WO2017050101A1 - Système d'entraînement de puissance et véhicule utilisant celui-ci - Google Patents

Système d'entraînement de puissance et véhicule utilisant celui-ci Download PDF

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Publication number
WO2017050101A1
WO2017050101A1 PCT/CN2016/097695 CN2016097695W WO2017050101A1 WO 2017050101 A1 WO2017050101 A1 WO 2017050101A1 CN 2016097695 W CN2016097695 W CN 2016097695W WO 2017050101 A1 WO2017050101 A1 WO 2017050101A1
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WO
WIPO (PCT)
Prior art keywords
gear
planet
input
ring gear
drive system
Prior art date
Application number
PCT/CN2016/097695
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English (en)
Chinese (zh)
Inventor
杨冬生
廉玉波
张金涛
罗红斌
Original Assignee
比亚迪股份有限公司
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Application filed by 比亚迪股份有限公司 filed Critical 比亚迪股份有限公司
Publication of WO2017050101A1 publication Critical patent/WO2017050101A1/fr

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/16—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/28—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or type of power take-off

Definitions

  • the present invention relates to a power drive system and a vehicle having the same.
  • the differential includes a driven gear of the final drive (main reduction drive gear), a planetary gear, a center wheel, etc., and the planetary gear is mounted on the stator through the square shaft and the sleeve.
  • the sub-plate of the moving gear is meshed with the center wheel, and the rotating and moving functions are realized by the rotating pair and the plane moving pair.
  • the center wheel is connected to the left and right shafts through the angular positioning pin and the cylindrical pair or spline to achieve the output rotation. The purpose of the moment.
  • the differential cancels the original left and right housings of the differential, the planetary gear shaft and the like, and the square shaft and the sleeve are directly used to mount the planetary gears on the auxiliary plate of the driven gear of the final drive, effectively
  • the number of parts of the differential is reduced, the structure is simplified, and the weight is reduced.
  • this differential utilizes a symmetrical bevel gear structure to achieve the inter-wheel differential, but only a partial innovation for the conventional symmetrical bevel gear differential does not really solve the excessive axial size of the differential structure.
  • the present invention aims to solve at least one of the above technical problems in the prior art to some extent.
  • the present invention proposes a power drive system in which the differential of the power drive system utilizes the principle of planetary differential to achieve a differential function, which is compact and simple.
  • the invention also proposes a vehicle having the power transmission system.
  • a power drive system includes: a differential including: a first planet carrier, a first planet gear, and a first ring gear, the first planet gear and the first planet a first planetary gear that meshes with the first ring gear; a second planet carrier, a second planet gear, and a second ring gear, the second planet gear being coupled to the second planet carrier, a second planet gear meshes with the second ring gear and the second planet gear also meshes with the first planet gear, wherein the first ring gear and the second ring gear constitute the differential gear Two power outputs; an input portion, the input portion, the first planet carrier and the second planet carrier are coaxially arranged and the input portion is coupled to the first planet carrier and the second planet carrier a power output shaft, the power output shaft is disposed in linkage with the input portion; and a plurality of input shafts, one of the plurality of input shafts is disposed to be selectively coupled to the power output shaft, The remaining ones of the plurality of input shafts are arranged to
  • the differential of the power drive system according to the embodiment of the present invention realizes the differential function by using the principle of planetary differential, and is compact and simple.
  • the power drive system further includes an engine configured to selectively engage at least one of the plurality of input shafts.
  • an output gear is disposed on the power output shaft, and the output gear is meshed with the input portion.
  • the power take-off shaft is provided with an idler driven gear
  • the idler driven gear is linked with the one of the plurality of input shafts
  • the system also includes a synchronizer configured to synchronize the power take off shaft with the idler driven gear.
  • the synchronizer is disposed on the power take-off shaft and is configured to engage the idler driven gear.
  • the power output shaft is fixedly provided with a fixed driven gear
  • the fixed driven gear is interlocked with the remaining ones of the plurality of input shafts.
  • the power take-off shaft is provided with an idler driven gear and is fixedly provided with a fixed driven gear
  • the power drive system further includes a synchronizer: the synchronizer is set for synchronization The power output shaft and the idler driven gear; each input shaft is fixedly provided with a fixed driving gear, and the empty sleeve driven gear and the fixed driven gear respectively mesh with corresponding fixed driving gears.
  • the first planet gear and the second planet gear partially overlap in the axial direction.
  • the first planet gear includes: a first tooth portion and a second tooth portion
  • the second planet gear includes: a third tooth portion and a fourth tooth portion, the first tooth portion Engaging with the first ring gear, the second tooth portion and the third tooth portion overlap and mesh with each other in the axial direction, and the fourth tooth portion meshes with the second ring gear.
  • the first ring gear and the second ring gear are symmetrical structures, and each of the first ring gear and the second ring gear includes: a body flat portion and a setting a plurality of teeth are disposed on an inner wall surface of the outer peripheral edge of the main body flat portion, and a plurality of teeth are disposed on an inner wall surface of the annular side wall portion, and a cavity is defined between the main body flat portion and the annular side wall portion.
  • a cavity of the first ring gear and a cavity of the second ring gear face each other to constitute an installation space, the first planet carrier and the first planet gear and the second planet carrier and the first The two planetary wheels are housed in the installation space.
  • the input portion is configured as an input end gear, the input end gear being configured to be annular and sleeved on the first ring gear and the second ring outer surface.
  • a gap is provided between the first ring gear and the second ring gear, the input The end gear surrounds and covers the gap.
  • the power drive system further includes: an intermediate connection structure for connecting the first planet carrier and the second planet carrier to the input portion, the intermediate connection The structure includes: a first connecting bracket for connecting the first planet carrier and the input portion, and a second connecting bracket for connecting the second planet carrier and The input portion, wherein each of the first connection bracket and the second connection bracket includes: a center body portion and a plurality of extension arm portions, the plurality of extension arm portions being disposed at the center body portion On the outer peripheral surface, the plurality of extending arm portions are radially distributed around the central body portion, wherein the plurality of extending arm portions are for connecting with the input portion.
  • each of the first planet gears is configured with a first planetary axle, and two ends of the first planetary axle are respectively coupled to the first planet carrier and the second planet carrier, each The second planet gears are provided with a second planetary axle, and the two ends of the second planetary axle are connected to the first planet carrier and the second planet carrier, respectively.
  • the revolution radius of the first planet gear is the same as the revolution radius of the second planet gear.
  • the power drive system further includes: a second motor generator and a third motor generator, the second motor generator is coupled with the first ring gear, and the third motor generator The second ring gear is linked.
  • the first outer ring surface of the first ring gear is provided with a first outer tooth
  • the outer peripheral surface of the second ring gear is provided with a second outer tooth
  • the second motor generator and The first external teeth are linked
  • the third motor generator is linked with the second external teeth
  • the plurality of input shafts include a first input shaft, a second input shaft, and a third input shaft, and the third input shaft is sleeved on the second input shaft, the Two input shafts are sleeved on the first input shaft, and the engine is connected to the first input shaft, the second input shaft and the third input shaft via a three-clutch.
  • the first ring gear is linked with the left front wheel
  • the second ring gear is linked with the right front wheel
  • the power drive system further includes: a fourth motor generator and a fifth motor generator
  • the fourth motor generator is associated with the left rear wheel
  • the fifth motor generator is coupled with the right rear wheel
  • the anti-skid synchronizer is configured to selectively synchronize the left rear wheel And a right rear wheel such that the left rear wheel and the right rear wheel rotate in synchronization.
  • a vehicle according to an embodiment of the present invention includes a power drive system according to the above embodiment of the present invention.
  • FIG. 1 is an exploded view of a viewing angle of a differential according to an embodiment of the present invention
  • FIG. 2 is an exploded view of another perspective of a differential according to an embodiment of the present invention.
  • FIG. 3 is a perspective view of a differential according to an embodiment of the present invention.
  • FIG. 4 is a schematic diagram of a planar principle of a differential according to an embodiment of the present invention.
  • Figure 5 is a perspective view of a differential in which a second planet carrier and a second ring gear are not shown, in accordance with an embodiment of the present invention
  • Figure 6 is a schematic view showing the meshing of the first planetary gear and the second planetary gear
  • Figure 7 is a schematic diagram of the meshing principle of the first planetary gear and the second planetary gear
  • Figure 8 is a perspective view of a first ring gear or a second ring gear in accordance with an embodiment of the present invention.
  • Figure 9 is a perspective view of a first ring gear or a second ring gear in accordance with another embodiment of the present invention.
  • Figure 10 is a schematic illustration of a power drive system in accordance with one embodiment of the present invention.
  • FIG 11 is a schematic illustration of a power drive system in accordance with another embodiment of the present invention.
  • Figure 12 is a schematic illustration of a power drive system in accordance with still another embodiment of the present invention.
  • FIG. 13 is a schematic illustration of a power drive system in accordance with still another embodiment of the present invention.
  • Figure 14 is a schematic illustration of a power drive system in accordance with still another embodiment of the present invention.
  • FIG. 15 is a schematic illustration of a power drive system in accordance with still another embodiment of the present invention.
  • Figure 16 is a schematic illustration of a power drive system in accordance with still another embodiment of the present invention.
  • FIG. 17 is a schematic illustration of a power drive system in accordance with still another embodiment of the present invention.
  • Figure 18 is a schematic illustration of a power drive system in accordance with still another embodiment of the present invention.
  • Figure 19 is a schematic illustration of a power drive system in accordance with still another embodiment of the present invention.
  • Figure 20 is a schematic illustration of a vehicle in accordance with an embodiment of the present invention.
  • first and second are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated.
  • features defining “first” and “second” may include one or more of the features either explicitly or implicitly.
  • the meaning of "a plurality” is at least two, such as two, three, etc., unless specifically defined otherwise.
  • the terms “installation”, “connected”, “connected”, “fixed” and the like shall be understood broadly, and may be either a fixed connection or a detachable connection, unless explicitly stated and defined otherwise. Or in one; can be Mechanical connections can also be electrical connections or can communicate with each other; they can be directly connected or indirectly connected via an intermediate medium, which can be the internal communication of two components or the interaction of two components. For those skilled in the art, the specific meanings of the above terms in the present invention can be understood on a case-by-case basis.
  • the first feature "on” or “under” the second feature may include direct contact of the first and second features, and may also include first and second features, unless otherwise specifically defined and defined. It is not in direct contact but through additional features between them.
  • the first feature "above”, “above” and “above” the second feature includes the first feature directly above and above the second feature, or merely indicating that the first feature level is higher than the second feature.
  • the first feature “below”, “below” and “below” the second feature includes the first feature directly below and below the second feature, or merely the first feature level being less than the second feature.
  • a power drive system 1000 according to an embodiment of the present invention, which can be applied to a vehicle, will be described in detail below with reference to the accompanying drawings.
  • a power drive system 1000 mainly includes a differential 100, a transmission 104, and a first motor generator 401.
  • the transmission 104 is coupled to the differential 100 and the first motor generator. Between machines 401.
  • differential 100 The specific structure of the differential 100 will first be described in detail below in accordance with the illustrated embodiment, and other configurations for the power drive system 1000 will be described after the construction of the differential 100 is described in detail.
  • a differential 100 according to an embodiment of the present invention will be described in detail below with reference to FIGS. 1-9.
  • the differential 100 can be used for inter-wheel differential or inter-axle differential for the example of inter-wheel differential.
  • the differential 100 enables the left and right drive wheels to roll at different angular velocities when the vehicle is turning or traveling on uneven roads to ensure a pure rolling motion between the drive wheels on both sides and the ground.
  • a differential 100 may include a first planet carrier 11, a first planet gear 12 and a first ring gear 13, and a second planet carrier 21, a second planet gear 22, and Second ring gear 23.
  • both the first planet carrier 11 and the second planet carrier 21 can be constructed as a circular plate-like structure, which can reduce the axial dimension of the differential 100 to some extent.
  • the first planet carrier 11 and the second planet carrier 21 may be of a split structure, that is, the first planet carrier 11 and the second planet carrier 21 are separated from each other, and since the individual small parts are relatively easy to form, the first will be The separate processing of the carrier 11 and the second carrier 21 can simplify the manufacturing process and improve the machining accuracy.
  • the first planet gears 12 are disposed on the first planet carrier 11, for example, each of the first planet gears 12 is provided with a first planet gear axle 14, a first planet gear axle 14
  • the two ends are rotatably supported on the first planet carrier 11 and the second planet carrier 21, respectively, such that both ends of the first planet axle 14 are rotatably supported by the first planet carrier 11 by bearings
  • the second planet carrier 21 is in a corresponding axial bore, and the first planet gear 12 can be fixed to the corresponding first planet axle 14.
  • the two ends of the first planetary axle 14 and the first planet carrier 11 and the second The carrier 21 can also be fixedly connected.
  • the two ends of the first planetary axle 14 are respectively welded and fixed to the shaft holes corresponding to each other on the first carrier 11 and the second carrier 21, and the first planetary gear 12 is at this time.
  • the purpose of connecting the first planet carrier 11 and the second planet carrier 21 can be achieved by the first planetary axle 14 such that the first planet carrier 11 and the second planet carrier 21 maintain the same speed and the same direction (ie, the first The carrier 11 and the second carrier 21 are interlocked, and with this connection, the first carrier 11 and the second carrier 21 can support/fix the first planetary axle 14 well, preventing the first planetary axle The 14 is disconnected from the single planet carrier causing the differential 100 to fail.
  • the first planet gear 12 meshes with the first ring gear 13, specifically in the form of internal engagement, that is, the first planet gear 12 is located inside the first ring gear 13 and with the first ring gear 13 The upper teeth mesh.
  • the first planet gears 12 may be plural and distributed inside the first ring gear 13 at circumferentially equiangular intervals, for example, the first planet gears 12 may be three, and any two adjacent first planet wheels 12 The angle between the intervals is 120°.
  • the second planet gears 22 are disposed on the second planet carrier 21, for example, each of the second planet gears 22 is provided with a second planet gear axle 24, such as a second planet axle.
  • the two ends of the two ends are rotatably supported by the bearings in the shaft holes corresponding to the first planet carrier 11 and the second planet carrier 21, and the second planet gears 22 can be fixed to the corresponding second planet gear axles. 24 on.
  • the two ends of the second planetary axle 24 may also be fixedly coupled to the first planet carrier 11 and the second planet carrier 21, for example, the two ends of the second planetary axle 24 are respectively coupled to the first planet carrier 11 and
  • the second planetary carrier 21 is welded and fixed to the corresponding axial hole.
  • the second planetary gear 22 is rotatably sleeved on the corresponding second planetary axle 24, for example, the second planetary gear 22 is rotatably fitted through the bearing.
  • the purpose of connecting the first planet carrier 11 and the second planet carrier 21 can be achieved by the second planetary gear shaft 24, so that the first planet carrier 11 and the second planet carrier 21 maintain the same speed and the same direction, and this is adopted.
  • the first planet carrier 11 and the second planet carrier 21 can support/fix the second planetary axle 24 well, preventing the second planetary axle 24 from being disconnected from the single planet carrier, thereby causing the differential 100 to fail.
  • first planet carrier 11 and the second planet carrier 21 in order to maintain the same speed and the same direction of movement of the first planet carrier 11 and the second planet carrier 21, not only the first planetary axle 14 and/or the second planetary axle may be employed.
  • the method of 24 is realized, and the first planet carrier 11 and the second planet carrier 21 can also be directly fixedly connected through the intermediate connection structure 6, or the first planet carrier 11 and the second planet carrier can be connected by using the planetary axle and the intermediate connection structure 6 at the same time. 21, and the specific configuration regarding the intermediate connection structure 6 will be described in detail below.
  • the second planetary gear 22 meshes with the second ring gear 23, specifically in the form of internal engagement, that is, the second planetary gear 22 is located inside the second ring gear 23 and with the second ring gear 23
  • the upper teeth mesh.
  • the second planet gears 22 may be plural and distributed inside the second ring gear 23 at circumferentially equiangular intervals, for example, the second planet gears 22 may be three, and any two adjacent two planet wheels 22 may be adjacent. The angle between the intervals is 120°.
  • FIG. 4 is a schematic diagram of the planar principle of the differential 100 according to an embodiment of the present invention, wherein Schematically showing the meshing relationship between the first planet gear 12 and the second planet gear 22 and the meshing relationship between the first planet gear 12 and the first ring gear 13, the second planet gear 22 and the second ring gear 23, Since FIG. 4 is a plan view and at the same time the above three meshing relationships are shown, the relative positional relationship of the components is merely illustrative and does not represent or imply the actual spatial arrangement of the components.
  • first planet gear 12 and the second planet gear 22 are multiple, the plurality of first planet gears 12 and the plurality of second planet gears 22 are respectively engaged.
  • first planetary gear 12 and the second planetary gear 22 are both three, and the first first planetary gear 12 can be associated with the corresponding first second planetary gear.
  • the second first planet gear 12 can mesh with the corresponding second second planet gear 22, and the third first planet gear 12 can mesh with the corresponding third second planet gear 22, so that there are many
  • the first planetary gear 12 and the second planetary gear 22, which are meshed with each other, are more stable when the differential 100 transmits power, and the power is transmitted between the plurality of sets of the first planetary gear 12 and the second planetary gear 22 that are meshed with each other. ,reliable.
  • the revolution axis of the first planet gear 12 coincides with the revolution axis of the second planet gear 22, that is, the first planet gear 12 and the second planet gear 22 have the same revolution axis O, and first The orbital radius of the planet gear 12 and the second planet gear 22 (i.e., the distance of the central axis of the planet gear from the revolution axis O) is the same.
  • the first planet gear 12 is in meshing engagement with the second planet gear 22.
  • the first planetary gear 12 it not only meshes with the first ring gear 13, but also meshes with the second planetary gear 22, and for the second planetary gear 22, it not only meshes with the second ring gear 23, At the same time, it also meshes with the first planet gear 12.
  • the first ring gear 13 and the second ring gear 23 can constitute two power output ends of the differential 100, and the first carrier 11 and the second carrier 21 correspond to each other to form a differential.
  • the power input end of 100 for example, in one embodiment of the invention, the first planet carrier 11 and the second planet carrier 21 are interlocked with the input unit 3, in other words, the input unit 3, the first planet carrier 11 and the second planet carrier 21
  • the state of motion is the same (ie, at the same speed, in the same direction).
  • the input portion 3, the first planet carrier 11 and the second planet carrier 21 are coaxially arranged.
  • the power output from the external power source can be input from the input unit 3, and can be output from the first ring gear 13 and the second ring gear 23, respectively, after the differential action of the differential 100.
  • the first ring gear 13 can be connected to the left half shaft, and the left half shaft can be connected to the left wheel.
  • the second ring gear 23 can be connected to the right half shaft, and the right half shaft can be connected to the right side wheel.
  • the power output from the power source such as the engine and/or the motor can be output to the input unit 3 through the deceleration of the final drive, and the input unit 3
  • the first planet carrier 11 and the second planet carrier 21 are driven to rotate synchronously. If the vehicle is traveling on a smooth road surface and there is no turning at this time, the left wheel and the right wheel are theoretically rotated at the same speed.
  • the differential 100 does not function as a differential, and the first carrier 11 and the second carrier 21 are at the same speed.
  • the first ring gear 13 and the second ring gear 23 rotate at the same speed and in the same direction, and the first planetary gear 12 and the second planetary gear 22 only revolve and do not rotate. If the vehicle is driving on an uneven road surface or the vehicle is turning, the left and right wheels are theoretically different in rotational speed, and the rotational speeds of the first ring gear 13 and the second ring gear 23 are also different, that is, there is a difference in rotational speed.
  • the first planet gear 12 and the second planet gear 22 are both revolving Also rotating, the rotation of the first planet gear 12 and the second planet gear 22 causes one of the first ring gear 13 and the second ring gear 23 to increase speed, the other to decelerate, the speed increasing ring gear and the decelerating ring gear
  • the difference in rotational speed is the difference in rotational speed between the left and right wheels, thereby achieving differential action.
  • the differential 100 utilizes the principle of planetary differential, has higher space utilization in structure and connection form, smaller axial dimension, and is more advantageous in production and assembly.
  • a structural form can not only avoid the dimensional defects in the axial direction and the radial direction of the bevel gear, but also can better utilize the hollow space inside the main reduction driven gear, thereby achieving better space utilization and greatly facilitating the difference.
  • the overall arrangement of the speedometer 100 assembly and the limitation on the weight, as well as higher reliability and better transmission efficiency, are beneficial to improve the reliability of the power transmission chain and the power output fluency during cornering. This is more practical than a symmetrical bevel gear differential.
  • the first planet gear 12 and the second planet gear 22 partially overlap in the axial direction (left-right direction in Figures 6-7), that is, the first planet gear 12 is only partially overlapped with the second planet gear 22, the remaining portions are staggered, the overlapping portions of the first planet gear 12 and the second planet gear 22 are engageable with each other, and the staggered portions are engageable with the respective ring gears.
  • the first planetary gear 12 may include a first tooth portion 151 and a second tooth portion 152 (with a broken line of K2 in FIG. 7), and the second planetary gear 22 may include a third tooth portion. 153 and the fourth tooth portion 154 (with a broken line of K1 in FIG. 7), the second tooth portion 152 and the third tooth portion 153 constitute an overlapping portion, that is, the second tooth portion 152 and the third tooth portion 153 are axially aligned.
  • the first tooth portion 151 and the fourth tooth portion 154 are axially offset and mesh with the corresponding ring gears, that is, the first tooth portion 151 is meshed with the first ring gear 13 and the fourth tooth portion 154 is overlapped and engaged.
  • the second ring gear 23 is engaged. It should be noted that the positions of the broken lines K1 and K2 can be adjusted according to actual conditions, and are not limited herein.
  • the axial dimension of the differential 100 is made more compact, and the volume of the differential 100 is more compact, which facilitates the installation and arrangement of the differential 100.
  • the number of teeth of the first ring gear 13 is equal to the number of teeth of the second ring gear 23, and the number of teeth of the first planet gear 12 is equal to the number of teeth of the second planet gear 22.
  • the first planetary gear 12 and the second planetary gear 22 are both spur gears, and the differential 100 using the spur gear is more compact in structure than the conventional symmetrical bevel gear differential, in particular It has higher space utilization in structure and connection form, smaller axial dimension, and is more advantageous in production and assembly.
  • first ring gear 13 and the second ring gear 23 will be described in detail below in conjunction with specific embodiments.
  • the first ring gear 13 and the second ring gear 23 are symmetric structures, in other words, the first ring gear 13 and the second ring gear 23 are symmetrically arranged, which can increase the versatility of the ring gear and reduce cost.
  • each of the first ring gear 13 and the second ring gear 23 includes a main body flat plate portion 161 and an annular side wall portion provided at an outer peripheral edge of the main body flat plate portion 161.
  • the main body flat portion 161 and the ring side Wall portion 162 can be an integrally formed component.
  • a plurality of gear teeth are disposed on the inner wall surface of the annular side wall portion 162, and the cavity A1, A2 is defined between the main body flat plate portion 161 and the annular side wall portion 162, that is, the main body flat portion 161 and the annular side of the first ring gear 13
  • a cavity A1 is defined between the wall portions 162, and a cavity A2 (FIG.
  • the installation space A is such that the structure of the differential 100 is relatively more compact, takes up less volume, and is easier to arrange, while the first ring gear 13 and the second ring gear 23 function as an outer casing to protect the housing therein.
  • the planet carrier and planet wheels enhance life.
  • the installation space A defined by the first ring gear 13 and the second ring gear 23 is relatively closed, and the external debris is not easily entered into the installation space A to affect the moving parts, thereby ensuring stable operation of the differential 100.
  • the input 3 is configured as an input gear.
  • the input end gear 3 is configured to be annular (the teeth of the input end gear 3 are formed on the outer peripheral surface) and sleeved on the outer surfaces of the first ring gear 13 and the second ring gear 23, It is understood that the inner diameter of the input end gear 3 may be larger than the outer diameters of the first ring gear 13 and the second ring gear 23, such that the input end gear 3 is placed outside the first ring gear 13 and the second ring gear 23 The components inside the two ring gears are not exposed, protecting the components inside the ring gear.
  • the first ring gear 13 and the second ring gear 23 are provided with a gap D in the axial direction, that is, the first ring gear 13 and the second ring gear 23 are axially spaced apart from each other, not Closely fit.
  • the width of the meshing portion of the first planet gear 12 and the second planet gear 22 determines the size of the gap D to some extent (in addition, the extending arm portion 63 of the intermediate connecting structure 6)
  • the thickness may also determine the gap D, which will be explained below.
  • the width D of the meshing portion of the two planet gears 22 is used to determine the gap D as an example, that is, the meshing of the first planet gear 12 with the second planet gear 22
  • the width of the portion may be equal to the minimum value of the gap D, so that by controlling the width of the meshing portion of the first planet gear 12 and the second planet gear 22, the size of the gap D can be indirectly controlled, for those skilled in the art,
  • the first planetary gear 12 and the second planetary gear 22 are ensured to stably transmit power and the service life of the first planetary gear 12 and the second planetary gear 22, and the first planetary gear 12 and the second planetary gear 22 can be meshed.
  • the width of the portion is relatively narrow, so that the gap D can be effectively reduced, so that the axial dimension of the differential 100 is smaller, more compact, and easier to arrange.
  • the input gear 3 surrounds and covers the gap D.
  • the sealing space of the installation space A is better, and the external debris is more difficult to enter into the installation space A to affect the moving parts, thereby further ensuring the stable operation of the differential 100, and at the same time saving the difference at least to some extent.
  • the axial space and radial space of the speeder are better, and the external debris is more difficult to enter into the installation space A to affect the moving parts, thereby further ensuring the stable operation of the differential 100, and at the same time saving the difference at least to some extent.
  • the input end gear 3 is the main reducer driven gear.
  • the hollow space inside the main reduction driven gear can be better utilized, thereby achieving better space utilization, and greatly facilitating the whole vehicle layout of the differential 100 assembly. Set and limit the weight.
  • the first ring gear 13 and the second ring gear 23 both include the main body flat plate portion 161 and the annular side wall portion 162, and the above FIG. 4 (combined view)
  • the gap D of 1 - 2) refers to the 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.
  • each of the first ring gear 13 and the second ring gear 23 further includes an annular flange portion 163, an annular flange The portion 163 extends from the end surface of the annular side wall portion 162 in a direction away from the main body flat portion 161.
  • the inner diameter of the annular flange portion 163 may be substantially equal to the outer diameter of the annular side wall portion 162, such that the ring The flange portion 163 corresponds to protrude outward in the radial direction from the annular side wall portion 162 (that is, the outer circumferential surface of the first ring gear 13 or the second ring gear 23).
  • 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, that is, The thickness of the annular flange portion 163 is thinner than the thickness of the annular side wall portion 162.
  • the gap D between the two ring gears refers to the gap between the annular side wall portions 162 of the two ring gears.
  • the gap D between the two ring gears refers to the gap between the annular flange portions 163 of the two ring gears.
  • the intermediate connection structure 6 will be described in detail below in conjunction with a specific embodiment.
  • the intermediate connection structure 6 functions to connect the first planet carrier 11 and the second planet carrier 21 to the input portion 3 such that the first planet carrier 11, the second planet carrier 21 and the input
  • the part 3 can be coaxially linked.
  • the intermediate connection structure 6 can also be fixedly connected to the first planet carrier 11 and the second planet carrier 21, respectively, and the input portion 3 is fixed to the outer surface of the intermediate connection structure 6, and the first planet carrier 11 can also be made.
  • the two planet carriers 21 and the input unit 3 can be coaxially linked.
  • the present invention provides a possible embodiment for the specific construction of the intermediate connection structure 6, which of course does not mean or suggest that the intermediate connection structure 6 of the present invention can only adopt the structure of this embodiment. That is, the intermediate connection structure 6 to be described in the following embodiments is only one possible implementation manner, and is not a limitation on the scope of protection of the present invention.
  • the input portion 3 in this embodiment is an annular input end gear 3
  • the intermediate connection structure 6 includes a first connection bracket 61 and a second connection bracket 62, and the first connection bracket 61 is used for connection.
  • the first carrier 11 and the input portion 3 (ie, the input end gear 3), and the second connecting bracket 62 is used to connect the second carrier 21 with the input portion 3 (ie, the input end gear 3), wherein the first connecting bracket 61 and the
  • the two connection brackets 62 may have the same structure, and each may include: a central body portion 64 and an extension arm portion 63 (in conjunction with FIG. 5), wherein the central body portion of the first connection bracket 61 and the central body of the second connection bracket 62
  • the portions may be integrally formed to form a common central body portion, but are not limited thereto.
  • the thickness of the extending arm portion 63 also determines the size of the gap D to some extent. Specifically, when the meshing width of the two planet wheels is equal to the overall thickness of the extending arm portion 63, the gap D can be sized to two planets The meshing width of the wheel or the overall thickness of the extended arm portion 63 is substantially equal. When the overall thickness of the extending arm portion 63 is greater than the meshing width of the two planet wheels, the gap D may be substantially equal in size to the entire thickness of the extending arm portion 63.
  • the gap D may be substantially equal to the meshing width of the two planet wheels.
  • the overall thickness of the extending arm portion 63 refers to the sum of the thickness of the extending arm portion 63 of the first connecting bracket 61 and the thickness of the extending arm portion 63 of the second connecting bracket 62.
  • the plurality of extending arm portions 63 are provided on the outer peripheral surface of the center body portion 64, and the plurality of extending arm portions 63 and the central body portion 64 may be integrally formed, but are not limited thereto.
  • the plurality of extension arm portions 63 are generally radially distributed around the central body portion 64. In the example of Fig. 5, the extension arm portions 63 are three and equally spaced.
  • the extension arm portion 63 is for connection with the input portion 3.
  • the outer end of the extension arm portion 63 may extend to and be fixed to the inner peripheral surface of the input portion 3, such as an annular final drive driven gear.
  • Each set of correspondingly engaged first planet gears 12 and second planet gears 22 are located between adjacent two extension arm portions 63, as in the example of Figure 5, the extension arm portions 63 are three, the three extensions The arm portion 63 defines three receiving chambers (each adjacent two extending arm portions 63 and an inner peripheral surface of the input end gear 3 define a receiving cavity), and each of the receiving chambers may be provided with a pair of first engaged The planet gear 12 and the second planet gear 22, such that the overall structure of the differential 100 is more compact, while making the center of gravity of the differential 100 closer to or at a central position, greatly improving the eccentricity of the differential 100 during high speed operation or The large eccentricity causes the differential 100 to be unstable in operation and low in life.
  • the first ring gear 13 may be coaxially coupled to the first output shaft 41
  • the second ring gear 23 may be coaxially coupled to the second output shaft 42.
  • the first carrier 11 is coaxially coupled to the first carrier shaft 111
  • the second carrier 21 is coaxially coupled to the second carrier shaft 211.
  • the first output shaft 41 can be It is a hollow shaft and can be coaxially sleeved on the first planet carrier shaft 111.
  • the second output shaft 42 can also be a hollow shaft and coaxially sleeved on the second planet carrier shaft 211.
  • the first carrier shaft 111 is coaxially fixed to the central body portion 64 of the first connecting bracket 61
  • the second carrier shaft 211 is coaxially fixed to the central body portion 64 of the second connecting bracket 62, but is not limited thereto.
  • first ring gear 13 and the second ring gear 23 have the same radial dimension, and each of the first ring gear 13 and the second ring gear 23 may be an integrally formed member.
  • the differential 100 according to an embodiment of the present invention has been described in detail above, and the remaining structure of the power drive system 1000 will be described in detail below.
  • the transmission 104 can include a plurality of input shafts 101, 102 and a power take-off shaft 103.
  • the power take off shaft 103 of the transmission 104 may be one, but is not limited thereto.
  • the power output shaft 103 is disposed in linkage with the input unit 3.
  • the power output shaft 103 is provided with an output gear 110, and the output gear 110 is meshed with the input unit 3.
  • the output gear 110 and the input portion 3 constitute a final drive, wherein the output gear 110 is configured as a main reducer drive gear, and the input portion 3 is correspondingly configured as a main reducer. Driven gear.
  • the structure of the power drive system 1000 is made more compact, and the differential 100 is built inside the driven gear of the final drive, so that the differential 100 can better utilize the internal space, facilitating the arrangement of the entire power drive system 1000.
  • One of the plurality of input shafts 101, 102 is arranged to be selectively engageable with the power take-off shaft 103.
  • one of the input shafts such as the first input shaft 101 (the second input shaft 102 in FIG. 11) can be linked with the power output shaft 103, and one of the input shafts is the first input shaft.
  • the 101 can also be disconnected from the power output shaft 103.
  • the remaining input shafts are all arranged in conjunction with the power output shaft 103. That is, when the input shafts are operated, the power output shaft 103 also follows the action, or the power output shaft 103 operates, and the input shafts also operate.
  • the first motor generator 401 is disposed in linkage with the one input shaft, such as the first input shaft 101, that is, the input shaft that is linked with the first motor generator 401 is selectively linked with the power output shaft 103.
  • Input shaft In some embodiments, the power take-off shaft 103 is provided with an idler driven gear 108, and the idler driven gear 108 is coupled with one of the input shafts.
  • the synchronizer 109 is configured to synchronize the power output shaft 103 with the air.
  • the set of driven gears 108 is configured to synchronize the power output shaft 103 with the air.
  • the synchronizer 109 when the synchronizer 109 is in the engaged state, the synchronizer 109 synchronizes the idler driven gear 108 and the power output shaft 103 so that the power from the first motor generator 401 can be engaged by the synchronizer 109.
  • the power output shaft 103 is output to the differential 100, and when the synchronizer 109 is in the off state, the first motor generator 401 is equivalent to being disconnected from the power output shaft 103.
  • the synchronizer 109 functions as a power switch of the first motor generator 401, and can control the output and disconnection of the power of the first motor generator 401.
  • the synchronizer 109 is disposed on the power take-off shaft 103 and is configured to engage the idler driven gear 108. Thereby, the structure is simple and easy to implement.
  • the power output shaft 103 is fixedly provided with a fixed driven gear 107, and the fixed driven gear 107 is interlocked with the remaining input shafts, that is, the input shaft 101 in the above embodiment of FIG. 10 or the input shaft 102 in the embodiment of FIG. 11 is removed. .
  • the power output shaft 103 is fixedly fixedly provided with a fixed driven gear 107
  • the empty sleeve has an idler driven gear 108
  • the input shaft is correspondingly fixedly provided with a fixed driving gear.
  • 105, 106, the idler driven gear 108 and the fixed driven gear 107 are respectively meshed with the corresponding fixed driving gears.
  • the total number of idler driven gears 108 and fixed driven gears 107 is the same as the number of fixed drive gears.
  • the number of the idler driven gear 108 and the fixed driven gear 107 is one.
  • the number of the fixed driving gears is two, the idler driven gear 108 and a fixed driving gear. Engagement constitutes a pair of gear pairs, and the fixed driven gear 107 meshes with another fixed drive gear to form another pair of gear pairs.
  • the transmission speed ratios of the two pairs of gear pairs are different, so the transmission 104 in this embodiment has two transmission gears of different speed ratios, so that the structure of the power drive system 1000 is relatively simple and compact, and can also satisfy the vehicle. The requirement of the normal driving speed ratio.
  • the plurality of input shafts include a first input shaft 101 and a second input shaft 102
  • the first input shaft 101 can be a solid shaft
  • the second input shaft 102 can be a hollow shaft
  • the sleeve 102 is disposed on the first input shaft 101.
  • 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 the axial length of the second input shaft 102.
  • One end of an input shaft 101 such as a right end, may extend from the interior of the second input shaft 102.
  • 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, and the first fixed driving gear 106 is fixedly disposed on the first input shaft 101.
  • the second fixed driving gear 105 is fixedly disposed on the second input shaft 102.
  • the idler driven gear 108 meshes with the first fixed drive gear 106
  • the fixed driven gear 107 meshes with the second fixed drive gear 105.
  • the first motor generator 401 is interlocked with the first input shaft 101, for example, the first motor generator 401 is interlocked with the first fixed driving gear 106 through a gear structure.
  • the first motor generator 401 can be driven by the gear 402 and the gear 403 and the first fixed driving gear 106.
  • the gear ratio required by the first motor generator 401 can be obtained by appropriately designing the number of teeth of the gear.
  • the idler driven gear 108 meshes with the second fixed drive gear 105
  • the fixed driven gear 107 meshes with the first fixed drive gear 106.
  • the first motor generator 401 is interlocked with the second input shaft 102, for example, the first motor generator 401 is coupled to the second fixed driving gear 105 through a gear structure.
  • the first motor generator 401 can be driven by the gear 402, the gear 403, the gear 404, the gear 405, and the second fixed driving gear 105.
  • the gear 404 and the gear 405 can be fixed on the same shaft 406, and the gear is properly designed. The number of teeth can obtain the required transmission ratio of the first motor generator 401.
  • the powertrain system 1000 can also include an engine 301 that is configured to selectively engage at least one of the plurality of input shafts.
  • the input shaft is two and a dual clutch 204 is disposed 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 can be two driven discs of the dual clutch 204, the third engagement
  • the portion 203 can be a housing of the dual clutch 204, at least one of the two driven disks can selectively engage the housing, that is, at least one of the first engagement portion 201 and the second engagement portion 202 can be selectively
  • the third joint portion 203 is joined to the ground.
  • the two driven disks can also be completely disconnected from the housing, that is, both the first engaging portion 201 and the second engaging portion 202 are in an open state with the third engaging portion 203.
  • the engine 301 is coupled to a third engagement portion 203, the first input shaft 101 is coupled to the first engagement portion 201, and the second input shaft 102 is coupled to the second engagement portion 202.
  • 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.
  • the second electric The generator 501 is interlocked with the first ring gear 13, and the third motor generator 503 is interlocked with the second ring gear 23.
  • the outer peripheral surface of the first ring gear 13 is provided with a first outer tooth 505, and the first outer tooth 505 may be integrally formed on the outer circumferential surface of the first ring gear 13.
  • the outer peripheral surface of the second ring gear 23 is provided with a second outer tooth 506, and the second outer tooth 506 is integrally formed on the outer peripheral surface of the second ring gear 23.
  • the second motor generator 501 is interlocked with the first external teeth 505, and the third motor generator 503 is interlocked with the second external teeth 506.
  • the motor shaft of the second motor generator 501 may be provided with a gear 502, the gear 502 meshes with the first external tooth 505, and the motor shaft of the third motor generator 503 may be provided with a gear 504, the gear 504 Engaged with the second outer teeth 506.
  • the manner in which the second motor generator 501 and the first ring gear 13 and the third motor generator 503 and the second ring gear 23 are interlocked is not limited to the manner described herein.
  • the second motor generator 501 and the third motor generator 503 are symmetrically distributed left and right with respect to the differential 100 such that the center of gravity of the power drive system 1000 can be centered or closer to the center position.
  • the input shaft includes a first input shaft 101, a second input shaft 102, and a third input shaft 1003.
  • the third input shaft 1003 can be a hollow shaft and sleeved on the second input shaft 102, the second input.
  • the shaft 102 can also be a hollow shaft and sleeved on the first input shaft 101, and the three input shafts can be coaxially arranged.
  • the engine 301 is coupled to the first input shaft 101, the second input shaft 102, and the third input shaft 1003 via a three clutch 205.
  • the three clutch 205 has a first driven disc 206, a second driven disc 207, a third driven disc 208, and a housing 209, and the housing 209 is selectively engageable with the first driven disc 206, the second At least one of the driven disc 207 and the third driven disc 208 is engaged, the first input shaft 101 is coupled to the first driven disc 206, and the second input shaft 102 is coupled to the second driven disc 207.
  • the third input shaft 1003 Connected to the third driven disk 208, the engine 301 is coupled to the housing 209.
  • the first driven disk 206, the second driven disk 207, and the third driven disk 208 are distributed in the axial direction.
  • the first driven disk 206, the second driven disk 207, and the third driven disk 208 are distributed in the radial direction.
  • the first engaging portion 201 is engaged with the third engaging portion 203
  • the second engaging portion 202 is disconnected from the third engaging portion 203
  • the synchronizer 109 is in an engaged state, at which time the power generated by the engine 301 passes through the first input shaft 101,
  • the power take-off shaft 103 is then output to the differential 100, and the differential 100 distributes the power to the drive wheels on both sides.
  • the second engaging portion 202 is engaged with the third engaging portion 203, the first engaging portion 201 is disconnected from the third engaging portion 203, and the synchronizer 109 is in an open state, at which time the power generated by the engine 301 passes through the second input shaft. 102.
  • the power output shaft 103 is output to the differential 100, and the differential 100 distributes the power to the drive wheels on both sides.
  • the dual clutch 204 is completely disconnected, the synchronizer 109 is in the engaged state, and the power generated by the first motor generator 401 is output to the differential 100 through the first input shaft 101 and the power output shaft 103, and the differential 100 is received by the differential 100.
  • Power division The drive wheels on both sides are assigned.
  • the first engaging portion 201 is engaged with the third engaging portion 203, the second engaging portion 202 is disconnected from the third engaging portion 203, and the synchronizer 109 is in an open state, at which time the power generated by the engine 301 passes through the first input shaft.
  • the 101 is output to the first motor generator 401, and drives the first motor generator 401 to generate electric power as an electric motor to realize a parking power generation function.
  • the main difference between the embodiment of FIG. 11 and the embodiment of FIG. 10 is that the first motor generator 401 is interlocked with the second input shaft 102, and the embodiment of FIG. 10 is that the first motor generator 401 is linked with the first input shaft 101. Some will not go into details.
  • the first ring gear 13 is coupled to the left front wheel 910a, such as the first ring gear 13 is coaxially coupled to the left front wheel 910a, and the second ring gear 23 is right.
  • the front wheel 910b is interlocked, for example, the second ring gear 23 is coaxially connected with the right front wheel 910b.
  • the fourth motor generator 901 is interlocked with the left rear wheel 910c through a gear structure.
  • the fourth motor generator 901 is interlocked with the left rear wheel 910c via the gears W1, W2, W3, and W4, and the gear W1 is coaxial with the fourth motor generator 901.
  • the gear W1 meshes with the gear W2
  • the gear W2 is coaxially coupled to the gear W3
  • the gear W3 meshes with the gear W4
  • the gear W4 can be fixedly disposed on the left half shaft 904
  • the left rear axle 910c is disposed on the left half shaft 904.
  • the fifth motor generator 902 is interlocked with the right rear wheel 910d through a gear structure, such as the fifth motor generator 902 is coupled with the right rear wheel 910d through the gears X1, X2, X3, X4, the gear X1 and the fifth motor generator
  • the 902 is coaxially connected, the gear X1 is meshed with the gear X2, the gear X2 is coaxially connected with the gear X3, the gear X3 is meshed with the gear X4, the gear X4 is fixedly disposed on the right half shaft 905, and the right rear wheel is provided on the right half shaft 905. 910d.
  • the anti-skid synchronizer 903 is provided for the synchronizing gear W4 and the gear X4, for example, the anti-skid synchronizer 903 is disposed on the gear W4 and is used to engage the gear X4.
  • the anti-skid synchronizer 903 is provided for the synchronizing gear W1 and the gear X1, for example, the anti-skid synchronizer 903 is disposed on the gear W1 and is used to engage the gear X1.
  • the anti-skid synchronizer 903 is provided for the synchronizing gear W2 and the gear X2, for example, the anti-skid synchronizer 903 is disposed on the gear W2 and is used to engage the gear X2.
  • the anti-skid synchronizer 903 is configured to synchronize the left and right axles 904, 905, such as the anti-skid synchronizer 903, on the left axle 904 and for engaging the right axle 905, this embodiment
  • the fourth fourth motor generator 901 and the fifth motor generator 902 are both wheel motors.
  • the anti-skid synchronizer 903 is arranged to selectively synchronize the left rear wheel 910c and the right rear wheel 910d, in other words, when the anti-slip synchronizer 903 is in the engaged state, the left rear wheel 910c and the right rear wheel 910d will rotate synchronously, ie At the same speed and in the same direction, the left rear wheel 910c and the right rear wheel 910d do not rotate at a differential speed.
  • the fourth motor generator 901 can separately drive the left rear wheel 910c
  • the fifth motor generator 902 can separately drive the right rear wheel 910d, and the two rear wheels are independent of each other and do not interfere with each other. In order to achieve the differential rotation function of the wheel.
  • 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, thereby enabling The technical solutions and/or technical features interact and support each other functionally, and the combined solution has a superior technical effect.
  • a person skilled in the art can partially overlap the first planet gear 12 and the second planet gear 22 with a scheme in which the first planet carrier 11 and the second planet carrier 21 are plate-shaped structures, which can effectively reduce the differential.
  • the axial dimension of 100 makes the differential 100 smaller.
  • a person skilled in the art can combine the scheme in which the first planetary gear 12 and the second planetary gear 22 partially overlap with the solution in which the planetary gear and the carrier are housed in the installation space, so that the shaft of the differential 100 can be effectively reduced.
  • a person skilled in the art may adjust the revolving axis of the first planet gear 12 to the revolving axis of the second planet gear 22 and the revolving radius of the first planet gear 12 to be the same as the revolving radius of the second planet gear 22 .
  • the combination makes the structure of the differential 100 more compact, smaller in size, and easier to arrange.
  • the input portion 3 can better utilize the hollow space inside the main reduction driven gear, thereby achieving better space utilization, greatly facilitating the overall vehicle layout of the differential assembly and the weight.
  • the input part 3 can configure the input part 3 as a combination of the annular input end gear and the input end gear 3 to surround and cover the gap, so that on the one hand, the structure of the differential 100 is relatively compact, and the gear 3 is input through the input end.
  • the cover gap can also make the installation space defined by the shells of the two planetary gear trains relatively more closed, fully protecting the components inside the installation space and improving the service life thereof.
  • the differential 100 can effectively save space and reduce weight.
  • the planetary gear differential 100 is compared to a conventional bevel gear differential.
  • the weight can be reduced by about 30%, while the axial dimension is reduced by about 70%, which not only reduces the friction of the bearing, but also achieves the torque of the left and right wheels.
  • the distribution makes the load distribution of the differential 100 more reasonable, the differential 100 is more rigid, and the transmission efficiency is also improved due to the use of the spur gear, for example, the efficiency of the conventional bevel gear transmission of the 6-level precision and the 7-level precision is about 0.97 ⁇ 0.98, and the efficiency of spur gear transmission with 6-level accuracy and 7-level precision is about 0.98-0.99.
  • the cylindrical gear reduces the working noise of the differential 100, reduces the heat generation, and greatly improves the differential speed.
  • the differential 100 according to the embodiment of the present invention has many advantages such as light weight, small size, low cost, high transmission efficiency, low noise, low heat generation, and high life.
  • the differential 100 according to the embodiment of the present invention can omit the sun gear, the elimination of the sun gear can have the following advantages:
  • the sun gear should be canceled instead of using the ring gear to achieve the differential speed, because the number of teeth of the ring gear can be set more than the sun gear, and the pitch circle is larger (the pitch circle refers to the node at the gear meshing transmission).
  • a pair of tangent circles are tangential, so that the load and the withstand torque can be distributed more evenly, which is advantageous for the improvement of the life of the differential 100.
  • there is no sun wheel and the lubrication and cooling of the differential 100 can be better realized. That is to say, since the sun gear is eliminated, a cavity can be formed inside the ring gear, and the ring gear meshes with the planetary gear to belong to the inner mesh.
  • the lubricating oil can be stored in the ring gear, and the cooling and lubrication effect is greatly improved.
  • the sun gear is eliminated, the components are reduced, the quality and cost of the differential 100 are reduced, and the differential 100 is further reduced in size and weight.
  • the power drive system 1000 having the differential 100 has obvious advantages mainly in space and in the drive mode.
  • the power drive system 1000 is particularly suitable for In a new energy vehicle, since the powertrain of the new energy vehicle is generally disposed in the engine compartment, the powertrain not only has a transmission, an engine, but also at least one electric motor, and adopts a compact according to an embodiment of the present invention due to limited space in the engine compartment.
  • the differential 100 is capable of gaining an advantage in space and is more convenient to arrange.
  • the axial dimension of the differential 100 according to the embodiment of the present invention is greatly reduced, the axial space is better arranged, and the differential 100 has two ring gears as power.
  • the output can better achieve a power connection to the two motors (as described above for connecting the motor through the external gear of the ring gear), which is difficult to achieve on conventional conical differentials.
  • the vehicle 10000 includes the power drive system 1000 in the above embodiment, and the power drive system 1000 can be used for a front drive, and of course, for a rear drive.
  • the present invention is not particularly limited thereto. It should be understood that other configurations of the vehicle 10000, such as the brake system, the travel system, the steering system, and the like, according to embodiments of the present invention are known in the art and are well known to those skilled in the art, and therefore will not be described herein. .

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Abstract

La présente invention concerne un système d'entraînement de puissance comprenant un différentiel (100). Le différentiel (100) comprend un premier porte-satellites (11), une première roue planétaire (12), une première couronne dentée (13), un second porte-satellites (21), une seconde roue planétaire (22) et une seconde couronne dentée (23), la première et la seconde roue planétaire étant respectivement raccordées aux premier et second porte-satellites, la première et la seconde roue planétaire étant respectivement en prise avec les première et seconde couronnes dentées, et la seconde roue planétaire (22) étant également en prise avec la première roue planétaire (12). Le dispositif comprend en outre une partie d'entrée (3), la partie d'entrée (3) et les premier et second porte-satellites étant reliés de manière coaxiale ; un arbre de sortie de puissance (103), l'arbre de sortie de puissance (103) étant relié à la partie d'entrée (3) ; une pluralité d'arbres de sortie (101, 102), l'un de la pluralité d'arbres d'entrée (101, 102) étant éventuellement lié à l'arbre de sortie de puissance (103), et les autres arbres d'entrée (101, 102) étant reliés à l'arbre de sortie de puissance (103) ; et un premier moteur-générateur (401), le premier moteur-générateur (401) étant relié à l'un de la pluralité d'arbres d'entrée (101, 102). La présente invention concerne en outre un véhicule présentant le système d'entraînement de puissance susmentionné. Le différentiel susmentionné utilise le principe de différentiel planétaire pour réaliser une fonction différentielle, et sa structure est compacte et simple.
PCT/CN2016/097695 2015-09-25 2016-08-31 Système d'entraînement de puissance et véhicule utilisant celui-ci WO2017050101A1 (fr)

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CN111114276B (zh) * 2018-10-31 2022-10-18 比亚迪股份有限公司 混合动力驱动系统及车辆
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