CN106553531B - Power driving system and vehicle with same - Google Patents

Power driving system and vehicle with same Download PDF

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Publication number
CN106553531B
CN106553531B CN201510624475.2A CN201510624475A CN106553531B CN 106553531 B CN106553531 B CN 106553531B CN 201510624475 A CN201510624475 A CN 201510624475A CN 106553531 B CN106553531 B CN 106553531B
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gear
power
planet
shaft
ring
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CN106553531A (en
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凌和平
翟震
郑峰
徐友彬
罗永孟
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BYD Co Ltd
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BYD Co Ltd
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Abstract

The invention discloses a power driving system and a vehicle. The power drive system includes: a differential, the differential comprising: the planetary gear set comprises a first planetary gear, a second planetary gear, a first gear ring, a second gear ring, a first planetary gear, a second planetary gear, a third planetary gear, a fourth planetary gear, a fifth planetary gear, a sixth planetary gear, a seventh planetary gear, a sixth planetary gear, a seventh; the transmission is respectively connected with the engine and the differential, and the engine can output the generated power to the power input end of the differential after passing through the transmission; first and second output portions respectively linked with the first and second gear rings; first and second motor generators operatively associated with the first and second output portions, respectively. The differential mechanism of the power driving system realizes the differential function by utilizing the planetary differential principle, and has compact and simple structure.

Description

Power driving system and vehicle with same
Technical Field
The invention relates to a power driving system for a vehicle and the vehicle with the power driving system.
Background
In one of the differential technologies known to the inventor, the differential includes a driven gear of a main reducer (main reducer driven gear), a planetary gear, a central wheel, etc., the planetary gear is mounted on an auxiliary plate of the driven gear through a square shaft and a shaft sleeve and is meshed with the central wheel, the rotating and moving functions of the planetary gear are realized by a rotating pair and a plane moving pair, and the central wheel is connected with a left half shaft and a right half shaft through an angular positioning pin and a cylindrical pair or a spline, so as to achieve the purpose of outputting torque. The differential eliminates the original components such as left and right shells, planetary gear shafts and the like of the differential, and directly installs the planetary gear on the auxiliary plate of the driven gear of the main reducer by using a square shaft and a shaft sleeve, thereby effectively reducing the number of parts of the differential, simplifying the structure and lightening the weight.
However, the differential mechanism utilizes a symmetrical bevel gear structure to realize inter-wheel differential, is only a partial innovation of the traditional symmetrical bevel gear differential mechanism, and cannot really solve the defects of overlarge axial size, large mass of a shell and a bevel gear and relative reliability deviation of the differential mechanism.
Disclosure of Invention
The present invention is directed to solving, at least to some extent, one of the above-mentioned problems in the prior art.
Therefore, the differential mechanism of the power driving system realizes the differential function by utilizing the planetary differential principle, and has compact and simple structure.
The invention also provides a vehicle with the power transmission system.
A power drive system according to an embodiment of the present invention includes: a differential, said differential comprising: the planet carrier comprises a first planet carrier, a first planet wheel and a first gear ring, wherein the first planet wheel is arranged on the first planet carrier, and is meshed with the first gear ring; the second planet gear is arranged on the second planet carrier, and is meshed with the second gear ring and the first planet gear; the first gear ring and the second gear ring form two power output ends of the differential, the first planet carrier and the second planet carrier form a power input end of the differential, and the revolution radiuses of the first planet wheel and the second planet wheel are different; the transmission is respectively connected with the engine and the differential, and the engine can output the generated power to the power input end of the differential after passing through the transmission; the first output part is linked with the first gear ring, and the second output part is linked with the second gear ring; a first motor generator linked with the first output unit, and a second motor generator linked with the second output unit.
The differential mechanism of the power driving system according to the embodiment of the invention realizes the differential function by utilizing the planetary differential principle, and has compact and simple structure.
In addition, the power driving system according to the embodiment of the invention may also have the following additional technical features:
according to some embodiments of the invention, the transmission comprises a power take-off shaft and a plurality of input shafts;
one of the plurality of input shafts is configured to be selectively coupled to the power take-off shaft, which is also configured to be coupled to the power input of the differential.
According to some embodiments of the invention, the power take-off shaft is provided with an idler driven gear, the idler driven gear being in linkage with the one of the input shafts, the power drive system further comprising a synchronizer arranged for synchronizing the power take-off shaft with the idler driven gear.
According to some embodiments of the invention, the power output shaft is provided with an idle driven gear and a fixed driven gear, the power drive system further comprising a synchronizer: the synchronizer is arranged for synchronizing the power output shaft and the idle driven gear;
each input shaft is fixedly provided with a fixed driving gear, and the empty sleeve driven gear and the fixed driven gear are respectively meshed with the corresponding fixed driving gears.
According to some embodiments of the invention, each of the input shafts is fixedly provided with a plurality of fixed driving gears, the power output shaft is idly provided with a plurality of idle driven gears engaged with the corresponding fixed driving gears, and each of the idle driven gears is engageable to the power output shaft by synchronization of the corresponding gear synchronizer.
According to some embodiments of the invention, the transmission comprises a power take-off shaft and a plurality of input shafts;
each of the input shafts is configured to be in linkage with the power output shaft, which is configured to also be in linkage with the power input end of the differential.
According to some embodiments of the present invention, a plurality of fixed driven gears are fixedly disposed on the power output shaft, and a fixed driving gear is fixedly disposed on each of the input shafts, and the fixed driven gears are engaged with the corresponding fixed driving gears.
According to some embodiments of the invention, the transmission comprises a first input shaft and a second input shaft, the second input shaft is sleeved on the first input shaft, and the power driving system further comprises an engine, and the engine is connected with the first input shaft and the second input shaft through a double clutch.
According to some embodiments of the invention, the power take-off shaft is coaxially fixed with the first and second planet carriers.
According to some embodiments of the invention, the first output is a left side gear and the second output is a right side gear; and
the first gear ring is provided with first external teeth, the second gear ring is provided with second external teeth, the first external teeth are meshed with the left half axle gear, and the second external teeth are meshed with the right half axle gear.
According to some embodiments of the invention, the transmission comprises:
a plurality of input shafts and a plurality of power output shafts, each of the power output shafts being arranged to output power from the engine to a power input of the differential.
According to some embodiments of the invention, the transmission further comprises:
the reverse gear output gear is linked with the power input end of the differential, the reverse gear intermediate gear is meshed with the reverse gear output gear, and the reverse gear intermediate gear is sleeved on one of the power output shafts in a hollow mode and can be connected to the one of the power output shafts through the synchronous action of the reverse gear synchronizer.
According to some embodiments of the present invention, a power output shaft idler output gear is sleeved on one of the power output shafts, the power output shaft idler output gear and the reverse intermediate gear share the reverse synchronizer, a power output shaft fixed output gear is fixedly arranged on each of the remaining power output shafts, and the power output shaft fixed output gear and the power output shaft idler output gear are respectively linked with the power input end of the differential.
According to some embodiments of the invention, the power drive system further comprises:
the intermediate shaft is coaxially fixed with the first planet carrier and the second planet carrier, an intermediate shaft gear is fixedly arranged on the intermediate shaft, and the intermediate shaft gear is respectively meshed with the power output shaft fixed output gear, the power output shaft idle output gear and the reverse gear output gear.
According to some embodiments of the invention, the power drive system further comprises: a third motor generator connected to the transmission, the third motor generator being operable to output the generated power to the power input of the differential through the transmission.
According to some embodiments of the invention, an end surface of the first gear ring facing the second gear ring is in the same plane as an end surface of the second gear ring facing the first gear ring.
According to some embodiments of the invention, each of the first ring gear and the second ring gear comprises:
the main part flat board portion with set up the annular side wall portion of the periphery edge of main part flat board portion, be provided with a plurality of teeth on the internal face of annular side wall portion, main part flat board portion with inject the cavity between the annular side wall portion, the cavity of first ring gear with the cavity orientation of second ring gear is in order to constitute installation space each other, first planet carrier with first planet wheel and the second planet carrier with the second planet wheel is accomodate in the installation space.
According to some embodiments of the invention, the first planet wheel is different in thickness in the axial direction from the second planet wheel.
According to some embodiments of the invention, the teeth of the thinner planet are fully meshed with the teeth of the thicker planet, and the teeth of the thicker planet extend axially to one side beyond the teeth of the thinner planet or the teeth of the thicker planet extend axially to both sides beyond the teeth of the thinner planet, respectively.
According to some embodiments of the invention, the revolution radius of the thicker planet is less than the revolution radius of the thinner planet.
According to some embodiments of the invention, the ring gear corresponding to the thicker planet gear is a small ring gear, the ring gear corresponding to the thinner planet gear is a large ring gear, and the outer diameter of the large ring gear is larger than the outer diameter of the small ring gear.
According to some embodiments of the invention, the first planet gear has a thickness greater than a thickness of the second planet gear, the first ring gear is a small ring gear, the second ring gear is a large ring gear, and a revolution radius of the first planet gear is smaller than a revolution radius of the second planet gear.
According to some embodiments of the invention, the first planet wheel has a first axis of revolution that is coincident with the second axis of revolution of the first planet wheel.
According to some embodiments of the invention, the first planet gear and the second planet gear are both cylindrical gears.
According to some embodiments of the invention each of said first planet wheels is provided with a first planet wheel axle, both ends of said first planet wheel axle being connected to said first planet carrier and said second planet carrier, respectively, and each of said second planet wheels is provided with a second planet wheel axle, both ends of said second planet wheel axle being connected to said first planet carrier and said second planet carrier, respectively.
According to some embodiments of the invention, the transmission comprises a first input shaft, a second input shaft and a third input shaft, the third input shaft is sleeved on the second input shaft, the second input shaft is sleeved on the first input shaft, and the engine is connected with the first input shaft, the second input shaft and the third input shaft through three clutches.
According to some embodiments of the invention, the first gear ring is linked with a left front wheel and the second gear ring is linked with a right front wheel;
the power drive system further includes:
a fourth motor generator linked with the left rear wheel and a fifth motor generator linked with the right rear wheel; and
an anti-skid synchronizer configured to selectively synchronize the left and right rear wheels such that the left and right rear wheels rotate in synchronization.
The vehicle according to the embodiment of the invention comprises the power driving system of the embodiment.
Drawings
FIG. 1 is an exploded view from one perspective of a differential according to an embodiment of the present invention;
FIG. 2 is an exploded view from another perspective of a differential according to an embodiment of the present invention;
FIG. 3 is a schematic plan view of a differential according to an embodiment of the present invention;
FIG. 4 is an assembled perspective view of a differential according to an embodiment of the present invention;
FIG. 5 is a schematic illustration of the positions of the first ring gear and the second ring gear in one of the embodiments;
FIG. 6 is a schematic illustration of the positions of a first ring gear and a second ring gear in another embodiment;
FIG. 7 is a schematic illustration of the positions of a first ring gear and a second ring gear in yet another embodiment;
FIG. 8 is a partial schematic view of a differential according to an embodiment of the present invention;
fig. 9 is a perspective view of the first and second planet gears;
fig. 10 is a schematic view of the meshing principle of the first planet wheel and the second planet wheel;
FIG. 11 is a perspective view of the first ring gear or the second ring gear according to an embodiment of the present invention;
FIG. 12 is a perspective view of the first ring gear or the second ring gear according to another embodiment of the present invention;
FIG. 13 is a schematic illustration of a power drive system according to one embodiment of the present invention;
FIG. 14 is a schematic illustration of a power drive system according to another embodiment of the present invention;
FIG. 15 is a schematic illustration of a power drive system according to yet another embodiment of the present invention;
FIG. 16 is a schematic illustration of a power drive system according to yet another embodiment of the present invention;
FIG. 17 is a schematic illustration of a power drive system according to yet another embodiment of the present invention;
FIG. 18 is a schematic illustration of a power drive system according to yet another embodiment of the present invention;
FIG. 19 is a schematic illustration of a power drive system according to yet another embodiment of the present invention;
FIG. 20 is a schematic illustration of a power drive system according to yet another embodiment of the present invention;
FIG. 21 is a schematic illustration of a power drive system according to yet another embodiment of the present invention;
FIG. 22 is a schematic illustration of a power drive system according to yet another embodiment of the present invention;
FIG. 23 is a schematic illustration of a power drive system according to yet another embodiment of the present invention;
FIG. 24 is a schematic illustration of a power drive system according to yet another embodiment of the present invention;
FIG. 25 is a schematic illustration of a power drive system according to yet another embodiment of the present invention;
FIG. 26 is a schematic illustration of a vehicle according to an embodiment of the invention.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are illustrative and intended to be illustrative of the invention and are not to be construed as limiting the invention.
In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", and the like, indicate orientations and positional relationships based on those shown in the drawings, and are used only for convenience of description and simplicity of description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be considered as limiting the present invention.
Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.
In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically connected, electrically connected or can communicate with each other; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In the present invention, unless otherwise expressly stated or limited, "above" or "below" a first feature means that the first and second features are in direct contact, or that the first and second features are not in direct contact but are in contact with each other via another feature therebetween. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.
A power drive system 1000 according to an embodiment of the present invention, which power drive system 1000 is applicable to a vehicle, will be described in detail below with reference to the accompanying drawings.
As shown in fig. 13, a power drive system 1000 according to some embodiments of the present invention mainly includes a differential 100, a transmission 104, an engine 301, a first motor generator 501, and a second motor generator 502. The transmission 104 is connected to the engine 301 and the differential 100, respectively, and the engine 301 can output the generated power to the power input end (e.g., the first planet carrier 11 and the second planet carrier 21) of the differential 100 through the transmission 104, that is, the transmission 104 can output the power from the engine 301 to the power input end (e.g., the first planet carrier 11 and the second planet carrier 21) of the differential 100 through a speed change function. Both the first motor generator 501 and the first ring gear 13 are linked to the first output portion 601, and both the second motor generator 502 and the second ring gear 23 are linked to the second output portion 602.
In a further embodiment, as shown in fig. 14-25, the power-driven system 1000 further includes a third motor generator 401, the third motor generator 401 is connected to the transmission 104, and the power generated by the third motor generator 401 can be output to the power input end (e.g. the first planet carrier 11 and the second planet carrier 21) of the differential 100 through the transmission 104, that is, in this embodiment, the transmission 104 can output the power from the engine 301 and/or the third motor generator 401 to the power input end of the differential 100 through a speed change function. The manner in which third motor generator 401 is connected to transmission 104 will be described in detail below with reference to specific embodiments.
The specific structure of differential 100 will first be described in detail with respect to the illustrated embodiment, and other configurations of power drive system 1000 will be described after a detailed description of the construction of differential 100.
The specific structure of differential 100 will first be described in detail with respect to the illustrated embodiment, and other configurations of power drive system 1000 will be described after a detailed description of the construction of differential 100.
The differential 100 according to the embodiment of the present invention will be described in detail with reference to fig. 1 to 12, wherein the differential 100 can be used for an inter-wheel differential speed or an inter-axle differential speed, for example, the inter-wheel differential speed, and the differential 100 can enable left and right driving wheels to roll at different angular velocities when the vehicle is running in a curve or on an uneven road surface, so as to ensure that the driving wheels on both sides make a pure rolling motion with the ground.
As shown in fig. 1 and 2, a differential 100 according to some embodiments of the present invention may include a first carrier 11, a first planet gear 12, and a first ring gear 13, and a second carrier 21, a second planet gear 22, and a second ring gear 23.
In conjunction with the embodiments of fig. 1 and 2, each of the first carrier 11 and the second carrier 21 may be configured as a circular plate-like structure, which may reduce the axial dimension of the differential 100 to some extent. In some embodiments, the first planet carrier 11 and the second planet carrier 21 may be a split structure, and since a single small component is relatively easy to form, the separate machining of the first planet carrier 11 and the second planet carrier 21 may simplify the manufacturing process and improve the machining precision.
As shown in fig. 3 in conjunction with fig. 1, 2 and 9, the first planet gears 12 are arranged on the first planet carrier 11, for example, each first planet gear 12 is provided with a first planet gear shaft 14 (shown in fig. 9), both ends of the first planet gear shaft 14 are rotatably supported on the first planet carrier 11 and the second planet carrier 21, respectively, for example, both ends of the first planet gear shaft 14 can be rotatably supported in shaft holes corresponding to each other on the first planet carrier 11 and the second planet carrier 21 through bearings, and then the first planet gears 12 can be fixed on the corresponding first planet gear shaft 14. Of course, both ends of the first planetary gear shaft 14 and the first and second planetary gear carriers 11 and 22 may also be fixedly connected, for example, both ends of the first planetary gear shaft 14 are respectively welded and fixed to the corresponding shaft holes of the first and second planetary gear carriers 11 and 22, in which case the first planetary gear 12 is rotatably sleeved on the corresponding first planetary gear shaft 14, for example, the first planetary gear 12 is rotatably sleeved on the first planetary gear shaft 14 through a bearing. Thus, the first planet carrier 11 and the second planet carrier 21 can be connected through the first planet shaft 14, so that the first planet carrier 11 and the second planet carrier 21 keep moving at the same speed and in the same direction (namely, the first planet carrier 11 and the second planet carrier 21 are linked). Furthermore, with this connection, the first planet carrier 11 and the second planet carrier 21 can support/fix the first planet axle 14 well, preventing the first planet axle 14 from being disconnected from the single planet carrier, which may cause the differential 100 to fail.
The first planetary gears 12 mesh with the first ring gear 13, and may be embodied in an inner mesh manner, that is, the first planetary gears 12 are located inside the first ring gear 13 and mesh with teeth on the first ring gear 13. The first planetary gears 12 are preferably plural and equally spaced in the circumferential direction inside the first ring gear 13, for example, as a preferred embodiment, the number of the first planetary gears 12 may be three, and any two adjacent first planetary gears 12 are spaced apart by an angle of 120 °.
Similarly, as shown in fig. 3 in combination with fig. 1, 2 and 9, the second planetary gears 22 are provided on the second planetary carrier 21, for example, each second planetary gear 22 is provided with one second planetary gear shaft 24, for example, both ends of the second planetary gear shaft 24 may be rotatably supported by bearings in the shaft holes of the first planetary carrier 11 and the second planetary carrier 21 corresponding to each other, and the second planetary gears 22 may be fixed to the corresponding second planetary gear shafts 24. Of course, both ends of the second planetary gear shaft 24 and the first and second planetary gear carriers 11 and 22 may also be fixedly connected, for example, both ends of the second planetary gear shaft 24 are respectively welded and fixed with the corresponding shaft holes of the first and second planetary gear carriers 11 and 22, at this time, the second planetary gear 22 is rotatably sleeved on the corresponding second planetary gear shaft 24, for example, the second planetary gear 22 may be rotatably sleeved on the second planetary gear shaft 24 through a bearing. Therefore, the purpose of connecting the first planet carrier 11 and the second planet carrier 21 can be achieved through the second planet shaft 24, so that the first planet carrier 11 and the second planet carrier 21 keep moving at the same speed and in the same direction. Moreover, by adopting the connection mode, the first planet carrier 11 and the second planet carrier 21 can well support/fix the second planet wheel shaft 24, and the second planet wheel shaft 24 is prevented from being disconnected with a single planet carrier, so that the differential 100 is prevented from being failed.
Furthermore, in other embodiments of the present invention, in order to keep the first planet carrier 11 and the second planet carrier 21 capable of moving at the same speed and in the same direction, the first planet carrier 11 and the second planet carrier 21 may be directly and fixedly connected through an intermediate component, that is, the same speed and the same direction of movement of the first planet carrier 11 and the second planet carrier 21 may be realized through the first planet shaft 14 and the second planet shaft 24 in the above embodiments, while the embodiment may realize the same speed and the same direction of movement of the first planet carrier 11 and the second planet carrier 21 directly through the provision of the intermediate component, for example, the intermediate component may be located between the first planet carrier 11 and the second planet carrier 21 and welded and fixed with the first planet carrier 11 and the second planet carrier 21, respectively.
The second planetary gears 22 are in mesh with the second ring gear 23, which may be in particular in the form of inner gearing, i.e. the second planetary gears 22 are located inside the second ring gear 23 and in mesh with teeth on the second ring gear 23. The second planetary gears 22 are preferably plural and equally spaced in the circumferential direction inside the second ring gear 23, for example, as a preferred embodiment, the number of the second planetary gears 22 may be three, and any two adjacent second planetary gears 22 are spaced by an angle of 120 °.
It should be noted that fig. 3 is a schematic plan view of a differential 100 according to an embodiment of the present invention, in which the meshing relationship between the first planetary gear 12 and the second planetary gear 22 and the meshing relationship between the first planetary gear 12 and the first ring gear 13 and between the second planetary gear 22 and the second ring gear 23 are schematically shown, and since fig. 3 is a plan view and the three meshing relationships are shown at the same time, the relative positional relationship among the components is only schematic and does not show or imply the actual spatial arrangement positions of the components.
In the embodiment where the first planetary gear 12 and the second planetary gear 22 are both plural, it is preferable that the plural first planetary gears 12 and the plural second planetary gears 22 are respectively engaged correspondingly. For example, as shown in fig. 1, 2 and 8, if the first planet wheel 12 and the second planet wheel 22 are three, the first planet wheel 12 can be meshed with the corresponding first second planet wheel 22, the second first planet wheel 12 can be meshed with the corresponding second planet wheel 22, and the third first planet wheel 12 can be meshed with the corresponding third second planet wheel 22, so that there are multiple sets of first planet wheels 12 and second planet wheels 22 meshed with each other, and when the differential 100 transmits power, the power is transmitted between the multiple sets of first planet wheels 12 and second planet wheels 22 meshed with each other more stably and reliably.
In addition, in another embodiment in which the first planetary gear 12 and the second planetary gear 22 are both plural, the plural first planetary gears 12 and the plural second planetary gears 22 are alternately arranged in the circumferential direction, and any adjacent first planetary gear 12 and second planetary gear 22 mesh. That is, in this embodiment, the plurality of first planetary gears 12 and the plurality of second planetary gears 22 are alternately arranged in the circumferential direction and form a ring shape, each of the first planetary gears 12 meshes with its adjacent two second planetary gears 22, and similarly, each of the second planetary gears 22 meshes with its adjacent two first planetary gears 12.
In this case, with reference to the embodiment of fig. 3, the revolution axis O of the first planet wheels 12 coincides with the revolution axis O of the second planet wheels 22.
In particular, as shown in fig. 1-3, 8-10, the first planet gears 12 are in meshing engagement with the second planet gears 22. In other words, for the first planet wheel 12, it meshes not only with the first ring gear 13, but also with the second planet wheel 22, and for the second planet wheel 22, it meshes not only with the second ring gear 23, but also with the first planet wheel 12.
As shown in fig. 3, the first ring gear 13 and the second ring gear 23 may form two power output ends of the differential 100, and the first planet carrier 11 and the second planet carrier 21 may form power input ends of the differential 100 (for example, in this case, the first planet carrier 11 and the second planet carrier 21 may be rigidly connected together), so that power output by an external power source may be input from the first planet carrier 11 and the second planet carrier 21, and may be output from the first ring gear 13 and the second ring gear 23 respectively after the differential action of the differential 100. At this time, as an alternative embodiment, the first planet carrier 11 and the second planet carrier 21 may be connected to a power source such as an engine, a motor, etc., and the first ring gear 13 and the second ring gear 23 may be connected to the corresponding half shafts, which are in turn connected to the corresponding wheels, through a gear transmission structure, but is not limited thereto.
The operation principle of the differential 100 will be briefly described below by taking an example in which the differential 100 is applied to an inter-wheel differential, the first gear ring 13 and the second gear ring 23 constitute a power output end of the differential 100, and the first carrier 11 and the second carrier 21 constitute a power input end of the differential 100, where at this time, the first gear ring 13 may be connected to a left half shaft through external teeth, the left half shaft may be connected to a left wheel, the second gear ring 23 may be connected to a right half shaft through external teeth, the right half shaft may be connected to a right wheel, and power output by a power source such as an engine and/or a motor may be output to the first carrier 11 and the second carrier 21 through a speed reduction effect of a main speed reducer. If the vehicle runs on a flat road surface and does not turn, the left wheel and the right wheel theoretically rotate at the same speed, the differential mechanism 100 does not play a role in differential speed at the moment, the first planet carrier 11 and the second planet carrier 21 rotate at the same speed and in the same direction, the first gear ring 13 and the second gear ring 23 rotate at the same speed and in the same direction, and the first planet wheel 12 and the second planet wheel 22 only revolve and do not rotate. If the vehicle runs on an uneven road or turns, the left wheel and the right wheel theoretically have different rotating speeds, the rotating speeds of the first gear ring 13 and the second gear ring 23 are also different, namely, a rotating speed difference exists, at the moment, the first planet wheel 12 and the second planet wheel 22 rotate while revolving, the rotation of the first planet wheel 12 and the second planet wheel 22 can accelerate one of the first gear ring 13 and the second gear ring 23 and decelerate the other one of the first gear ring and the second gear ring 23, and the rotating speed difference between the accelerated gear ring and the decelerated gear ring is the rotating speed difference between the left wheel and the right wheel, so that the differential action is realized.
Thus, the differential 100 according to the embodiment of the present invention utilizes the planetary differential principle, and has higher space utilization rate in structure and connection form, smaller axial dimension, and more advantages in production and assembly. Such structural style not only can avoid the axial and radial size defects of the bevel gear, but also can better utilize the hollow space inside the driving and driven gear, thereby realizing better space utilization rate, greatly facilitating the whole vehicle arrangement of the differential mechanism 100 assembly and the limitation of the weight, and simultaneously having higher reliability and better transmission efficiency, being beneficial to improving the reliability of a power transmission chain and the power output fluency during the bending, and having higher practicability compared with the symmetrical bevel gear differential mechanism.
Specifically, the revolving radii of the first planet wheels 12 and the second planet wheels 22 are different, that is, referring to fig. 3, the revolving radius of the first planet wheels 12 refers to a radius R1 of the first planet wheels 12 revolving around the revolving axis O, and the revolving radius of the second planet wheels 22 refers to a radius R2 of the second planet wheels 22 revolving around the revolving axis O, referring to fig. 3, R1 ≠ R2, as R2 > R1. That is, the revolving trajectories of the first planetary gear 12 and the second planetary gear 22 are staggered in the radial direction. In the example of the invention, the revolution radius of the first planetary gear 12 is relatively small, and the revolution radius of the second planetary gear 22 is relatively large.
Since the first planet gears 12 and the second planet gears 22 have different revolving radii, in some embodiments, the inner diameter of the first ring gear 13 and the inner diameter of the second ring gear 23 are different, and a planet gear with a small revolving radius (e.g., the first planet gear 12) corresponds to a small ring gear with a small radius (e.g., the first ring gear 13), and a planet gear with a large revolving radius (e.g., the second planet gear 22) corresponds to a small ring gear with a large radius (e.g., the second ring gear 23), so that the large ring gear 23 and the small ring gear 13 are radially staggered to avoid the motion interference between the ring gear and the moving parts such as the planet gears, thereby effectively reducing the axial clearance between the first ring gear 12 and the second ring gear 22, for example, referring to fig. 3, 5-6, which is D, by reducing the axial clearance D, thereby making the differential 100 smaller in axial dimension and more compact.
The configurations of the first ring gear 13 and the second ring gear 23 are described in detail below in conjunction with specific embodiments.
In some embodiments of the present invention, the first gear ring 13 and the second gear ring 23 are of a symmetrical structure, in other words, the first gear ring 13 and the second gear ring 23 are symmetrically arranged, which can increase the versatility of the gear rings and reduce the cost.
Referring to fig. 5 in combination with fig. 1 and 2, an end face B1 (see fig. 2) of the first gear ring 13 facing the second gear ring 23 and an end face B2 (see fig. 1) of the second gear ring 23 facing the first gear ring 13 are in the same plane B3 (see fig. 5), in other words, in this embodiment, as shown in fig. 5, the end faces B1 and B2 are in the same plane B3 at the same time, i.e., coincide with B3, so that the axial gap D between the first gear ring 13 and the second gear ring 23 is zero (as shown in fig. 5), which can greatly reduce the axial size of the differential 100, make the differential 100 smaller and more compact, and facilitate the arrangement of the whole power transmission system.
In another embodiment, as shown in fig. 7, one of the first ring gear 13 and the second ring gear 23 having a relatively small radius, for example, the small ring gear 13, is at least partially embedded in one of the first ring gear 13 and the second ring gear 23 having a relatively large radius, for example, the large ring gear 23, and the gap D between the first ring gear 13 and the second ring gear 23 in the axial direction can be understood as negative, so that the axial dimension of the differential 100 can be reduced as well, and the parts in the two ring gears can be better protected by the first ring gear 13 and the second ring gear 23.
Of course, alternatively, as shown in fig. 6, the first gear ring 13 and the second gear ring 23 may be axially offset and spaced apart by a distance D. It will be appreciated that the embodiment of fig. 5 having zero clearance D and the embodiment of fig. 7 having negative clearance D is preferred over the embodiment of fig. 6 (the embodiment of fig. 6 having positive clearance D) from the standpoint of reducing the axial dimension of the differential 100 alone.
Note that the gap D in fig. 3 (see fig. 1 to 2 and 5 to 7) refers to a distance between the annular side wall portion 162 of the first ring gear 13 and the annular side wall portion 162 of the second ring gear 23. For example, referring to the embodiment of fig. 1-3, 5-7, the first and second ring gears 13, 23 each include a main body flat plate portion 161 and an annular side wall portion 162.
While in other embodiments of the present invention, as in the embodiment with reference to fig. 11 and 12, each of the first and second ring gears 13 and 23 further includes an annular flange portion 163, the annular flange portion 163 extending from an end surface of the annular side wall portion 162 in a direction away from the main body flat plate portion 161, in the embodiment of fig. 11, an inner diameter of the annular flange portion 163 may be substantially equal to an outer diameter of the annular side wall portion 162, so that the annular flange portion 163 corresponds to protruding the annular side wall portion 162 (i.e., the outer peripheral surface of the first or second ring gear 13 or 23) outward in the radial direction. In the embodiment of fig. 12, the outer diameter of the annular flange portion 163 may be substantially equal to the outer diameter of the annular side wall portion 162, and the inner diameter of the annular flange portion 163 may be larger than the inner diameter of the annular side wall portion 162, i.e., the thickness of the annular flange portion 163 is thinner than the thickness of the annular side wall portion 162.
However, in the ring gear structure of the embodiment shown in fig. 1 to 3 and 5 to 7, the gap D between two ring gears refers to the gap between the annular side wall portions 162 of the two ring gears. Whereas in the ring gear structure in the embodiment of fig. 11 and 12, the clearance D between the two ring gears indicates the clearance between the annular flange portions 163 of the two ring gears.
For the embodiment in which the small ring gear is embedded in the large ring gear, as shown in fig. 1-2 and in conjunction with fig. 3, each of the first ring gear 13 and the second ring gear 23 includes: the main body flat plate portion 161 and the annular side wall portion 162 provided at the outer peripheral edge of the main body flat plate portion 161 may be integrally molded components. The annular side wall portion 162 is provided with a plurality of gear teeth on an inner wall surface thereof, wherein, as shown in fig. 4, the annular side wall portion 162 of one of the ring gears having a relatively small radius, such as the first ring gear 13 (i.e., the small ring gear 13), is at least partially fitted into the annular side wall portion 162 of one of the ring gears having a relatively large radius, such as the second ring gear 23 (i.e., the large ring gear 23).
Of course, for embodiments in which the small ring gear is embedded in the large ring gear, the gear structure of fig. 11-12 may also be used, for example, the large ring gear may be the gear structure of fig. 11 or 12, i.e., the large ring gear has an annular flange portion 163, while the small ring gear may be the conventional gear structure of the embodiment of fig. 1-3 (without the annular flange portion 163), in which case the annular side wall portion 162 of the small ring gear may be at least partially embedded in the annular flange portion of the large ring gear. Alternatively, both the small ring gear and the large ring gear may adopt the ring gear structure in fig. 11 and 12, in which case the annular flange portion 163 of the small ring gear may be at least partially embedded in the annular flange portion of the large ring gear, but is not limited thereto.
Furthermore, it should be understood that although several embodiments of the small ring gear embedded in the large ring gear are described above, this is not a limitation to the scope of the present invention, and after reading the above description, those skilled in the art will understand the embedding principle of the ring gear fully, and similar modifications can be made to the structure of the small ring gear and/or the large ring gear, which also fall into the scope of the present invention.
Referring to fig. 3, the cavity a1, a2 (see fig. 3) is defined between the main body flat plate portion 161 and the annular side wall portion 162, specifically, the cavity a1 is defined between the main body flat plate portion 161 and the annular side wall portion 162 of the first ring gear 13, the cavity a2 is defined between the main body flat plate portion 161 and the annular side wall portion 162 of the second ring gear 23, and the cavity a1 in the first ring gear 13 and the cavity a2 in the second ring gear 23 face each other to form an installation space a (see fig. 3), in which the first planet carrier 11 and the first planet gear 12, and the second planet carrier 21 and the second planet gear 22 are accommodated, so that the first ring gear 13 and the second ring gear 23 function as an outer casing, and can protect the planet carriers and the planet gears accommodated therein, and improve the life. And the end face B1 of the first gear ring 13 and the end face B2 of the second gear ring 23 are matched with each other, or the small gear ring 13 with small size is matched with the embodiment that at least part of the small gear ring 13 is embedded into the large gear ring 23 with large size, so that the installation space A is relatively closed, external sundries are not easy to enter the installation space A to influence moving parts, and the stable work of the differential 100 is ensured.
The meshing relationship of the first planetary gear 12 and the second planetary gear 22 will be described in detail below with reference to specific embodiments.
In the embodiment of the present invention, the first planetary gear 12 and the second planetary gear 22 have different thicknesses in the axial direction (see fig. 10), which helps to reduce the axial size of the differential 100. Further, the teeth of the thinner planet, e.g. the second planet 22, are fully meshed with the teeth of the thicker planet, e.g. the first planet 12, and the teeth of the thicker planet extend axially to one side beyond the teeth of the thinner planet, or the teeth of the thicker planet extend axially to both sides beyond the teeth of the thinner planet, respectively. In the example of the present invention, the teeth of the thicker planet wheels extend axially beyond the teeth of the thinner planet wheels to only one side, for example, as shown in fig. 9 and 10, the thicker first planet wheel 12 extends to the left beyond the thinner second planet wheel 22, and the right side of the thicker first planet wheel 12 and the right side of the thinner second planet wheel 22 may be substantially flush, which facilitates control of the axial dimension of the differential 100.
Because the first planet wheel 12 and the second planet wheel 22 have different revolving radii, the revolving radius of the thicker planet wheel such as the first planet wheel 12 is smaller than the revolving radius of the thinner planet wheel such as the second planet wheel 22 for the embodiment with different thicknesses of the planet wheels. Moreover, the ring gear corresponding to the thicker planet wheel, such as the first planet wheel 12, is a small ring gear with a smaller radial size, such as the first ring gear 13, the ring gear corresponding to the thinner planet wheel, such as the second planet wheel 22, is a large ring gear with a relatively larger radial size, such as the second ring gear 23, and the outer diameter (outer surface) of the large ring gear 23 is larger than that of the small ring gear 13. For example, in the present example, the thickness of the first planetary gear 12 is greater than the thickness of the second planetary gear 22, so that the first ring gear 13 corresponding to the thicker first planetary gear 12 is a small ring gear, the second ring gear 23 corresponding to the thinner second planetary gear 22 is a large ring gear, and the revolution radius of the first planetary gear 12 is smaller than the revolution radius of the second planetary gear 22.
In addition, it should be noted that the planet gear with the smaller revolution radius is meshed with one of the ring gears with the relatively smaller radius, in this case, the planet gear with the smaller revolution radius is a planet gear with a relatively thicker thickness, one part of the planet gear is meshed with the internal teeth of one of the ring gears with the relatively smaller radius, and the other part of the planet gear is meshed with the planet gear with the larger revolution radius, that is, the thinner planet gear.
As an alternative embodiment, the internal diameter of the large ring gear 23 is larger than the external diameter of the small ring gear 13, where the internal diameter of the large ring gear 23 refers to the radial dimension of the addendum circle of the internal teeth of the large ring gear 23, in other words, the diameter of the addendum circle of the internal teeth of the large ring gear 23 is larger than the external diameter of the small ring gear 13. Therefore, the small gear ring 13 can be wholly or at least partially embedded in the large gear ring 23, that is, the axial gap D is reduced to a negative value (that is, the small gear ring 13 is embedded in the large gear ring 23), so that the two gear rings, that is, the two planetary gears, cannot generate motion interference or sliding friction, the stability of the differential 100 is improved, and meanwhile, the inner space is relatively more closed, and the inner planet carrier, the planetary gears and other components are protected.
The power input and power output of differential 100 are described in detail below in connection with specific embodiments.
As shown in fig. 1 to 3, the differential 100 further includes differential input shafts 31, 32 and differential output shafts 41, 42, the differential input shafts 31, 32 are connected to the first carrier 11 and the second carrier 21, respectively, and as in the example of fig. 3, one differential input shaft 31 is connected to the right side of the first carrier 11, and the other differential input shaft 32 is connected to the left side of the second carrier 21. The differential output shafts 41, 42 are connected to the first ring gear 13 and the second ring gear 23, respectively, and as in the example of fig. 3, one differential output shaft 41 is connected to the right side of the first ring gear 13, and the other differential output shaft 42 is connected to the left side of the second ring gear 23. The differential input shafts 31, 32, the differential output shafts 41, 42, the first ring gear 13 and the second ring gear 23 may be arranged coaxially.
Further, as shown in fig. 3, the differential input shaft includes: a first differential input shaft 31 and a second differential input shaft 32, the first differential input shaft 31 being connected to the first planet carrier 11, the second differential input shaft 32 being connected to the second planet carrier 21, the differential output shaft may comprise: first differential output shaft 41 and second differential output shaft 42, first differential output shaft 41 links to each other with first ring gear 13, second differential output shaft 42 links to each other with second ring gear 23, first differential input shaft 31 and second differential input shaft 32 and first differential output shaft 41 and second differential output shaft 42 all can be the hollow shaft structure, wherein as preferred embodiment, first differential output shaft 41 overlaps coaxially on first differential input shaft 31, and second differential output shaft 42 overlaps coaxially on second differential input shaft 32, and differential 100 is more compact in structure, the volume is littleer from this.
However, the differential input shaft and the differential output shaft are only an alternative embodiment, in the embodiment of the power driving system of fig. 13-25, the differential 100 outputs power to the outside through the external teeth of the ring gear, while referring to fig. 13-16, 18-25, the power output shaft 103 of the transmission 104 may be directly and coaxially fixed with the first planet carrier 11 and the second planet carrier 21, while in the embodiment of fig. 17, the power output shaft 103 may be linked with the first planet carrier 11 and the second planet carrier 21 through the intermediate shaft 701, and the intermediate shaft 701 may be coaxially fixed with the first planet carrier 11 and the second planet carrier 21.
According to some embodiments of the present invention, the first planet gears 12 and the second planet gears 22 are cylindrical gears, and the differential 100 using cylindrical gears is more compact than a conventional symmetrical bevel gear differential, and in particular, has a higher space utilization rate in structure and connection form, a smaller axial size, and is more advantageous in production and assembly.
The specific structure of the differential 100 will now be briefly described with reference to the embodiment of fig. 1-3. Referring to fig. 1 to 3, a plurality of first planetary gear shafts 14 and a plurality of second planetary gear shafts 24 are arranged between the first planet carrier 11 and the second planet carrier 21, a plurality of first planetary gears 12 are correspondingly connected to the first planetary gear shafts 14, and a plurality of second planetary gears 22 are correspondingly connected to the second planetary gear shafts 24. The thickness of the first planet gears 12 is greater than the thickness of the second planet gears 22, and the teeth of the thinner second planet gears 22 are fully meshed with the teeth of the thicker first planet gears 12, and the teeth of the thicker first planet gears 12 can extend to the left beyond the thinner second planet gears 22. The first gear ring 13 corresponding to the thicker first planet wheel 12 is a small gear ring, the second gear ring 23 corresponding to the thinner second planet wheel 22 is a large gear ring, and the end face B1 of the small gear ring 13 and the end face B2 of the large gear ring 23 can be in the same plane, so that the axial gap D between the small gear ring 13 and the large gear ring 23 is zero, and the mounting cavities A in the two gear rings are relatively closed.
In summary, the differential 100 according to the embodiment of the present invention employs the planetary gear in the form of the cylindrical gear, which has higher space utilization rate in structure and connection form, smaller axial size, and is more advantageous in production and assembly. The compact differential mechanism 100 also realizes avoidance of planetary gear mechanisms on two sides in space and size (namely different revolution radiuses of the planetary gears) by shifting the planetary gears and the gear rings on one side, and the structural design greatly saves axial gaps of another group of corresponding planetary gears and gear rings in space for avoiding, so that the compact differential mechanism 100 is smaller in axial size and more compact.
Having described the differential 100 in detail, the remaining structure of the power drive system 1000 will now be described.
Referring to fig. 13-25, the transmission 104 may include a plurality of input shafts 101, 102 and a power output shaft 103. In some embodiments, as shown in fig. 13-16, 18-23, the power take-off shaft 103 of the transmission 104 may be one, but is not limited thereto. For example, referring to the embodiment of fig. 17, the power output shafts may be two, i.e., a first power output shaft 103a and a second power output shaft 103 b.
As shown in fig. 13-23, the power take-off shaft 103 is arranged to be interlocked with the power input of the differential 100, i.e. the power take-off shaft 103 is arranged to be interlocked with the first planet carrier 11 and the second planet carrier 21.
Referring to the embodiment of fig. 13-15 and 20-23, one of the input shafts 101, 102, such as the first input shaft 101 (the second input shaft 102 in fig. 15), can be selectively coupled with the power output shaft 103, in other words, one of the input shafts, such as the first input shaft 101, can be coupled with the power output shaft 103, while the one of the input shafts, such as the first input shaft 101, can be disconnected from the power output shaft 103, as shown in fig. 13-14 and 20-23. The remaining input shafts are all arranged to be interlocked with the power output shaft 103, i.e. when these input shafts are operated, the power output shaft 103 follows the operation, or when the power output shaft 103 is operated, these input shafts follow the operation. Referring to the embodiment of fig. 11, however, each input shaft 101, 102 is configured to be selectively coupled to a power output shaft 103.
Referring to the embodiment of fig. 14, 20-23, a third motor generator 401 is provided in association with one of the input shafts, such as the first input shaft 101, i.e., the input shaft 101 associated with the third motor generator 401 is the input shaft 101 selectively associated with the power take-off shaft 103. In a further embodiment, the power take-off shaft 103 is provided with an idler driven gear 108, the idler driven gear 108 is coupled to one of the input shafts, and the synchronizer 109 is configured to synchronize the power take-off shaft 103 with the idler driven gear 108. It is understood that the synchronizer 109 synchronizes the idler driven gear 108 and the power take-off shaft 103 when the synchronizer 109 is in the engaged state, so that the power from the third motor generator 401 can be output from the power take-off shaft 103 to the differential 100 by the engagement of the synchronizer 109, and that the third motor generator 401 is equivalently disconnected from the power take-off shaft 103 when the synchronizer 109 is in the disconnected state. Thus, synchronizer 109 functions as a power switch of third motor generator 401, and is able to control the output and disconnection of power of third motor generator 401.
As an alternative embodiment, a synchronizer 109 is provided on the power take-off shaft 103 and is used to engage the idler driven gear 108. Therefore, the structure is simple and easy to realize.
As shown in fig. 13-15 and 20-23, the transmission of the rest of the input shaft and the power output shaft 103 can be realized by a gear transmission mode. For example, a fixed driven gear 107 is fixedly arranged on the power output shaft 103, and the fixed driven gear 107 is interlocked with the rest of the input shaft, namely, the input shaft 101 in the embodiment of fig. 13-14 and 20-23 or the input shaft 102 in the embodiment of fig. 15 is removed.
For example, referring to the embodiment of fig. 13-15, the power output shaft 103 is also fixedly provided with a fixed driven gear 107 and an empty driven gear 108, while the input shaft is correspondingly fixedly provided with fixed driving gears 105 and 106, and the empty driven gear 108 and the fixed driven gear 107 are respectively meshed with the corresponding fixed driving gears. For example, the sum of the total number of the idler driven gears 108 and the fixed driven gears 107 is the same as the number of the fixed drive gears.
Referring to the example of fig. 13-15, the number of the idle driven gear 108 and the fixed driven gear 107 is one, correspondingly, the number of the fixed driving gears is two, the idle driven gear 108 is meshed with one fixed driving gear to form a pair of gear pairs, and the fixed driven gear 107 is meshed with the other fixed driving gear to form another pair of gear pairs.
As shown in fig. 13-23, the plurality of input shafts includes a first input shaft 101 and a second input shaft 102, the first input shaft 101 may be a solid shaft, the second input shaft 102 may be a hollow shaft, the second input shaft 102 is sleeved on the first input shaft 101, for example, the second input shaft 102 is coaxially sleeved on the first input shaft 101, the axial length of the first input shaft 101 is greater than that of the second input shaft 102, and one end, for example, the right end, of the first input shaft 101 may extend out from the inside of the second input shaft 102.
Further, as shown in fig. 13-23, each input shaft may be fixedly provided with only one fixed driving gear, that is, the fixed driving gear includes a first fixed driving gear 106 and a second fixed driving gear 105, the first fixed driving gear 106 is fixedly disposed on the first input shaft 101, and the second fixed driving gear 105 is fixedly disposed on the second input shaft 102.
As shown in fig. 14 and 20 to 23, the free driven gear 108 is engaged with the first fixed driving gear 106, the fixed driven gear 107 is engaged with the second fixed driving gear 105, and the third motor generator 401 is linked with the first input shaft 101, for example, the third motor generator 401 is linked with the first fixed driving gear 106 through a gear structure, specifically, the third motor generator 401 is driven with the first fixed driving gear 106 through a gear 402 and a gear 403, and the gear number of the above-mentioned gears is reasonably designed to obtain the transmission speed ratio required by the third motor generator 401.
In the example of fig. 15, the free driven gear 108 is engaged with the second fixed driving gear 105, the fixed driven gear 107 is engaged with the first fixed driving gear 106, and the third motor generator 401 is linked with the second input shaft 102, for example, the third motor generator 401 is linked with the second fixed driving gear 105 through a gear structure, specifically, the third motor generator 401 is driven by the second fixed driving gear 105 through the gear 402, the gear 403, the gear 404, and the gear 405, wherein the gear 404 and the gear 405 can be fixed on the same shaft 406, and the gear number of the above gears can be reasonably designed to obtain the transmission speed ratio required by the third motor generator 401.
Further, as shown in fig. 13-23, the power drive system 1000 may further include an engine 301, the engine 301 being configured to be selectively engageable with at least one of a plurality of input shafts, specifically, two input shafts, and a dual clutch 204 being provided between the engine 301 and the two input shafts. The dual clutch 204 includes: a first engagement portion 201, a second engagement portion 202 and a third engagement portion 203, wherein the first engagement portion 201 and the second engagement portion 202 may be two driven discs of a dual clutch 204, the third engagement portion 203 may be a housing of the dual clutch 204, at least one of the two driven discs may selectively engage the housing, that is, at least one of the first engagement portion 201 and the second engagement portion 202 may selectively engage the third engagement portion 203. Of course, both driven discs may also be completely disconnected from the housing, i.e. both the first engagement portion 201 and the second engagement portion 202 are in a disconnected state from the third engagement portion 203.
Referring to fig. 13 to 25, the engine 301 is connected to the third engaging portion 203, the first input shaft 101 is connected to the first engaging portion 201, and the second input shaft 102 is connected to the second engaging portion 202. In this way, the power generated by the engine 301 can be selectively output to the first input shaft 101 and the second input shaft 102 through the dual clutch 204.
In other embodiments, as shown in fig. 18-19, each input shaft is arranged to be linked with the power output shaft 103, in other words, as shown in fig. 18-19, the power output shaft 103 follows the motion when any one input shaft rotates, or the power output shaft 103 rotates and the input shafts follow the motion when the power output shaft 103 rotates.
As shown in fig. 18 to 19, the third motor generator 401 is provided in conjunction with one of the input shafts. As shown in fig. 18, the third motor generator 401 is linked with the first input shaft 101, and specifically, the third motor generator 401 is driven by the first fixed driving gear 106 through the gear 402 and the gear 403. In the example of fig. 19, the third motor generator 401 is linked with the second input shaft 102, and specifically, the third motor generator 401 is driven by the gear 402, the gear 403, the gear 404, and the gear 405 to the second fixed driving gear 105, wherein the gear 404 and the gear 405 may be fixed on the same shaft 406.
In some embodiments, the transmission of the input shafts 101 and 102 and the power output shaft 103 may be implemented by using a conventional gear pair.
For example, as shown in fig. 18 to 19, a plurality of fixed driven gears 107a, 107b are fixedly provided on the power output shaft 103, and a fixed driving gear (for example, a first fixed driving gear 106 and a second fixed driving gear 105) is fixedly provided on each input shaft, and the fixed driven gears are engaged with the corresponding fixed driving gears.
As shown in fig. 18 to 19, the fixed driven gear 107a is engaged with the fixed driving gear 105 to form one pair of gear pairs, and the fixed driven gear 107b is engaged with the fixed driving gear 106 to form the other pair of gear pairs. It will be appreciated that the two pairs of gear pairs have different transmission speed ratios, and therefore the transmission 104 in this embodiment has two transmission gears with different speed ratios, so that the structure of the power drive system 1000 is relatively simple and compact, and the requirement of the vehicle for the transmission speed ratio in normal running can also be met.
The main differences between some of these embodiments (i.e. the embodiments shown in fig. 18-19) and the embodiments of fig. 14 and 15 described above are: the synchronizer 109 is eliminated, the idler driven gear 108 is directly fixed on the power output shaft 103 instead to form a fixed driven gear, and the rest parts are basically the same as the embodiment in fig. 14 and 15, so that the details are not repeated.
In the example of fig. 16, i.e. in the embodiment of a plurality of input shafts and a single power output shaft 103, an input shaft fixed motor gear 111a is fixedly arranged on one of the input shafts, e.g. the first input shaft 101, a power output shaft free motor gear 111b is arranged on the power output shaft 103 in a free manner, the power output shaft free motor gear 111b is meshed with the input shaft fixed motor gear 111a, and a third motor generator 401 is linked with the input shaft fixed motor gear 111a, e.g. the third motor generator 401 is driven with the input shaft fixed motor gear 111a through a gear 402 and a gear 403. In this embodiment, the power drive system 1000 also includes a synchronizer 109, the synchronizer 109 being configured to synchronize the power take-off shaft 103 with the power take-off shaft idler motor gear 111b, e.g., the synchronizer 109 is disposed on the power take-off shaft 103 and is configured to engage the power take-off shaft idler motor gear 111 b.
That is, one major difference of the embodiment of fig. 16 compared to the embodiments of fig. 14-15 described above is that: the motor gear (third motor generator 401) of the embodiment of fig. 16 realizes the output of the motor power through the gear pair separately provided (i.e., the input shaft fixed motor gear 111a and the power output shaft free motor gear 111b), while in the embodiment of fig. 14-15, the motor gear realizes the output of the motor power through the corresponding gear pair.
In addition, there is a main difference between the embodiment of fig. 16 and the embodiment of fig. 14-15, namely that the transmission gears are different. Specifically, in the embodiment of fig. 16, a plurality of fixed drive gears are fixedly disposed on each input shaft, while in the embodiment of fig. 14-15, only one fixed drive gear is fixedly disposed on each input shaft. Correspondingly, in the embodiment of fig. 16, since a plurality of fixed driving gears are fixedly provided on each input shaft, a plurality of idler driven gears are provided on the power output shaft 103 in an idler manner, each idler driven gear is meshed with a corresponding fixed driving gear, and each idler driven gear is engageable to the power output shaft 103 through synchronization of a corresponding gear synchronizer.
For example, referring to the example of fig. 16, a second-gear fixed driving gear 2a, a fourth-gear fixed driving gear 4a and a sixth-gear fixed driving gear 6a are fixedly disposed on the first input shaft 101, a first-gear fixed driving gear 1a, a third-gear fixed driving gear 3a, a fifth-gear fixed driving gear 5a and a seventh-gear fixed driving gear 7a are fixedly disposed on the second input shaft 102, and a first-gear idler driven gear 1b, a second-gear idler driven gear 2b, a third-gear idler driven gear 3b, a fourth-gear idler driven gear 4b, a fifth-gear idler driven gear 5b, a sixth-gear idler driven gear 6b and a seventh-gear idler driven gear 7b are idly disposed on the power output shaft 103.
One of the idler driven gears 1b is engaged with one of the idler fixed driving gears 1a to form a first-gear pair, the second idler driven gear 2b is engaged with the second-gear fixed driving gear 2a to form a second-gear pair, the third idler driven gear 3b is engaged with the third-gear fixed driving gear 3a to form a third-gear pair, the fourth idler driven gear 4b is engaged with the fourth-gear fixed driving gear 4a to form a fourth-gear pair, the fifth idler driven gear 5b is engaged with the fifth-gear fixed driving gear 5a to form a fifth-gear pair, the sixth idler driven gear 6b is engaged with the sixth-gear fixed driving gear 6a to form a sixth-gear pair, and the seventh idler driven gear 7b is engaged with the seventh-gear fixed driving gear 7a to form a seventh-gear pair.
Further, as shown in fig. 16, a three-gear synchronizer 13c, a five-seven-gear synchronizer 57c, a two-gear synchronizer 2c, and a four-six-gear synchronizer 46c are provided on the power output shaft 103, the three-gear synchronizer 13c is provided between the first-gear idler driven gear 1b and the third-gear idler driven gear 3b and selectively engages the first-gear idler driven gear 1b or the third-gear idler driven gear 3b, the five-seven-gear synchronizer 57c is provided between the fifth-gear idler driven gear 5b and the seven-gear idler driven gear 7b and selectively engages the fifth-gear idler driven gear 5b or the seven-gear idler driven gear 7b, the two-gear synchronizer 2c is provided for engaging the second-gear idler driven gear 2b, a fourth-sixth speed synchronizer 46c is located between the fourth-speed idler driven gear 4b and the sixth-speed idler driven gear 6b and is used to selectively engage the sixth-speed idler driven gear 6b and the fourth-speed idler driven gear 4 b.
Therefore, the transmission 107 is provided with seven forward gears with different speed ratios, and the running requirements of the vehicle can be better met.
Referring to fig. 17, a transmission 104 in another embodiment will be described, the transmission 104 in this embodiment is mainly different from the transmission 100 in the embodiments of fig. 13 to 16 and 18 to 19 in the number of power output shafts 103, one power output shaft 103 in the above embodiment, and a plurality of, e.g., two, power output shafts 103 in this embodiment, and since the number of power output shafts 103 is increased, other configurations are also different from the above embodiment, which will be described in detail with reference to the drawings.
Referring to fig. 17, the transmission 104 in this embodiment includes a plurality of input shafts 101, 102 and a plurality of power output shafts, for example, a plurality of power output shafts including a first power output shaft 103a and a second power output shaft 103 b. Wherein the third motor generator 401 is operatively connected to one of the plurality of power output shafts, e.g. 103b, each of which is arranged to output power from the engine 301 and/or the third motor generator 401 to the power input of the differential 100 (e.g. the first and second planetary carriers 11, 21).
Further, as shown in fig. 17, the transmission 104 may further include a motor power shaft 103c, the third motor generator 401 is coaxially connected to the motor power shaft 103c, and the motor power shaft 103c is provided to be interlocked with one of the power output shafts, for example, the motor power shaft 103c is interlocked with the second power output shaft 103 b.
Regarding the linkage manner of the motor power shaft 103c and the second power output shaft 103b, referring to fig. 17, the first motor gear 103d is fixedly arranged on the motor power shaft 103c, the second motor gear 103e is fixedly arranged on one of the power output shafts, such as the second power output shaft 103b, and the first motor gear 103d is meshed with the second motor gear 103 e. In short, in this embodiment, the second power output shaft 103b and the motor power shaft 103d are geared, that is, power transmission is realized by the first motor gear 103d and the second motor gear 103e which are engaged with each other.
For the transmission 104 of this embodiment, its reverse configuration, see fig. 17, the reverse output gear 601 meshes with the power input (e.g., the first and second planet carriers 11, 21) of the differential 100, the reverse idler gear 604 meshes with the reverse output gear 601, the reverse idler gear 604 is idler on one of the power output shafts, e.g., the second power output shaft 103b, and the reverse idler gear 604 is engageable to that power output shaft 103b through the synchronizing action of the reverse synchronizer 604 c. Specifically, the reverse output gear 601 may be a duplicate gear having gear portions 602, 603, the gear portion 602 being engaged with the power input end (e.g., the first and second planetary carriers 11, 21) of the differential 100, and the gear portion 603 being engaged with the reverse intermediate gear 604, which may be idly mounted on the motor power shaft 103c, but is not limited thereto.
The reverse transmission path is generally divided into two paths, one of which is driven by the engine 301, for example, the engine 301 outputs generated power to the second power output shaft 103b through the dual clutch 204, the first input shaft 101 or the second input shaft 102, the reverse synchronizer 604c engages the reverse idler gear 604, and the power is output from the reverse output gear 601 through the reverse idler gear 604. The other is driving of the third motor generator 401, for example, the third motor generator 401 outputs the generated power to the second power output shaft 102b through the first motor gear 103d and the second motor gear 103e, the reverse synchronizer 604c engages the reverse idler gear 604, and the part of the power is output from the reverse output gear 601 through the reverse idler gear 604. Of course, the engine 301 and the third motor generator 401 may output reverse power at the same time, and at this time, two portions of reverse power are coupled to the second power output shaft 102b and then output from the reverse output gear 601 through the reverse idler gear 604.
Referring to fig. 17, since the transmission 104 has a plurality of power output shafts in this embodiment, and each power output shaft can output power to the outside, each power output shaft is provided with an output structure capable of outputting power to the power input ends (e.g., the first carrier 11 and the second carrier 21) of the differential 100. Specifically, a power output shaft free-sleeve output gear 605 is freely sleeved on one of the power output shafts, for example, the second power output shaft 103b, a power output shaft fixed output gear 606 is fixedly arranged on each of the remaining power output shafts, for example, the first power output shaft 103a, and the power output shaft free-sleeve output gear 605 and the power output shaft fixed output gear 606 are respectively linked with the power input ends (for example, the first planet carrier 11 and the second planet carrier 21) of the differential 100.
For example, in the specific example of fig. 17, the first power output shaft 103a is fixedly provided with a power output shaft fixed output gear 606, the second power output shaft 103b is idly provided with a power output shaft idle output gear 605, and the transmission 104 further includes an intermediate shaft 701, and the intermediate shaft 701 is coaxially fixed with the first carrier 11 and the second carrier 21, so that the intermediate shaft 701, the first carrier 11 and the second carrier 21 can rotate in the same direction and at the same speed. An intermediate shaft gear 702 is fixedly arranged on the intermediate shaft 701, and the intermediate shaft gear 702 is respectively meshed with the power output shaft fixed output gear 606, the power output shaft idle output gear 605 and the reverse gear output gear 601.
Wherein the power take off idler output gear 605 is on the same power take off shaft 103b as the reverse idler output gear 604, as a preferred embodiment the power take off idler output gear 605 shares a reverse synchronizer 604c with the reverse idler output gear 604, the reverse synchronizer 604c moving the power take off idler output gear 605 to the left and the reverse idler output gear 604 to the right as seen in fig. 17. Therefore, a synchronizer can be saved, the mechanical structure is simplified, the control strategy is simplified, and the cost is reduced.
In addition, for the power driving system 1000 in the embodiment of fig. 17, the engine 301 is connected to the first input shaft 101 and the second input shaft 102 through the dual clutch 204, which is the same as that in the other embodiments and will not be described again.
In this embodiment, referring to fig. 17, a first-gear fixed driving gear 1a, a third-gear fixed driving gear 3a and a fifth-gear fixed driving gear 5a are fixedly disposed on the first input shaft 101, a second-gear fixed driving gear 2a and a fourth-sixth-gear fixed driving gear 46a are fixedly disposed on the second input shaft 102, a second-gear idler driven gear 2b, a fourth-gear idler driven gear 4b, a third-gear idler driven gear 3b and a first-gear idler driven gear 1b are disposed on the first power output shaft 103a, and a fifth-gear idler driven gear 5b and a sixth-gear idler driven gear 6b are disposed on the second power output shaft 103 b.
As shown in fig. 17, one of the idler driven gears 1b is engaged with one of the idler fixed drive gears 1a to form a first-gear pair, the second idler driven gear 2b is engaged with the second-gear fixed drive gear 2a to form a second-gear pair, the third idler driven gear 3b is engaged with the third-gear fixed drive gear 3a to form a third-gear pair, the fourth idler driven gear 4b is engaged with the fourth-sixth-gear fixed drive gear 46a to form a fourth-gear pair, the fifth idler driven gear 5b is engaged with the fifth-gear fixed drive gear 5a to form a fifth-gear pair, and the sixth idler driven gear 6b is engaged with the fourth-sixth-gear fixed drive gear 46a to form a sixth-gear pair.
Further, as shown in fig. 17, a second-fourth speed synchronizer 24c and a third-third speed synchronizer 13c are provided on the first power output shaft 103a, a fifth-sixth speed synchronizer 56c is provided on the second power output shaft 103b, the third-third speed synchronizer 13c is provided between the first-third speed idler driven gear 1b and the third-third speed idler driven gear 3b and is used for engaging the first-third speed idler driven gear 1b or the third-fourth speed idler driven gear 3b, the second-fourth speed synchronizer 24c is provided between the second-second speed idler driven gear 2b and the fourth-third speed idler driven gear 4b and is used for engaging the second-second speed idler driven gear 2b or the fourth-speed idler driven gear 4b, and the fifth-sixth speed synchronizer 56c is provided between the fifth-third speed idler driven gear 5b and the sixth-speed idler driven gear 6b and is used for engaging the fifth-fourth speed idler driven gear 5b or the sixth-speed idler driven gear 6 b.
Therefore, the transmission 107 is provided with six forward gears with different speed ratios, and the running requirements of the vehicle can be better met.
For a single power take-off shaft 103 transmission embodiment, the power take-off shaft 103 may be directly coaxially fixed to both carriers. Referring to fig. 13-16, 18-23 and in conjunction with fig. 1-12, the power take-off shaft 103 is coaxially fixed with the first and second planetary carriers 11, 21, thereby making the connection of the transmission 104 with the differential 100 more compact, i.e. directly coaxially fixing the power take-off shaft 103 with both planetary carriers, thereby enabling the size of the power drive system 1000 to be reduced at least to some extent.
In a further embodiment, as shown in fig. 13-23, the power drive system 1000 further includes a first output 601 and a second output 602, the first output 601 being in communication with the first ring gear 13 and the second output 602 being in communication with the second ring gear 23. Further, the first output portion 601 is a left side gear, the second output portion 602 is a right side gear, and the first ring gear 13 is provided with first external teeth 603, the second ring gear 23 is provided with second external teeth 604, the first external teeth 603 are engaged with the left side gear 601, and the second external teeth 604 are engaged with the right side gear 602, so that the power passing through the differential 100 can be finally output to the left and right wheels through the left side gear 603 and the right side gear 604.
As shown in fig. 13-25, the first motor generator 501 is configured to be linked with the first output part 601, and the second motor generator 502 is configured to be linked with the second output part 602, for example, a gear 503 may be disposed on a motor shaft of the first motor generator 501, the gear 503 is engaged with the left side gear 601, and a gear 504 is disposed on a motor shaft of the second motor generator 502, and the gear 504 is engaged with the right side gear 602.
As shown in fig. 13 to 25, the first motor generator 501 and the second motor generator 502 are distributed left-right symmetrically with respect to the differential 100, so that the center of gravity of the power drive system 100 can be located at the center position or closer to the center position.
Referring to the embodiment of fig. 24-25, one of the main differences between the power drive system 1000 in this embodiment and the power drive system 1000 in the embodiment of fig. 12-23 is that: the number of input shafts. In some embodiments, the input shafts include a first input shaft 101, a second input shaft 102, and a third input shaft 1003, the third input shaft 1003 may be a hollow shaft and is sleeved on the second input shaft 102, the second input shaft 102 may also be a hollow shaft and is sleeved on the first input shaft 101, and the three input shafts may be coaxially arranged. The engine 301 is connected with the first input shaft 101, the second input shaft 102 and the third input shaft 1003 through a three-clutch 205, specifically, the three-clutch 205 has a first driven disk 206, a second driven disk 207, a third driven disk 208 and a housing 209, the housing 209 is selectively engageable with at least one of the first driven disk 206, the second driven disk 207 and the third driven disk 208, the first input shaft 101 is connected with the first driven disk 206, the second input shaft 102 is connected with the second driven disk 207, the third input shaft 1003 is connected with the third driven disk 208, and the engine 301 is connected with the housing 209. In the embodiment of fig. 24, the first driven disk 206, the second driven disk 207 and the third driven disk 208 are axially distributed, and in the embodiment of fig. 25, the first driven disk 206, the second driven disk 207 and the third driven disk 208 are radially distributed.
Exemplary operating conditions of the power drive system 1000 according to an embodiment of the present invention are briefly described below with reference to fig. 14.
Low-speed pure electric: the double clutch 204 is fully disengaged, the synchronizer 109 is disengaged, and the first motor generator 501 and the second motor generator 502 are operated in a motor mode to directly output power to the outside. The mode has the advantages of short power transmission path and low transmission energy loss, and is suitable for urban congestion road conditions.
High-speed pure electric: the double clutch 204 is completely disengaged, the synchronizer 109 is engaged, and the first motor generator 501, the second motor generator 502, and the third motor generator 401 all operate to output power to the outside.
Engine low gear: the first engaging portion 201 is engaged with the third engaging portion 203, the second engaging portion 202 is disengaged from the third engaging portion 203, and the synchronizer 109 is in an engaged state, and at this time, power generated by the engine 301 is output to the differential 100 through the first input shaft 101 and the power output shaft 103, and the differential 100 distributes the power to the driving wheels on both sides.
High-speed gear of the engine: the second engaging portion 202 is engaged with the third engaging portion 203, the first engaging portion 201 is disengaged from the third engaging portion 203, and the synchronizer 109 is in a disengaged state, in which the power generated by the engine 301 is output to the differential 100 through the second input shaft 102 and the power output shaft 103, and the differential 100 distributes the power to the drive wheels on both sides.
Parking power generation: the first engaging portion 201 is engaged with the third engaging portion 203, the second engaging portion 202 is disengaged from the third engaging portion 203, and the synchronizer 109 is in the disengaged state, in which the power generated by the engine 301 is output to the third motor generator 401 through the first input shaft 101, and the third motor generator 401 is driven as a motor to generate power, thereby realizing the parking power generation function.
Recovering braking energy: the synchronizer 109 may be in an off state where the first motor generator 501 and the second motor generator 502 recover braking energy. Or the synchronizer 109 is in the engaged state, in which the first motor generator 501, the second motor generator 502, and the third motor generator 401 all recover the braking energy.
Driving to generate electricity: the engine 301 can selectively drive the first motor generator 501 and the second motor generator 502 to generate power or drive the third motor generator 401 to generate power by different engagement states of the dual clutch 204 and engagement/disengagement states of the synchronizer 109, and certainly, can also drive the three motors to generate power at the same time, and meanwhile, the engine 301 also outputs power to the outside to drive the vehicle to run.
A range extending mode: the first engaging portion 201 engages the third engaging portion 203, the second engaging portion 202 is disengaged from the third engaging portion 203, the engine 301 outputs power to drive the third motor generator 401 to generate power, and the first motor generator 501 and the second motor generator 502 drive the vehicle to run as motor output power.
The embodiment of fig. 13 differs from the embodiment of fig. 14 mainly in that the third motor generator 401 is omitted, and the remaining components are identical and will not be described again.
The main difference between the embodiment of fig. 15 and the embodiment of fig. 14 is that the third motor generator 401 in the embodiment of fig. 15 is linked with the second input shaft 102, and the rest of the structure is kept the same, which is not described herein again.
One of the main differences between the embodiment of fig. 16 and the embodiment of fig. 14 is that the embodiment of fig. 16 has more transmission gears than the embodiment of fig. 14, and these gears are controlled and engaged by corresponding gear synchronizers, which is well understood by those skilled in the art, and therefore, the detailed description thereof is omitted.
One of the main differences between the embodiment of fig. 17 and the embodiment of fig. 14 is that the power output shaft of the embodiment of fig. 17 has a plurality of gears, and a plurality of transmission gears are correspondingly provided, and the gears are controlled and engaged by corresponding gear synchronizers, which is easily understood by those skilled in the art, and therefore, the description thereof is omitted.
One of the main differences between the embodiment of fig. 18-19 and the embodiment of fig. 14 is that the synchronizer 109 is eliminated, and the idler driven gear 108 is directly fixed on the power output shaft 103, so that the transmission conditions of the embodiment of fig. 18-19 and the embodiment of fig. 14 are similar, but there are some differences, for example, the embodiment of fig. 18-19 cannot achieve the parking power generation condition, which should be easily understood by those skilled in the art, and thus, the description is omitted.
For the embodiment of fig. 20-23, the difference is the addition of a rear drive differential lock as compared to the embodiment of fig. 14.
Referring to fig. 20 to 23 in combination with fig. 1 to 12, the first ring gear 13 is linked with the left front wheel 910a, for example, the first ring gear 13 is linked with the left front wheel 910a via the first external teeth 603 and the left side gear 601, the second ring gear 23 is linked with the right front wheel 910b, for example, the second ring gear 23 is linked with the right front wheel 910b via the second external teeth 604 and the right side gear 602. The fourth motor generator 901 is linked with the left rear wheel 910c by a gear structure, for example, the fourth motor generator 901 is linked with the left rear wheel 910c by gears W1, W2, W3, W4, the gear W1 is coaxially connected with the fourth motor generator 901, the gear W1 is engaged with the gear W2, the gear W2 is coaxially connected with the gear W3, the gear W3 is engaged with the gear W4, the gear W4 is fixedly provided on the left half shaft 904, and the left rear wheel 910c is provided on the left half shaft 904. Similarly, the fifth motor generator 902 is linked with the right rear wheel 910d through a gear structure, for example, the fifth motor generator 902 is linked with the right rear wheel 910d through gears X1, X2, X3 and X4, the gear X1 is coaxially connected with the fifth motor generator 902, the gear X1 is engaged with the gear X2, the gear X2 is coaxially connected with the gear X3, the gear X3 is engaged with the gear X4, the gear X4 is fixedly disposed on the right half shaft 905, and the right rear wheel 910d is disposed on the right half shaft 905.
In the example of fig. 20, an anti-skid synchronizer 903 is provided for synchronizing the gear W4 with the gear X4, e.g., the anti-skid synchronizer 903 is provided on the gear W4 and for engaging the gear X4. In the example of fig. 21, an anti-skid synchronizer 903 is provided for synchronizing the gear W1 with the gear X1, e.g., the anti-skid synchronizer 903 is provided on the gear W1 and for engaging the gear X1. In the example of fig. 22, an anti-skid synchronizer 903 is provided for synchronizing the gear W2 with the gear X2, e.g., the anti-skid synchronizer 903 is provided on the gear W2 and for engaging the gear X2.
In the example of fig. 23, an antiskid synchronizer 903 is provided for synchronizing a left half shaft 904 and a right half shaft 905, and the fourth motor generator 901 and the fifth motor generator 902 are both wheel-side motors in this embodiment, as the antiskid synchronizer 903 is provided on the left half shaft 904 and for engaging the right half shaft 905.
In summary, the anti-skid synchronizer 903 is configured to selectively synchronize the left rear wheel 910c and the right rear wheel 910d, in other words, when the anti-skid synchronizer 903 is in the engaged state, the left rear wheel 910c and the right rear wheel 910d will rotate synchronously, i.e. at the same speed and in the same direction, and at this time, the left rear wheel 910c and the right rear wheel 910d will not rotate at different speeds. When the anti-skid synchronizer 903 is in a disconnected state, the fourth motor generator 901 can drive the left rear wheel 910c alone, the fifth motor generator 902 can drive the right rear wheel 910d alone, and the two rear wheels are independent and do not interfere with each other, so that the function of differential rotation of the wheels is realized.
In addition, for the technical solutions and/or technical features described in the above embodiments, those skilled in the art can combine the technical solutions and/or technical features in the above embodiments without conflict or contradiction, and 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, so that functional interaction and support of each technical solution and/or technical feature with each other can be achieved, and the combined solution has a more superior technical effect.
For example, a person skilled in the art may combine the solution that the end surface of the first gear ring 13 facing the second gear ring 23 and the end surface of the second gear ring 23 facing the first gear ring 13 are located on the same plane with the solution of the configuration of the first gear ring 13 and the second gear ring 23, thereby making the axial gap between the two gear rings of the differential 100 zero, so that the two gear rings can define a relatively closed installation space, fully protect the components in the installation space, increase the service life of the differential, reduce the cost, and effectively reduce the axial size of the differential 100.
For another example, a person skilled in the art may combine the scheme that the thickness of the first planet wheel 12 is greater than the thickness of the second planet wheel 22 with the scheme that the first ring gear 13 is a small ring gear, the second ring gear 23 is a large ring gear, and the revolving radius of the first planet wheel 12 is smaller than the revolving radius of the second planet wheel 22, so that the formed differential 100 has a more compact structure, a smaller volume, and is more conveniently arranged inside an engine compartment of a vehicle.
For another example, a person skilled in the art may combine a scheme in which an end surface of the first gear ring 13 facing the second gear ring 23 and an end surface of the second gear ring 23 facing the first gear ring 13 are located on the same plane with a scheme in which the end surfaces of the second gear ring 23 facing the first gear ring 13 are located in a meshing relationship with the thinner planetary gears and the thicker planetary gears, so that on one hand, an axial gap between the two gear rings of the differential 100 is zero, and thus the two gear rings can define a relatively closed installation space, thereby sufficiently protecting components in the installation space, increasing the service life of the differential and reducing the cost, and on the other hand, the axial size of the differential 100 can be further.
It should be understood, of course, that the above descriptions of examples are only illustrative, and those skilled in the art can freely combine technical solutions and/or combinations of technical features without conflict, and the combined solutions have more advantageous technical effects.
In addition, it is understood that the combined technical solutions also fall into the protection scope of the present invention.
Overall, the differential 100 according to the embodiment of the present invention can effectively save space and reduce weight, and particularly, such a planetary gear type differential 100 can reduce the weight by about 30% and the axial dimension by about 70% as compared with the conventional bevel gear type differential, not only can reduce the friction of the bearings, but also can realize the torque distribution of the left wheel and the right wheel, so that the load distribution of the differential mechanism 100 is more reasonable, the rigidity of the differential mechanism 100 is better, in addition, the transmission efficiency is also improved to a certain extent due to the adoption of the cylindrical gear, for example, the efficiency of the conventional bevel gear transmission with 6-grade precision and 7-grade precision is about 0.97-0.98, and the transmission efficiency of the cylindrical gears with 6-level precision and 7-level precision is about 0.98-0.99, and in addition, the cylindrical gears are adopted, so that the working noise of the differential mechanism 100 is reduced, the heat productivity is reduced, and the service life of the differential mechanism 100 is greatly prolonged. In short, the differential 100 according to the embodiment of the present invention has many advantages of light weight, small size, low cost, high transmission efficiency, low noise, low heat generation, long service life, and the like.
Meanwhile, since the differential 100 according to an embodiment of the present invention may omit a sun gear, the omission of the sun gear may have the following advantages:
from mechanical analysis, the differential is realized by eliminating the sun gear and utilizing the gear ring, because the number of teeth of the gear ring is more than that of the sun gear, and the pitch circle is larger (the pitch circle refers to a pair of circles tangent at the node when the gears are in meshing transmission), so that the load and bearing torque can be more evenly distributed, which is beneficial to prolonging the service life of the differential 100. Meanwhile, the differential mechanism 100 can be better lubricated and cooled due to the fact that the sun wheel is not arranged, namely, a cavity can be formed inside the planetary wheel due to the fact that the sun wheel is omitted, the gear ring and the planetary wheel are meshed in an inner meshing relation (the sun wheel and the planetary wheel are meshed outside), lubricating oil can be stored in the gear ring, and therefore cooling and lubricating effects can be greatly improved. In addition, since the sun gear is eliminated, the number of parts is reduced, the mass and cost of the differential 100 are reduced, and the differential 100 becomes more compact and lighter.
While the power driving system 1000 having the differential 100 according to the embodiment of the present invention has significant advantages in space and driving manner, taking the advantage of space as an example, the power driving system 1000 is particularly suitable for a new energy vehicle, since a power assembly of the new energy vehicle is generally disposed in an engine compartment, the power assembly not only has a transmission, an engine, but also has at least one electric machine, and since the engine compartment has limited space, the compact differential 100 according to the embodiment of the present invention can obtain advantages in space, and is more convenient to dispose. Also for example, taking the advantage of driving manner as an example, the axial space is better arranged due to the greatly reduced axial dimension of the differential 100 according to the embodiment of the present invention, and the differential 100 having two ring gears as power take-off can better achieve power connection with two electric machines (such as the above-described connection of the electric machines through the external teeth of the ring gears), which is difficult to achieve on the conventional conical differential.
Briefly describing a vehicle 10000 according to an embodiment of the present invention, as shown in fig. 26, the vehicle 10000 includes a power driving system 1000 in the above embodiment, and the power driving system 1000 may be used for forward driving or backward driving, but the present invention is not limited thereto. It should be understood that other configurations of the vehicle 10000 according to the embodiment of the present invention, such as a brake system, a driving system, a steering system, etc., are known in the art and well known to those skilled in the art, and thus will not be described in detail herein.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples described in this specification can be combined and combined by those skilled in the art.
Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art within the scope of the present invention.

Claims (28)

1. A power drive system, comprising:
a differential, said differential comprising:
the planet carrier comprises a first planet carrier, a first planet wheel and a first gear ring, wherein the first planet wheel is arranged on the first planet carrier, and is meshed with the first gear ring;
the second planet gear is arranged on the second planet carrier, and is meshed with the second gear ring and the first planet gear;
wherein, first ring gear with the second ring gear constitutes two power take off ends of differential mechanism, first planet carrier with the second planet carrier constitutes differential mechanism's power take off end, just first planet wheel with the revolution radius of second planet wheel is different, first ring gear with at least one in the second ring gear includes: an annular side wall portion provided on an inner wall surface thereof with a plurality of teeth for meshing with the planetary gears, and an annular flange portion extending from an end surface of the annular side wall portion of one of the ring gears toward the other ring gear or provided on end surfaces of the annular side wall portions of the two ring gears, respectively, and extending opposite to each other, the annular flange portion having an inner diameter larger than that of the annular side wall portion;
the transmission is respectively connected with the engine and the differential, and the engine can output the generated power to the power input end of the differential after passing through the transmission; and
a first output portion and a second output portion, the first output portion being in linkage with the first gear ring, the second output portion being in linkage with the second gear ring;
a first motor generator linked with the first output unit, and a second motor generator linked with the second output unit.
2. The power drive system according to claim 1, characterized in that an end surface of the first ring gear facing the second ring gear is in the same plane as an end surface of the second ring gear facing the first ring gear.
3. The power drive system according to claim 2, characterized in that each of the first ring gear and the second ring gear includes:
the main part flat board portion with set up the annular side wall portion of the periphery edge of main part flat board portion, be provided with a plurality of teeth on the internal face of annular side wall portion, main part flat board portion with inject the cavity between the annular side wall portion, the cavity of first ring gear with the cavity orientation of second ring gear is in order to constitute installation space each other, first planet carrier with first planet wheel and the second planet carrier with the second planet wheel is accomodate in the installation space.
4. The power-drive system of claim 1, wherein the first planet gears are different thicknesses in the axial direction than the second planet gears.
5. A power drive system according to claim 4, characterised in that the teeth of the thinner planet are fully meshed with the teeth of the thicker planet, and in that the teeth of the thicker planet extend axially to one side beyond the teeth of the thinner planet or to both sides beyond the teeth of the thinner planet, respectively.
6. The power drive system of claim 4, wherein the thicker planets have a smaller revolution radius than the thinner planets.
7. The power-driven system of claim 4, wherein the thicker planet gears correspond to a small gear ring, the thinner planet gears correspond to a large gear ring, and the outer diameter of the large gear ring is larger than that of the small gear ring.
8. The power-driven system of claim 4, wherein the first planet gears have a thickness greater than a thickness of the second planet gears, the first ring gear is a small ring gear, the second ring gear is a large ring gear, and a revolution radius of the first planet gears is less than a revolution radius of the second planet gears.
9. The power-drive system of claim 1, wherein the revolution axis of the first planet is coincident with the revolution axis of the second planet;
the first and second planet carriers being spaced apart, the first and second planet gears being arranged in direct mesh between the first and second planet carriers such that the first and second planet carriers are located on opposite outer sides of the first and second planet gears, respectively;
the annular flange portion has an outer diameter substantially equal to an outer diameter of the annular side wall portion, or an inner diameter substantially equal to an outer diameter of the annular side wall portion such that the annular flange portion projects radially outward from the annular side wall portion.
10. The power-drive system of claim 1, wherein the first and second planets are cylindrical gears.
11. A power drive system according to claim 1, characterized in that each first planet wheel is provided with a first planet wheel axle, which at both ends are connected to the first planet carrier and the second planet carrier, respectively, and each second planet wheel is provided with a second planet wheel axle, which at both ends are connected to the first planet carrier and the second planet carrier, respectively.
12. The power drive system of claim 1, wherein the transmission includes a power take-off shaft and a plurality of input shafts;
one of the plurality of input shafts is configured to be selectively coupled to the power take-off shaft, which is also configured to be coupled to the power input of the differential.
13. A power drive system according to claim 12, wherein an idler driven gear is provided on the power take-off shaft in an idler arrangement, the idler driven gear being in linkage with the one of the input shafts, the power drive system further comprising a synchronizer arranged to synchronize the power take-off shaft with the idler driven gear.
14. A power drive system according to claim 12, wherein the power take-off shaft is idly provided with an idly-sleeved driven gear and fixedly provided with a fixed driven gear, the power drive system further comprising a synchronizer: the synchronizer is arranged for synchronizing the power output shaft and the idle driven gear;
each input shaft is fixedly provided with a fixed driving gear, and the empty sleeve driven gear and the fixed driven gear are respectively meshed with the corresponding fixed driving gears.
15. A power drive system according to claim 12, wherein a plurality of fixed drive gears are fixedly provided on each of the input shafts, a plurality of idler driven gears are provided on the power output shaft and are in meshing engagement with the corresponding fixed drive gears, each of the idler driven gears being engageable to the power output shaft by synchronization of a corresponding gear synchronizer.
16. The power drive system of claim 1, wherein the transmission includes a power take-off shaft and a plurality of input shafts;
each of the input shafts is configured to be in linkage with the power output shaft, which is configured to also be in linkage with the power input end of the differential.
17. A power drive system according to claim 16, wherein a plurality of fixed driven gears are fixedly disposed on the power output shaft, a fixed drive gear is fixedly disposed on each of the input shafts, and the fixed driven gears are engaged with the corresponding fixed drive gears.
18. The power drive system according to claim 1, wherein the transmission comprises a first input shaft and a second input shaft, the second input shaft is sleeved on the first input shaft, and the power drive system further comprises an engine, and the engine is connected with the first input shaft and the second input shaft through a double clutch.
19. A power drive system according to claim 12, wherein the power take-off shaft is fixed coaxially with the first and second planet carriers.
20. A power drive system according to claim 1, wherein the first output section is a left side gear and the second output section is a right side gear; and
the first gear ring is provided with first external teeth, the second gear ring is provided with second external teeth, the first external teeth are meshed with the left half axle gear, and the second external teeth are meshed with the right half axle gear.
21. The power drive system of claim 1, wherein the transmission comprises:
a plurality of input shafts and a plurality of power output shafts, each of the power output shafts being arranged to output power from the engine to a power input of the differential.
22. The power drive system of claim 21, wherein the transmission further comprises:
the reverse gear output gear is linked with the power input end of the differential, the reverse gear intermediate gear is meshed with the reverse gear output gear, and the reverse gear intermediate gear is sleeved on one of the power output shafts in a hollow mode and can be connected to the one of the power output shafts through the synchronous action of the reverse gear synchronizer.
23. A power drive system according to claim 22, wherein a power output shaft idler output gear is disposed on one of the power output shafts, the power output shaft idler output gear and the reverse intermediate gear share the reverse synchronizer, and a power output shaft fixed output gear is fixedly disposed on each of the remaining power output shafts, and the power output shaft fixed output gear and the power output shaft idler output gear are respectively linked with the power input end of the differential.
24. The power drive system of claim 23, further comprising:
the intermediate shaft is coaxially fixed with the first planet carrier and the second planet carrier, an intermediate shaft gear is fixedly arranged on the intermediate shaft, and the intermediate shaft gear is respectively meshed with the power output shaft fixed output gear, the power output shaft idle output gear and the reverse gear output gear.
25. The power drive system of claim 1, further comprising: a third motor generator connected to the transmission, the third motor generator being operable to output the generated power to the power input of the differential through the transmission.
26. A power drive system according to claim 1, wherein the transmission comprises a first input shaft, a second input shaft and a third input shaft, the third input shaft is sleeved on the second input shaft, the second input shaft is sleeved on the first input shaft, and the engine is connected with the first input shaft, the second input shaft and the third input shaft through three clutches.
27. The power-driven system according to claim 1, wherein the first ring gear is linked with a left front wheel, and the second ring gear is linked with a right front wheel;
the power drive system further includes:
a fourth motor generator linked with the left rear wheel and a fifth motor generator linked with the right rear wheel; and
an anti-skid synchronizer configured to selectively synchronize the left and right rear wheels such that the left and right rear wheels rotate in synchronization.
28. A vehicle characterized by comprising a power drive system according to any one of claims 1-27.
CN201510624475.2A 2015-09-25 2015-09-25 Power driving system and vehicle with same Active CN106553531B (en)

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JP3998932B2 (en) * 2001-08-02 2007-10-31 本田技研工業株式会社 Four-wheel drive system for vehicles
CN200984967Y (en) * 2006-12-20 2007-12-05 比亚迪股份有限公司 Mixed power vehicle driving system
CN101722841A (en) * 2008-10-28 2010-06-09 比亚迪股份有限公司 Power assembly for vehicles
DE102012216404A1 (en) * 2012-09-14 2014-03-20 Schaeffler Technologies AG & Co. KG Spur gear differential for use as distributor gear for distributing drive power between front and rear axles of vehicle, has axles whose angular distances are defined on pitch circle so that integral multiple of angle value represents value
CN102848908B (en) * 2012-09-19 2015-05-13 长城汽车股份有限公司 Power driving device of electric vehicle and electric vehicle
CN103144528B (en) * 2013-02-20 2015-10-07 上海中科深江电动车辆有限公司 Be applied to double-clutch speed changer and the using method thereof of hybrid vehicle
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