CN110657205A - Transmission, power driving system and vehicle - Google Patents
Transmission, power driving system and vehicle Download PDFInfo
- Publication number
- CN110657205A CN110657205A CN201810712805.7A CN201810712805A CN110657205A CN 110657205 A CN110657205 A CN 110657205A CN 201810712805 A CN201810712805 A CN 201810712805A CN 110657205 A CN110657205 A CN 110657205A
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- transmission
- gear
- synchronizer
- carrier
- planetary 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
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2038—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with three engaging means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention discloses a transmission, a power driving system and a vehicle, wherein the transmission comprises: the transmission includes a first planetary gear mechanism, a second planetary gear mechanism, a third planetary gear mechanism, an input shaft, an intermediate shaft, an output shaft, a first synchronizer, a second synchronizer and a third synchronizer, wherein the first synchronizer connects the input shaft with the first sun gear or the first carrier, the second synchronizer connects the output shaft with the third carrier or the third sun gear, and the third synchronizer fixes the third ring gear with a shell of the transmission or connects the third ring gear with the second carrier. According to the transmission, the three-planet-row three-synchronizer structure is arranged, so that the gear can be shifted quickly, smoothly and reliably, and the transmission 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: a first planetary gear mechanism comprising a first sun gear, a first planet carrier, and a first ring gear, the first ring gear being fixedly connected to the transmission housing; the second planetary gear mechanism comprises a second sun gear, a second planet carrier and a second gear ring, and the second gear ring is fixedly connected with the shell of the transmission; a third planetary gear mechanism including a third sun gear, a third planet carrier, and a third ring gear; an input shaft and an output shaft; an intermediate shaft connected to the first carrier, the second sun gear, and the third sun gear; a first synchronizer connecting the input shaft with the first sun gear or the first carrier; a second synchronizer connecting the output shaft with the third carrier or the third sun gear; a third synchronizer that fixes the third ring gear to the case of the transmission or connects the third ring gear to the second carrier.
According to the transmission, the three-planet-row three-synchronizer structure is arranged, so that the gear can be shifted quickly, smoothly and reliably, and the transmission is simple in structure and convenient to maintain.
In some embodiments, an axis of the input shaft, an axis of the intermediate shaft, and an axis of the output shaft are collinear, and the first planetary gear mechanism, the second planetary gear mechanism, and the third planetary gear mechanism are arranged in order in an axial direction.
In some embodiments, the first planetary gear mechanism is disposed between the first synchronizer and the second planetary gear mechanism, and the third planetary gear mechanism is disposed between the third synchronizer and the second planetary gear mechanism.
In some embodiments, the first planetary gear mechanism, the second planetary gear mechanism, and the third planetary gear mechanism are each a single stage planetary gear mechanism.
In some embodiments, the transmission is in first gear, the first synchronizer connects the input shaft with the first sun gear, the second synchronizer connects the output shaft with the third planet carrier, and a third synchronizer fixes the third ring gear with a housing of the transmission.
In some embodiments, the transmission is in second gear, the first synchronizer connects the input shaft with the first sun gear, the second synchronizer connects the output shaft with the third planet carrier, and the third synchronizer connects the third ring gear with the second planet carrier.
In some embodiments, the transmission is engaged in third gear, the first synchronizer connects the input shaft with the first sun gear, and the second synchronizer connects the output shaft with the third sun gear.
In some embodiments, the transmission is in fourth gear, the first synchronizer connects the input shaft with the first carrier, the second synchronizer connects the output shaft with the third carrier, and the third synchronizer fixes the third ring gear with a housing of the transmission.
In some embodiments, the transmission is in fifth gear, the first synchronizer connects the input shaft with the first carrier, the second synchronizer connects the output shaft with the third carrier, and a third synchronizer connects the third ring gear with the second carrier.
In some embodiments, the transmission is in sixth gear, the first synchronizer connects the input shaft with the first carrier, and the second synchronizer connects the output shaft with the third sun gear.
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 drive motor is arranged coaxially with the input shaft, and the drive motor is arranged on a side of the first planetary gear mechanism facing away from the second planetary gear mechanism.
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 planetary gear mechanism 1; a first sun gear 11; a first ring gear 12; a first carrier 13; a first planet 14;
a second planetary gear mechanism 2; a second sun gear 21; a second ring gear 22; a second carrier 23; a second planet wheel 24;
a third planetary gear mechanism 3; the third sun gear 31; the third ring gear 32; a third carrier 33; a third planet gear 44;
an input shaft 4; an intermediate shaft 5; an output shaft 6;
a first synchronizer 7; a second synchronizer 8; a third synchronizer 9.
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 mechanism includes a first planetary gear mechanism 1, a second planetary gear mechanism 2, a third planetary gear mechanism 3, an input shaft 4, an output shaft 6, an intermediate shaft 5, a first synchronizer 7, a second synchronizer 8, and a third synchronizer 9.
Torque of the vehicle can be input to the transmission 100 through the input shaft 4, and torque can be finally output from the output shaft 6 in the transmission 100 through the first planetary gear mechanism 1, the second planetary gear mechanism 2, and the third planetary gear mechanism 3. The synchronizer is used to connect the various components within the transmission 100 to effect a gear shift.
In some embodiments, the output end of the transmission 100 may further include an output gear, the output gear is hollow-sleeved outside the intermediate shaft 5, the torque can be transmitted out of the transmission 100 through the output gear, and the output gear is configured to change the transmission direction of the output torque, so that the size of the transmission 100 in the axial direction of the input shaft 4 can be reduced, and the transmission 100 can be more conveniently arranged on a vehicle.
The first planetary gear mechanism 1 may include a plurality of first planet gears 14, the plurality of first planet gears 14 may be connected to the first carrier 13, the second planetary gear mechanism 2 may include a plurality of second planet gears 24, the plurality of second planet gears 24 may be connected to the second carrier 23, the third planetary gear mechanism 3 may include a plurality of third planet gears 34, and the plurality of third planet gears 34 may be connected to the third carrier 33. 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 first planetary gear set 1 includes a first sun gear 11, a first planetary gear 14, a first carrier 13, and a first ring gear 12, and the first ring gear 12 is fixedly connected to the housing 10 of the transmission 100, so that when torque is transmitted in the first planetary gear set 1, torque can be input into the first planetary gear set 1 from the first carrier 13 or the first sun gear 11, and output from the first planetary gear set 1 to the intermediate shaft 5 from the first carrier 13.
The second planetary gear set 2 comprises a second sun gear 21, a second planet gear 24, a second planet carrier 23 and a second ring gear 22, the second ring gear 22 being fixedly connected to the housing 10 of the transmission 100, so that when torque is transmitted in the second planetary gear set 2, torque can be input into the second planetary gear set 2 from the second planet carrier 23 and/or the second sun gear 21 and transmitted to the third planetary gear set 3 from the second sun gear 21 and/or the second planet carrier 23.
The third planetary gear mechanism 3 includes a third sun gear 31, a third planetary gear 34, a third carrier 33, and a third ring gear 32, so that when torque is transmitted in the third planetary gear mechanism 3, torque can be input by the third sun gear 31 and/or the third ring gear 32, and output to an output shaft by the third carrier 33, and finally transmitted out of the transmission 100.
The intermediate shaft 5 is connected to the first carrier 13, the intermediate shaft 5 is connected to the second sun gear 21, and the intermediate shaft 5 is connected to the third sun gear 31, so that torque can be transmitted from the first carrier 13 to the intermediate shaft 5 in the first planetary gear mechanism 1, and transmitted to the second planetary gear mechanism 2 and the third planetary gear mechanism 3 via the intermediate shaft 5.
The first synchronizer 7 connects the input shaft 4 with the first sun gear 11 or the input shaft 4 with the first carrier 13: when the first synchronizer 7 connects the input shaft 4 with the first sun gear 11, torque can be input to the first planetary gear mechanism 1 from the input shaft 4 through the first sun gear 11 and output from the first carrier 13; when the first synchronizer 7 connects the input shaft 4 with the first carrier 13, torque can be transmitted from the input shaft 4 to the first planetary gear mechanism 1, and from the first carrier 13 to the second planetary gear mechanism 2 and the third planetary gear mechanism 3.
The second synchronizer 8 connects the output shaft 6 with the third carrier 33 or the output shaft 6 with the third sun gear 31: when the second synchronizer 8 connects the output shaft 6 with the third carrier 33, in the third planetary gear mechanism 3, torque is transmitted from the third carrier 33 out of the transmission 100 through the output shaft 6; when the second synchronizer 8 connects the output shaft 6 with the third sun gear 31, torque is transmitted from the third sun gear 31 to the transmission 100 through the output shaft 6 in the third planetary gear mechanism 3.
The third synchronizer 9 fixes the third ring gear 32 to the housing 10 of the transmission 100 or connects the third ring gear 32 to the second carrier 23: when the third synchronizer 9 fixes the third ring gear 32 to the housing 10 of the transmission 100, torque can be transmitted from the third sun gear 31 to the third planetary gear mechanism 3 via the intermediate shaft 5, and transmitted out of the third planetary gear mechanism 3 by the third sun gear 31 or the third carrier 33; when the third synchronizer 9 connects the third ring gear 32 with the second carrier 23, torque can be transmitted from the third sun gear 31 to the third planetary gear mechanism 3 via the intermediate shaft 5, and torque can also be transmitted from the third ring gear 32 to the third planetary gear mechanism via the second carrier 23.
According to the transmission provided by the embodiment of the invention, the three-planet-row three-synchronizer structure of the first synchronizer 7, the second synchronizer 8 and the third synchronizer 9 is arranged, 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 problem of drag torque 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 three-planet-row three-synchronizer structure 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 axis of the input shaft 4, the axis of the intermediate shaft 5, and the axis of the output shaft 6 are collinear, and the first planetary gear mechanism 1, the second planetary gear mechanism 2, and the third planetary gear mechanism 3 are arranged in order along the axial direction, so that the arrangement of the input shaft 4, the output shaft 6, and the intermediate shaft 5 can be facilitated, and the transmission direction of the torque from the input shaft 4 to the output shaft 6 is not changed.
In some embodiments, as shown in fig. 1, the first planetary gear mechanism 1 is disposed between the first synchronizer 7 and the second planetary gear mechanism 2, and the third planetary gear mechanism 3 is disposed between the third synchronizer 9 and the second planetary gear mechanism 2. In some examples, the first synchronizer 7 is disposed on a side of the first planetary gear mechanism 1 facing away from the second planetary gear mechanism 2, so that the disposition of the first synchronizer 7 is facilitated, and the disposition position of the first synchronizer 7 can make the distances of the first planetary gear mechanism 1 and the second planetary gear mechanism 2 closer, and thus the length of the intermediate shaft 5 can be made shorter, improving the stability of the transmission 100, the second synchronizer 8 is disposed on a side of the third planetary gear mechanism 3 facing away from the second planetary gear mechanism 2, so that the disposition of the second synchronizer 8 is facilitated, and the disposition position of the second synchronizer 8 can make the distances of the second planetary gear mechanism 2 and the third planetary gear mechanism 3 closer, and thus the length of the intermediate shaft 5 can be made shorter, improving the stability of the transmission 100, the third synchronizer 9 is disposed radially outside the third planetary gear mechanism 3, the second synchronizer 8 is arranged on the side of the third planetary gear mechanism 3 facing away from the third planetary gear mechanism 3, so that the space in the radial direction of the transmission 100 can be utilized, the length of the transmission 100 in the axial direction can be saved, and the structure of the transmission 100 can be more compact.
In some embodiments, the first planetary gear mechanism 1, the second planetary gear mechanism 2, and the third planetary gear mechanism 3 are all single-stage planetary gear mechanisms, i.e., planetary gear mechanisms in which the sun gear reaches the first stage planetary gear, i.e., the first stage planetary gear mechanism can drive the ring gear, and the single-stage planetary gear mechanisms have simple structures, and can effectively enhance the torque transmission efficiency of the transmission 100.
In some embodiments, the transmission 100 according to the embodiment of the invention may have 6 gears, i.e., first, second, third, fourth, fifth, and sixth, in which the speed ratio of the first gear to the sixth gear decreases in order, i.e., the speed ratio u1 of the first gear > the speed ratio u2 of the second gear > the speed ratio u3 of the third gear > the speed ratio u4 of the fourth gear > the speed ratio u5 of the fifth gear > the speed ratio u6 of the sixth gear.
According to the transmission provided by the embodiment of the invention, the first synchronizer, the second synchronizer and the third synchronizer are arranged, so that the transmission can have a six-gear shifting structure, and for medium and heavy trucks, due to the large torque requirement range, uncertain load and complex working condition, the six-gear structure is adopted, 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.
The operating states of the first synchronizer 7, the second synchronizer 8, and the third synchronizer 9 of each gear of the transmission 100, and the torque transmission paths during the transmission 100 in which torque is transmitted from the input shaft 4 to the output shaft 6 are described below with reference to fig. 1.
The positions of the respective synchronizers in the gear change described below are described with reference to fig. 1, and of course, the arrangement direction and the arrangement position of the respective synchronizers are not limited thereto.
When the transmission 100 is in first gear, the first synchronizer 7 connects the input shaft 4 with the first sun gear 11, the second synchronizer 8 connects the output shaft 6 with the third carrier 33, and the third synchronizer 9 fixes the third ring gear 32 with the housing 10 of the transmission 100.
Thus, torque is transmitted from the input shaft 4 to the transmission 100, the input shaft 4 transmits torque to the first sun gear 11, the torque is output from the first carrier 13 of the first planetary gear mechanism 1 to the intermediate shaft 5 because the first ring gear 12 is fixed to the transmission 100 housing 10, the torque is transmitted to the second sun gear 21 and the third sun gear 31 through the intermediate shaft 5, the output shaft 6 is connected to the third carrier 33, in the third planetary gear mechanism 3, the torque transmitted to the third planetary gear mechanism 3 is input from the third sun gear 31 and output from the third carrier 33, and the third carrier 33 transmits torque to the output shaft 6.
Thus, in the first gear of the transmission 100, in the first planetary gear mechanism 1, torque is input from the first sun gear 11 and output from the first carrier 13 to the intermediate shaft 5, at which time the torque has the same rotational direction with respect to the input shaft 4 and the rotational speed is reduced, the torque is transmitted to the third planetary gear mechanism 3 through the intermediate shaft 5 and input from the third sun gear 31, the third carrier 33 is output to the output shaft, the torque has the same rotational direction with respect to the input shaft 4 through the third planetary gear mechanism 3 and is reduced again, and in the first gear, after the torque is transmitted from the input shaft 4 to the transmission 100, the torque is transmitted out of the transmission 100 through the two-stage reduction of the first planetary gear mechanism 1 and the third planetary gear mechanism 3, and the torque transmission directions of the input shaft 4 and the output shaft 6 are unchanged.
When the transmission 100 is in second gear, the first synchronizer 7 connects the input shaft 4 with the first sun gear 11, the second synchronizer 8 connects the output shaft 6 with the third carrier 33, and the third synchronizer 9 connects the third ring gear 32 with the second carrier 23.
Thus, torque is transmitted from the input shaft 4 to the transmission 100, the input shaft 4 transmits torque to the first sun gear 11, torque is output from the first carrier 13 of the first planetary gear mechanism 1 to the planetary gear mechanism intermediate shaft 5 due to the first ring gear 12 being fixed to the housing 10 of the transmission 100, torque is transmitted to the second sun gear 21 and the third sun gear 31 via the intermediate shaft 5, torque is input from the second sun gear 21 and output from the second carrier 23 in the second planetary gear mechanism 2, and torque is transmitted to the third ring gear 32 of the third planetary gear mechanism 3 via the second carrier 23, so that torque is input from the third ring gear 32 and the third sun gear 31, output from the third carrier 33, and transmitted to the output shaft 6 in the third planetary gear mechanism 3.
In the second gear of the transmission 100, in the first planetary gear system, torque is thus input by the first sun gear 11, and is output by the first carrier 13, at this time, the rotation direction of the first carrier 13 relative to the input shaft 4 is the same, the rotation speed is reduced, in the second planetary gear mechanism 2, the second sun gear 21 is input, the second carrier 23 is output, the second carrier 23 transmits torque to the third ring gear 32, the rotation speed of the third ring gear 32 is reduced relative to the rotation speed of the second sun gear 21, and the rotation directions are the same, in the first gear, the input of the third planetary gear mechanism 3 is the third sun gear 31, and in the second gear, the input of the third planetary gear mechanism 3 is the third sun gear 31 and the third ring gear 32, therefore, when the rotation speed of the input shaft 4 is constant with respect to the first gear, the output rotation speed of the third carrier 33 is larger in the second gear, so that the speed ratio u1 of the first gear is larger than the speed ratio u2 of the second gear.
When the transmission 100 is engaged in the third gear, the first synchronizer 7 connects the input shaft 4 with the first sun gear 11, and the second synchronizer 8 connects the output shaft 6 with the third sun gear 31.
Thus, torque is transmitted from the input shaft 4 to the transmission 100, the input shaft 4 transmits torque to the first sun gear 11, the first ring gear 12 is fixed to the housing 10 of the transmission 100, torque is input from the first sun gear 11 in the first planetary gear mechanism 1, and is output from the first carrier 13 to the intermediate shaft 5, and torque is transmitted to the second sun gear 21 and the third sun gear 31 via the intermediate shaft 5, and torque is transmitted from the third sun gear 31 to the output shaft 6.
Therefore, when the transmission 100 is in the third gear, torque is input from the first sun gear 11 and output from the first carrier 13 in the first planetary gear system, and at this time, the rotation direction of the first carrier 13 with respect to the input shaft 4 is the same and the rotation speed is reduced, and when the transmission 100 is in the third gear, torque is input from the input shaft 4 into the transmission 100 with respect to the second gear, and then the torque is output to the output shaft 6 after being decelerated by the first planetary gear mechanism 1, so that the speed ratio u2 of the second gear is greater than the speed ratio u3 of the third gear.
When the transmission 100 is in fourth gear, the first synchronizer 7 connects the input shaft 4 with the first carrier 13, the second synchronizer 8 connects the output shaft 6 with the third carrier 33, and the third synchronizer 9 fixes the third ring gear 32 with the housing 10 of the transmission 100.
Thus, torque is transmitted from the input shaft 4 to the transmission 100, the input shaft 4 transmits torque to the first carrier 13, torque is output from the first carrier 13 of the first planetary gear mechanism 1 to the intermediate shaft 5, and torque is transmitted to the second sun gear 21 and the third sun gear 31 via the intermediate shaft 5, at which time the output shaft 6 is connected to the third carrier 33, and torque is input from the third sun gear 31 to the third planetary gear mechanism 3 in the third planetary gear mechanism 3 and is output from the third carrier 33 to the output shaft 6.
Accordingly, when the transmission 100 is in the fourth gear, in the first planetary gear system, torque is input from the first carrier 13 and output from the first carrier 13, at this time, the rotational direction and the rotational speed of the first carrier 13 with respect to the input shaft 4 are not changed, torque is input from the first carrier 13 to the third sun gear 31 of the third planetary gear mechanism 3 via the intermediate shaft 5 and output from the third carrier 33 to the output shaft 6, at this time, the rotational direction of the output shaft 6 with respect to the input shaft 4 is the same and the rotational speed is reduced, at the fourth gear, torque is transmitted to the output shaft 6 within the transmission 100 only through the reduction of the third planetary gear mechanism 3, and the speed ratio of the first planetary gear mechanism 1 can be made larger than that of the third planetary gear mechanism 3, so that the speed ratio u3 of the third gear is made larger than the speed ratio u4 of the fourth gear.
When the transmission 100 is engaged in fifth gear, the first synchronizer 7 connects the input shaft 4 with the first carrier 13, the second synchronizer 8 connects the output shaft 6 with the third carrier 33, and the third synchronizer 9 connects the third ring gear 32 with the second carrier 23.
Thus, torque is transmitted from the input shaft 4 to the transmission 100, the input shaft 4 transmits torque to the first carrier 13, torque is transmitted from the first carrier 13 of the first planetary gear mechanism 1 to the second sun gear 21 and the third sun gear 31 via the intermediate shaft 5, torque is input from the second sun gear 21 in the second planetary gear mechanism 2, and is output from the second carrier 23 to the third ring gear 32, and torque is input from the third ring gear 32 and the third sun gear 31, is output from the third carrier 33, and is transmitted to the output shaft 6 in the third planetary gear mechanism 3.
In the fifth gear of the transmission 100, in the first planetary gear system, torque is thus input from the first carrier 13, and is output by the first carrier 13, while the rotation direction and rotation speed of the first carrier 13 with respect to the input shaft 4 are unchanged, in the second planetary gear mechanism 2, the second sun gear 21 is input, the second carrier 23 is output, the second carrier 23 transmits torque to the third ring gear 32, the rotational speed of the third ring gear 32 is reduced relative to the rotational speed of the second sun gear 21, and the steering is the same, in the fourth gear, the input of the third planetary gear mechanism 3 is the third sun gear 31, and in the fifth gear, the input of the third planetary gear mechanism 3 is the third sun gear 31 and the third ring gear 32, therefore, when the rotation speed of the input shaft 4 is constant with respect to the fourth gear, the output rotation speed of the third carrier 33 in the fifth gear is larger, so that the speed ratio u4 of the fourth gear is larger than the speed ratio u5 of the fifth gear.
When the transmission 100 is in the sixth gear, the first synchronizer 7 connects the input shaft 4 with the first carrier 13, and the second synchronizer 8 connects the output shaft 6 with the third sun gear 31.
Thus, torque is transmitted from the input shaft 4 to the transmission 100, the input shaft 4 transmits torque to the first carrier 13, torque is input from the first carrier 13 in the first planetary gear mechanism 1 and is transmitted from the first carrier 13 to the intermediate shaft 5, torque is transmitted to the second sun gear 21 and the third sun gear 31 via the intermediate shaft 5, and torque is transmitted from the third sun gear 31 to the output shaft 6.
Therefore, in the transmission 100 in the sixth gear, torque is input from the first carrier 13, output from the first carrier 13 to the intermediate shaft 5, and transmitted to the output shaft 6 via the intermediate shaft 5, that is, torque is not reduced during the transmission, and the output shaft 6 rotates at the same speed as the input shaft 4 in the sixth gear with respect to the fifth gear, so that the speed ratio u5 of the fifth gear is greater than the speed ratio u6 of the sixth gear.
In summary, the transmission 100 of the present invention belongs to a horizontal transmission, 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. At the same time, transmission 100 is less expensive to manufacture and easier to maintain.
The synchronizer is adopted for shifting, a clutch is not needed, the structure is simplified, and the transmission 100 adopts a six-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 and the transmission 100 of any one of the above embodiments, wherein the driving motor is in power coupling connection with the input shaft 4. 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 driving motor is arranged coaxially with the input shaft 4, and the driving motor is arranged on the side of the first planetary gear mechanism 1 facing away from the second planetary gear mechanism 2, so that various components of the power driving system can be arranged along the axis of the input shaft 4, thereby facilitating the arrangement of the power driving system, and unnecessary gears and the like are not needed to change the route of torque transmission, thereby improving the torque transmission efficiency of the power driving system.
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 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 (13)
1. A transmission, comprising:
a first planetary gear mechanism comprising a first sun gear, a first planet carrier, and a first ring gear, the first ring gear being fixedly connected to the transmission housing;
the second planetary gear mechanism comprises a second sun gear, a second planet carrier and a second gear ring, and the second gear ring is fixedly connected with the shell of the transmission;
a third planetary gear mechanism including a third sun gear, a third planet carrier, and a third ring gear;
an input shaft and an output shaft;
an intermediate shaft connected to the first carrier, the second sun gear, and the third sun gear;
a first synchronizer connecting the input shaft with the first sun gear or the first carrier;
a second synchronizer connecting the output shaft with the third carrier or the third sun gear;
a third synchronizer that fixes the third ring gear to the case of the transmission or connects the third ring gear to the second carrier.
2. The transmission of claim 1, wherein an axis of the input shaft, an axis of the intermediate shaft, and an axis of the output shaft are collinear, and the first planetary gear mechanism, the second planetary gear mechanism, and the third planetary gear mechanism are arranged in axial sequence.
3. The transmission of claim 2, wherein the first planetary gear mechanism is disposed between the first synchronizer and the second planetary gear mechanism, and the third planetary gear mechanism is disposed between the third synchronizer and the second planetary gear mechanism.
4. The transmission of claim 1, wherein the first planetary gear mechanism, the second planetary gear mechanism, and the third planetary gear mechanism are each a single stage planetary gear mechanism.
5. The transmission of any of claims 1-4, wherein the transmission is engaged in first gear, the first synchronizer connects the input shaft with the first sun gear, the second synchronizer connects the output shaft with the third carrier, and a third synchronizer fixes the third ring gear with a housing of the transmission.
6. The transmission of any one of claims 1-4, wherein the transmission is in second gear, the first synchronizer connects the input shaft with the first sun gear, the second synchronizer connects the output shaft with the third carrier, and the third synchronizer connects the third ring gear with the second carrier.
7. The transmission of any one of claims 1-4, wherein the transmission is engaged in third gear, the first synchronizer connecting the input shaft with the first sun gear, the second synchronizer connecting the output shaft with the third sun gear.
8. The transmission of any of claims 1-4, wherein the transmission is in fourth gear, the first synchronizer connects the input shaft with the first carrier, the second synchronizer connects the output shaft with the third carrier, and the third synchronizer fixes the third ring gear with a housing of the transmission.
9. The transmission of any one of claims 1-4, wherein the transmission is in fifth gear, the first synchronizer connects the input shaft with the first carrier, the second synchronizer connects the output shaft with the third carrier, and a third synchronizer connects the third ring gear with the second carrier.
10. The transmission of any one of claims 1-4, wherein the transmission is in sixth gear, the first synchronizer connecting the input shaft with the first carrier, and the second synchronizer connecting the output shaft with the third sun gear.
11. A power drive system, comprising:
a drive motor;
the transmission of any one of claims 1-10, said drive motor being in torque-coupling connection with said input shaft.
12. A power drive system according to claim 11, characterized in that the drive motor is arranged coaxially with the input shaft, and the drive motor is arranged on a side of the first planetary gear mechanism facing away from the second planetary gear mechanism.
13. A vehicle, characterized by comprising: a power drive system according to claim 9 or 10.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810712805.7A CN110657205B (en) | 2018-06-29 | 2018-06-29 | Transmission, power driving system and vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810712805.7A CN110657205B (en) | 2018-06-29 | 2018-06-29 | Transmission, power driving system and vehicle |
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| Publication Number | Publication Date |
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| CN110657205A true CN110657205A (en) | 2020-01-07 |
| CN110657205B CN110657205B (en) | 2022-05-13 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201810712805.7A Active CN110657205B (en) | 2018-06-29 | 2018-06-29 | Transmission, power driving system and vehicle |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112253702A (en) * | 2020-09-11 | 2021-01-22 | 张欣 | Stepless speed change mechanism |
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| CN110657205B (en) | 2022-05-13 |
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