CN117588530B - Planetary transmission, electric drive axle comprising planetary transmission and electric automobile - Google Patents
Planetary transmission, electric drive axle comprising planetary transmission and electric automobile Download PDFInfo
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- CN117588530B CN117588530B CN202410079163.7A CN202410079163A CN117588530B CN 117588530 B CN117588530 B CN 117588530B CN 202410079163 A CN202410079163 A CN 202410079163A CN 117588530 B CN117588530 B CN 117588530B
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 132
- 230000007704 transition Effects 0.000 claims description 19
- 239000010720 hydraulic oil Substances 0.000 claims description 16
- 230000009471 action Effects 0.000 claims description 12
- 230000007246 mechanism Effects 0.000 claims description 8
- 238000005265 energy consumption Methods 0.000 abstract description 4
- 238000010586 diagram Methods 0.000 description 6
- 125000006850 spacer group Chemical group 0.000 description 5
- 230000009467 reduction Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 238000002485 combustion reaction Methods 0.000 description 2
- 238000007792 addition Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/037—Gearboxes for accommodating differential gearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2718/00—Mechanisms for speed-change of planetary gearing, the speed change control being dependent on function parameters of the gearing
- F16H2718/08—Control dependent on speed
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
The invention belongs to the technical field of automobile transmission devices, and relates to a planetary transmission, an electric drive axle comprising the planetary transmission and an electric automobile, wherein the planetary transmission comprises a transmission unit and a clutch unit; the transmission unit comprises an input shaft, a sun gear, a planetary gear set, a first planet carrier, a second planet carrier, a gear ring and an output gear; the clutch unit includes a first clutch and a second clutch; the electric drive axle comprising the planetary transmission can obviously shorten an automobile transmission chain, has compact structure, greatly reduces the weight relative to the existing axle and transmission assembly, can effectively reduce the space occupied by transmission chain components, optimizes the space layout of a vehicle, improves the available space of drivers and passengers, has better power performance and lower energy consumption, and is provided with a limited slip differential, thereby well preventing the wheels from slipping.
Description
Technical Field
The invention belongs to the technical field of automobile transmission devices, and particularly relates to a planetary transmission, an electric drive axle comprising the planetary transmission and an electric automobile.
Background
In the transmission structure of an automobile, a conventional driving mode utilizes a gearbox to output power of an internal combustion engine, and the power passes through a transmission shaft and reaches an axle. At this time, power is distributed to the two half shafts by a differential in the axle, thereby driving the wheels to rotate. The driving chain of the driving mode has low driving efficiency, large energy loss and large volume of parts. Such an electrically driven vehicle axle is easy to industrialize if the internal combustion engine is replaced by only the electric motor, but requires high performance of the electric motor, and requires the electric motor to maintain a high-efficiency output over a wide range of rotational speed changes, which is liable to cause energy waste.
Another implementation of the electrically driven axle is that the output shaft of the motor is connected to a transmission, which in turn transmits power to a differential, where the motor, the transmission and the main shaft of the differential are parallel to each other, forming a driving unit. At present, the transmission connected with the electric drive axle has large integral structure, is difficult to assemble and occupies more vehicle layout space. Moreover, there is a need for improvements in the existing electrically driven axles in terms of effectively preventing wheel slip.
Disclosure of Invention
In order to solve the defects of the prior art in the background art, the invention provides the planetary transmission, the electric drive axle comprising the planetary transmission and the electric automobile.
The invention realizes the aim of the invention through the following technical scheme: a planetary transmission is provided, comprising a transmission unit and a clutch unit;
the transmission unit comprises an input shaft, a sun gear, a planetary gear set, a first planet carrier, a second planet carrier, a gear ring and an output gear; the sun gear is arranged on the input shaft, the sun gear is in meshed connection with the planetary gear set, the planetary gear set comprises three planetary gears, each planetary gear is arranged on a first planetary carrier and a second planetary carrier through a pin shaft, the first planetary carrier is arranged on the input shaft through a first deep groove ball bearing, the second planetary carrier is arranged on the input shaft through a second deep groove ball bearing, the planetary gears are in meshed connection with the gear ring, and the first planetary carrier is fixedly connected with the output gear through a third spline pair;
the clutch unit includes a first clutch and a second clutch;
the first clutch comprises an outer clutch shell, an inner clutch mounting bracket, a first outer friction plate set and a first inner friction plate set; the outer clutch housing is fixedly connected with the planetary transmission housing; the inner clutch shell and the inner clutch mounting bracket are fixedly connected together through bolts; the outer clutch shell is of an inner and outer cylinder structure with one end open, and an inner cylinder of the outer clutch shell is arranged on the input shaft through a first tapered roller bearing; a first disc spring and a first piston which is contacted with the first disc spring are arranged between the inner cylinder and the outer cylinder of the outer clutch shell, and a closed cavity enclosed by the first piston and the outer clutch shell is connected with a first hydraulic pipe; a first outer friction plate set and a first inner friction plate set are arranged in a cavity enclosed by the outer clutch shell and the inner clutch shell, the first outer friction plate set is fixedly connected with the outer clutch shell, and the first inner friction plate set is fixedly connected with the inner clutch shell; the first piston compresses the first outer friction plate group and the first inner friction plate group together against the elasticity of the first belleville spring under the action of hydraulic oil in the first hydraulic pipe, and the friction force between the first outer friction plate group and the first inner friction plate group is utilized to enable the first outer friction plate group and the first inner friction plate group to be fixedly connected, so that the outer clutch shell is fixedly connected with the inner clutch mounting bracket through the inner clutch shell, the inner clutch mounting bracket is fixedly connected with the gear ring through the first spline pair, and the gear ring is finally fixedly connected with the planetary transmission shell under the action of the hydraulic oil due to the fact that the outer clutch shell is fixedly connected with the planetary transmission shell;
The second clutch comprises an inner clutch shell, an inner clutch mounting bracket, a spline hub, a second outer friction plate group and a second inner friction plate group; the inner clutch shell is fixedly connected with the second outer friction plate set; the spline hub is arranged on the input shaft, one end of the spline hub is provided with an external spline, the other end of the spline hub is provided with an internal spline, the second planet carrier is provided with an external spline, the internal spline of the spline hub is matched with the external spline on the second planet carrier to form a second spline pair, the spline hub is fixedly connected with the second planet carrier through the second spline pair, and the spline hub is fixedly connected with a second internal friction plate group through the external spline; a second disc spring and a second piston which is in contact with the second disc spring are arranged in a closed space surrounded by the spline hub and the inner clutch housing, and a closed cavity surrounded by the second piston and the inner clutch housing is connected with a second hydraulic pipe; the second piston compresses the second outer friction plate group and the second inner friction plate group together against the elasticity of the second belleville spring under the action of hydraulic oil in the second hydraulic pipe, and the friction force between the second outer friction plate group and the second inner friction plate group is utilized to enable the second outer friction plate group and the second inner friction plate group to be fixedly connected; because the second outer friction plate set is fixedly connected with the inner clutch shell and the inner clutch mounting bracket, the inner clutch mounting bracket is fixedly connected with the gear ring through the first spline pair, and the second inner friction plate set is fixedly connected with the spline hub and the second planet carrier, when the second clutch works, the second piston finally enables the second planet carrier to be fixedly connected with the gear ring under the action of hydraulic oil in the second hydraulic pipe.
Further, the first outer friction plate group comprises a plurality of first outer friction plates, the first outer friction plates are discs with uniform external teeth, the external teeth of the first outer friction plates are matched with tooth grooves on the inner surface of the outer clutch shell, the first inner friction plate group comprises a plurality of first inner friction plates, the first inner friction plates are discs with uniform internal teeth, the internal teeth of the first inner friction plates are matched with the tooth grooves on the outer surface of the inner clutch shell, and the first outer friction plates are staggered with the first inner friction plates; the second outer friction plate group comprises a plurality of second outer friction plates, the second outer friction plates are discs with uniform external teeth, the external teeth of the second outer friction plates are matched with tooth grooves on the inner surface of the inner clutch shell, the second inner friction plate group comprises a plurality of second inner friction plates, the second inner friction plates are discs with uniform internal teeth, the internal teeth of the second inner friction plates are matched with spline grooves on the outer surface of the spline hub, and the second outer friction plates and the second inner friction plates are arranged in a staggered mode.
Further, one end of the input shaft connected with the motor is further provided with an elastic retainer ring at the outer side of the first deep groove ball bearing, the other opposite end is provided with threads, the input shaft is sequentially provided with a nut and a spacer bush from outside to inside through a thread pair, a first tapered roller bearing is arranged on the input shaft at the inner side of the spacer bush, the outer clutch housing is arranged on the first tapered roller bearing through an inner cylinder, the nuts are provided with two nuts, and an adjusting ring is arranged between the two nuts.
Further, the inner clutch housing is also of an inner cylinder structure with one end open, the setting direction of the closed end of the inner clutch housing is the same as that of the closed end of the outer clutch housing, the inner cylinder of the inner clutch housing is arranged on a second tapered roller bearing, the second tapered roller bearing is arranged on the input shaft, and a second disc spring and a second piston which is in contact with the second disc spring are arranged between the inner cylinder and the outer cylinder of the inner clutch housing.
Further, a retainer ring is arranged between the inner clutch housing and the outer clutch housing, and the retainer ring is sleeved on the stepped outer side wall of the inner clutch housing. The retainer ring is used for adjusting the gap between the inner clutch housing and the outer clutch housing.
Further, a third tapered roller bearing is arranged outside the first planet carrier, and the first planet carrier is mounted on the planetary transmission shell through the third tapered roller bearing.
Further, an input shaft of the planetary transmission is connected with an electric motor through a clutch, and the electric motor is connected with a storage battery through a control system.
The motor transmits power to the input shaft from the left side, and when the first clutch and the second clutch do not work, the sun gear, the planetary gear set and the gear ring are in a disordered state, namely, the power cannot be transmitted.
Low gear: the first clutch is engaged and the second clutch is disengaged, i.e.: the second clutch does not work, the first clutch works, hydraulic oil in the first hydraulic pipe enters the right cavity of the first piston of the first clutch, and because the outer clutch housing is fixed on the planetary transmission housing and does not rotate all the time, at the moment, the outer clutch housing, the inner clutch mounting bracket, the first outer friction plate group and the first inner friction plate group are connected into a whole, and are fixed and the gear ring is also fixed. A power transmission route: the motor transmits power to the input shaft from the left side, the input shaft drives the sun gear, the sun gear drives the planetary gear set, the planetary gear set rotates on the fixed gear ring, the planetary gear set drives the first planet carrier and the second planet carrier to jointly rotate, the first planet carrier drives the output gear to rotate through the third spline pair, the output gear outputs power to the outside, and the speed is output to the outside according to the reduction ratio of a planetary transmission unit consisting of the sun gear, the planetary gear set and the gear ring. After the motor is started, the sun gear rotates along with the input shaft, the sun gear is meshed with the planetary gear set, and the planetary gear set is meshed with the gear ring. The planetary gear set revolves around the sun gear while rotating, and the planet carrier rotates together with the planetary gear set simultaneously to realize speed reduction and transmit power to the output gear through the third spline pair.
High gear: the second clutch is engaged and the first clutch is disengaged, i.e.: the first clutch does not work, the second clutch works, hydraulic oil in the second hydraulic pipe enters a right cavity of a second piston of the second clutch, and at the moment, the second outer friction plate group, the second inner friction plate group, the spline hub, the second planet carrier, the inner clutch housing, the inner clutch mounting bracket and the gear ring are fixedly connected into a whole. A power transmission route: the motor transmits power to the input shaft from the left side, the input shaft drives the sun gear, the sun gear drives the planetary gear set, the planetary gear set drives the first planet carrier and the second planet carrier, and the second planet carrier is fixedly connected with the gear ring into a whole, so that a planetary transmission unit formed by the sun gear, the planetary gear set and the gear ring integrally rotates, the power is not output to the outside by decelerating any more, and at the moment, the rotation speed of an output gear on the first planet carrier is the same as the output rotation speed of the motor.
In a preferred embodiment of the present invention, the planetary gears in the planetary gear set are a first double gear, the first double gear includes a first driving gear and a first driven gear, the first driving gear and the first driven gear are fixedly mounted on the pin shaft, the first driven gear is meshed with the gear ring, and the first driving gear is meshed with a sun gear arranged on the input shaft.
In another preferred embodiment of the present invention, the planetary gears in the planetary gear set are second duplex gears, the second duplex gears comprise a second driving gear and a second driven gear, the second driving gear and the second driven gear are fixedly installed on the pin shaft, and the second driving gear is meshed with a sun gear arranged on the input shaft; one end of the pin shaft is fixedly arranged on the first planet carrier, the other end of the pin shaft is fixedly arranged on the second planet carrier, an inner spline is arranged on the side surface of the upper end part of the second planet carrier, an outer spline is arranged on the inner clutch mounting bracket, and the inner spline on the second planet carrier is fixedly connected with the outer spline on the inner clutch mounting bracket through a fourth spline pair; the output gear is a third duplex gear which is rotatably arranged outside the planet carrier, a third driving gear in the third duplex gear is meshed with a second driven gear in the second duplex gear, and the third driven gear in the third duplex gear outputs power outwards. In a low-speed gear, the first clutch is combined, the second clutch is disconnected, the second planet carrier is connected with the outer clutch shell, the inner clutch mounting support, the first outer friction plate group and the first inner friction plate group into a whole, the motor is fixed, the sun gear rotates along with the input shaft after being started, the sun gear is meshed with the second driving gear, the second driving gear and the second driven gear are fixedly arranged on the pin shaft, the second driven gear rotates along with the second driving gear, the third driving gear in the third duplex gear is meshed with the second driven gear of the second duplex gear, and the third driven gear in the third duplex gear outputs power outwards and has a transmission ratio of the planetary transmission. In the high gear, the first clutch is not operated, and the second clutch is operated. Because the second planetary gear set is provided with the fourth spline pair, the second planetary gear set, the inner clutch shell and the inner clutch mounting bracket are fixed together, and the second clutch is used for fixing the second outer friction plate set, the second inner friction plate set, the spline hub and the second planetary gear set, so that the input shaft, the sun gear, the second driving gear, the second driven gear and the third driving gear and the third driven gear in the third duplex gear form an integral locking, and at the moment, the output rotating speed of the third driven gear is the same as the output rotating speed of the motor.
The invention also provides an electric drive axle comprising the planetary transmissions, wherein the electric drive axle comprises any one of the planetary transmissions, an intermediate transition gear set and an axle in transmission connection with the planetary transmission through the intermediate transition gear set; the planetary transmission is arranged in a planetary transmission shell which is fixedly connected with the axle housing; the intermediate transition gear set comprises a first gear, a second gear and a third gear, the third gear and the second gear are coaxially arranged, the second gear is meshed with the first gear, the first gear is in transmission connection with a differential mechanism in an axle housing of an axle, and the third gear is meshed with an output gear of the planetary transmission.
Further, the axle comprises a left half shaft, a right half shaft, a hub and a brake drum which are arranged in pairs and are bilaterally symmetrical, the output ends of the left half shaft and the right half shaft are fixedly connected with the hub and the brake drum respectively, the brake drum is connected with an air chamber, the input ends of the left half shaft and the right half shaft are arranged in an axle housing of the axle and form a differential together with other components, and the differential is in transmission connection with a gear one of the intermediate transition gear sets.
Further, a first gear of the intermediate transition gear set is arranged on the transmission shaft, two ends of the transmission shaft are arranged in a first bearing, the first bearing is arranged in a bearing cover, and an adjusting nut is arranged outside the bearing cover.
Further, the axle further comprises a cam shaft bracket fixedly connected with the axle housing and an adjusting arm.
As an optimization, the differential is a limited slip differential, comprising a left half shaft, a left half shaft gear, a left shell, at least one left differential gear, a right half shaft gear, a right shell, at least one right differential gear and a middle shell; the left half shaft is connected with a left half shaft gear through a spline and is connected with a left shell through a bearing, and the left half shaft gear is meshed with a left differential gear; the right half shaft is connected with a right half shaft gear through a spline and is connected with a right shell through a bearing, and the right half shaft gear is meshed with a right differential gear; the left side shaft gear, the left differential gear, the right side shaft gear and the right differential gear form a limited slip differential gear set together, the limited slip differential gear set is positioned in a middle shell, and two sides of the middle shell are fixedly connected with the left shell and the right shell respectively; the left differential gear is rotatably arranged on the left end cover of the middle shell, and the right differential gear is rotatably arranged on the right end cover of the middle shell; the limited slip differential is in transmission connection with a gear one of the intermediate transition gear sets through a right half shaft or a left half shaft.
Further, the left differential gear and the right differential gear are respectively three, and are respectively and uniformly distributed on the left end cover and the right end cover of the middle shell.
The invention also provides an electric automobile, which adopts the electric drive axle comprising the planetary transmission as a drive axle.
Advantageous effects
1. The electric drive axle comprising the planetary transmission can obviously shorten an automobile transmission chain, has compact structure, greatly reduces the weight relative to the existing axle and transmission assembly, can effectively reduce the space occupied by transmission chain components, optimizes the space layout of a vehicle, improves the available space of drivers and passengers, and has better power performance and lower energy consumption.
2. The axle main transmission gear has the advantages that the axle main transmission gear is provided with the limited slip differential, so that the slipping phenomenon can be effectively prevented when the automobile slips.
3. The invention can realize the speed change of two gears by utilizing the planetary transmission.
Drawings
FIG. 1 is a schematic diagram showing the structural composition of a planetary transmission according to embodiment 1 of the present invention;
FIG. 2 is an enlarged view of FIG. 1 at A;
FIG. 3 is an enlarged view of FIG. 1 at B;
FIG. 4 is a simplified planetary transmission drive scheme of embodiment 1 of the present invention;
FIG. 5 is a schematic view of the structure of a first outer friction plate according to embodiment 1 of the present invention;
FIG. 6 is a schematic view of the structure of the first inner friction plate according to embodiment 1 of the present invention;
FIG. 7 is a schematic view of the inner clutch mounting bracket of embodiment 1 of the present invention;
fig. 8 is a schematic view showing the structure of a ring gear according to embodiment 1 of the present invention;
FIG. 9 is a schematic view of a spline hub structure according to embodiment 1 of the present invention;
FIG. 10 is a schematic structural diagram of a planetary transmission according to embodiment 2 of the present invention;
FIG. 11 is a simplified planetary transmission drive scheme of embodiment 2 of the present invention;
FIG. 12 is a schematic structural diagram showing a planetary transmission according to embodiment 3 of the present invention;
FIG. 13 is a simplified planetary transmission drive scheme of embodiment 3 of the present invention;
fig. 14 is a schematic diagram of an electrically driven bridge structure according to embodiment 1 of the present invention;
FIG. 15 is a left side view of the electrically driven bridge of FIG. 1;
FIG. 16 is a schematic diagram of an intermediate transition gearset structure according to embodiment 1 of the invention;
FIG. 17 is a top plan view of the intermediate transition gearset member of FIG. 16;
FIG. 18 is a schematic diagram of a differential mechanism structure according to an embodiment of the present invention;
in the figure: 1. planetary transmission housing, 2, hub, 3, brake drum, 4, camshaft, 5, axle, 6, differential, 61, left half shaft, 62, left housing, 63, left half shaft gear, 64, left differential gear, 65, intermediate housing, 651, left end cover, 652, right end cover, 66, right differential gear, 67, right half shaft gear, 68, right housing, 69, right half shaft, 7, air chamber, 8, axle housing, 9, camshaft carrier, 10, adjusting arm, 11, first gear, 12, second gear, 13, third gear, 14, output gear, 141, third driving gear, 142, third driven gear, 15, adjusting nut, 16, bearing cap, 17, drive shaft, 18, first bearing, 19, third tapered roller bearing, 20, first planet carrier, 21, first deep groove ball bearing, 22, circlip, 23, sun gear, 24, pin, 25, planetary gear set, 26, ring gear, 27, second carrier, 28, inner clutch mounting bracket, 29, inner clutch housing, 30, retainer ring, 31, outer clutch housing, 32, first piston, 33, first belleville spring, 34, first tapered roller bearing, 35, spacer, 36, adjusting ring, 37, nut, 38, first outer friction plate set, 39, first inner friction plate set, 40, second piston, 41, second outer friction plate set, 42, second inner friction plate set, 43, spline hub, 44, second belleville spring, 45, input shaft, 46, first double gear, 461, first driving gear, 462, first driven gear, 47, second double gear, 471, second driving gear, 472, second driven gear, 51, first spline pair, 52, second spline pair, 53, third spline pair, 54, first hydraulic pipe, 55, second hydraulic pipe, 56, fourth spline pair, 57. deep groove ball bearings II, 58, a second tapered roller bearing, C1, a first clutch, C2 and a second clutch.
Detailed Description
The invention will be further described with reference to the drawings and examples for the purpose of illustrating the features of the invention.
Referring to fig. 1 to 9, in the planetary transmission of embodiment 1, the embodiment of the present invention is implemented by the following technical scheme: a planetary transmission is provided, comprising a transmission unit and a clutch unit;
the transmission unit comprises an input shaft 45, a sun gear 23, a planetary gear set 25, a first planet carrier 20, a second planet carrier 27, a gear ring 26 and an output gear 14; the input shaft 45 is provided with a sun gear 23, the sun gear 23 is in meshed connection with a planetary gear set 25, the planetary gear set 25 comprises three planetary gears, each planetary gear is mounted on a first planetary carrier 20 and a second planetary carrier 27 through a pin shaft 24, the first planetary carrier 20 is mounted on the input shaft 45 through a first deep groove ball bearing 21, the second planetary carrier 27 is mounted on the input shaft 45 through a second deep groove ball bearing 57, the planetary gears are meshed with a gear ring 26, and the first planetary carrier 20 is fixedly connected with the output gear 14 through a third spline pair 53;
the clutch unit comprises a first clutch C1 and a second clutch C2;
the first clutch C1 includes an outer clutch housing 31, an inner clutch housing 29, an inner clutch mounting bracket 28, a first outer friction plate set 38 and a first inner friction plate set 39; the outer clutch housing 31 is fixedly connected to the planetary transmission housing 1 (not shown in the drawings); the inner clutch housing 29 and the inner clutch mounting bracket 28 are fixedly connected together by bolts (not shown in the drawings); the outer clutch housing 31 has an inner and outer cylinder structure with one end open, and an inner cylinder of the outer clutch housing 31 is mounted on the input shaft 45 through a first tapered roller bearing 34; a first disc spring 33 and a first piston 32 contacting the first disc spring 33 are arranged between the inner cylinder and the outer cylinder of the outer clutch housing 31, and a closed chamber enclosed by the first piston 32 and the outer clutch housing 31 is connected with a first hydraulic pipe 54; a first outer friction plate set 38 and a first inner friction plate set 39 are arranged in a cavity enclosed by the outer clutch housing 31 and the inner clutch housing 29, the first outer friction plate set 38 is fixedly connected with the outer clutch housing 31, and the first inner friction plate set 39 is fixedly connected with the inner clutch housing 29; the first piston 32 compresses the first outer friction plate set 38 and the first inner friction plate set 39 together against the elastic force of the first belleville spring 33 under the action of hydraulic oil in the first hydraulic pipe 54, and the friction force between the first outer friction plate set 38 and the first inner friction plate set 39 is utilized to enable the first outer friction plate set 38 and the first inner friction plate set 39 to be fixedly connected, so that the outer clutch housing 31 is fixedly connected with the inner clutch mounting bracket 28 through the inner clutch housing 29, the inner clutch mounting bracket 28 is fixedly connected with the gear ring 26 through the first spline pair 51, and the outer clutch housing 31 is fixedly connected with the planetary transmission housing 1, so that the first piston 32 finally enables the gear ring 26 to be fixedly connected with the planetary transmission housing 1 under the action of hydraulic oil when the first clutch C1 works;
The second clutch C2 includes an inner clutch housing 29, an inner clutch mounting bracket 28, a spline hub 43, a second outer set of friction plates 41, and a second inner set of friction plates 42; the inner clutch housing 29 is fixedly connected with the second outer friction plate set 41 through an inner spline; the spline hub 43 is mounted on the input shaft 45, one end of the spline hub 43 is provided with an external spline, the other end of the spline hub 43 is provided with an internal spline, the second planet carrier 27 is provided with an external spline, the internal spline of the spline hub 43 is matched with the external spline on the second planet carrier 27 to form a second spline pair 52, the spline hub 43 is fixedly connected with the second planet carrier 27 through the second spline pair 52, and the spline hub 43 is fixedly connected with the second inner friction plate group 42 through the external spline; a second belleville spring 44 and a second piston 40 contacting the second belleville spring 44 are arranged in a closed space enclosed by the spline hub 43 and the inner clutch housing 29, and a closed cavity enclosed by the second piston 40 and the inner clutch housing 29 is connected with a second hydraulic pipe 55; the second piston 40 compresses the second outer friction plate group 41 and the second inner friction plate group 42 together against the elastic force of the second belleville spring 44 under the action of hydraulic oil in the second hydraulic pipe 55, and the friction force between the second outer friction plate group 41 and the second inner friction plate group 42 is utilized to enable the second outer friction plate group 41 and the second inner friction plate group 42 to be fixedly connected; because the second outer friction plate set 41 is fixedly connected with the inner clutch housing 29 and the inner clutch mounting bracket 28, the inner clutch mounting bracket 28 is fixedly connected with the gear ring 26 through the first spline pair 51, and the second inner friction plate set 42 is fixedly connected with the spline hub 43 and the second planet carrier 27, when the second clutch C2 works, the second piston 40 finally makes the second planet carrier 27 fixedly connected with the gear ring 26 under the action of hydraulic oil in the second hydraulic pipe 55.
The first outer friction plate set 38 includes a plurality of first outer friction plates, the first outer friction plates are discs with uniform external teeth, the external teeth of the first outer friction plates are matched with the tooth grooves of the inner surface of the outer clutch housing 31, the first inner friction plate set 39 includes a plurality of first inner friction plates, the first inner friction plates are discs with uniform internal teeth, the internal teeth of the first inner friction plates are matched with the tooth grooves of the outer surface of the inner clutch housing 29, and the first outer friction plates are staggered with the first inner friction plates; the second outer friction plate set 41 includes a plurality of second outer friction plates, the second outer friction plates are discs with uniform external teeth, the external teeth of the second outer friction plates are matched with the tooth grooves of the inner surface of the inner clutch housing 29, the second inner friction plate set 42 includes a plurality of second inner friction plates, the second inner friction plates are discs with uniform internal teeth, the internal teeth of the second inner friction plates are matched with the spline grooves of the outer surface of the spline hub 43, and the second outer friction plates are staggered with the second inner friction plates.
The one end of the input shaft 45 connected with a motor (not shown in the figure), the outside of the first deep groove ball bearing 21 is also provided with an elastic retainer ring 22, the opposite end is provided with threads, the input shaft 45 is sequentially provided with a nut 37 and a spacer 35 from outside to inside through a thread pair, the input shaft 45 at the inner side of the spacer 35 is provided with a first tapered roller bearing 34, the outer clutch housing 31 is arranged on the first tapered roller bearing 34 through an inner cylinder, the nut 37 is provided with two pieces, and an adjusting ring 36 is arranged between the two pieces of nuts 37.
The inner clutch housing 29 is also an inner and outer cylinder structure with one open end, the arrangement direction of the closed end of the inner clutch housing 29 is the same as the arrangement direction of the closed end of the outer clutch housing 31, the inner cylinder of the inner clutch housing 29 is mounted on the second tapered roller bearing 58, the second tapered roller bearing 58 is mounted on the input shaft 45, and a second disc spring 44 and a second piston 40 contacting the second disc spring 44 are arranged between the inner cylinder and the outer cylinder of the inner clutch housing 29.
A retaining ring 30 is further provided between the inner clutch housing 29 and the outer clutch housing 31, the retaining ring 30 being fitted over the stepped outer side wall of the inner clutch housing 29. The retainer ring 30 is used to adjust the gap between the inner clutch housing 29 and the outer clutch housing 31.
The third tapered roller bearing 19 is provided on the outside of the first carrier 20, and the first carrier 20 is mounted on the planetary transmission housing 1 (not shown in the drawing) via the third tapered roller bearing 19.
The input shaft 45 of the planetary transmission is connected via a clutch to an electric motor, which is connected via a control system to a battery (not shown).
The motor transmits power to the input shaft 45 from the left side, and when the first clutch C1 and the second clutch C2 are not operated, the sun gear 23, the planetary gear set 25, and the ring gear 26 are in a disordered state, that is, power cannot be transmitted.
Low gear: the first clutch C1 is engaged and the second clutch C2 is disengaged, i.e.: the second clutch C2 is not operated, the first clutch C1 is operated, hydraulic oil in the first hydraulic pipe 54 enters the right cavity of the first piston 32 of the first clutch C1, and since the outer clutch housing 31 is fixed to the planetary transmission housing 1 and is not rotated all the time, at this time, the outer clutch housing 31, the inner clutch housing 29, the inner clutch mounting bracket 28, the first outer friction plate group 38, and the first inner friction plate group 39 are integrally connected, fixed, and the ring gear 26 is also fixed. A power transmission route: the motor transmits power to the input shaft 45 from the left side, the input shaft 45 drives the sun gear 23, the sun gear 23 drives the planetary gear set 25, the planetary gear set 25 rotates on the fixed gear ring 26, the planetary gear set 25 drives the first planet carrier 20 and the second planet carrier 27 to jointly rotate, the first planet carrier 20 drives the output gear 14 to rotate through the third spline pair 53, the output gear 14 outputs power to the outside, and the speed is output to the outside according to the reduction ratio of a planetary transmission unit consisting of the sun gear 23, the planetary gear set 25 and the gear ring 26. After the motor is started, the sun gear 23 rotates with the input shaft 45, the sun gear 23 meshes with the planetary gear set 25, and the planetary gear set 25 meshes with the ring gear 26. The planetary gear set 25 revolves around the sun gear 23 while rotating, and the first carrier 20 rotates together with the planetary gear set 25 at the same time, effecting deceleration, and transmitting power to the output gear 14 through the third spline pair 53.
High gear: the second clutch C2 is engaged and the first clutch C1 is disengaged, i.e.: the first clutch C1 is not operated, the second clutch C2 is operated, and the hydraulic oil in the second hydraulic pipe 55 enters the right chamber of the second piston 40 of the second clutch C2, and at this time, the second outer friction plate group 41, the second inner friction plate group 42, the spline hub 43, the second carrier 27, the inner clutch housing 29, the inner clutch mounting bracket 28 and the ring gear 26 are fixedly connected as a whole. A power transmission route: the motor transmits power to the input shaft 45 from the left side, the input shaft 45 drives the sun gear 23, the sun gear 23 drives the planetary gear set 25, the planetary gear set 25 drives the first planet carrier 20 and the second planet carrier 27, and the second planet carrier 27 is fixedly connected with the gear ring 26 into a whole, so that a planetary transmission unit formed by the sun gear 23, the planetary gear set 25 and the gear ring 26 integrally rotates and does not decelerate to output power to the outside, and at the moment, the rotation speed of the output gear 14 on the first planet carrier 20 is the same as the output rotation speed of the motor.
The present invention also provides a preferred type of planetary transmission, the planetary transmission of example 2, please refer to fig. 10 and 11, the structure of example 2 is substantially the same as that of example 1, the main difference being that the planetary gear of planetary gear set 25 of example 1 is replaced by a first double gear 46, and the planetary transmission of this structure is suitable for use in a vehicle which is subject to heavy loads. The first duplex gear 46 includes a first driving gear 461 and a first driven gear 462, the first driving gear 461 and the first driven gear 462 are fixedly mounted on the pin shaft 24, the first driven gear 462 is meshed with the ring gear 26, and the first driving gear 461 is meshed with the sun gear 23 provided on the input shaft 45.
The present invention also provides another preferred type of planetary transmission, the planetary transmission of example 3, referring to fig. 12 and 13, in which the ring gear 26 is eliminated in example 3 as compared to both the planetary transmissions of example 1 and example 2. The planetary transmission with the structure is suitable for being applied to vehicles bearing light loads. The planetary gears in the planetary gear set 25 in embodiment 3 are changed to the second duplex gear 47, the second duplex gear 47 includes a second driving gear 471 and a second driven gear 472, the second driving gear 471 and the second driven gear 472 are fixedly mounted on the pin shaft 24, and the second driving gear 471 is meshed with the sun gear 23 provided on the input shaft 45; one end of the pin shaft 24 is fixedly arranged on the first planet carrier 20, the other end of the pin shaft is fixedly arranged on the second planet carrier 27, an inner spline is arranged on the side face of the upper end of the second planet carrier 27, an outer spline is arranged on the inner clutch mounting bracket 28, the inner spline on the second planet carrier 27 is fixedly connected with the outer spline on the inner clutch mounting bracket 28 through the fourth spline pair 56, the output gear 14 in the embodiment 3 is replaced by a third duplicate gear, the third duplicate gear is rotatably arranged outside the first planet carrier 20, a third driving gear 141 in the third duplicate gear is meshed with a second driven gear 472 of the second duplicate gear 47, and a third driven gear 142 in the third duplicate gear outputs power. In the low-speed gear, the first clutch C1 is combined, the second clutch C2 is disengaged, the second planet carrier 27 is connected with the outer clutch housing 31, the inner clutch housing 29, the inner clutch mounting bracket 28, the first outer friction plate group 38 and the first inner friction plate group 39 into a whole, the sun gear 23 rotates along with the input shaft 45 after the motor is started, the sun gear 23 is meshed with the second driving gear 471, the second driving gear 471 and the second driven gear 472 are fixedly arranged on the pin shaft 24, the second driven gear 472 rotates along with the second driving gear 471, the third driving gear 141 in the third duplex gear is meshed with the second driven gear 472 of the second duplex gear 47, and the third driven gear 142 in the third duplex gear outputs power to the outside and has the gear ratio of the planetary transmission. In the high gear, the first clutch C1 is not operated, and the second clutch C2 is operated. Because of the fourth spline pair 56, the second carrier 27 is fixed to the inner clutch housing 29 and the inner clutch mounting bracket 28, and the second clutch C2 fixes the second outer friction plate group 41, the second inner friction plate group 42, the spline hub 43 and the second carrier 27, so that the input shaft 45, the sun gear 23, the second driving gear 471, the second driven gear 472 and the third driving gear 141 and the third driven gear 142 of the third double gear are integrally locked, and at this time, the rotational speed of the output of the third driven gear 142 is the same as the rotational speed of the output of the motor.
Referring to fig. 14 to 17, the present embodiment further provides an electric drive axle including a planetary transmission, the electric drive axle including any one of the planetary transmissions provided in the embodiments of the present invention, an intermediate transition gear set, and an axle 5 drivingly connected to the planetary transmission through the intermediate transition gear set; the planetary transmission is arranged in a planetary transmission shell 1, and the planetary transmission shell 1 is fixedly connected with an axle housing 8; the intermediate transition gear set comprises a first gear 11, a second gear 12 and a third gear 13, the third gear 13 and the second gear 12 are coaxially arranged, the second gear 12 is meshed with the first gear 11, the first gear 11 is in transmission connection with the differential mechanism 6 in the axle housing 8 of the axle 5, and the third gear 13 is meshed with the output gear 14 of the planetary transmission.
The axle 5 comprises a left half shaft 61, a right half shaft 69, a hub 2 and a brake drum 3 which are arranged in pairs and are bilaterally symmetrical, the output ends of the left half shaft 61 and the right half shaft 69 are fixedly connected with the hub 2 and the brake drum 3 respectively, the brake drum 3 is connected with an air chamber 7, the input ends of the left half shaft 61 and the right half shaft 69 are arranged in an axle housing 8 of the axle 5 and form a differential mechanism 6 together with other components, and the differential mechanism 6 is in transmission connection with a first gear 11 of an intermediate transition gear set.
The first gear 11 of the intermediate transition gear set is arranged on a transmission shaft 17, two ends of the transmission shaft 17 are arranged in a first bearing 18, the first bearing 18 is arranged in a bearing cover 16, and an adjusting nut 15 is arranged outside the bearing cover 16.
The axle 5 further comprises a camshaft support 9 fixedly connected to the axle housing 8 and an adjusting arm 10.
Referring to fig. 18, the differential 6 includes a left axle shaft 61, a left axle gear 63, a left housing 62, at least one left differential gear 64, a right axle shaft 69, a right axle gear 67, a right housing 68, at least one right differential gear 66, and an intermediate housing 65; the left half shaft 61 is connected with a left half shaft gear 63 through a spline and is connected with a left shell 62 through a bearing, and the left half shaft gear 63 is meshed with a left differential gear 64; the right half shaft 69 is connected with the right half shaft gear 67 through a spline and is connected with the right shell 68 through a bearing, and the right half shaft gear 67 is meshed with the right differential gear 66; the left side gear 63, the left differential gear 64, the right side gear 67 and the right differential gear 66 form a limited slip differential gear set together, the limited slip differential gear set is positioned in the middle shell 65, and two sides of the middle shell 65 are fixedly connected with the left shell 62 and the right shell 68 respectively; the left differential gear 64 is rotatably mounted on a left end cover 651 of the middle housing 65, and the right differential gear 66 is rotatably mounted on a right end cover 652 of the middle housing 65; the limited slip differential 6 is in driving connection with the first gear 11 of the intermediate transition gear set via a right half shaft 69 or a left half shaft 61.
The left differential gear 64 and the right differential gear 66 are respectively and uniformly arranged on a left end cover 651 and a right end cover 652 of the middle shell 65.
The electric drive axle comprising the planetary transmission of the embodiment of the invention has the advantages that the planetary transmission with four groups of duplex gears is adopted in the transmission, the speed change range is large, the structure is compact, the power is directly transmitted through the intermediate transition gear set, the transmission chain is greatly shortened, the occupied space of the transmission chain is integrally reduced, the space arrangement of vehicles is optimized, the total weight of a vehicle power system is greatly reduced, the energy consumption of the whole vehicle is favorably saved, and the integral performance of the electric vehicle is favorably improved.
The embodiment of the invention also provides an electric automobile, which adopts the electric drive axle comprising the planetary transmission as a drive axle. The electric automobile with the electric drive axle comprising the planetary transmission has the advantages that the riding space of personnel can be designed to be larger, the power performance is better, and the energy consumption is lower.
The above examples and drawings are only for illustrating the technical aspects of the present invention, but not for limiting the same, and it should be understood by those skilled in the art that the present invention is described in detail with reference to the preferred embodiments, and that the changes, modifications, additions or substitutions made by those skilled in the art without departing from the spirit of the present invention and the scope of the claims of the present invention. Other related art structures not disclosed in detail in the present invention are prior art in the field.
Claims (10)
1. A planetary transmission, characterized in that: the planetary transmission comprises a transmission unit and a clutch unit;
the transmission unit comprises an input shaft, a sun gear, a planetary gear set, a first planet carrier, a second planet carrier, a gear ring and an output gear; the sun gear is arranged on the input shaft, the sun gear is in meshed connection with the planetary gear set, the planetary gear set comprises three planetary gears, each planetary gear is arranged on a first planetary carrier and a second planetary carrier through a pin shaft, the first planetary carrier is arranged on the input shaft through a first deep groove ball bearing, the second planetary carrier is arranged on the input shaft through a second deep groove ball bearing, the planetary gears are in meshed connection with the gear ring, and the first planetary carrier is fixedly connected with the output gear through a third spline pair;
the clutch unit includes a first clutch and a second clutch;
the first clutch comprises an outer clutch shell, an inner clutch mounting bracket, a first outer friction plate set and a first inner friction plate set; the outer clutch housing is fixedly connected with the planetary transmission housing; the inner clutch shell and the inner clutch mounting bracket are fixedly connected together through bolts; the outer clutch shell is of an inner and outer cylinder structure with one end open, and an inner cylinder of the outer clutch shell is arranged on the input shaft through a first tapered roller bearing; a first disc spring and a first piston which is contacted with the first disc spring are arranged between the inner cylinder and the outer cylinder of the outer clutch shell, and a closed cavity enclosed by the first piston and the outer clutch shell is connected with a first hydraulic pipe; a first outer friction plate set and a first inner friction plate set are arranged in a cavity enclosed by the outer clutch shell and the inner clutch shell, the first outer friction plate set is fixedly connected with the outer clutch shell, and the first inner friction plate set is fixedly connected with the inner clutch shell; the first piston compresses the first outer friction plate group and the first inner friction plate group together against the elasticity of the first belleville spring under the action of hydraulic oil in the first hydraulic pipe, and the friction force between the first outer friction plate group and the first inner friction plate group is utilized to enable the first outer friction plate group and the first inner friction plate group to be fixedly connected, so that the outer clutch shell is fixedly connected with the inner clutch mounting bracket through the inner clutch shell, the inner clutch mounting bracket is fixedly connected with the gear ring through the first spline pair, and the gear ring is finally fixedly connected with the planetary transmission shell under the action of the hydraulic oil due to the fact that the outer clutch shell is fixedly connected with the planetary transmission shell;
The second clutch comprises an inner clutch shell, an inner clutch mounting bracket, a spline hub, a second outer friction plate group and a second inner friction plate group; the inner clutch shell is fixedly connected with the second outer friction plate set; the spline hub is arranged on the input shaft, one end of the spline hub is provided with an external spline, the other end of the spline hub is provided with an internal spline, the second planet carrier is provided with an external spline, the internal spline of the spline hub is matched with the external spline on the second planet carrier to form a second spline pair, the spline hub is fixedly connected with the second planet carrier through the second spline pair, and the spline hub is fixedly connected with a second internal friction plate group through the external spline; a second disc spring and a second piston which is in contact with the second disc spring are arranged in a closed space surrounded by the spline hub and the inner clutch housing, and a closed cavity surrounded by the second piston and the inner clutch housing is connected with a second hydraulic pipe; the second piston compresses the second outer friction plate group and the second inner friction plate group together against the elasticity of the second belleville spring under the action of hydraulic oil in the second hydraulic pipe, and the friction force between the second outer friction plate group and the second inner friction plate group is utilized to enable the second outer friction plate group and the second inner friction plate group to be fixedly connected; because the second outer friction plate set is fixedly connected with the inner clutch shell and the inner clutch mounting bracket, the inner clutch mounting bracket is fixedly connected with the gear ring through the first spline pair, and the second inner friction plate set is fixedly connected with the spline hub and the second planet carrier, when the second clutch works, the second piston finally enables the second planet carrier to be fixedly connected with the gear ring under the action of hydraulic oil in the second hydraulic pipe.
2. The planetary transmission according to claim 1, characterized in that: the first outer friction plate group comprises a plurality of first outer friction plates, the first outer friction plates are discs with uniform external teeth, the external teeth of the first outer friction plates are matched with tooth grooves on the inner surface of the outer clutch shell, the first inner friction plate group comprises a plurality of first inner friction plates, the first inner friction plates are discs with uniform internal teeth, the internal teeth of the first inner friction plates are matched with the tooth grooves on the outer surface of the inner clutch shell, and the first outer friction plates are staggered with the first inner friction plates; the second outer friction plate group comprises a plurality of second outer friction plates, the second outer friction plates are discs with uniform external teeth, the external teeth of the second outer friction plates are matched with tooth grooves on the inner surface of the inner clutch shell, the second inner friction plate group comprises a plurality of second inner friction plates, the second inner friction plates are discs with uniform internal teeth, the internal teeth of the second inner friction plates are matched with spline grooves on the outer surface of the spline hub, and the second outer friction plates and the second inner friction plates are arranged in a staggered mode.
3. The planetary transmission according to claim 1, characterized in that: a retainer ring is further arranged between the inner clutch housing and the outer clutch housing, and the retainer ring is sleeved on the stepped outer side wall of the inner clutch housing.
4. The planetary transmission according to claim 1, characterized in that: the planet carrier I is arranged on the outer portion of the planet carrier I and is mounted on the planetary transmission shell through the third tapered roller bearing.
5. The planetary transmission according to claim 1, characterized in that: the planetary gear in the planetary gear set is a first duplex gear, the first duplex gear comprises a first driving gear and a first driven gear, the first driving gear and the first driven gear are fixedly arranged on the pin shaft, the first driven gear is meshed with the gear ring, and the first driving gear is meshed with a sun gear arranged on the input shaft.
6. The planetary transmission according to claim 1, characterized in that: the planetary gears in the planetary gear set are second duplex gears, the second duplex gears comprise second driving gears and second driven gears, the second driving gears and the second driven gears are fixedly arranged on the pin shafts, and the second driving gears are meshed with sun gears arranged on the input shafts; one end of the pin shaft is fixedly arranged on the first planet carrier, the other end of the pin shaft is fixedly arranged on the second planet carrier, an inner spline is arranged on the side surface of the upper end part of the second planet carrier, an outer spline is arranged on the inner clutch mounting bracket, and the inner spline on the second planet carrier is fixedly connected with the outer spline on the inner clutch mounting bracket through a fourth spline pair; the output gear is a third duplex gear which is rotatably arranged outside the planet carrier, a third driving gear in the third duplex gear is meshed with a second driven gear in the second duplex gear, and the third driven gear in the third duplex gear outputs power outwards.
7. An electrically driven axle comprising a planetary transmission, characterized by: the electric drive axle comprises the planetary transmission, an intermediate transition gear set and an axle which is in transmission connection with the planetary transmission through the intermediate transition gear set, wherein the planetary transmission is as defined in any one of claims 1 to 6; the planetary transmission is arranged in a planetary transmission shell which is fixedly connected with the axle housing; the intermediate transition gear set comprises a first gear, a second gear and a third gear, the third gear and the second gear are coaxially arranged, the second gear is meshed with the first gear, the first gear is in transmission connection with a differential mechanism in an axle housing of an axle, and the third gear is meshed with an output gear of the planetary transmission.
8. The electrically driven axle incorporating a planetary transmission as set forth in claim 7, wherein: the differential mechanism is a limited slip differential mechanism and comprises a left half shaft, a left half shaft gear, a left shell, at least one left differential gear, a right half shaft gear, a right shell, at least one right differential gear and a middle shell; the left half shaft is connected with a left half shaft gear through a spline and is connected with a left shell through a bearing, and the left half shaft gear is meshed with a left differential gear; the right half shaft is connected with a right half shaft gear through a spline and is connected with a right shell through a bearing, and the right half shaft gear is meshed with a right differential gear; the left side shaft gear, the left differential gear, the right side shaft gear and the right differential gear form a limited slip differential gear set together, the limited slip differential gear set is positioned in a middle shell, and two sides of the middle shell are fixedly connected with the left shell and the right shell respectively; the left differential gear is rotatably arranged on the left end cover of the middle shell, and the right differential gear is rotatably arranged on the right end cover of the middle shell; the limited slip differential is in transmission connection with a gear one of the intermediate transition gear sets through a right half shaft or a left half shaft.
9. The electrically driven axle incorporating a planetary transmission as set forth in claim 8, wherein: the left differential gear and the right differential gear are respectively and uniformly distributed on the left end cover and the right end cover of the middle shell.
10. An electric automobile, characterized in that: the electric vehicle adopts the electric drive axle comprising the planetary transmission as a drive axle according to claim 9.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202410079163.7A CN117588530B (en) | 2024-01-19 | 2024-01-19 | Planetary transmission, electric drive axle comprising planetary transmission and electric automobile |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202410079163.7A CN117588530B (en) | 2024-01-19 | 2024-01-19 | Planetary transmission, electric drive axle comprising planetary transmission and electric automobile |
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| CN117588530B true CN117588530B (en) | 2024-03-29 |
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|---|---|---|---|---|
| WO2006104294A1 (en) * | 2005-03-30 | 2006-10-05 | Wooyoung Hydraulics Co., Ltd | Compact variable transmission installed between bevel and differential gear |
| CN108468764A (en) * | 2018-05-21 | 2018-08-31 | 福州钻智汽车科技有限公司 | A kind of double three shift transmissions of actuator formula for electric vehicle |
| CN111536214A (en) * | 2020-05-28 | 2020-08-14 | 郭辰 | Novel gearbox of wheel type excavator |
| CN112576702A (en) * | 2020-12-10 | 2021-03-30 | 意宁液压股份有限公司 | Speed reducer with variable transmission ratio for vehicle |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US10677332B2 (en) * | 2017-09-19 | 2020-06-09 | Schaffler Technologies AG & Co. KG | Hybrid module including electric motor on front differential |
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Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2006104294A1 (en) * | 2005-03-30 | 2006-10-05 | Wooyoung Hydraulics Co., Ltd | Compact variable transmission installed between bevel and differential gear |
| CN108468764A (en) * | 2018-05-21 | 2018-08-31 | 福州钻智汽车科技有限公司 | A kind of double three shift transmissions of actuator formula for electric vehicle |
| CN111536214A (en) * | 2020-05-28 | 2020-08-14 | 郭辰 | Novel gearbox of wheel type excavator |
| CN112576702A (en) * | 2020-12-10 | 2021-03-30 | 意宁液压股份有限公司 | Speed reducer with variable transmission ratio for vehicle |
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