce an axial dimension of the differential 100 to some extent.
  • the first planetary carrier 11 and the second planetary carrier 21 may be configured as separated structures, i.e., the first planetary carrier 11 and the second planetary carrier 21 are separated from each other. Because it is relatively easy to mold an individual small component, separately and individually machining the first planetary carrier 11 and the second planetary carrier 21 can simplify a corresponding manufacturing process and improve machining precision thereof.
  • the first planetary gear 12 is disposed on the first planetary carrier 11.
  • each first planetary gear 12 is provided with a first planetary gear shaft 14, two ends of the first planetary gear shaft 14 may be rotatably carried on the first planetary carrier 11 and the second planetary carrier 21 respectively.
  • the two ends of the first planetary gear shaft 14 may be rotatably carried in shaft holes corresponding to each other in the first planetary carrier 11 and the second planetary carrier 21 by means of bearings, and the first planetary gear 12 may be fixed to the corresponding first planetary gear shaft 14.
  • the two ends of the first planetary gear shaft 14 may be fixedly connected to the first planetary carrier 11 and the second planetary carrier 21.
  • the two ends of the first planetary gear shaft 14 are respectively welded and fixed to the shaft holes corresponding to each other in the first planetary carrier 11 and the second planetary carrier 21, and the first planetary gear 12 is rotatably fitted over the corresponding first planetary gear shaft 14.
  • the first planetary gear 12 is rotatably fitted over the first planetary gear shaft 14 by means of a bearing.
  • an objective of connecting the first planetary carrier 11 with the second planetary carrier 21 may be implemented by the first planetary gear shaft 14, so as to enable the first planetary carrier 11 and the second planetary carrier 21 to move at a same speed and in a same direction (that is, a linkage between the first planetary carrier 11 and the second planetary carrier 21 is carried out) .
  • first planetary carrier 11 and the second planetary carrier 21 can favorably carry or fix the first planetary gear shaft 14, so as to prevent the differential 100 from being failed due to a disconnection between the first planetary gear shaft 14 and an individual planetary carrier.
  • the first planetary gear 12 is meshed with the first gear ring 13, specifically in an internal meshing form, that is, the first planetary gear 12 is located at an inner side of the first gear ring 13 and is meshed with teeth on the first gear ring 13.
  • a plutality of first planetary gears 12 are provided, and distributed at the inner side of the first gear ring 13 at equal angle intervals along a circumferential direction.
  • three first planetary gears 12 may be provided and an interval angle between any two adjacent first planetary gears 12 is 120°.
  • each second planetary gear 22 is provided with a second planetary gear shaft 24, two ends of the second planetary gear shaft 24 may be rotatably carried in shaft holes corresponding to each other in the first planetary carrier 11 and the second planetary carrier 21 by means of bearings, and the second planetary gear 22 may be fixed to the corresponding second planetary gear shaft 24.
  • the two ends of the second planetary gear shaft 24 may also be fixedly connected to the first planetary carrier 11 and the second planetary carrier 21.
  • the two ends of the second planetary gear shaft 24 are respectively welded and fixed to the shaft holes corresponding to each other in the first planetary carrier 11 and the second planetary carrier 21, and the first planetary gear 22 is rotatably fitted over the corresponding second planetary gear shaft 24.
  • the second planetary gear 22 is rotatably fitted over the second planetary gear shaft 24 by means of a bearing.
  • an objective of connecting the first planetary carrier 11 with the second planetary carrier 21 can be implemented by the second planetary gear shaft 24, so as to enable the first planetary carrier 11 and the second planetary carrier 21 to move at a same speed and in a same direction.
  • first planetary carrier 11 and the second planetary carrier 21 can favorably carry or fix the second planetary gear shaft 24, so as to prevent the differential 100 from being failed due to a disconnedtion between the second planetary gear shaft 24 and an individual planetary carrier.
  • first planetary carrier 11 and the second planetary carrier 21 in order to enable the first planetary carrier 11 and the second planetary carrier 21 to move at a same speed and in a same direction, not only the first planetary gear shaft 14 and/or the second planetary gear shaft 24 may be used, but also an intermediate connecting mechanism 6 may be used to connect the first planetary carrier 11 to the second planetary carrier 21 directly and fixedly. Or, the first planetary carrier 11 may also be connected to the second planetary carrier 21 by means of the planetary gear shafts and the intermediate connecting mechanism 6 simultaneously. The details of the intermediate connecting mechanism 6 will be described hereinafter.
  • the second planetary gear 22 is meshed with the second gear ring 23, specifically in an internal mesahing form, that is, the second planetary gear 22 is located at an inner side of the second gear ring 23 and is meshed with teeth on the second gear ring 23.
  • a plurality of second planetary gears 22 are provided, and distributed at the inner side of the second gear ring 23 at equal angle intervals along a circumferential direction.
  • three second planetary gears 22 may be provided and an interval angle between any two adjacent second planetary gears 22 is 120°.
  • FIG. 4 is a planar schematic diagram showing a principle of a differential 100 according to an embodiment of the present disclosure, in which a meshing relationship between the first planetary gear 12 and the second planetary gear 22 and mesahing relationships between the first planetary gear 12 and the first gear ring 13 and between the second planetary gear 22 and the second gear ring 23 are illustratively shown. Because FIG. 4 is a planar diagram and shows the foregoing three meshing relationships at the same time, relative position relationships among components are merely illustrative and do not indicate or imply positions of the components in an actual spatial disposition.
  • the plurality of first planetary gears 12 are correspondingly meshed with the plurality of second planetary gears 22 respectively.
  • the first one of the three first planetary gears 12 may be meshed with the corresponding first one of the three second planetary gears 22
  • the second one of three first planetary gears 12 may be meshed with the corresponding second one of the three second planetary gears 22
  • the third one of the three first planetary gears 12 may be meshed with the corresponding third one of the three second planetary gears 22.
  • a revolution axis of the first planetary gear 12 conincides with a revolution axis of the second planetary gear 22, i.e., the first planetary gear 12 and the second planetary gear 22 have a same revolution axis O, and a revolution radius (that is, a distance between an central axis of the first planetary gear 12 and the revolution axis O) of the first planetary gear 12 is the same with a revolution radius (that is, a distance between an central axis of the second planetary gear 22 and the revolution axis O) of the second planetary gear 22.
  • the first planetary gear 12 is meshed with and fitted with the second planetary gear 22.
  • the first planetary gear 12 is meshed with the first gear ring 13 and also is meshed with the second planetary gear 22 at the same time
  • the second planetary gear 22 is meshed with the second gear ring 23 and also is meshed with the first planetary gear 12 at the same time.
  • the first gear ring 13 and the second gear ring 23 may be configured as two power output ends of the differential 100, and the first planetary carrier 11 and the second planetary carrier 21 may be correspondingly configured as power input ends of the differential 100.
  • the first planetary carrier 11, the second planetary carrier 21 and an input unit 3 are linked.
  • motion states of the input unit 3, the first planetary carrier 11 and the second planetary carrier 21 are the same (that is, the input unit 3, the first planetary carrier 11 and the second planetary carrier 21 move at a same speed and in a same direction) .
  • the input unit 3, the first planetary carrier 11 and second planetary carrier 21 are arranged coaxially, such that power from an external power source may be input from the input unit 3 and output from the first gear ring 13 and the second gear ring 23 after a speed differential action of the differential 100.
  • the input unit 3 may be connected to the power source, such as an engine, a motor or the like.
  • the first planetary carrier 11 and the second planetary carrier 21 may be connected to corresponding half shafts through gear transmission structures, and the half shafts may be further connected to corresponding wheels, which however is not limited to this.
  • a working principle of the differential 100 is briefly described by taking the following example that the differential 100 is applied to the inter-wheel speed differential, in which, at this time, the first gear ring 13 may be connected to a left half shaft through, for example, a gear transmission structure, and the left half shaft may be connected to a left-side wheel, the second gear ring 23 may be connected to a right half shaft through, for example, a gear transmission structure, and the right half shaft may be connected to a right-side wheel, and the power output by a power source, such as an engine and/or a motor, may be output to the input unit 3 after a deceleration action of a final drive, and the input unit 3 drives the first planetary carrier 11 and the second planetary carrier 21 to rotate synchronically.
  • a power source such as an engine and/or a motor
  • the differential 100 does not perform the speed differential action, such that the first planetary carrier 11 and the second planetary carrier 21 rotate at a same speed and in a same direction, and the first gear ring 13 and the second gear ring 23 rotate at a same speed and in a same direction, i.e., the first planetary gear 12 and the second planetary gear 22 only revolve and do not rotate.
  • the left-side wheel and the right-side wheel theoretically have different rotation speeds, and the first gear ring 13 and the second gear ring 23 also have different rotation speeds, that is, a rotation speed difference exists, and thus, at this time, the first planetary gear 12 and the second planetary gear 22 rotate while revolving.
  • Rotations of the first planetary gear 12 and the second planetary gear 22 may accelerate one of the first gear ring 13 and the second gear ring 23 and decelerate the other one of the first gear ring 13 and the second gear ring 23, and a rotation speed difference between the accelerated gear ring and the decelerated gear ring is a rotation speed difference between the left and right wheels, thereby implementing the speed differential action.
  • the differential 100 utilizes a planetary differential principle, has a high space utilization ratio in terms of the structure and the connection form, provides a small axial dimension, and also have much advantages in production and assembly.
  • a structural form can avoid dimension defects of an angle gear in axial and radial directions thereof, and also can additionally utilize a hollow space inside a driven gear of the final drive preferably, thereby achieving a high space utilization ratio, greatly facilitating the entire vehicle arrangement in which the differential 100 is assembled and meeting limitation requirements to the weight and size.
  • the differential 100 according to embodiments of the present disclosure has high reliability and preferable transmission efficiency, which is beneficial to improving reliability of a power transmission chain and smoothness of the power output during turning, and thus is more practical with respect to a symmetrical angle gear differential.
  • the first planetary gear 12 and the second planetary gear 22 are partially overlaped in the axial direction (referring to a left-right direction in FIG. 6 and FIG. 7) , that is, part of the first planetary gear 12 and part of the second planetary gear 22 are overlaped, and rest of the first planetary gear 12 is staggered from rest of the second planetary gear 22.
  • the overlaped parts of the first planetary gear 12 and the second planetary gear 22 may be meshed with each other, and the staggerd parts thereof may be meshed with the corresponding gear rings respectively.
  • the first planetary gear 12 may include a first tooth portion 151 and a second tooth portion 152 (divided by a dashed line K2 in FIG. 7)
  • the second planetary gear 22 may include a third tooth portion 153 and a fourth tooth portion 154 (divided by a dashed line K1 in FIG. 7)
  • the second tooth portion 152 and the third tooth portion 153 are configured as the overlapped parts, that is, the second tooth portion 152 and the third tooth portion 153 are overlaped and meshed with each other in the axial direction.
  • the first tooth portion 151 and the fourth tooth portion 154 are staggered from each other in the axial direction and meshed with the corresponding gear rings respectively.
  • first tooth portion 151 is meshed with the first gear ring 13
  • fourth gear tooth portion 154 is meshed with the second gear ring 23.
  • positions of the dashed lines K1 and K2 may be adjusted according to a practical situation, which is not limited herein.
  • the differential 100 has a compact axial dimension and a small volume, which is in favor of the installation and arrangement of the differential 100.
  • the number of teeth of the first gear ring 13 may be the same with the number of teeth of the second gear ring 23, and the number of teeth of the first planetary gear 12 may be the same with the number of teeth of the second planetary gear 22.
  • both the first planetary gear 12 and the second planetary gear 22 are cylindrical gears.
  • the differential 100 using cylindrical gears has a more compact structure.
  • the differential 100 using the cylindrical gears has a higher space utilization ratio in terms of the structure and connection form, provides a smaller axial dimension, and has more advantages in production and assembly.
  • the first gear ring 13 and the second gear ring 23 are symmetrical structures. In other words, the first gear ring 13 and the second gear ring 23 are symmetrically disposed, thereby increasing universality of the gear rings and reducing costs thereof.
  • each of the first gear ring 13 and the second gear ring 23 may include a main flat plate portion 161 and an annular sidewall portion 162 disposed at a peripheral edge of the main flat plate portion 161.
  • the main flat plate portion 161 and the annular sidewall portion 162 may be configured as integrally molded components.
  • a plurality of gear teeth are disposed on an inner wall surface of the annular sidewall portion 162, and a cavity A1 or A2 is defined between the main flat plate portion 161 and the annular sidewall portion 162.
  • a cavity A1 is defined between the main flat plate portion 161 and the annular sidewall portion 162 of the first gear ring 13; and a cavity A2 is defined between the main flat plate portion 161 and the annular sidewall portion 162 of the second gear ring 23 (as shown in FIG. 4) .
  • the cavity A1 defined in the first gear ring 13 and the the cavity A2 defined in the second gear ring 23 face each other to form a mounting space A (referring to FIG. 4) .
  • the first planetary carrier 11 and the first planetary gear 12 as well as the second planetary carrier 21 and the second planetary gear 22 are accommodated inside the mounting space A, such that the differential 100 is relatively compact in structure, occupies a small space, and is easy to be arranged.
  • first gear ring 13 and the second gear ring 23 serves as an outer housing to protect the planetary carriers and the planetary gears housed therein so as to improve lifes thereof. Further, the mounting space A defined by the first gear ring 13 and the second gear ring 23 is relatively closed to stop the outside impurities from entering the mounting space A and affecting the moving parts therein, thus ensuring a stable operation of the differential 100.
  • the input unit 3 is configured as an input gear.
  • the input gear 3 is configured to have an annular shape (teeth of the input gear 3 are formed on an outer circumferential surface of the input gear 3) and fitted over outer surfaces of the first gear ring 13 and the second gear ring 23.
  • an inner diameter of the input gear 3 may be larger than outer diameters of the first gear ring 13 and the second gear ring 23, so that by sleeving the input unit 3 on the outer surfaces of the first gear ring 13 and the second gear ring 23, components housed in the two gear rings are allowed not to be exposed, thus protecting the components in the gear rings.
  • a gap D is provided between the first gear ring 13 and the second gear ring 23 along the axial direction. That is, the first gear ring 13 and the second gear ring 23 are axially spaced from each other, instead of closely adhering to each other.
  • a width of a meshed portion between the first planetary gear 12 and the second planetary gear 22 determines a size of the gap D to some extent (in addition, a thickness of an extending arm portion 63 of the intermediate connecting mechanism 6 may also determine the size of the gap D, which will be described hereinafter, and only the example that the width of the meshed portion of the two planetary gears determines the gap D is taken for explanation herein) , i.e.
  • the width of the menshed portion between the first planetary gear 12 and the second planetary gear 22 may be equal to a minimum size of the gap D, thus by controlling the width of the meshed portion between the first planetary gear 12 and the second planetary gear 22, the size of the gap D may be controlled indirectly.
  • the width of the meshed portion between the first planetary gear 12 and the second planetary gear 22 is relatively narrow, so that the gap D can be effectively reduced, and thereby the axial dimension of the differential 100 may be relatively small and compact, and the differential 100 is easy to be arranged.
  • the gap D is surrounded and covered by the input gear 3.
  • the closeness of the mounting space A is better, and it is more difficult for the outside impurities to enter the mounting space A to affect the operating components therein, thus further ensuring the working stability of the differential 100, and meanwhile, saving the axial space and the radial space of the differential at least to some extent.
  • the input gear 3 is configured as a driven gear of the final drive.
  • the hollow interior space of the driven gear of the final drive may be used better, so as to realize the better space utilization ratio, thus greatly facilitating the entire vehicle arangement in which the differential 100 is assembled and meeting the limitation requirements to weight and size thereof.
  • both of the first gear ring 13 and the second gear ring 23 include the main flat plate portion 161 and the annular sidewall portion 162, and thus the foregoing gap D in FIG. 4 (in combination with FIG. 1, FIG. 2, and FIG. 5 to FIG. 7) refers to a distance between an annular sidewall portion 162 of the first gear ring 13 and an annular sidewall portion 162 of the second gear ring 23.
  • each of the first gear ring 13 and the second gear ring 23 further includes an annular flange portion 163, and the annular flange portion 163 extends from an end surface of the annular sidewall portion 162 in a direction of departing from the main flat plate portion 161.
  • an inside diameter of the annular flange portion 163 may be approximately equal to an outside diameter of the annular sidewall portion 162, which is equivalent to that the annular flange portion 163 protrudes radially outwards beyond the annular sidewall portion 162 (i.e., a peripheral surface of the first gear ring 13 or the second gear ring 23) .
  • the outside diameter of the annular flange portion 163 may be approximately equal to the outside diameter of the annular sidewall portion 162, and the inside diameter of the annular flange portion 163 may be larger than the inside diameter of the annular sidewall portion 162, that is, a thickness of the annular flange portion 163 is smaller than a thickness of the annular sidewall portion 162.
  • the gap D between the two gear rings refers to a gap between the annular sidewall portions 162 of the two gear rings.
  • the gap D between the two gear rings refers to a gap between the annular flange portions 163 of the two gear rings.
  • the intermediate connecting mechanism 6 is configured to connect the first planetary carrier 11 and the second planetary carrier 21 to the input unit 3, so that the first planetary carrier 11, the planetary carrier 21 and the input unit 3 can be coaxially linked.
  • the intermediate connecting mechanism 6 may be fixedly connected to the first planetary carrier 11 and the planetary carrier 21, and the input unit 3 is fixed to the outer surface of the intermediate connecting mechanism 6, such that the first planetary carrier 11, the second planetary carrier 21 and the input unit 3 also can be coaxially linked.
  • the present disclosure provides a feasible embodiment, however, this does not mean or imply that the intermediate connecting mechanism 6 of the present disclosure can only be configured as the stricture in the embodiment. That is, the intermediate connecting mechanism 6 to be described in the following embodiment only is a possible example, but shall not be construed as a limitation to the protection scope of the present disclosure.
  • the input unit 3 is configured as an annular input gear 3.
  • the intermediate connecting mechanism 6 includes a first connecting bracket 61 and a second connecting bracket 62.
  • the first connecting bracket 61 is used for connecting the first planetary carrier 11 with the input unit 3 (that is, the input gear 3)
  • the second connecting bracket 62 is used for connecting the second planetary carrier 21 with the input unit 3 (that is, the input gear 3) .
  • the structure of the first connecting bracket 61 may be the same with that of the second connecting bracket 62, and each of the first connecting bracket 61 and the second connecting bracket 62 may include a central body portion 64 and an extending arm portion 63 (combined with FIG. 5) , in which the central body portion of the first connecting bracket 61 and the central body portion of the second connecting bracket 62 may be configured as an integral structure to form a common central body portion, but not limited to this.
  • the above-mentioned width of the meshed portion of the two planetary gears may determine the size of the gap D to a certain extent, and at the same time, the thickness of the extending arm portion 63 of the the intermediate connecting mechanism 6 may also determine the size of the gap D to a certain extent.
  • the size of the gap D may be substantially equal to the width of the meshed portion of the two planetary gears or the entire thickness of the extending arm portions 63; when the width of the meshed portion of the two planetary gears is less than the entire thickness of the extending arm portions 63, the size of the gap D may substantially equal to the entire thickness of the extending arm portions 63; when the width of the meshed portion of the wo planetary gears is larger than the entire thickness of the extending arm portions 63, the size of the gap D may substantially equal to the width of the meshed portion of the two planetary gears.
  • the entire thickness of the extending arm portions 63 refers to a sum of the thickness of the extending arm portion 63 of the first connecting bracket 61 and the thickness of the extending arm portion 63 of the second connecting bracket 62.
  • a plurality of extending arm portions 63 are provided.
  • the plurality of extending arm portions 63 are disposed on an outer circumferential surface of the central body portion 64.
  • the plurality of extending arm portions 63 may be integrally formed with the central body 64, but not limited to this.
  • the plurality of extending arm portions 63 are radially distributed around the central body portion 64.
  • three extending arm portions 63 are provided, and the three extending arm portions 63 are spaced from one another by equal angle intervals.
  • the extending arm portions 63 are connected to the input unit 3.
  • an outer end of the extending arm portion 63 may extend to the inner circumferential surface of the input unit 3 (for exmple, an annular driven gear of the final drive) and be fixed thereto.
  • each group of the first planetary gear 12 and the second planetary gear 22 correspondingly meshed with each other is located between two adjacent extending arm portions 63.
  • three extending arm portions 63 are provided, and the three extending arm portions 63 may define three receiving chambers (each adjacent two extending arm portions 63 and the inner circumferential surface of the input gear 3 define one receiving chamber) .
  • Each receiving chamber may receive a pair of the first planetary gear 12 and the second planetary gear 22 meshed with each other, such that the overall structure of the differential 100 is compact, and meanwhile, a gravity center of the differential 100 is allowed to be close to or located at a center position, thus avoiding the unstable operation and the short life of the differential 100 casused by an eccentricity or a relatively large eccentricity when the differential 100 operates in a high speed.
  • a fisrt output shaft 41 is coaxially connected to the first gear ring 13, and a second output shaft 42 is coaxially connected to the second gear ring 23.
  • the first plantary carrier 11 is coaxially provided with a first plantary carrier shaft 111
  • the second plantary carrier 21 is coaxially provided with a second plantary carrier shaft 211.
  • the first output shaft 41 may be a hollow shaft and be coaxially fitted over the first planetary carrier shaft 111
  • the second output shaft 42 may also be hollow shaft and be coaxially fitted over the the second planetary carrier shaft 211.
  • the first plantary carrier shaft 111 is fixed coaxially with the central body portion 64 of the first connecting bracket 61, and the second plantary carrier shaft 211 is fixed coaxially with the central body portion 64 of the second connecting bracket 62, however, it is not limited to this.
  • a radial dimension of the first gear ring 13 is equal to a radial dimension of the second gear ring 23, and each of the first gear ring 13 and the second gear ring 23 may be configured as an integrally molded component.
  • the combined technical solution may be a superposition of two or more technical solutions, a superposition of two or more technical features, or a superposition of two or more technical solutions and technical features.
  • the technical solutions and/or the technical features can interact with and support each other in terms of function, and the combined solution has better technical effects.
  • one skilled in the art may combine the solution that the first planetary gear 12 and the second planetary gear 22 are partially overlapped with the solution that the first planetary carrier 11 and the second planetary carrier 21 are configured as plate-shaped structures, and thus the axial dimension of the differential 100 can be reduced effectively, so that the differential 100 has a smaller volume.
  • one skilled in the art may combine the solution that the first planetary gear 12 and the second planetary gear 22 are partially overlapped with the solution that the planetary gears and the planetary carriers are received in the mounting space, such that an axial dimension of the differential 100 may be effectively reduced, and also the planetary gears and the planetary carriers are enclosed in the mounting space to avoid damage thereon from outside, thereby increasing the service life and reducing the maintenance cost.
  • one skilled in the art may combine the solution that the revolution axis of the first planetary gear 12 conincides with the revolution axis of the second planetary gear 22 with the solution that the revolution radius of the first planetary gear 12 is the same with the revolution radius of the second planetary gear 22, so that the differential 100 has a more compact structure and a smaller volume, and is easier to be arranged.
  • those skilled in the art may combine the solution that the input unit 3 is configured as the annular input gear and fitted over the outer peripheral surfaces of the first gear ring 13 and the second gear ring 23 with the solution that the input gear 3 is configured as the driven gear of the final drive, and thereby the differential 100 can make better use of the hollow interior space of the driven gear of the final drive, thus realizing the better space utilization ratio, and greatly facilitating the entire vehicle arangement in which the differential 100 is assembled. Furthermore, because the input unit 3 is directly configured as the annual driven gear of the final drive, an additional driven gear of the final drive is not needed to be provided invidually, thus not only reducing the components of the overall power drive system and the costs thereof, but also making the differential 100 more compact in size.
  • those skilled in the art may combine the solution that the input unit 3 is configured as the annual input gear with the solution that the input gear 3 surrounds and covers the gap D.
  • the structure of the differential 100 is more compact, and with the input gear 3 covering the gap, the mounting space defined by the two gear rings is more closed, thus fully protecting the internal components in the mounting space, and increasing the service lifes thereof.
  • the differential 100 can effectively save space and reduce the weight.
  • the planetary gear differential 100 can reduce the weight by approximately 30%and meanwhile reduce the axial dimension by approximately 70%, so as to reduce the friction of the bearing, and also to implement the torque distribution between the left and right wheels, so that the load distribution of the differential 100 is more proper and the rigidity of the differential 100 is better.
  • the transmission efficiency is also improved to some extent. For example, the transmission efficiency of a conventional angle gear of 6-level precision or 7-level precision is approximately 0.97 to 0.98, and the transmission efficiency of the cylindrical gear of 6-level precision or 7-level precision is approximately 0.98 to 0.99.
  • the use of the cylindrical gear also reduces working noise of the differential 100 and meanwhile reduces heat generation, thereby greatly prolonging the service life of the differential 100.
  • the differential 100 according to embodiments of the present disclosure has many advantages such as a light weight, a small dimension, low costs, high transmission efficiency, low noise, less heat generation, and a long service life.
  • a sun gear is omitted from the differential 100 according to the embodiments of the present disclosure, and omission of the sun gear has the following advantages.
  • the sun gear shall be omitted, and the speed differential shall be implemented by using a gear ring.
  • the gear ring may be provided with more teeth, and meanwhile has a larger pitch circle (the pitch circle refers to a pair of circles that are tangent to each other at a pitch point during the meahsing transmission of gears) , such that the load may be distributed more evenly and the torque may be carried more evenly, which is beneficial to prolonging the service life of the differential 100.
  • the differential 100 may be lubricated and cooled more favorably.
  • the sun gear is omitted, a cavity may be formed inside the gear ring, the meshing between the gear ring and the planetary gear is an internal meshaing (however, the meshing between the sun gear and the planetary gear is an external meshing) , and thus lubricating oil may be stored inside the gear ring, so that the cooling and lubricating effects are greatly improved.
  • the sun gear is omitted, the number of parts is decreased, and the mass and cost of the differential 100 are reduced, so that the differential 100 is much smaller and lighter.
  • the power transmission system 100 includes the differential 100 according to the foregoing embodiments of the presnet dislcolsure.
  • the power transmission system 1000 includes the differential 100, a transmission 200 and a power source 300.
  • the power output from the power source 300 is output to the differential 100 after the speed changing action of the transmission 200 and then is distributed by the differential 100 to the driving wheels on two sides.
  • the power transmission system 1000 shown in FIG. 10 is merely an example, instead of a limitation to the protection scope of the present disclosure.
  • other configurations, such as the engine and the transmission, of the power transmission system according to the embodiment of the present disclosure all belong to the prior art and are well known to those skilled in the art, and therefore, are not described again herein one by one.
  • the vehicle 10000 includes the power transmission system 1000 according to the foregoing embodiment of the present dislcosure.
  • the power transmission system 1000 may be used for a front wheel drive, and certainly, may also be used for a rear wheel drive, which is not specifically defined and limited by the present disclosure herein.
  • other configurations, such as a braking system, a traveling system, and a steering system, of the vehicle according to the embodiment of the present disclosure all belong to the prior art and are well known to those skilled in the art, and therefore, are not described again herein one by one.
  • a description of a reference term such as “an embodiment” , “some embodiments” , “exemplary embodiments” , “examples” , “specific examples” , or “some examples” means that a specific feature, structure, material, or characteristic that is described with reference to the embodiment or the example is included in at least one embodiment or example of the present disclosure.
  • exemplary descriptions of the foregoing terms do not necessarily refer to a same embodiment or example.
  • the described specific feature, structure, material, or characteristic may be combined in a proper manner in any one or more embodiments or examples.
  • those skilled in the art can joint and combine different embodiments or examples described in the present description.

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PCT/CN2016/098897 2015-09-25 2016-09-13 Differential, power transmission system and vehicle WO2017050159A1 (en)

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CN110832227A (zh) * 2017-05-16 2020-02-21 舍弗勒技术股份两合公司 紧凑型行星差速器

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CN113104098B (zh) * 2021-04-19 2023-01-13 江西七叶花装备智能科技股份有限公司 一种驱动转向调节控制件

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CN109891130B (zh) * 2017-10-31 2022-09-09 罗灿 非锥齿轮差速器

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