CN114294385A - Unpowered-interruption two-gear variable-speed electric drive axle and electric automobile - Google Patents
Unpowered-interruption two-gear variable-speed electric drive axle and electric automobile Download PDFInfo
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Abstract
The invention discloses a power-interruption-free two-gear variable-speed electric drive axle which mainly comprises a motor, a planetary gear train, a first hydraulic multi-plate friction clutch, a second hydraulic multi-plate friction clutch, a main reducer assembly, a differential assembly, a hub assembly and a transmission shell, wherein a one-way clutch is arranged in the planetary gear train and connected with the transmission shell; the first hydraulic multi-plate clutch is connected with a sun gear and a planet carrier of the planetary gear train, and the second hydraulic multi-plate friction clutch is connected with a gear ring and the transmission shell of the planetary gear train. The invention also discloses an electric automobile which is driven by the two-gear variable-speed electric drive axle without power interruption, and the two-gear shift operation without power interruption can be realized by controlling the actions of the first hydraulic multi-plate friction clutch and the second hydraulic multi-plate friction clutch and assisting the one-way clutch.
Description
Technical Field
The invention relates to the field of electric automobiles, in particular to the technical field of electric automobile transmission, and specifically relates to a two-gear variable-speed electric drive axle without power interruption and an electric automobile.
Background
At the present stage, the output and the sales of the electric automobile are increased day by day, the market ratio is gradually enlarged, and the future development prospect is good. Although compared with internal combustion engine automobiles, electric automobiles have obvious advantages of energy conservation and environmental protection, along with the proposal of the carbon peak-reaching policy, the energy conservation requirement of the electric automobiles is higher and higher, so the design problem of the high-efficiency driving system of the electric automobiles is more and more emphasized.
According to different motor-driven wheel modes, the electric automobile can be divided into an electric wheel driving mode and a centralized driving mode; the electric wheel driving type automobile generally integrates a motor directly in a wheel or at the wheel edge, the driving mode can increase unsprung mass, the smoothness and driving stability of the automobile are influenced, the working environment of the motor is relatively severe, and the requirements on the efficiency and the size of the motor are high; the centralized driving automobile has stable and reliable power transmission system, relatively mature technology and easier spatial arrangement of the motor, can improve the driving range of the automobile by adopting a large motor, can enable the automobile to run under various working conditions, and has low unsprung mass and higher riding comfort; therefore, the centralized driving automobile can improve the driving range of the electric automobile to the maximum extent and meet the requirement of people on the comfort of the automobile, and is a main product form of the electric automobile in the current automobile market.
However, at present, a common centralized driving electric vehicle on the market generally has no transmission, generally, the output torque is increased through a main speed reducer with a large speed ratio, and because the speed ratio is fixed, the speed ratio cannot be reasonably switched according to the actual running condition of the electric vehicle, and the dual requirements of the electric vehicle on low-speed running dynamic property and high-speed running economy cannot be met. At present, a few centralized driving electric automobiles adopting two-gear speed change often adopt a synchronizer and a motor active speed regulation method, but the problems of power loss and interruption caused by the gear shifting process exist in the gear shifting process, and in addition, the riding comfort of drivers and passengers and the driving performance of the automobiles are influenced by generated gear shifting impact. Therefore, in order to take power performance, economy and driving smoothness of the electric vehicle into consideration, a novel speed change system which can realize unpowered interruption is matched for the centralized driving of the electric vehicle is very necessary.
Disclosure of Invention
The invention designs and develops an unpowered interrupted two-gear variable-speed electric drive axle, and aims to realize unpowered interrupted gear shifting operation of high and low two gears of an electric automobile by arranging two hydraulic multi-plate friction clutches and a one-way clutch to be matched with a planetary gear mechanism, meet different requirements of a driver on low-speed dynamic property and high-speed economical property of the electric automobile, and reduce impact degree and power loss in the gear shifting process by virtue of smoothness and rapidness of the gear shifting process so as to realize better driving performance.
The technical scheme provided by the invention is as follows:
an unpowered two-speed transaxle comprising:
the motor is used for driving the axle to drive the automobile to run;
the planetary gear train is used for transmission with different speed ratios;
the main reducer assembly is used for speed reduction and torque increase transmission;
a transmission housing;
the hub assembly is used for transmitting force and moment between the left wheel, the right wheel and the drive axle;
a differential assembly for evenly distributing drive to said hub assembly;
the first hydraulic multi-plate friction clutch is used for connecting or disconnecting the motor and the power output end of the planetary gear train;
and the second hydraulic multi-plate friction clutch is used for connecting or disconnecting the planetary gear train and the transmission shell.
Preferably, the method further comprises the following steps:
a motor housing;
an inner rotor rotatably supported at both side centers of the motor housing;
the motor shaft is in interference fit with the central spline hole of the inner rotor and outputs motor electromagnetic torque;
a winding secured to the motor housing;
a permanent magnet fixed to an outer cylindrical surface of the inner rotor.
Preferably, the method further comprises the following steps:
the first hydraulic multi-plate friction clutch shell is fixedly connected with the output end of the motor shaft through a spline;
a first piston disposed in the first hydraulic multi-plate friction clutch housing so as to be in contact therewith;
the inner side of the first piston cover is sleeved on the motor shaft, and the outer side of the first piston cover is in contact with the first piston;
a first spring disposed in the first hydraulic multi-plate friction clutch housing, and having one end abutting against the first piston and the other end abutting against the first piston cover;
one side of the first wave spring washer is abutted against the first piston and the first piston cover;
the central hole of the first friction plate group is connected with the input end of the planetary gear train through a spline;
the first pressure plate is arranged on one side of the first friction plate group and is arranged in an abutting mode, and the other side of the first pressure plate is arranged in an abutting mode with the other side of the first wave-shaped spring washer;
the first steel sheet set and the first friction sheet set are mutually staggered and abutted, and the outer circle of the first steel sheet set is connected with the first hydraulic multi-sheet friction clutch shell through a spline;
the first pressure plate is arranged on the other side of the first friction plate group and arranged in an abutting mode;
the first clamping ring is arranged in a manner of abutting against the first pressure plate;
the first piston is pushed by hydraulic oil, the first pressing plate is pressed to the first pressing plate, and the first friction plate group and the first steel plate group are pressed mutually to generate friction force.
Preferably, the method further comprises the following steps:
the sun gear is fixedly connected with the motor shaft through a spline;
the planet carrier is rotatably supported on the motor shaft and is fixedly connected with the first friction plate and the first pressure plate spline;
a plurality of planet wheels which are in external meshing transmission with the sun wheel and are supported on the planet carrier through planet wheel shafts;
an inner gear ring which is in internal gearing transmission with the planet gears and is rotatably supported on the planet carrier;
and an inner race of the one-way clutch is fixedly connected with the inner gear ring, and an outer race of the one-way clutch is fixedly connected with the transmission shell.
Preferably, the method further comprises the following steps:
a second hydraulic multi-plate friction clutch housing fixedly connected with the transmission housing;
a second piston provided in the second hydraulic multi-plate friction clutch housing so as to be in contact therewith;
the inner side of the second piston cover is sleeved on the planet carrier, and the outer side of the second piston cover is in contact with the second piston;
a second spring disposed in the second hydraulic multi-plate friction clutch housing, and having one end abutting against the second piston and the other end abutting against the second piston cover;
one side of the second wave spring washer is abutted against the second piston and the second piston cover;
the central hole of the second friction plate set is connected with the inner gear ring of the planetary gear train through a spline;
the second pressure plate is arranged on one side of the second friction plate group and is arranged in an abutting mode, and the other side of the second pressure plate is arranged in an abutting mode with the other side of the second wave-shaped spring washer;
the second steel sheet set and the second friction sheet set are mutually staggered and abutted, and the outer circle of the second steel sheet set is connected with the second hydraulic multi-sheet friction clutch shell through a spline;
the second pressure plate is arranged on the other side of the second friction plate group and arranged in an abutting mode;
the second clamping ring is arranged in a manner of abutting against the second pressure plate;
and the second piston is pushed by hydraulic oil, so that the second pressing plate presses the second pressing plate, and the second friction plate group and the second steel plate group are mutually pressed to generate friction force.
Preferably, the method further comprises the following steps:
the main speed reducer driving gear is fixedly connected with a planet carrier output shaft of the planetary gear train;
an oil slinger rotatably supported on a carrier output shaft of the planetary gear train;
the shaft sleeve can be sleeved on the planet carrier output shaft of the planetary gear train in an empty way and axially limits the driving gear of the main speed reducer;
a main reducer driving gear that is in meshing reduction transmission with the main reducer driving gear;
and the main speed reducer shell is fixedly connected with the transmission shell and is used for accommodating and supporting all parts in the main speed reducer assembly.
Preferably, the method further comprises the following steps:
a differential case rotatably supported within said transmission case and said final drive case and adapted to house components of said differential assembly;
the cross shaft is fixedly connected with the differential shell through bolts;
the differential planet gear is sleeved on the cross shaft in an empty way;
the half shaft gear is in meshing transmission with the differential planet gear and is connected with one end of a half shaft through a spline;
and one end of the half shaft is in splined connection with the half shaft gear, and the other end of the half shaft can rotatably penetrate through the differential shell and is connected with the hub assembly.
Preferably, the method further comprises the following steps:
a transmission case for housing the planetary gear train, the first hydraulic multi-plate friction clutch, and the second hydraulic multi-plate friction clutch;
and the drive axle shell and the transmission shell are cast into a whole and are used for accommodating the differential assembly.
Preferably, the method further comprises the following steps:
the wheel hub is fixedly connected with a flange face bolt at the other end of the half shaft and outputs the half shaft torque to drive a wheel;
the half shaft sleeve is fixedly connected with the main speed reducer shell and the drive axle shell in an interference fit mode respectively;
a hub bearing disposed between the axle housing and the hub for supporting the hub and a wheel.
Preferably, the method further comprises the following steps:
an electric automobile uses the no-power-interruption two-gear speed-changing electric drive axle.
Compared with the prior art, the invention has the following beneficial effects:
1. according to the unpowered interrupted two-gear variable-speed electric drive axle provided by the invention, in the gear shifting process, the friction torque generated by the sliding friction of the clutch can still output power, so that the unpowered interrupted gear shifting from the first forward gear to the second forward gear can be realized by the two-gear variable-speed drive axle;
2. for the common gears, namely the first gear and the second gear, the engagement and the disengagement of the one-way clutch are determined by the rotating speed relation of the inner race and the outer race of the one-way clutch in the gear shifting process, the gear shifting process can be completed only by controlling one hydraulic multi-plate friction clutch, and the control is relatively simple and has good response characteristic;
3. the two-gear variable-speed drive axle without power interruption provided by the invention has the advantages that for the two gears of the common working gear, only the combination of the first friction clutch needs to be controlled, the second friction clutch and the one-way clutch are in a free separation state, the motor directly outputs power through the planet carrier, the driving efficiency of the whole power system is very high, the energy consumed by the actuator is very small, and the running economy is good.
Drawings
Fig. 1 is a mechanical schematic diagram of the two-speed variable-speed electric transaxle without power interruption according to the present invention.
Fig. 2 is a schematic view of the structure of the two-speed variable-speed electric drive axle without power interruption according to the present invention.
FIG. 3 is a schematic diagram of the power transmission path of the two-speed variable-speed electric transaxle without power interruption in the forward and first gear state according to the present invention.
Fig. 4 is a schematic diagram of a power transmission route when the two-speed variable-speed electric drive axle without power interruption is in a forward two-speed state according to the present invention.
FIG. 5 is a schematic power transmission path of the two-speed variable electric transaxle without power interruption in reverse gear of the present invention.
Detailed Description
The present invention is further described in detail below with reference to the attached drawings so that those skilled in the art can implement the invention by referring to the description text.
As shown in figure 1, the invention designs and develops an unpowered interrupted two-gear variable-speed electric drive axle, and aims to realize unpowered interrupted gear shifting operation of high and low two gears of an electric automobile by arranging two hydraulic multi-plate friction clutches and a one-way clutch to be matched with a planetary gear mechanism, meet different requirements of a driver on low-speed power performance and high-speed economy of the electric automobile, and reduce impact degree and power loss in the gear shifting process by virtue of smoothness and rapidness of the gear shifting process so as to realize better driving performance.
The two-gear speed change electric drive axle without power interruption mainly comprises a motor 100, a No. 1 hydraulic multi-plate friction clutch 200, a planetary gear train 300, a No. 2 hydraulic multi-plate friction clutch 400, a main reducer assembly 500, a differential assembly 600 and a hub assembly 700.
The motor 100 comprises a number 1 screw 101, a motor housing 102, a transmission housing 103, an oil drain screw 104, a motor housing cover 105, a motor housing cover end cover 106, a motor shaft 107, a winding 108, a permanent magnet 109, an inner rotor 110, a number 1 tapered roller bearing 111 and a number 2 tapered roller bearing 112;
wherein, motor casing 102 installs between motor case lid 105 and transmission housing 103, the three is as an organic whole through number 1 screw 101 fixed connection along the circumferencial direction equipartition, motor case lid end cover 106 passes through hexagon head bolt fixed connection with motor case lid 105, permanent magnet 109 is fixed on inner rotor 110, winding 108 is fixed on motor casing 102, oil drain screw 104 installs in transmission housing 103 upper end, inner rotor 110 carries out axial spacing through motor shaft 107 shoulder, motor case lid 105 supports through number 1 tapered roller bearing 111 and number 2 tapered roller bearing 112 with motor casing 102 respectively, and carry out axial spacing to number 1 tapered roller bearing 111 and number 2 tapered roller bearing 112 through the both sides shoulder of inner rotor 110, inner rotor 110 is equipped with hollow splined hole, with motor shaft 107 left end spline fixed connection.
The No. 1 hydraulic multi-plate friction clutch 200 is positioned on the right side of the motor assembly 100 and comprises a No. 1 oil cylinder piston 201, a No. 1 hydraulic multi-plate friction clutch shell 202, a No. 1 wave spring washer 203, a No. 1 pressure plate 204, a No. 1 steel plate group 205, a No. 1 snap ring 206, a No. 1 spring 207, a No. 1 piston cover 208, a No. 1 friction plate group 209 and a No. 1 pressure plate 210;
the No. 1 hydraulic multi-plate friction clutch shell 202 is fixedly connected with the motor shaft 107 through a spline and is axially limited through a shaft shoulder of the motor shaft 107; the outer side of the No. 1 oil cylinder piston 201 is supported in a No. 1 hydraulic multi-plate friction clutch shell 202, the right end of the No. 1 oil cylinder piston is in contact with a No. 1 spring 207, and the No. 1 oil cylinder piston is supported on a motor shaft 107 through a movable shaft sleeve; the outer side of a No. 1 piston cover 208 is supported in a No. 1 oil cylinder piston 201, the right side of the No. 1 piston cover is supported on a motor shaft 107, the motor shaft 107 is axially limited by a shaft shoulder of the motor shaft 107 and a No. 1 spring 207, a No. 1 wave-shaped spring washer 203 is sleeved between the No. 1 oil cylinder piston 201 and a No. 1 pressing plate 204, the No. 1 pressing plate 204 and a No. 1 friction plate group 209 are arranged in a contact mode, the No. 1 friction plate group 209 and the No. 1 steel plate group 205 are arranged in a mutually staggered and contact mode, and the excircle of the latter is connected with a No. 1 hydraulic multi-plate friction clutch shell 202 through a spline; the No. 1 snap ring 206 is clamped in the No. 1 hydraulic multi-plate friction clutch shell 202; the left side of the No. 1 pressure plate 210 is arranged in a manner of abutting against the No. 1 friction plate group 209, and the right side is axially limited by the No. 1 snap ring 206; when the operating mechanism of the No. 1 hydraulic multi-plate friction clutch 200 is electrified, the No. 1 oil cylinder piston 201 can move rightwards under the action of high-pressure oil, and pushes the No. 1 wave spring washer 203 and the No. 1 pressure plate 204 rightwards, so that the No. 1 friction plate group 209 and the No. 1 steel plate group 205 are pressed tightly, friction force is generated under the condition of a rotation trend, so that the No. 1 hydraulic multi-plate friction clutch 200 is engaged, and the No. 1 spring 207 is in a compressed state; when the operating mechanism of the hydraulic multi-plate friction clutch 200 1 is powered off, the cylinder piston 201 moves leftwards under the action of the elastic force of the spring 207 1, the pressure plate 1 204, the friction plate group 1 209 and the steel plate group 1 205 are not pressed, and the friction force gradually decreases until the friction force becomes 0, so that the hydraulic multi-plate friction clutch 200 1 is separated.
The planetary gear train 300 is a single-row single-stage planetary gear train, is located on the right side of the No. 1 hydraulic multi-plate friction clutch 200, and comprises a planetary gear 301, an inner gear ring 302, a planetary carrier 303, a sun gear 304, a planetary carrier cover 305, a one-way clutch inner race 306, a one-way clutch outer race 307, a No. 3 tapered roller bearing 308, a needle bearing 309, a No. 4 tapered roller bearing 310, a No. 1 shaft sleeve 311 and a No. 2 screw 312;
the sun gear 304 is fixedly connected with the motor shaft 107 through a spline, axial limiting is carried out through a shaft shoulder of the motor shaft 107 and a clamping ring, the planet carrier cover 305 is supported on the motor shaft 107 through a No. 3 tapered roller bearing 308 and is fixedly connected with a No. 1 friction plate group 209 through a spline, axial limiting is carried out on the planet carrier cover 305 through the No. 3 tapered roller bearing 308, and axial limiting is carried out on the No. 3 tapered roller bearing through the shaft shoulder of the motor shaft 107; the No. 1 planet gear extends out of the cylindrical shaft towards two sides and extends into radial outer circular holes of the planet carrier cover 305 and the planet carrier 303 and can rotate freely, the planet carrier cover 305 and the planet carrier 303 are fixedly connected through screws, the planet carrier 303 extends towards the right side to form a solid shaft, the left end of the solid shaft is supported on the motor shaft 107 through a needle roller bearing 309, the right end of the solid shaft is supported on the transmission housing 103 and the right axle housing 510 through a No. 5 tapered roller bearing 505 and a No. 6 tapered roller bearing 506, the needle roller bearing 309 performs axial limiting through a shaft shoulder of the motor shaft 107, the No. 5 tapered roller bearing 505 performs axial limiting through the transmission housing 103 and a No. 2 shaft sleeve 516, and the No. 6 tapered roller bearing 506 performs axial limiting through a slinger 502; the inner gear ring 302 is supported on the planet carrier 302 through a No. 4 tapered roller bearing 310 and is fixedly connected with a No. 2 friction plate set 406 through a spline, and the No. 4 tapered roller bearing 310 performs axial limiting through the inner gear ring 302 and a No. 1 shaft sleeve 311; the outer ring 307 of the one-way clutch is fixedly connected with the transmission housing 103 through a No. 2 screw 312, the inner ring gear 302 of the one-way clutch is fixedly connected with the inner ring gear 306 through a spline, the inner ring gear 302 of the one-way clutch is axially limited by the inner ring gear 306 of the one-way clutch, and when the inner ring gear 306 of the one-way clutch rotates forwards relative to the outer ring 307 of the one-way clutch, the one-way clutch is connected; when the outer race 307 of the one-way clutch rotates forward relative to the inner race 306 of the one-way clutch, the one-way clutch is disconnected.
The No. 2 hydraulic multi-plate friction clutch 400 is positioned on the right side of the planetary gear train 300 and comprises a No. 2 pressure plate 401, a No. 2 steel plate group 402, a No. 2 pressure plate 403, a No. 2 wave spring washer 404, a No. 2 hydraulic multi-plate friction clutch shell 405, a No. 2 friction plate group 406, a No. 2 spring 407, a No. 2 snap ring 408, a No. 2 oil cylinder piston 409 and a No. 2 piston cover 410;
the No. 2 hydraulic multi-plate friction clutch shell 405 is supported on the transmission shell 103, the outer side of the No. 2 oil cylinder piston 409 is supported in the No. 2 hydraulic multi-plate friction clutch shell 405, the left end of the No. 2 oil cylinder piston is in contact with the No. 2 spring 407, and the No. 2 oil cylinder piston is supported on the planet carrier 303 through a movable shaft sleeve; the outer side of a No. 2 piston cover 410 is supported in a No. 2 oil cylinder piston 409, the left side of the piston cover is supported on a planet carrier 303 and axially limited by a No. 1 shaft sleeve 311, a No. 2 wave-shaped spring washer 404 is sleeved between the No. 2 oil cylinder piston 409 and a No. 2 pressing plate 403, the No. 2 pressing plate 403 and a No. 2 friction plate set 406 are arranged in a butting mode, the No. 2 friction plate set 406 and the No. 2 steel plate set 402 are arranged in a mutually-staggered and butting mode, the central hole of the piston cover is connected with an inner gear ring 302 through a spline, and the excircle of the piston cover is connected with a second hydraulic multi-plate friction clutch shell 405 through a spline; the No. 2 snap ring 408 is clamped in the No. 2 hydraulic multi-plate friction clutch shell 405; the right side of the No. 2 pressure plate 401 is arranged in a manner of abutting against the No. 2 friction plate group 406, and the left side of the No. 2 pressure plate is axially limited by a No. 2 snap ring 408; the working principle is the same as that of the hydraulic multi-plate friction clutch 200 No. 1, and the description is omitted.
The main reducer assembly 500 is located on the right side of the No. 2 hydraulic multi-plate friction clutch 400 and comprises a main reducer driving gear 501, an oil retainer ring 502, a No. 1 hexagon head bolt 503, a No. 2 hexagon head bolt 504, a No. 5 tapered roller bearing 505, a No. 6 tapered roller bearing 506, a No. 1 felt ring oil seal 507, a gasket 508, a No. 3 shaft sleeve 509, a right axle housing 510, a No. 7 tapered roller bearing 511, a lip-shaped sealing ring 512, a main reducer driven gear 513, a spring gasket 514, a flange type bearing cover 515 and a No. 2 shaft sleeve 516;
the driving gear 501 of the main speed reducer is fixedly connected with the planet carrier 303 through a spline, and is axially limited through a shaft shoulder of the planet carrier 303 and a No. 3 shaft sleeve 509; the right axle housing 510 is fixedly connected with the transmission housing 103 through a No. 1 hexagon head bolt 503, the flange type bearing cover 515 is fixedly connected with the right axle housing 510 through a No. 2 hexagon head bolt 504, the main reducer driven gear 513 is fixedly connected with the differential right shell 609 through a No. 4 hexagon head bolt 608, and the No. 7 tapered roller bearing 511 is supported in the differential right shell 609 and is axially limited through the right axle housing 510 and the differential right shell 609.
The differential assembly 600 is positioned on the left side of the driven gear 513 of the main speed reducer and comprises a differential left shell 601, a No. 3 hexagon head bolt 602, a No. 1 gasket 603, a cross shaft 604, a differential planet wheel 605, a side gear 606, a No. 2 gasket 607, a No. 4 hexagon head bolt 608, a differential right shell 609 and a No. 8 tapered roller bearing 610;
the differential left shell 601 is supported on the side gear 606 and fixedly connected with the differential right shell 609 through a No. 4 hexagon head bolt 608, and the No. 8 tapered roller bearing 610 is supported on the differential left shell 601 and axially limited through the transmission housing 103; four shaft necks of a cross shaft 604 are embedded in holes formed by corresponding grooves on two half end surfaces of the differential case; the differential planet wheel 605 is sleeved on the cross shaft 604 in a floating way and meshed with the side gear 606; the side gear 606 is fixedly connected to the axle shaft 712 via splines.
The hub assembly 700 is positioned on the right side of the driven gear 513 of the main speed reducer and comprises a hub 701, a dust cover 702, a No. 2 felt ring oil seal 703, a gasket 704, a No. 9 tapered roller bearing 705, a No. 10 tapered roller bearing 706, a No. 4 hexagon head bolt 707, a No. 3 felt ring oil seal 708, a pin 709, a No. 3 gasket 710, a locking nut 711, a half shaft 712, a half shaft sleeve 713, an inner nut 714 and a cover-lifting screw 715;
the No. 9 tapered roller bearing 705 is supported on the axle sleeve 713 and axially limited by the washer 704 and the hub 701; the No. 10 tapered roller bearing 706 is supported on the axle sleeve 713 and is axially limited by the inner nut 714 and the hub 701; the hub 701 is supported on a number 9 tapered roller bearing 705 and a number 10 tapered roller bearing 706, and is fixedly connected to the half shaft 712 by a number 4 hexagonal head bolt 707.
In this embodiment, as a preference, the characteristic parameter of the planet row of the planetary gear train 300 is greater than 1, and the characteristic parameter of the planet row is generally defined in the mechanical field and refers to the ratio of the number of teeth of the ring gear and the sun gear in the planetary gear train.
In the assembly process, a motor 100, a transmission shell 103, a No. 1 screw 101, a No. 1 hydraulic multi-plate friction clutch 200, a planetary gear train 300, a No. 2 hydraulic multi-plate friction clutch 400, a differential 600 and a half shaft 712 are used as a power assembly, the upper half part of the assembly is fixed with a motor box cover end cover 106 through a motor shaft 107 extending out of the left end, and is fixedly connected with a main speed reducer driving gear 501 through a planet carrier 303 extending out of the right end; the lower half assembly is fixedly connected with a main speed reducer driven gear 513 through a differential right shell 609, and is fixedly connected with a hub 701 through half shafts 712 extending out of two ends.
FIG. 2 shows the primary connection of the non-power-interrupting two-speed transaxle; as shown in fig. 3, 4 and 5, the two-speed transaxle without power interruption provided by the present invention has three operation modes: a forward first gear state, a forward second gear state and a reverse gear state;
the following explains the working principle of the three modes respectively: in the aspect of the speed relation, the rotation direction of the wheels is set to be a positive direction when the electric automobile moves forward, the rotation direction of the wheels is set to be a negative direction when the electric automobile moves backward, the No. 1 hydraulic multi-plate friction clutch 200 and the No. 2 hydraulic multi-plate friction clutch 400 are in a separated state under a normal state, the inner race is separated from the outer race when the one-way clutch rotates forward, and the inner race is jointed with the outer race when a reverse torque is applied;
1. a forward first gear state: when the electric automobile is in a forward first gear state, an Electronic Control Unit (ECU) of the automobile does not send an instruction, the No. 1 oil cylinder piston 201 and the No. 2 oil cylinder piston 409 do not move, and the No. 1 hydraulic multi-plate friction clutch 200 and the No. 2 hydraulic multi-plate friction clutch 400 are both in a separated state, namely the planet carrier 303 and the motor shaft 107 are in a separated state; the motor 100 rotates forwards, the sun gear 304 rotates forwards synchronously to output forward torque, for a single-stage planetary line, the output torque of the inner gear ring is in the same direction as the output torque of the sun gear, therefore, the inner gear ring 302 also outputs forward torque, and simultaneously, under the action of reverse torque, the inner race 306 of the one-way clutch fixedly connected with the inner gear ring 302 also starts to rotate under the action of reverse torque, at the moment, the inner race 306 of the one-way clutch rotates forwards relative to the outer race 307 of the one-way clutch, the inner race 306 of the one-way clutch and the outer race 307 of the one-way clutch are gradually jointed to be locked, at the moment, the inner gear ring 302 is locked, namely, the rotating speed is 0, at the moment, the rotating speed of the motor shaft 107 and the sun gear 304 is n, and according to the rotating speed formula of the single-stage planetary gear system, the rotating speed of the planet carrier 303 is obtained
(k is a characteristic parameter of the planetary gear set 300, and k is>1) The planet carrier 303 is the output shaft of the transmission, and the output rotating speed of the transmission is
The transmission ratio is k +1, namely the first gear transmission ratio i of the transmissiong1Setting the transmission ratio of the main speed reducer as i as k +10The rotational speed of the half shaft 712 and the hub 701 is then
Therefore, as shown in fig. 3, when the electric vehicle is in a forward first gear state, power is transmitted to the hub 701 sequentially through the inner rotor 110, the motor shaft 107, the sun gear 304, the number 1 planetary gear 301, the planet carrier 303, the main reducer driving gear 501, the main reducer driven gear 513, the differential left shell 601, the differential right shell 609 and the half shaft 712, so that the electric vehicle is driven to run forwards;
2. a forward two-gear state: when the electric automobile is switched from a forward first gear state to a forward second gear state, the No. 2 oil cylinder piston 409 still does not move, the No. 2 hydraulic multi-plate friction clutch 400 is still in a separation state, an ECU of the automobile sends a command to an electric oil pump of the No. 1 hydraulic multi-plate friction clutch 200, high-pressure oil generated by the electric oil pump is conveyed to the No. 1 hydraulic multi-plate friction clutch oil cylinder through an electromagnetic valve, the electric current of the electromagnetic valve is controlled by the ECU to control the oil flow and the channel change of the oil, the No. 1 oil cylinder piston 201 is pushed to move rightwards, the No. 1 spring 207 is gradually compressed, the No. 1 wave spring washer 203 and the No. 1 pressure plate 204 are also forced to move rightwards, the No. 1 pressure plate 210 and the No. 1 snap ring 206 are fixed, the No. 1 steel sheet group 205 and the No. 1 friction sheet group 209 are pressed, and under the action of the rotation of a driving part of the clutch, a friction force is generated between the No. 1 steel sheet group 205 and the No. 1 friction sheet group 209, at this time, the No. 1 hydraulic multi-plate friction clutch 200 is in an engaged state, the motor shaft 107 and the planet carrier 303 are fixedly connected, and when the rotation speed of the motor shaft 107 and the rotation speed of the sun gear 304 are n, the rotation speed n of the planet carrier 303 is npcDuring an upshift, the rotational speed is changed to
Therefore, the No. 1 hydraulic multi-plate friction clutch 200 applies a reverse torque to the motor shaft 107 to reduce the speed of the motor shaft in the sliding process, applies a forward torque to the planet carrier 303 to increase the speed of the motor shaft, and can obtain the rotating speed of the inner gear ring 302 according to a rotating speed formula of a single-row single-stage planetary gear train
According to npcVariation knowing n during the entire clutch engagement processr>0, namely the ring gear always keeps the forward rotation, the one-way clutch rotates forward along with the forward rotation, the outer race 307 of the one-way clutch rotates forward relative to the inner race 306 of the one-way clutch, the inner race 306 of the one-way clutch and the outer race 307 of the one-way clutch are gradually disconnected to be separated, and when No. 1 hydraulic pressureAfter the multi-plate friction clutch 200 is completely engaged, the rotation speed of the planet carrier 303 is n, the rotation speed of the inner gear ring 302 is also n according to the rotation speed formula of the single-row single-stage planetary gear train, the output rotation speed of the transmission is also n, the transmission ratio is 1, namely the transmission ratio i of the second gear of the transmissiong21, the rotational speed of the half shaft 712 and the hub 701 is
Therefore, as shown in fig. 4, when the electric vehicle is in the forward two-gear state, power is transmitted to the hub 701 through the inner rotor 110, the motor shaft 107, the planet carrier 303, the main reducer driving gear 501, the main reducer driven gear 513, the differential left shell 601, the differential right shell 609 and the half shaft 712 in sequence, so that the electric vehicle is driven to run forward;
3. a reverse gear state: when the electric automobile is in a reverse gear state, the piston 201 of the oil cylinder No. 1 does not move, the hydraulic multi-plate friction clutch No. 1 is still in a separation state, the ECU of the automobile gives an instruction to the electric oil pump of the hydraulic multi-plate friction clutch No. 2 400, high-pressure oil generated by the electric oil pump is conveyed to the oil cylinder No. 2 through the electromagnetic valve, the electric current of the electromagnetic valve is controlled by the ECU to control the oil flow and the oil passage change, the piston 409 of the oil cylinder No. 2 is pushed to move leftwards, the spring 407 No. 2 is gradually compressed, the wave spring washer No. 2 404 and the pressure plate 403 No. 2 are also forced to move leftwards, the pressure plate No. 2 401 and the snap ring 2 are fixed, the steel sheet group No. 2 402 and the friction sheet group 2 406 are pressed, and under the action of the rotation of the driving part of the clutch, a friction force is generated between the steel sheet group No. 2 402 and the friction sheet group 2 406, at this time, the No. 2 hydraulic multi-plate friction clutch 400 is in an engaged state, the ring gear 302 is fixedly connected with the transmission housing 103, the ring gear 302 is locked at this time, that is, the rotating speed is 0, only the motor 100 needs to output negative torque at this time, the motor shaft 107 rotates reversely, the power transmission path is as shown in fig. 5, and the rest of the working principles are completely the same as the forward first gear state, and are not repeated here.
While embodiments of the invention have been described above, it is not limited to the applications set forth in the description and the embodiments, which are fully applicable in various fields of endeavor to which the invention pertains, and further modifications may readily be made by those skilled in the art, it being understood that the invention is not limited to the details shown and described herein without departing from the general concept defined by the appended claims and their equivalents.
Claims (10)
1. An unpowered two-speed transaxle comprising:
the motor is used for driving the axle to drive the automobile to run;
the planetary gear train is used for transmission with different speed ratios;
the main reducer assembly is used for speed reduction and torque increase transmission;
a transmission housing;
the hub assembly is used for transmitting force and moment between the left wheel, the right wheel and the drive axle;
a differential assembly for evenly distributing drive to said hub assembly;
the first hydraulic multi-plate friction clutch is used for connecting or disconnecting the motor and the power output end of the planetary gear train;
and the second hydraulic multi-plate friction clutch is used for connecting or disconnecting the planetary gear train and the transmission shell.
2. The uninterruptible two speed variable electric transaxle of claim 1 wherein the electric motor comprises:
a motor housing;
an inner rotor rotatably supported at the center of the motor housing;
the motor shaft is in interference fit with the central spline hole of the inner rotor and outputs motor electromagnetic torque;
a winding secured to the motor housing;
a permanent magnet fixed to an outer cylindrical surface of the inner rotor.
3. The uninterruptible two speed variable electric transaxle of claim 1 wherein the first hydraulic multi-plate friction clutch comprises:
the first hydraulic type multi-plate friction clutch shell is fixedly connected with the motor shaft through a spline;
a first piston disposed in the first hydraulic multi-plate friction clutch housing so as to be in contact therewith;
the inner side of the first piston cover is sleeved on the motor shaft, and the outer side of the first piston cover is in contact with the first piston;
a first spring disposed in the first hydraulic multi-plate friction clutch housing, and having one end abutting against the first piston and the other end abutting against the first piston cover;
one side of the first wave spring washer is abutted against the first piston and the first piston cover;
the central hole of the first friction plate group is connected with the input end of the planetary gear train through a spline;
the first pressure plate is arranged on one side of the first friction plate group and is arranged in an abutting mode, and the other side of the first pressure plate is arranged in an abutting mode with the other side of the first wave-shaped spring washer;
the first steel sheet set and the first friction sheet set are mutually staggered and abutted, and the outer circle of the first steel sheet set is connected with the first hydraulic multi-sheet friction clutch shell through a spline;
the first pressure plate is arranged on the other side of the first friction plate group and arranged in an abutting mode;
the first clamping ring is arranged in a manner of abutting against the first pressure plate;
the first piston is pushed by hydraulic oil, the first pressing plate is pressed to the first pressing plate, and the first friction plate group and the first steel plate group are pressed mutually to generate friction force.
4. The uninterruptible two speed transaxle of claim 1 wherein the planetary gear set comprises:
the sun gear is fixedly connected with the motor shaft through a spline;
the planet carrier is rotatably supported on a motor shaft and is fixedly connected with a first friction plate group and a first pressure plate of the first hydraulic multi-plate friction clutch through splines;
a plurality of planet wheels which are in external meshing transmission with the sun wheel and are supported on the planet carrier through planet wheel shafts;
an inner gear ring which is in internal gearing transmission with the plurality of planet gears and is rotatably supported on the planet carrier;
and an inner race of the one-way clutch is fixedly connected with the inner gear ring, and an outer race of the one-way clutch is fixedly connected with the transmission shell.
5. The uninterruptible two speed electric transaxle of claim 1 wherein the second hydraulic multi-plate friction clutch comprises:
a second hydraulic multi-plate friction clutch housing fixedly connected with the transmission housing;
a second piston provided in the second hydraulic multi-plate friction clutch housing so as to be in contact therewith;
the inner side of the second piston cover is sleeved on the planet carrier, and the outer side of the second piston cover is in contact with the second piston;
a second spring disposed in the second hydraulic multi-plate friction clutch housing, and having one end abutting against the second piston and the other end abutting against the second piston cover;
one side of the second wave spring washer is abutted against the second piston and the second piston cover;
the central hole of the second friction plate set is connected with the inner gear ring of the planetary gear train through a spline;
the second pressure plate is arranged on one side of the second friction plate group and is arranged in an abutting mode, and the other side of the second pressure plate is arranged in an abutting mode with the other side of the second wave-shaped spring washer;
the second steel sheet set and the second friction sheet set are mutually staggered and abutted, and the outer circle of the second steel sheet set is connected with the second hydraulic multi-sheet friction clutch shell through a spline;
the second pressure plate is arranged on the other side of the second friction plate group and arranged in an abutting mode;
the second clamping ring is arranged in a manner of abutting against the second pressure plate;
and the second piston is pushed by hydraulic oil, so that the second pressing plate presses the second pressing plate, and the second friction plate group and the second steel plate group are mutually pressed to generate friction force.
6. The uninterruptible two speed variable electric transaxle of claim 1 wherein the final drive assembly comprises:
the main speed reducer driving gear is fixedly connected with a planet carrier output shaft of the planetary gear train;
an oil slinger rotatably supported on a carrier output shaft of the planetary gear train;
the shaft sleeve can be sleeved on the planet carrier output shaft of the planetary gear train in an empty way and axially limits the driving gear of the main speed reducer;
a main reducer driven gear in meshing reduction transmission with the main reducer driving gear;
and the main speed reducer shell is fixedly connected with the transmission shell and is used for accommodating and supporting all parts in the main speed reducer assembly.
7. The uninterruptible two speed electric drive axle of claim 1, wherein the differential assembly comprises:
a differential case rotatably supported within said transmission case and said final drive case and adapted to house components of said differential assembly;
the cross shaft is fixedly connected with the differential shell through bolts;
the differential planet gear is sleeved on the cross shaft in an empty way;
the half shaft gear is in meshing transmission with the differential planet gear and is connected with one end of a half shaft through a spline;
and one end of the half shaft is connected with the half shaft gear through a spline, and the other end of the half shaft can rotatably penetrate through the differential shell and is connected with the hub assembly.
8. The uninterruptible two speed electric transaxle of claim 1 wherein the transmission housing comprises:
a transmission case for housing the planetary gear train, the first hydraulic multi-plate friction clutch, and the second hydraulic multi-plate friction clutch;
and the drive axle shell and the transmission shell are cast into a whole and are used for accommodating the differential assembly.
9. The uninterruptible two speed electric transaxle of claim 1 wherein the hub assembly comprises:
the wheel hub is fixedly connected with a flange face bolt at the other end of the half shaft and outputs the half shaft torque to drive a wheel;
the half shaft sleeve is fixedly connected with the main speed reducer shell and the drive axle shell in an interference fit mode respectively;
a hub bearing disposed between the axle housing and the hub for supporting the hub and a wheel.
10. An electric vehicle, characterized in that an uninterruptible two speed electric transaxle of claims 1-9 is used.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210001617.XA CN114294385A (en) | 2022-01-04 | 2022-01-04 | Unpowered-interruption two-gear variable-speed electric drive axle and electric automobile |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210001617.XA CN114294385A (en) | 2022-01-04 | 2022-01-04 | Unpowered-interruption two-gear variable-speed electric drive axle and electric automobile |
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| CN114294385A true CN114294385A (en) | 2022-04-08 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202210001617.XA Pending CN114294385A (en) | 2022-01-04 | 2022-01-04 | Unpowered-interruption two-gear variable-speed electric drive axle and electric automobile |
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Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE488062C (en) * | 1924-07-07 | 1929-12-19 | Alan Ernest Leofric Chorlton | Epicyclic gearbox |
| SU139287A1 (en) * | 1960-07-26 | 1960-11-30 | В.И. Власов | Planetary Coupling |
| US5024636A (en) * | 1989-06-27 | 1991-06-18 | Fairfield Manufacturing Company, Inc. | Planetary wheel hub |
| WO2013177785A1 (en) * | 2012-05-31 | 2013-12-05 | Robert Bosch Gmbh | Planetary gear transmission and electric vehicle |
| JP2017222199A (en) * | 2016-06-13 | 2017-12-21 | 三菱自動車工業株式会社 | Transaxle apparatus |
| WO2019098218A1 (en) * | 2017-11-17 | 2019-05-23 | アイシン・エィ・ダブリュ株式会社 | Vehicle drive apparatus |
| WO2019241773A1 (en) * | 2018-06-15 | 2019-12-19 | Dana Automotive Systems Group, Llc | Multi-speed gearbox with high torque ratio and the drive axle made therewith |
-
2022
- 2022-01-04 CN CN202210001617.XA patent/CN114294385A/en active Pending
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE488062C (en) * | 1924-07-07 | 1929-12-19 | Alan Ernest Leofric Chorlton | Epicyclic gearbox |
| SU139287A1 (en) * | 1960-07-26 | 1960-11-30 | В.И. Власов | Planetary Coupling |
| US5024636A (en) * | 1989-06-27 | 1991-06-18 | Fairfield Manufacturing Company, Inc. | Planetary wheel hub |
| WO2013177785A1 (en) * | 2012-05-31 | 2013-12-05 | Robert Bosch Gmbh | Planetary gear transmission and electric vehicle |
| JP2017222199A (en) * | 2016-06-13 | 2017-12-21 | 三菱自動車工業株式会社 | Transaxle apparatus |
| WO2019098218A1 (en) * | 2017-11-17 | 2019-05-23 | アイシン・エィ・ダブリュ株式会社 | Vehicle drive apparatus |
| US20200278011A1 (en) * | 2017-11-17 | 2020-09-03 | Aisin Aw Co., Ltd. | Vehicle drive system |
| WO2019241773A1 (en) * | 2018-06-15 | 2019-12-19 | Dana Automotive Systems Group, Llc | Multi-speed gearbox with high torque ratio and the drive axle made therewith |
| US20190383373A1 (en) * | 2018-06-15 | 2019-12-19 | Dana Automotive Systems Group, Llc | Multi-speed gearbox with high torque ratio & the drive axle made therewith |
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