CN110657207A - Transmission, power driving system and vehicle - Google Patents
Transmission, power driving system and vehicle Download PDFInfo
- Publication number
- CN110657207A CN110657207A CN201810713599.1A CN201810713599A CN110657207A CN 110657207 A CN110657207 A CN 110657207A CN 201810713599 A CN201810713599 A CN 201810713599A CN 110657207 A CN110657207 A CN 110657207A
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- Prior art keywords
- planetary gear
- transmission
- stage planetary
- gear mechanism
- 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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
- B60K17/08—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing of mechanical type
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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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/78—Special adaptation of synchronisation mechanisms to these gearings
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
- H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
Abstract
The invention discloses a transmission, a power driving system and a vehicle, wherein the transmission comprises: the transmission comprises an input shaft, a double-stage planetary gear mechanism, n single-stage planetary gear mechanisms and n +1 synchronizers, wherein the 1 st synchronizer is used for connecting a second sun gear of the 1 st single-stage planetary gear mechanism with a first gear ring or a first sun gear, the ith synchronizer is used for connecting a second sun gear of the ith single-stage planetary gear mechanism with a second planet carrier of the (i-1) th single-stage planetary gear mechanism or a second sun gear of the (i-1) th single-stage planetary gear mechanism, the n +1 th synchronizer is used for connecting an output end of the transmission with a second planet carrier of the nth single-stage planetary gear mechanism or a second sun gear of the nth single-stage planetary gear mechanism, i is more than or equal to 2 and less than or equal to n, and i and n are natural numbers. According to the transmission, the n +1 planetary row n +1 synchronizer structure is arranged, so that the transmission can realize quick, smooth and reliable gear shifting, and is simple in structure and convenient to maintain.
Description
Technical Field
The invention belongs to the technical field of vehicle manufacturing, and particularly relates to a transmission, a power driving system and a vehicle.
Background
Hybrid drive automobiles, electric automobiles and extended range electric automobiles are the development direction of future automobiles and are also the main form of new energy automobiles. In the related technology, the structure of the power transmission system is complex, the working mode is complex, the control strategy is complicated, the energy conversion efficiency needs to be improved, the motive energy of the engine and the electric energy of the battery can not be fully utilized, and the problems of secondary energy conversion, complex control and low efficiency exist. Specifically, in the related art, a plate clutch and a plate brake of a vehicle control shifting, but when these two components are not operated, drag torque exists due to lubrication, resulting in inefficiency of the entire transmission.
In addition, in the multi-gear transmission in the related art, gears are mostly selected by a shifting fork and a sliding sleeve when the clutch cuts off power, the number of pairs of gears is large, the occupied space is large, and the structure is complex, so that the improvement space exists.
Disclosure of Invention
The present invention is directed to solving at least one of the problems of the prior art. Therefore, an object of the present invention is to provide a transmission with high efficiency, simple structure and smooth gear shifting.
The invention also provides a power driving system with the transmission.
The invention also provides a vehicle with the power driving system.
The transmission according to the present invention includes: the double-stage planetary gear mechanism comprises a first sun gear, a first planetary gear, a first planet carrier and a first gear ring, wherein the first planet carrier is fixedly connected with a shell of the transmission; the single-stage planetary gear mechanism comprises a first sun gear, a first planet carrier and a first gear ring, and the single-stage planetary gear mechanism comprises n single-stage planetary gear mechanisms; an input shaft connected to the first sun gear; n +1 synchronizers for connecting the second sun gear of the 1 st of the single pinion planetary gear mechanisms with the first ring gear or the second sun gear of the 1 st of the single pinion planetary gear mechanisms with the first sun gear, the ith of the synchronizers for connecting the second sun gear of the ith of the single pinion planetary gear mechanisms with the second carrier of the i-1 th of the single pinion planetary gear mechanisms or the second sun gear of the ith of the single pinion planetary gear mechanisms with the second sun gear of the i-1 th of the single pinion planetary gear mechanisms, the n +1 th of the synchronizers for connecting the output of the transmission with the second carrier of the nth of the single pinion planetary gear mechanisms or the output of the transmission with the second sun gear of the nth of the single pinion planetary gear mechanisms, wherein i is more than or equal to 2 and less than or equal to n, and i and n are natural numbers.
According to the transmission, the n +1 planetary row n +1 synchronizer structure is arranged, so that the transmission can realize quick, smooth and reliable gear shifting, and is simple in structure and convenient to maintain.
In some embodiments, the double-stage planetary gear mechanism, the 1 st single-stage planetary gear mechanism, the 2 nd single-stage planetary gear mechanism, …, the ith single-stage planetary gear mechanism, …, and the nth single-stage planetary gear mechanism are arranged in sequence along an axial direction of the input shaft.
In some embodiments, the 1 st said synchronizer is disposed between said dual stage planetary gear mechanism and the 1 st said single stage planetary gear mechanism, …, the ith said synchronizer is disposed between the i-1 st said single stage planetary gear mechanism and the ith said single stage planetary gear mechanism, …, the n +1 th said synchronizer is disposed on a side of the nth said single stage planetary gear mechanism facing away from the n-1 st said single stage planetary gear mechanism.
In some embodiments, the output of the transmission is arranged on a side of the n +1 th synchronizer facing away from the nth single planetary gear mechanism.
In some embodiments, the output of the transmission comprises: the output shaft is connected with the n +1 th synchronizer, and the output gear is fixedly connected with the output shaft.
In some embodiments, the transmission according to the present invention further comprises: n intermediate shafts, the ith intermediate shaft being connected to the second sun gear of the ith single-stage planetary gear mechanism.
In some embodiments, the input shaft is arranged coaxially with the n intermediate shafts and arranged in axial sequence.
In some embodiments, the transmission according to the present invention further comprises: the driving gear is meshed with the idler, the idler is meshed with the driven gear, and the driven gear is connected with the input shaft.
In some embodiments, the transmission has 2n +1 gears.
The power drive system according to the present invention includes: the transmission according to the invention comprises a drive motor which is connected in a power-coupling manner to the input shaft.
The power driving system of the invention has corresponding advantages by arranging the speed changer of the invention, and the detailed description is omitted.
In some embodiments, the transmission is a transmission including a drive gear, an idler gear, and a driven gear, the drive motor is coupled to the drive gear, and the drive motor and the bipolar planetary gear mechanism are both disposed on a same side of the drive gear.
The vehicle according to the invention comprises the power drive system according to the invention.
The vehicle provided by the invention has the same advantages compared with the prior art by arranging the power driving system provided by the invention, and the detailed description is omitted.
Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.
Drawings
The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:
fig. 1 is a schematic structural diagram of a transmission according to an embodiment of the present invention.
Reference numerals:
a transmission 100; a housing 10;
a first sun gear 11; a first ring gear 12; a first carrier 13; a first planet 14;
a second sun gear 211 of the first single planetary gear mechanism; a second ring gear 212 of the first single-stage planetary gear mechanism; a second carrier 213 of the first single-stage planetary gear mechanism; the second planetary gear 214 of the first single-stage planetary gear mechanism;
a second sun gear 221 of the second single planetary gear mechanism; a second ring gear 222 of the second single-stage planetary gear mechanism; a second carrier 223 of the second single-stage planetary gear mechanism; the second planetary gear 224 of the second single-stage planetary gear mechanism;
an input shaft 3; a first intermediate shaft 41; second countershaft 42; an output shaft 51; an output gear 52;
a first synchronizer 61; a second synchronizer 62; a third synchronizer 63;
a drive gear 71; an idler pulley 72; a driven gear 73;
a driving motor 200;
a differential 300.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the accompanying drawings are illustrative only for the purpose of explaining the present invention, and are not to be construed as limiting the present invention.
A transmission 100 according to an embodiment of the present invention is described below with reference to fig. 1.
As shown in fig. 1, a transmission 100 according to an embodiment of the present invention includes: the planetary gear train comprises an input shaft 3, a double-stage planetary gear mechanism, n single-stage planetary gear mechanisms and n +1 synchronizers.
The torque of the vehicle can be input to the transmission 100 through the input shaft 3, and the torque can be finally output from the output end of the transmission 100 in the transmission 100 through the double-stage planetary gear mechanism and the n single-stage planetary gear mechanisms. The synchronizer is used to connect the various components within the transmission 100 to effect a gear shift.
The double-stage planetary gear mechanism and the n single-stage planetary gear mechanisms 1 may include a plurality of planetary gears that are connected to a planetary carrier. When the sun gear of each planetary gear mechanism rotates, each sun gear can drive the corresponding planet gear to rotate, and the planet carrier corresponding to the planet gear can selectively rotate. When the gear ring is fixed and the planet carrier is not fixed, the sun gear is input, and the planet gear rotates and drives the planet carrier to output; when the planet carrier is fixed and the gear ring is not fixed, the sun gear inputs, and the planet gear rotates and drives the gear ring to output; when the planet carrier and the gear ring are not fixed, the sun gear and the gear ring are input, and the planet gear rotates and drives the planet carrier to output; when the planet carrier and the gear ring are not fixed, the sun gear and the planet carrier input, and the planet gear rotates and drives the gear ring to output.
The single-stage planetary gear mechanism is simple in structure and can effectively enhance the torque transmission efficiency of the transmission, the double-stage planetary gear mechanism is the planetary gear mechanism with the double-stage planetary gears, and the sun wheel can drive the gear ring when reaching the two-stage planetary gears. The planet carrier of the double-stage planetary gear mechanism has fewer teeth, so that the double-stage planet is convenient to produce, and the rotation directions of the sun gear and the gear ring are the same when the planet carrier is fixed.
Because the rotation speed at the output shaft is relatively high and the torque is relatively small, the double-stage planetary gear mechanism is more suitable for the working conditions of high speed and low torque than the single-stage planetary gear mechanism, in some embodiments, as shown in fig. 1, the input end of the double-stage planetary gear mechanism can be connected with the input shaft 3, and the output end of the double-stage planetary gear mechanism can be connected with the input end of the single-stage planetary gear mechanism, that is, the torque can be transmitted to other single-stage planetary gear mechanisms after passing through the double-stage planetary gear mechanism first after entering the transmission.
The double-stage planetary gear mechanism includes a first sun gear 11, a first planetary gear 14, a first carrier 13, and a first ring gear 12, the first carrier 13 is fixedly connected to the housing 10 of the transmission 100, and the input shaft 3 is connected to the first sun gear 11, so that when torque is transmitted in the double-stage planetary gear mechanism, torque can be input to the first planetary gear mechanism from the first sun gear 11 through the input shaft 3 and output from the first planetary gear mechanism from the first ring gear 12.
Each single-stage planetary gear mechanism includes a second sun gear, a second planetary gear, a second planet carrier, and a second ring gear, and n second ring gears are fixedly connected to the housing 10 of the transmission 100, so that in each single-stage planetary gear mechanism, torque can be input into the single-stage planetary gear mechanism from the second sun gear of the single-stage planetary gear mechanism and output from the second planet carrier of the single-stage planetary gear mechanism.
The transmission 100 of the present invention includes: 1 double-stage planetary gear mechanism, n single-stage planetary gear mechanisms and n +1 synchronizers, wherein i and n are natural numbers, and i is more than or equal to 2 and less than or equal to n. For the sake of convenience of description, the 1 st single-stage planetary gear mechanism is defined as a first single-stage planetary gear mechanism, the 2 nd single-stage planetary gear mechanism is defined as a second single-stage planetary gear mechanism, the 1 st synchronizer is the first synchronizer 61, the 2 nd synchronizer is the second synchronizer 62, and so on.
The 1 st synchronizer is used to connect the second sun gear of the 1 st single-stage planetary gear set to the first ring gear 12 or to connect the second sun gear of the 1 st single-stage planetary gear set to the first sun gear 11: when the first synchronizer 61 connects the second sun gear 211 of the first single pinion planetary gear mechanism with the first ring gear 12, torque can be input to the first single pinion planetary gear mechanism from the first ring gear 12 of the double pinion planetary gear mechanism through the second sun gear 211 of the first single pinion planetary gear mechanism; when a synchronizer connects the second sun gear 211 of the first single planetary gear mechanism with the first sun gear 11, torque can be input from the first sun gear 11 of the dual planetary gear mechanism to the first single planetary gear mechanism through the second sun gear 211 of the first single planetary gear mechanism.
The ith synchronizer is used for connecting the second sun gear of the ith single-stage planetary gear mechanism with the second planet carrier of the (i-1) th single-stage planetary gear mechanism or connecting the second sun gear of the ith single-stage planetary gear mechanism with the second sun gear of the (i-1) th single-stage planetary gear mechanism, wherein i is more than or equal to 2 and less than or equal to n, namely the ith synchronizer is not the first synchronizer and not the last synchronizer: when the ith synchronizer connects the second sun gear of the ith single-stage planetary gear mechanism with the second carrier of the (i-1) th single-stage planetary gear mechanism, the torque of the ith single-stage planetary gear mechanism is input to the ith single-stage planetary gear mechanism from the second carrier of the (n-i) th single-stage planetary gear mechanism; when the ith synchronizer connects the second sun gear of the ith single pinion planetary gear mechanism with the second sun gear of the (i-1) th single pinion planetary gear mechanism, the torque of the ith single pinion planetary gear mechanism is input to the ith single pinion planetary gear mechanism from the second sun gear of the (n-i) th single pinion planetary gear mechanism.
The (n + 1) th synchronizer (i.e., the last synchronizer) is used to connect the output of the transmission 100 with the second carrier of the nth single-stage planetary gear mechanism or to connect the output of the transmission 100 with the second sun gear of the nth single-stage planetary gear mechanism: when the (n + 1) th synchronizer connects the output of the transmission 100 with the second carrier of the nth single stage planetary gear mechanism, torque is output from the transmission 100 by the second carrier of the nth single stage planetary gear mechanism; when the (n + 1) th synchronizer connects the output of the transmission 100 with the second sun gear of the nth single planetary gear mechanism, torque is output from the transmission 100 by the second sun gear of the nth single planetary gear mechanism.
According to the transmission 100 provided by the embodiment of the invention, by arranging the n +1 th synchronizer and the n +1 planetary gear structure (namely 1 double-stage planetary gear mechanism and n single-stage planetary gear mechanisms), namely the structure of the n +1 planetary gear row n +1 synchronizer, the gear shifting mode of the transmission enables the motor control synchronizer to shift gears, the structure is simple, the gear shifting is fast, the efficiency is high, and the dragging torque problem of a multi-plate clutch and a multi-plate brake does not exist. Meanwhile, the cost is lower, the maintenance is simpler and more convenient, the synchronizer is adopted for shifting, and the structure of the transmission 100 is simplified without a clutch.
According to the transmission 100 provided by the embodiment of the invention, the n +1 synchronizer structure of the n +1 planet row is arranged, so that the gear shifting can be realized quickly, smoothly and reliably, and the transmission 100 is simple in structure and convenient to maintain.
Some embodiments of a transmission 100 according to the present invention are described below with reference to fig. 1.
In some embodiments, as shown in fig. 1, the double-stage planetary gear mechanism, the 1 st single-stage planetary gear mechanism, the 2 nd single-stage planetary gear mechanism, …, the ith single-stage planetary gear mechanism, … and the nth single-stage planetary gear mechanism are sequentially arranged along the axial direction of the input shaft 3, that is, all the planetary gear mechanisms (including the double-stage planetary gear mechanism and each single-stage planetary gear mechanism) in the speed reducer can be sequentially arranged along the axial direction of the input shaft 3, so that the arrangement of each planetary gear mechanism can be facilitated, and the transmission direction of the torque from the double-stage planetary gear mechanism to the last single-stage planetary gear mechanism is unchanged, thereby facilitating the transmission of the torque in the transmission 100.
In some embodiments, as shown in fig. 1, the 1 st synchronizer is disposed between the dual stage planetary gear mechanism and the 1 st single stage planetary gear mechanism, …, the ith synchronizer is disposed between the i-1 st single stage planetary gear mechanism and the ith single stage planetary gear mechanism, …, the (n + 1) th synchronizer is disposed on a side of the nth single stage planetary gear mechanism facing away from the n-1 th single stage planetary gear mechanism.
Thus, the 1 st synchronizer may be disposed between the double-stage planetary gear mechanism and the 1 st single-stage planetary gear mechanism.
In the case of the nth synchronizer (where 2 ≦ n, i.e., the synchronizer is neither the 1 st nor the last synchronizer), the nth synchronizer may be disposed between the two single-stage planetary gear mechanisms connected thereto, the nth synchronizer may be disposed between the nth single-stage planetary gear mechanism and the n +1 th single-stage planetary gear, for example, n ≦ 2, and the 2 nd synchronizer may be disposed between the 2 nd single-stage planetary gear mechanism and the third single-stage planetary gear mechanism.
The (n + 1) th synchronizer (i.e., the last synchronizer) is disposed on the side facing away from the (n-1) th single-stage planetary gear mechanism, i.e., the last synchronizer may be disposed on the side facing away from the second last single-stage planetary gear mechanism, and when n is 2, the 3 rd synchronizer may be disposed on the side facing away from the 2 nd single-stage planetary gear mechanism, so that the distances between the respective planetary gear mechanisms can be made close, facilitating the disposition of the synchronizers and the respective planetary gear mechanisms in the transmission 100.
In some embodiments, as shown in fig. 1, the output of the transmission 100 is arranged on the side of the (n + 1) th synchronizer facing away from the nth single stage planetary gear mechanism, i.e., the output is arranged on the side facing away from the last single stage planetary gear mechanism, which can facilitate the arrangement of the output of the transmission 100.
In some embodiments, as shown in FIG. 1, the output of the transmission 100 includes: an output shaft 51 and an output gear 52, the output shaft 51 is connected with the (n + 1) th synchronizer, the output gear 52 is fixedly connected with the output shaft 51, namely, the output shaft 51 is connected with the last synchronizer, so that the last synchronizer can connect the output shaft 51 with the second sun gear of the last single-stage planetary gear mechanism or connect the output shaft 51 with the second planet carrier of the last single-stage planetary gear mechanism, and further, the torque can be selectively output from the second sun gear or the second planet carrier of the last single-stage planetary gear mechanism from the transmission 100.
In some embodiments, as shown in fig. 1, a transmission 100 according to an embodiment of the present invention further includes: n countershafts, the ith countershaft being connected to the second sun gear of the ith single-stage planetary gear set, for example, i ═ 1, and the 1 st countershaft being connected to the second sun gear of the 1 st single-stage planetary gear set; the 2 nd intermediate shaft is connected to the second sun gear of the 2 nd single-stage planetary gear mechanism, and the intermediate shaft is provided to transmit torque between the planetary gear mechanisms.
In some embodiments, as shown in fig. 1, the input shaft 3 is arranged coaxially with the n intermediate shafts and arranged in series in the axial direction, so that the transmission of torque in the transmission 100 can be facilitated and the transmission of torque in the transmission 100 can be made more efficient.
In some embodiments, as shown in fig. 1, a transmission 100 according to an embodiment of the present invention further includes: the transmission comprises a driving gear 71, an idler gear 72 and a driven gear 73, wherein the driving gear 71 is meshed with the idler gear 72, the idler gear 72 is meshed with the driven gear 73, the driven gear 73 is connected with an input shaft 3, torque can be transmitted to the input shaft 3 through the driving gear 71, the idler gear 72 and the driven gear 73 in sequence at a motor or an engine of a vehicle, the torque is transmitted to a first planetary gear mechanism through the input shaft 3, and the driving gear 71, the idler gear 72 and the driven gear 73 can change the torque transmission direction of the motor or the engine of the vehicle, so that the transmission 100 and the motor or the engine of the vehicle can be arranged side by side. That is, the axis of the transmission 100 is parallel to the axis of the motor or the engine, so that the length of the power drive system of the vehicle in the axial direction can be reduced, and the space for disposing the power drive system on the vehicle can be saved.
In some embodiments, the transmission 100 according to the embodiment of the invention may have 2n +1 gears, i.e., first gear, second gear, …, ith gear, …, 2n +1 gears, wherein the speed ratio of the first gear to the 2n +1 gears is reduced in order, i.e., the speed ratio u1 of the first gear > the speed ratio u2 > … of the second gear > the speed ratio ui > … of the ith gear > the speed ratio u2n +1 of the 2n +1 gears.
According to the transmission 100 provided by the embodiment of the invention, the transmission 100 can have a 2n +1 gear shifting structure by arranging n +1 synchronizers, and for medium and heavy trucks, the 2n +1 gear structure is adopted due to large torque demand range, uncertain load and complex working condition, so that the motor is ensured to operate in a high-efficiency area, and the electric energy is saved. The synchronizer is adopted for shifting, and a clutch is not used, so that the structure is simplified.
Referring to fig. 1, a transmission 100 according to an embodiment of the present invention is described below, taking n-2 as an example, where the transmission 100 includes 1 two-stage planetary gear mechanism, 2 single-stage planetary gear mechanism, 3 synchronizers, and 2 countershafts as examples to describe a transmission path of torque in the transmission 100:
for convenience of description, the 1 st single-stage planetary gear mechanism is defined as a first single-stage planetary gear mechanism, the 2 nd single-stage planetary gear mechanism is defined as a second single-stage planetary gear mechanism, the 1 st synchronizer is defined as a first synchronizer 61, the 2 nd synchronizer is defined as a second synchronizer 62, the 3 rd synchronizer is defined as a third synchronizer 63, the 1 st countershaft is defined as a first countershaft 41, the 2 nd countershaft is defined as a second countershaft 42, the 3 rd countershaft is defined as a third countershaft, the transmission 100 may have 8 total gears, and the speed ratio u1 of the first gear is greater than the speed ratio u2 of the second gear is greater than the speed ratio u3 of the third gear is greater than the speed ratio u4 of the fourth gear is greater than the speed ratio u5 of the fifth gear is greater than the speed ratio u6 of the sixth gear is greater than the speed ratio u7 of the seventh gear is greater than the speed ratio u8 of the eighth gear.
In some examples, the speed ratio of first gear 18 ≦ u1 ≦ 28, e.g., u1 ≦ 20; the speed ratio of the second gear is 11.8 ≦ u2 ≦ 14.8, for example, u2 ≦ 13; the speed ratio of the third gear is 7.8 ≦ u3 ≦ 9.8, e.g., u3 ≦ 9; the speed ratio of the fourth gear is 5.8 ≦ u4 ≦ 6.8, for example, u4 ≦ 6; the speed ratio of the fifth gear is 3.8 ≦ u5 ≦ 5.5, for example, u5 ≦ 4; the speed ratio of 2.8 of the sixth gear is less than or equal to u6 and less than or equal to 3.5, for example, u6 is 3; the speed ratio of the seventh gear is 1.8 ≦ u7 ≦ 2.4, e.g., u7 ≦ 2.2; the speed ratio u8 of the eighth gear is 1.
Wherein the first two-stage planetary gear mechanism comprises: a first sun gear 11, a first ring gear 12, a first carrier 13, and a first planetary gear 14; the first single-stage planetary gear includes: a second sun gear 211 of the first single pinion planetary gear mechanism, a second ring gear 212 of the first single pinion planetary gear mechanism, a second carrier 213 of the first single pinion planetary gear mechanism, a second planet gear 214 of the first single pinion planetary gear mechanism; the second single-stage planetary gear mechanism includes: a second sun gear 221 of the second single pinion planetary gear mechanism, a second ring gear 222 of the second single pinion planetary gear mechanism, a second planet carrier 223 of the second single pinion planetary gear mechanism, and a second planet gear 224 of the second single pinion planetary gear mechanism.
The operating states of the first synchronizer 61, the second synchronizer 62, and the third synchronizer 63 of each gear of the transmission 100, and the torque transmission path during the transmission 100 in which torque is transmitted from the input shaft 3 to the output shaft 51 are described below with reference to fig. 1.
When the transmission 100 is in the first gear, the first synchronizer 61 connects the second sun gear 211 of the first single-stage planetary gear mechanism with the first ring gear 12 of the dual-stage planetary gear mechanism, the second synchronizer 62 connects the second carrier 213 of the first single-stage planetary gear mechanism with the second sun gear 221 of the second single-stage planetary gear mechanism, and the third synchronizer 63 connects the second carrier 223 of the second single-stage planetary gear mechanism with the output shaft 51.
Thus, torque is transmitted from the input shaft 3 to the transmission 100, the input shaft 3 transmits torque to the first sun gear 11, torque is output from the first ring gear 12 of the double-pinion planetary gear mechanism to the first intermediate shaft 41, and torque is transmitted through the first intermediate shaft 41 to the second sun gear 211 of the first single-pinion planetary gear mechanism, in which torque is input from the second sun gear 211 of the first single-pinion planetary gear mechanism and output from the second carrier 213 of the first single-pinion planetary gear mechanism to the second intermediate shaft 42, and in which torque is input from the second sun gear 221 of the second single-pinion planetary gear mechanism and output from the second carrier 223 of the second single-pinion planetary gear mechanism to the output shaft 51.
Thus, in the first gear of the transmission 100, in the first planetary gear mechanism, torque is input from the first sun gear 11 and output from the first ring gear 12 to the first intermediate shaft 41, at which time the torque is in the same rotational direction with respect to the input shaft 3 and the rotational speed is reduced, the torque is transmitted to the first single stage planetary gear mechanism via the first intermediate shaft 41 and input from the second sun gear 211 of the first single stage planetary gear mechanism, the second carrier 213 of the first single stage planetary gear mechanism is output to the second intermediate shaft 42, the torque is in the same rotational direction with respect to the first intermediate shaft 41 via the first single stage planetary gear mechanism and the rotational speed is reduced, the torque is transmitted to the second single stage planetary gear mechanism via the second intermediate shaft 42 and input from the second sun gear 221 of the second single stage planetary gear mechanism, the second carrier 223 of the second single stage planetary gear mechanism is output to the output shaft 51, the torque is transmitted to the transmission 100 through the two-stage planetary gear mechanism, the three-stage speed reduction of the first single-stage planetary gear mechanism and the second single-stage planetary gear mechanism after being transmitted to the transmission 100 from the input shaft 3 in the first gear, and the torque transmission directions of the input shaft 3 and the output shaft 51 are unchanged.
When the transmission 100 is in the second gear, the first synchronizer 61 connects the second sun gear 211 of the first single planetary gear mechanism with the first sun gear 11, the second synchronizer 62 connects the second carrier 213 of the first single planetary gear mechanism with the second sun gear 221 of the second single planetary gear mechanism, and the third synchronizer 63 connects the second carrier 223 of the second single planetary gear mechanism with the output shaft 51.
Thus, torque is transmitted from the input shaft 3 to the transmission 100, the input shaft 3 transmits torque to the first sun gear 11, the torque is output from the first sun gear 11 of the double-pinion planetary gear mechanism to the first intermediate shaft 41, and the torque is transmitted to the second sun gear 211 of the first single-pinion planetary gear mechanism through the first intermediate shaft 41, in which the torque is input from the second sun gear 211 of the first single-pinion planetary gear mechanism and is output from the second carrier 213 of the first single-pinion planetary gear mechanism to the second intermediate shaft 42, and in which the torque is input from the second sun gear 221 of the second single-pinion planetary gear mechanism and is output from the second carrier 223 of the second single-pinion planetary gear mechanism to the output shaft 51.
Thus, in the first gear of the transmission 100, in the first planetary gear mechanism, torque is input from the first sun gear 11 and output from the first sun gear 11 to the first intermediate shaft 41, while torque is in the same rotational direction and at the same rotational speed as the input shaft 3, torque is transmitted to the first single-stage planetary gear mechanism via the first intermediate shaft 41 and input from the second sun gear 211 of the first single-stage planetary gear mechanism, the second carrier 213 of the first single-stage planetary gear mechanism is output to the second intermediate shaft 42, torque is in the same rotational direction as the first intermediate shaft 41 via the first single-stage planetary gear mechanism, rotational speed is reduced, torque is transmitted to the second single-stage planetary gear mechanism via the second intermediate shaft 42 and input from the second sun gear 221 of the second single-stage planetary gear mechanism, the second carrier 223 of the second single-stage planetary gear mechanism is output to the output shaft 51, the torque is transmitted from the input shaft 3 to the transmission 100 in the second gear, and then the torque is transmitted out of the transmission 100 through the two-stage speed reduction of the first single-stage planetary gear mechanism and the second single-stage planetary gear mechanism, and the torque transmission directions of the input shaft 3 and the output shaft 51 are unchanged, and the speed ratio u1 of the first gear of the transmission 100 is greater than the speed ratio u2 of the second gear with respect to the three-stage speed reduction in the first gear.
When the transmission 100 is in the third gear, the first synchronizer 61 connects the second sun gear 211 of the first single-stage planetary gear mechanism with the first ring gear 12 of the dual-stage planetary gear mechanism, the second synchronizer 62 connects the second sun gear 211 of the first single-stage planetary gear mechanism with the second sun gear 221 of the second single-stage planetary gear mechanism, and the third synchronizer 63 connects the second carrier 223 of the second single-stage planetary gear mechanism with the output shaft 51.
Thus, torque is transmitted from the input shaft 3 to the transmission 100, the input shaft 3 transmits torque to the first sun gear 11, the torque is output from the first ring gear 12 of the double pinion planetary gear mechanism 1 to the first intermediate shaft 41, and the torque is transmitted to the second sun gear 211 of the first single pinion planetary gear mechanism by the first intermediate shaft 415, in which the torque is input from the second sun gear 211 of the first single pinion planetary gear mechanism and is output from the second sun gear 211 of the first single pinion planetary gear mechanism to the second intermediate shaft 42, and in which the torque is input from the second sun gear 221 of the second single pinion planetary gear mechanism and is output from the second carrier 223 of the second single pinion planetary gear mechanism to the output shaft 51.
Thus, in the third gear of the transmission 100, in the first planetary gear mechanism, torque is input from the first sun gear 11 and output from the first ring gear 12 to the first intermediate shaft 41, at which time the torque is in the same rotational direction with respect to the input shaft 3 and the rotational speed is reduced, the torque is transmitted to the first single-stage planetary gear mechanism via the first intermediate shaft 41 and is input from the second sun gear 211 of the first single-stage planetary gear mechanism, the second sun gear 211 of the first single-stage planetary gear mechanism is output to the second intermediate shaft 42, the torque is in the same rotational direction with respect to the first intermediate shaft 41 via the first single-stage planetary gear mechanism and is not changed in rotational speed, the torque is transmitted to the second single-stage planetary gear mechanism via the second intermediate shaft 42 and is input from the second sun gear 221 of the second single-stage planetary gear mechanism, the second carrier 223 of the second single-stage planetary gear mechanism is output to the output shaft 51, the rotation direction of the torque transmitted from the input shaft 3 to the transmission 100 in the third gear is the same through the second single-stage planetary gear mechanism relative to the second intermediate shaft 42, the rotation speed is reduced, the torque is transmitted out of the transmission 100 through the two-stage speed reduction of the double-stage planetary gear mechanism and the second single-stage planetary gear mechanism, the torque transmission direction of the input shaft 3 and the torque transmission direction of the output shaft 51 are unchanged, and when the transmission 100 is in the third gear relative to the second gear, the double-stage planetary gear mechanism, the first single-stage planetary gear mechanism and the second single-stage planetary gear mechanism can be designed such that when the rotation speed of the input shaft 3 is constant, the rotation speed of the output shaft 51 of the third gear is faster than that of the output gear 52 of the second gear, and therefore, the speed ratio u2 of the second gear is greater than the speed ratio u 35.
When the transmission 100 is in the fourth gear, the first synchronizer 61 connects the second sun gear 211 of the first single-stage planetary gear mechanism with the first ring gear 12 of the dual-stage planetary gear mechanism, the second synchronizer 62 connects the second carrier 213 of the first single-stage planetary gear mechanism with the second sun gear 221 of the second single-stage planetary gear mechanism, and the third synchronizer 63 connects the second sun gear 221 of the second single-stage planetary gear mechanism with the output shaft 51.
In this way, when the transmission 100 is in the fourth gear, torque is transmitted from the input shaft 3 to the transmission 100, the input shaft 3 transmits the torque to the first sun gear 11, the torque is output from the first ring gear 12 of the double-stage planetary gear mechanism to the first intermediate shaft 41, and the torque is transmitted from the first intermediate shaft 41 to the second sun gear 211 of the first single-stage planetary gear mechanism, in which the torque is input from the second sun gear 211 of the first single-stage planetary gear mechanism and is output from the second carrier 213 of the first single-stage planetary gear mechanism to the second intermediate shaft 42, and in which the torque is input from the second sun gear 221 of the second single-stage planetary gear mechanism and is output from the second sun gear 221 of the second single-stage planetary gear mechanism to the output shaft 51.
Thus, in the fourth gear of the transmission 100, in the first planetary gear mechanism, torque is input from the first sun gear 11 and output from the first ring gear 12 to the first intermediate shaft 41, at which time the torque is in the same rotational direction with respect to the input shaft 3 and the rotational speed is reduced, the torque is transmitted to the first single stage planetary gear mechanism via the first intermediate shaft 41 and is input from the second sun gear 211 of the first single stage planetary gear mechanism, the second carrier 213 of the first single stage planetary gear mechanism is output to the second intermediate shaft 42, the torque is in the same rotational direction with respect to the first intermediate shaft 41 via the first single stage planetary gear mechanism and the rotational speed is reduced, the torque is transmitted to the second single stage planetary gear mechanism via the second intermediate shaft 42 and is input from the second sun gear 221 of the second single stage planetary gear mechanism, the second sun gear 221 of the second single stage planetary gear mechanism is output to the output shaft 51, the second single-stage planetary gear mechanism has the same rotation direction of the torque relative to the second intermediate shaft 42, the rotation speed is unchanged, in the fourth gear, after the torque is transmitted from the input shaft 3 to the transmission 100, the torque is transmitted out of the transmission 100 through two-stage speed reduction of the double-stage planetary gear mechanism and the first single-stage planetary gear mechanism, and the torque transmission direction of the input shaft 3 and the torque transmission direction of the output shaft 51 are unchanged, and the double-stage planetary gear mechanism, the first single-stage planetary gear mechanism and the second single-stage planetary gear mechanism can be designed such that when the rotation speed of the input shaft 3 is constant, the rotation speed of the output shaft 51 of the fourth gear is faster than that of the output gear 52 of the third gear, so that the speed ratio u3 of the third gear is greater than the speed ratio u 2.
When the transmission 100 is in the fifth gear, the first synchronizer 61 connects the second sun gear 211 of the first single-stage planetary gear mechanism with the first sun gear 11 of the two-stage planetary gear mechanism, the second synchronizer 62 connects the second sun gear 211 of the first single-stage planetary gear mechanism with the second sun gear 221 of the second single-stage planetary gear mechanism, and the third synchronizer 63 connects the second carrier 223 of the second single-stage planetary gear mechanism with the output shaft 51.
Thus, torque is transmitted from the input shaft 3 to the transmission 100, the input shaft 3 transmits torque to the first sun gear 11, the torque is output from the first sun gear 11 of the double-pinion planetary gear mechanism to the first intermediate shaft 41, and the torque is transmitted to the second sun gear 211 of the first single-pinion planetary gear mechanism via the first intermediate shaft 41, in which the torque is input from the second sun gear 211 of the first single-pinion planetary gear mechanism and is output from the second sun gear 211 of the first single-pinion planetary gear mechanism to the second intermediate shaft 42, and in which the torque is input from the second sun gear 221 of the second single-pinion planetary gear mechanism and is output from the second carrier 223 of the second single-pinion planetary gear mechanism to the output shaft 51.
Thus, in the fifth gear of the transmission 100, in the first planetary gear mechanism, torque is input from the first sun gear 11 and output from the first sun gear 11 to the first intermediate shaft 41, at this time, the torque is the same in the rotational direction with respect to the input shaft 3 and the rotational speed is unchanged, torque is transmitted to the first single-stage planetary gear mechanism via the first intermediate shaft 41 and is input from the second sun gear 211 of the first single-stage planetary gear mechanism, the second sun gear 211 of the first single-stage planetary gear mechanism is output to the second intermediate shaft 42, torque is the same in the rotational direction with respect to the first intermediate shaft 41 via the first single-stage planetary gear mechanism and the rotational speed is unchanged, torque is transmitted to the second single-stage planetary gear mechanism via the second intermediate shaft 42 and is input from the second sun gear 221 of the second single-stage planetary gear mechanism, the second carrier 223 of the second single-stage planetary gear mechanism is output to the output shaft 51, the torque is transmitted from the input shaft 3 to the transmission 100 in the first gear through the second single-stage planetary gear mechanism, and then is transmitted out of the transmission 100 through the first-stage speed reduction of the second single-stage planetary gear mechanism, and the torque transmission directions of the input shaft 3 and the output shaft 51 are unchanged, and the speed ratio u5 of the fifth gear of the transmission 100 is greater than the speed ratio u4 of the fourth gear relative to the second-stage speed reduction in the fourth gear.
When the transmission 100 is in the sixth gear, the first synchronizer 61 connects the second sun gear 211 of the first single-stage planetary gear mechanism with the first sun gear 11 of the two-stage planetary gear mechanism, the second synchronizer 62 connects the second carrier 213 of the first single-stage planetary gear mechanism with the second sun gear 221 of the second single-stage planetary gear mechanism, and the third synchronizer 63 connects the second sun gear 221 of the second single-stage planetary gear mechanism with the output shaft 51.
Thus, torque is transmitted from the input shaft 3 to the transmission 100, the input shaft 3 transmits torque to the first sun gear 11, the torque is output from the first sun gear 11 of the double-pinion planetary gear mechanism to the first intermediate shaft 41, and the torque is transmitted to the second sun gear 211 of the first single-pinion planetary gear mechanism through the first intermediate shaft 41, in which the torque is input from the second sun gear 21131 of the first single-pinion planetary gear mechanism and is output from the second carrier 213 of the first single-pinion planetary gear mechanism to the second intermediate shaft 42, and in which the torque is input from the second sun gear 221 of the second single-pinion planetary gear mechanism and is output from the second sun gear 221 of the second single-pinion planetary gear mechanism to the output shaft 51.
Thus, in the sixth gear of the transmission 100, in the first planetary gear mechanism, torque is input from the first sun gear 11 and output from the first sun gear 11 to the first intermediate shaft 41, while torque is in the same rotational direction and at the same rotational speed as the input shaft 3, torque is transmitted to the first single-stage planetary gear mechanism via the first intermediate shaft 41 and input from the second sun gear 211 of the first single-stage planetary gear mechanism, the second carrier 213 of the first single-stage planetary gear mechanism is output to the second intermediate shaft 42, torque is in the same rotational direction as the first intermediate shaft 41 via the first single-stage planetary gear mechanism, rotational speed is reduced, torque is transmitted to the second single-stage planetary gear mechanism via the second intermediate shaft 42 and input from the second sun gear 221 of the second single-stage planetary gear mechanism, the second sun gear 221 of the second single-stage planetary gear mechanism is output to the output shaft 51, the torque passing through the second single-stage planetary gear mechanism has the same rotation direction and constant rotation speed relative to the second intermediate shaft 42, and when the transmission 100 is in the sixth gear, relative to the fifth gear, the first single-stage planetary gear mechanism and the second single-stage planetary gear mechanism can be designed such that when the input shaft 3 rotates for a certain speed, the rotation speed of the output shaft 51 of the sixth gear is faster than that of the output gear 52 of the fifth gear, so that the speed ratio u6 of the sixth gear is greater than the speed ratio u5 of the fifth gear.
When the transmission 100 is in the seventh gear, the first synchronizer 61 connects the second sun gear 211 of the first single-stage planetary gear mechanism with the first ring gear 12 of the dual-stage planetary gear mechanism, the second synchronizer 62 connects the second sun gear 211 of the first single-stage planetary gear mechanism with the second sun gear 221 of the second single-stage planetary gear mechanism, and the third synchronizer 63 connects the second sun gear 221 of the second single-stage planetary gear mechanism with the output shaft 51.
Thus, torque is transmitted from the input shaft 3 to the transmission 100, the input shaft 3 transmits torque to the first sun gear 11, torque is output from the first ring gear 12 of the double planetary gear mechanism to the first intermediate shaft 41, and torque is transmitted through the first intermediate shaft 41 to the second sun gear 211 of the first single planetary gear mechanism in which torque is input from the second sun gear 21131 of the first single planetary gear mechanism and output from the second sun gear 211 of the first single planetary gear mechanism to the second intermediate shaft 42, and torque is input from the second sun gear 221 of the second single planetary gear mechanism in which torque is output from the second sun gear 221 of the second single planetary gear mechanism to the output shaft 51.
Thus, in the seventh gear of the transmission 100, in the first planetary gear mechanism, torque is input from the first sun gear 11 and output from the first ring gear 12 to the first intermediate shaft 41, at which time the torque is in the same rotational direction with respect to the input shaft 3 and the rotational speed is reduced, the torque is transmitted to the first single-stage planetary gear mechanism via the first intermediate shaft 41 and is input from the second sun gear 211 of the first single-stage planetary gear mechanism, the second sun gear 211 of the first single-stage planetary gear mechanism is output to the second intermediate shaft 42, the torque is in the same rotational direction with respect to the first intermediate shaft 41 via the first single-stage planetary gear mechanism and the rotational speed is not changed, the torque is transmitted to the second single-stage planetary gear mechanism via the second intermediate shaft 42 and is input from the second sun gear 221 of the second single-stage planetary gear mechanism, the second sun gear 221 of the second single-stage planetary gear mechanism is output to the output shaft 51, the torque passing through the second single-stage planetary gear mechanism has the same rotation direction and constant rotation speed relative to the second intermediate shaft 42, and when the transmission 100 is in the seventh gear, relative to the sixth gear, the two-stage planetary gear mechanism and the first single-stage planetary gear mechanism can be designed such that when the input shaft 3 rotates at a constant speed, the rotation speed of the output shaft 51 of the seventh gear is faster than that of the output gear 52 of the sixth gear, so that the speed ratio u6 of the sixth gear is greater than the speed ratio u7 of the seventh gear.
When the transmission 100 is engaged in the eighth gear, the first synchronizer 61 connects the second sun gear 211 of the first single-stage planetary gear mechanism with the first sun gear 11 of the two-stage planetary gear mechanism, the second synchronizer 62 connects the second sun gear 211 of the first single-stage planetary gear mechanism with the second sun gear 221 of the second single-stage planetary gear mechanism, and the third synchronizer 63 connects the second sun gear 221 of the second single-stage planetary gear mechanism with the output shaft 51.
Thus, torque is transmitted from the input shaft 3 to the transmission 100, the input shaft 3 transmits torque to the first sun gear 11, the torque is output from the first sun gear 11 of the double-pinion planetary gear mechanism to the first intermediate shaft 41, and the torque is transmitted to the second sun gear 211 of the first single-pinion planetary gear mechanism through the first intermediate shaft 41, in which the torque is input from the second sun gear 21131 of the first single-pinion planetary gear mechanism and is output from the second sun gear 211 of the first single-pinion planetary gear mechanism to the second intermediate shaft 42, and in which the torque is input from the second sun gear 221 of the second single-pinion planetary gear mechanism and is output from the second sun gear 221 of the second single-pinion planetary gear mechanism to the output shaft 51.
Thus, in the eighth gear of the transmission 100, in the first planetary gear mechanism, torque is input from the first sun gear 11 and output from the first sun gear 11 to the first intermediate shaft 41, at this time, the torque is the same in the rotational direction with respect to the input shaft 3 and the rotational speed is unchanged, the torque is transmitted to the first single-stage planetary gear mechanism via the first intermediate shaft 41 and is input from the second sun gear 211 of the first single-stage planetary gear mechanism, the second sun gear 211 of the first single-stage planetary gear mechanism is output to the second intermediate shaft 42, the torque is the same in the rotational direction with respect to the first intermediate shaft 41 via the first single-stage planetary gear mechanism and the rotational speed is unchanged, the torque is transmitted to the second single-stage planetary gear mechanism via the second intermediate shaft 42 and is input from the second sun gear 221 of the second single-stage planetary gear mechanism, the second sun gear 221 of the second single-stage planetary gear mechanism is output to the output shaft 51, the torque is transmitted to the output shaft 51 through the first intermediate shaft 41 and the second intermediate shaft 42 directly from the input shaft 3 to the output shaft 100 without being reduced in speed in the transmission 100 in the eighth gear, so that the speed ratio u7 of the 7 th gear is larger than the speed ratio u8 of the eighth gear.
In summary, the transmission 100 of the present invention belongs to a horizontal transmission 100, and adopts a three-planetary-row three-synchronizer structure, and the gear shifting manner thereof can be a motor-controlled synchronizer gear shifting manner, and has the advantages of simple structure, fast gear shifting, and high torque transmission efficiency, and the problem of drag torque of a multi-plate clutch and a multi-plate brake does not exist. Meanwhile, the transmission 100 has lower manufacturing cost and simpler maintenance, and the transmission 100 according to the embodiment of the present invention may also adopt a structure of multiple planetary rows and multiple transmissions 100, and has the same advantages as described above and will not be described herein again.
The synchronizer is adopted for shifting, a clutch is not needed, the structure is simplified, and the transmission 100 adopts a multi-gear speed change structure, so that the electric energy can be saved when the motor operates in a high-efficiency area.
A power drive system according to an embodiment of the present invention includes: a driving motor 200 and the transmission 100 of any one of the above embodiments, wherein the driving motor 200 is in power coupling connection with the input shaft 3. In this way, the power driving system according to the embodiment of the present invention has the advantages of fast gear shifting, high torque transmission efficiency, smooth gear shifting, and simple structure by providing the transmission 100 according to the embodiment of the present invention.
In some embodiments, the transmission 100 according to the embodiment of the present invention is a transmission 100 having a driving gear 71, an idler gear 72, and a driven gear 73, the driving motor 200 and the bipolar planetary gear mechanism are both disposed on the same side of the driving gear 71, and the driving motor 200 and the axis of the input shaft 3 may be arranged in parallel, that is, the driving motor 200 and the transmission 100 may be arranged side by side, so that the axial length of the power driving system may be reduced, and the space for disposing the power driving system on the vehicle may be saved.
A vehicle according to an embodiment of the present invention includes: in the power driving system of the embodiment, the vehicle is provided with the power driving system, so that the vehicle has the advantages of smooth gear shifting, quick gear shifting and high torque transmission efficiency, the output torque range of the vehicle is large, the load is stable, the vehicle can cope with complex road conditions, and the power driving system has the advantage of saving energy.
In some examples, as shown in fig. 1, the vehicle may further include a differential 300, wherein an input end of the differential 300 is connected to an output end of the speed reducer, so that the torque output by the transmission 100 can be input into the differential 300 and finally drive wheels of the vehicle to rotate, thereby realizing the running of the vehicle.
In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the invention and to simplify the description, and are not intended to indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and are not to be considered limiting of the invention.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an illustrative embodiment," "an example," "a specific example," or "some examples" or the like mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
While embodiments of the invention have been shown and described, it will be understood by those of ordinary skill in the art that: various changes, modifications, substitutions and alterations can be made to the embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.
Claims (12)
1. A transmission, comprising:
the double-stage planetary gear mechanism comprises a first sun gear, a first planetary gear, a first planet carrier and a first gear ring, wherein the first planet carrier is fixedly connected with a shell of the transmission;
the single-stage planetary gear mechanism comprises a first sun gear, a first planet carrier and a first gear ring, and the single-stage planetary gear mechanism comprises n single-stage planetary gear mechanisms;
an input shaft connected to the first sun gear;
n +1 synchronizers for connecting the second sun gear of the 1 st of the single pinion planetary gear mechanisms with the first ring gear or the second sun gear of the 1 st of the single pinion planetary gear mechanisms with the first sun gear, the ith of the synchronizers for connecting the second sun gear of the ith of the single pinion planetary gear mechanisms with the second carrier of the i-1 th of the single pinion planetary gear mechanisms or the second sun gear of the ith of the single pinion planetary gear mechanisms with the second sun gear of the i-1 th of the single pinion planetary gear mechanisms, the n +1 th of the synchronizers for connecting the output of the transmission with the second carrier of the nth of the single pinion planetary gear mechanisms or the output of the transmission with the second sun gear of the nth of the single pinion planetary gear mechanisms, wherein i is more than or equal to 2 and less than or equal to n, and i and n are natural numbers.
2. The transmission of claim 1 wherein the dual stage planetary gear mechanism, the 1 st of the single stage planetary gear mechanisms, the 2 nd of the single stage planetary gear mechanisms, …, the ith of the single stage planetary gear mechanisms, …, the nth of the single stage planetary gear mechanisms are arranged in sequence along an axial direction of the input shaft.
3. The transmission of claim 2 wherein the 1 st synchronizer is disposed between the dual stage planetary gear mechanism and the 1 st of the single stage planetary gear mechanisms, …, the ith synchronizer is disposed between the i-1 st of the single stage planetary gear mechanisms and the ith of the single stage planetary gear mechanisms, …, the n +1 th synchronizer is disposed on a side of the nth of the single stage planetary gear mechanisms that faces away from the n-1 st of the single stage planetary gear mechanisms.
4. The transmission of claim 3, wherein the output of the transmission is arranged on a side of the n +1 th synchronizer facing away from the nth single stage planetary gear mechanism.
5. The transmission of claim 1, wherein the output of the transmission comprises: the output shaft is connected with the n +1 th synchronizer, and the output gear is fixedly connected with the output shaft.
6. The transmission of claim 1, further comprising: n intermediate shafts, the ith intermediate shaft being connected to the second sun gear of the ith single-stage planetary gear mechanism.
7. The transmission of claim 6 wherein said input shaft is coaxially disposed with n of said intermediate shafts and is axially disposed in sequence.
8. The transmission of claim 1, further comprising: the driving gear is meshed with the idler, the idler is meshed with the driven gear, and the driven gear is connected with the input shaft.
9. The transmission of any of claims 1-8, wherein the transmission has 2n+1And (4) each gear.
10. A power drive system, comprising:
a drive motor;
the transmission of any one of claims 1-9, said drive motor being in power-coupled connection with said input shaft.
11. The power drive system according to claim 10, characterized in that the transmission is the transmission according to claim 8,
the driving motor is connected with the driving gear, and both the driving motor and the bipolar planetary gear mechanism are arranged on the same side of the driving gear.
12. A vehicle, characterized by comprising: a power drive system according to claim 10 or 11.
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| CN201810713599.1A CN110657207B (en) | 2018-06-29 | 2018-06-29 | Transmission, power driving system and vehicle |
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| CN201810713599.1A CN110657207B (en) | 2018-06-29 | 2018-06-29 | Transmission, power driving system and vehicle |
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| CN110657207B CN110657207B (en) | 2022-04-15 |
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| DE102010053414A1 (en) * | 2010-12-06 | 2012-06-06 | GM Global Technology Operations LLC | Drive unit, in particular rear-drive unit, for a four-wheel drive of a motor vehicle |
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| CN104136808A (en) * | 2012-03-14 | 2014-11-05 | 腓特烈斯港齿轮工厂股份公司 | Multistage transmission |
| CN205401632U (en) * | 2016-03-30 | 2016-07-27 | 长城汽车股份有限公司 | Buncher and vehicle |
| CN107344488A (en) * | 2016-05-06 | 2017-11-14 | 陕西汉德车桥有限公司 | Pure two grades of transaxles of electric commercial vehicle and pure electric commercial vehicle |
| KR101858187B1 (en) * | 2017-12-14 | 2018-06-27 | 주식회사 카펙발레오 | Torque converter for vehicle and controlling method thereof |
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2018
- 2018-06-29 CN CN201810713599.1A patent/CN110657207B/en active Active
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5813488A (en) * | 1996-06-14 | 1998-09-29 | Deere & Company | Electric wheel drive for a utility vehicle |
| DE102010053414A1 (en) * | 2010-12-06 | 2012-06-06 | GM Global Technology Operations LLC | Drive unit, in particular rear-drive unit, for a four-wheel drive of a motor vehicle |
| CN102162505A (en) * | 2011-04-27 | 2011-08-24 | 北京理工华创电动车技术有限公司 | Planet gear type automatic speed change system for electric automobile |
| CN104136808A (en) * | 2012-03-14 | 2014-11-05 | 腓特烈斯港齿轮工厂股份公司 | Multistage transmission |
| CN203906680U (en) * | 2014-04-09 | 2014-10-29 | 天津天海同步科技股份有限公司 | Two-gear automatic transmission for electric vehicle |
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| CN107344488A (en) * | 2016-05-06 | 2017-11-14 | 陕西汉德车桥有限公司 | Pure two grades of transaxles of electric commercial vehicle and pure electric commercial vehicle |
| KR101858187B1 (en) * | 2017-12-14 | 2018-06-27 | 주식회사 카펙발레오 | Torque converter for vehicle and controlling method thereof |
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| CN110657207B (en) | 2022-04-15 |
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