CN110657201B - Transmission, power driving system and vehicle - Google Patents
Transmission, power driving system and vehicle Download PDFInfo
- Publication number
- CN110657201B CN110657201B CN201810713252.7A CN201810713252A CN110657201B CN 110657201 B CN110657201 B CN 110657201B CN 201810713252 A CN201810713252 A CN 201810713252A CN 110657201 B CN110657201 B CN 110657201B
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02039—Gearboxes for particular applications
- F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
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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
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds
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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
- F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two 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
- F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two 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 first planetary gear mechanism comprises a first sun gear, a first planet carrier and a first gear ring, the second planetary gear mechanism comprises a second sun gear, a second planet carrier and a second gear ring, the second gear ring is connected with the output end of the transmission, the first synchronizer fixes the first gear ring with the shell of the transmission or connects the first gear ring with the first sun gear, and the second synchronizer fixes the second planet carrier with the shell of the transmission or connects the second planet carrier with the second sun gear. According to the transmission, the double-planet-row double-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 including a first sun gear, a first planet gear, a first carrier, and a first ring gear; 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 connected with the output end of the transmission; an input shaft connected with the first sun gear; the first planet carrier is connected with the intermediate shaft, and the intermediate shaft is connected with the second sun gear; a first synchronizer that fixes the first ring gear to a housing of a transmission or connects the first ring gear to the first sun gear; a second synchronizer fixing the second carrier with a case of the transmission or connecting the second carrier with the second sun gear.
According to the transmission, the double-planet-row double-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, the output of the transmission comprises an output shaft, and the axes of the input shaft, the intermediate shaft, and the output shaft are collinear.
In some embodiments, the output of the transmission comprises an output shaft, the intermediate shaft is arranged between the input shaft and the output shaft, the first synchronizer is arranged on a side of the first planetary gear mechanism facing away from the second planetary gear mechanism, and the second synchronizer is arranged between the first planetary gear mechanism and the second planetary gear mechanism.
In some embodiments, one of the first planetary gear mechanism and the second planetary gear mechanism is a single-stage planetary gear mechanism and the other of the first planetary gear mechanism and the second planetary gear mechanism is a double-stage planetary gear mechanism.
In some embodiments, the transmission is engaged in first gear, the first synchronizer fixes the first ring gear to a housing of the transmission, and the second synchronizer fixes the second carrier to the housing of the transmission.
In some embodiments, the transmission is in second gear, the first synchronizer fixes the first ring gear to a housing of the transmission, and the second synchronizer connects the first carrier to the second carrier.
In some embodiments, the transmission is in third gear, the first synchronizer connects the first sun gear with the first ring gear, and the second synchronizer fixes the second carrier with a housing of the transmission.
In some embodiments, the transmission is in fourth gear, the first synchronizer connects the first sun gear with the first ring gear, and the second synchronizer connects the first carrier with the second carrier.
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.
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 21; a second ring gear 22; a second carrier 23; a second planet wheel 24;
an input shaft 4; an intermediate shaft 5; an output shaft 6;
a first synchronizer 7; a second synchronizer 8.
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: a first planetary gear mechanism, a second planetary gear mechanism, an input shaft 4, an intermediate shaft 5, a first synchronizer 7, and a second synchronizer 8.
The torque of the vehicle can be input to the transmission 100 via the input shaft 4, and the torque can be finally output from the output of the transmission in the transmission 100 via the first planetary gear mechanism and the second planetary gear mechanism. The synchronizer is used to connect the various components within the transmission 100 to effect a gear shift.
The first planetary gear mechanism may include a plurality of first planet gears 14, the plurality of first planet gears 14 being connected to the first planet carrier 13, and the second planetary gear mechanism may include a plurality of second planet gears 24, the plurality of second planet gears 24 being connected to the second planet carrier 23. 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 comprises a first sun gear 11, a first planet gear 14, a first planet carrier 13 and a first ring gear 12, so that when torque is transmitted in the first planetary gear set, torque can be input by the first sun gear 11 and/or the first ring gear 12 and output by the first planet carrier 13 to the intermediate shaft 5.
The second planetary gear mechanism comprises a second sun gear 21, second planet gears 24, a second planet carrier 23 and a second ring gear 22, the output of the transmission 100 comprises the output shaft 6, and the second ring gear 22 is connected to the output shaft 6 of the transmission 100, so that torque can be input to the second planetary gear mechanism by the second sun gear 21 and/or the second planet carrier 23 and output to the output shaft 6 by the second ring gear 22.
The input shaft 4 is connected to the first sun gear 11, the first carrier 13 is connected to the intermediate shaft 5, and the intermediate shaft 5 is connected to the second sun gear 21, torque can be transmitted from the first carrier 13 to the intermediate shaft 5 in the first planetary gear mechanism, and via the intermediate shaft 5 to the second sun gear 21 of the second planetary gear mechanism.
In some embodiments, the output end of the transmission 100 may further include an output gear, the output gear is 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 synchronizer 7 fixes the first ring gear 12 to the housing 10 of the transmission 100 or connects the first ring gear 12 to the first sun gear 11: when the first synchronizer 7 fixes the first ring gear 12 with the housing 10 of the transmission 100, torque can be input to the first planetary gear mechanism by the input shaft 4 through the first sun gear 11 and output by the first carrier 13; when the first synchronizer 7 connects the first ring gear 12 with the first sun gear 11, torque can be input to the first planetary gear mechanism by the input shaft 4 through the first sun gear 11 and the first ring gear 12 and output by the first carrier 13, which is constructed such that the first planetary gear mechanism can output two speed ratios.
The second synchronizer 8 fixes the second carrier 23 to the housing 10 of the transmission 100 or connects the second carrier 23 to the second sun gear 21: when the second synchronizer 8 fixes the second carrier 23 with the housing 10 of the transmission 100, torque can be input to the second planetary gear mechanism through the second sun gear 21 by the intermediate shaft 5 and output by the second ring gear 22; when the second synchronizer 8 is to connect the second carrier 23 with the second sun gear 21, torque can be input to the second planetary gear mechanism by the intermediate shaft 5 through the second sun gear 21 and the second carrier 23 and output to the output shaft 6 by the second ring gear 22, which is configured such that the second planetary gear mechanism can output two speed ratios.
According to the transmission 100 provided by the embodiment of the invention, the first synchronizer 7 and the second synchronizer 8 are arranged, so that the transmission 100 can have a four-gear shifting structure, and for medium and heavy trucks, the four-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.
According to the transmission 100 provided by the embodiment of the invention, the first synchronizer 7 and the second synchronizer 8 are arranged in a double-planet-row double-synchronizer structure, 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, a double-planet-row double-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 and the second planetary gear mechanism are arranged in order in 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 unchanged.
In some embodiments, as shown in fig. 1, the intermediate shaft 5 is disposed between the input shaft 4 and the output shaft 6, the first synchronizer 7 is disposed on a side of the first planetary gear mechanism facing away from the second planetary gear mechanism, and the second synchronizer 8 is disposed between the first planetary gear mechanism and the second planetary gear mechanism, so that the first synchronizer 7 and the second synchronizer 8 are conveniently disposed, and the first synchronizer 7 and the second synchronizer 8 are disposed at positions where the first planetary gear mechanism and the second planetary gear mechanism are closer to each other, so that the length of the intermediate shaft 5 can be shorter, the stability of the transmission 100 can be improved, 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, one of the first planetary gear mechanism and the second planetary gear mechanism is a single-stage planetary gear mechanism and the other of the first planetary gear mechanism and the second planetary gear mechanism is a double-stage planetary gear mechanism, i.e., when the first planetary gear mechanism is a single-stage planetary gear mechanism, the second planetary gear mechanism is a double-stage planetary gear mechanism, or when the first planetary gear mechanism is a double-stage planetary gear mechanism, the second planetary gear mechanism is a single-stage planetary gear mechanism.
The single-stage planetary gear mechanism, i.e., the planetary gear mechanism in which the sun gear reaches the first-stage planetary gear, i.e., the ring gear can be driven, is simple in structure, and can effectively enhance the torque transmission efficiency of the transmission 100. The number of the planet carrier teeth of the double-stage planetary gear mechanism is less, and the rotation directions of the sun gear and the ring gear are the same when the planet carrier is fixed.
The following embodiment will be described with reference to fig. 1, taking as an example that the first planetary gear mechanism is a single-stage planetary gear mechanism and the second planetary gear mechanism is a double-stage planetary gear mechanism.
In some embodiments, the transmission 100 according to the embodiment of the present invention may have a plurality of gears, i.e., a first gear, a second gear, a third gear and a fourth gear, wherein the speed ratio of the first gear to the fourth 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, and in some examples, the speed ratio u1 of the first gear is 8, the speed ratio u2 of the second gear is 4, the speed ratio u3 of the third gear is 2, and the speed ratio u4 of the fourth gear is 1.
The operation states of the first synchronizer 7 and the second synchronizer 8 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 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 fixes the first ring gear 12 to the housing 10 of the transmission 100, and the second synchronizer 8 fixes the second carrier 23 to 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, in the first planetary gear mechanism, torque transmitted to the first planetary gear mechanism is input from the first sun gear 11 and output from the first carrier 13, the first carrier 13 transmits torque to the intermediate shaft 5, and torque is transmitted to the second sun gear 21 via the intermediate shaft 5, in the second planetary gear mechanism, torque transmitted to the second planetary gear mechanism is input from the second sun gear 21 and output from the second ring gear 22, and the second ring gear 22 transmits torque to the output shaft 6.
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 carrier 13 to the intermediate shaft 5, at this 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 second planetary gear mechanism through the intermediate shaft 5 and input from the second sun gear 21, the second ring gear 22 is output to the output shaft 6, the torque has the same rotational direction with respect to the input shaft 4 through the second planetary gear mechanism and is reduced again, 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 and the second planetary gear mechanism, and the torque transmission directions of the input shaft 4 and the output shaft 6 are not changed.
When the transmission 100 is in the second gear, the first synchronizer 7 fixes the first ring gear 12 to the case 10 of the transmission 100, and the second synchronizer 8 connects the first carrier 13 to the second carrier 23.
In this way, torque is transmitted from the input shaft 4 to the transmission 100, the input shaft 4 transmits torque to the first sun gear 11, in the first planetary gear mechanism, torque transmitted to the first planetary gear mechanism is input by the first sun gear 11 and output by the first carrier 13, the first carrier 13 transmits torque to the intermediate shaft 5, and torque is transmitted to the second sun gear 21 through the intermediate shaft 5, in the second planetary gear mechanism, torque is transmitted to the second carrier 23 through the first carrier 13 since the second synchronizer 8 connects the first carrier 13 with the second carrier 23, torque transmitted to the second planetary gear mechanism is input by the second sun gear 21 and the second carrier 23 and output by the second ring gear 22, and the second ring gear 22 transmits torque to the output shaft 6.
Thus, when the transmission 100 is in the second gear, in the first planetary gear mechanism, torque is input from the first sun gear 11 and output from the first carrier 13 to the intermediate shaft 5, at this time, the torque is in the same direction as the rotation direction of the input shaft 4 and the rotation speed is reduced, the torque is transmitted to the second sun gear 21 through the intermediate shaft 5 and input to the second planetary gear mechanism through the second sun gear 21 and the second carrier 23, the torque is output to the output shaft 6 through the second ring gear 22, the torque is in the same direction as the rotation direction of the input shaft 4 through the second planetary gear mechanism and is reduced again, 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 and the second planetary gear mechanism, the torque transmission direction of the input shaft 4 and the output shaft 6 is not changed, in the first gear, the input end of the second planetary gear mechanism is the second sun gear 21, in the second gear, the input ends of the second planetary gear mechanism are the second sun gear 21 and the second carrier 23, so that when the rotation speed of the input shaft 4 is constant relative to the first gear, the output rotation speed of the second carrier 23 in the second gear is greater, so that the speed ratio u1 of the first gear is greater than the speed ratio u2 of the second gear.
When the transmission 100 is in the third gear, the first synchronizer 7 connects the first sun gear 11 with the first ring gear 12, and the second synchronizer 8 fixes the second carrier 23 with the casing 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, and in the first planetary gear mechanism, input from the first ring gear 12 and the first sun gear 11, output from the first carrier 13, and transmits torque to the intermediate shaft 5, and in the second planetary gear mechanism, torque is transmitted to the second sun gear 21 via the intermediate shaft 5 due to the second synchronizer 8 connecting the first carrier 13 with the second carrier 23, and in the second planetary gear mechanism, torque transmitted to the second planetary gear mechanism is input from the second sun gear 21 and output from the second ring gear 22, and the second ring gear 22 transmits torque to the output shaft 6.
Thus, when the transmission 100 is in the third gear, the first planetary gear mechanism is input with the first ring gear 12 and the first sun gear 11, output from the first carrier 13, and transmits the torque to the intermediate shaft 5, at which the torque is in the same direction of rotation as the input shaft 4 and the rotation speed is reduced, to the second sun gear 21 of the second planetary gear mechanism via the intermediate shaft 5, in the second planetary gear mechanism, torque is input from the second sun gear 21 and output from the second carrier 23 to the output shaft 6, and at this time, the torque is in the same direction as the rotation direction of the input shaft 4, the rotation speed is reduced, and in the second gear, when the transmission 100 is in the third gear, the first planetary gear mechanism and the second planetary gear mechanism may be designed such that when the input shaft 4 rotates at a constant speed, the output shaft 6 of the third gear rotates at a speed faster than the output shaft 6 of the second gear, 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 the fourth gear, the first synchronizer 7 connects the first sun gear 11 with the first ring gear 12, and the second synchronizer 8 connects the first carrier 13 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, in the first planetary gear mechanism, input by the first ring gear 12 and the first sun gear 11, output from the first carrier 13, and transmits torque to the intermediate shaft 5, in the second planetary gear mechanism, torque is transmitted to the second carrier 23 through the first carrier 13 due to the second synchronizer 8 connecting the first carrier 13 with the second carrier 23, torque transmitted to the second planetary gear mechanism is input by the second sun gear 21 and the second carrier 23 and output by the second ring gear 22, and the second ring gear 22 transmits torque to the output shaft 6.
Thus, in the fourth gear of the transmission 100, the first planetary gear mechanism is input from the first ring gear 12 and the first sun gear 11, output from the first carrier 13, and transmit torque to the intermediate shaft 5, at which time the torque is in the same direction as the rotation of the input shaft 4 and the rotation speed is reduced, the torque is transmitted to the second sun gear 21 via the intermediate shaft 5, and is input to the second planetary gear mechanism via the second sun gear 21 and the second carrier 23, the torque is output to the output shaft 6 via the second ring gear 22, the torque is in the same direction as the rotation of the input shaft 4 via the second planetary gear mechanism, and is reduced again, 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 via the two-stage reduction of the first planetary gear mechanism and the second planetary gear mechanism, and the torque transmission directions of the input shaft 4 and the output shaft 6 are not changed, in the third gear, the input of the second planetary gear mechanism is the second sun gear 21, and in the fourth gear, the input of the second planetary gear mechanism is the second sun gear 21 and the second carrier 23, so that the output rotation speed of the second carrier 23 is greater in the fourth gear when the rotation speed of the input shaft 4 is constant relative to the third gear, so that the speed ratio u3 of the third gear is greater than the speed ratio u4 of the fourth gear.
In summary, the transmission 100 of the present invention belongs to a horizontal transmission 100, and adopts a double-planetary-row double-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 four-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 addition, the two synchronizers reasonably utilize the space between the planet rows, the design is more compact on the whole, and the requirements of the vehicle on the durability, the power transmission efficiency, the size, the cost and the like of the transmission 100 can be well met.
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 facing away from the second planetary gear mechanism, so that various components of the power driving system can be arranged along the axis of the input shaft 4, the arrangement of the power driving system is further facilitated, and unnecessary gears and the like are not needed to change the route of torque transmission, and the torque transmission efficiency of the power driving system is improved.
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 (9)
1. A transmission, comprising:
a first planetary gear mechanism including a first sun gear, a first planet gear, a first carrier, and a first ring gear;
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 connected with the output end of the transmission;
an input shaft connected with the first sun gear;
the first planet carrier is connected with the intermediate shaft, and the intermediate shaft is connected with the second sun gear;
a first synchronizer that fixes the first ring gear to a housing of a transmission or connects the first ring gear to the first sun gear;
a second synchronizer that fixes the second carrier with a housing of the transmission or connects the second carrier with the second sun gear;
the transmission is engaged in a first gear, the first synchronizer fixes the first ring gear to a housing of the transmission, and the second synchronizer fixes the second carrier to the housing of the transmission.
2. The transmission of claim 1, wherein the output of the transmission comprises an output shaft, and wherein the axes of the input shaft, the intermediate shaft, and the output shaft are collinear.
3. The transmission of claim 1, wherein the output of the transmission comprises an output shaft, the intermediate shaft is disposed between the input shaft and the output shaft, the first synchronizer is disposed on a side of the first planetary gear mechanism facing away from the second planetary gear mechanism, and the second synchronizer is disposed between the first planetary gear mechanism and the second planetary gear mechanism.
4. The transmission of claim 1, wherein one of the first planetary gear mechanism and the second planetary gear mechanism is a single-stage planetary gear mechanism and the other of the first planetary gear mechanism and the second planetary gear mechanism is a double-stage planetary gear mechanism.
5. The transmission of any one of claims 1-4, wherein the transmission is in second gear, the first synchronizer fixes the first ring gear to a housing of the transmission, and the second synchronizer connects the first carrier to the second carrier.
6. The transmission of any of claims 1-4, wherein the transmission is in third gear, the first synchronizer connects the first sun gear with the first ring gear, and the second synchronizer fixes the second carrier with a housing of the transmission.
7. The transmission of any one of claims 1-4, wherein the transmission is in fourth gear, the first synchronizer connects the first sun gear with the first ring gear, and the second synchronizer connects the first carrier with the second carrier.
8. A powertrain system, comprising:
a drive motor;
the transmission of any one of claims 1-7, said drive motor being in power-coupled connection with said input shaft.
9. A vehicle, characterized by comprising: the drivetrain of claim 8.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810713252.7A CN110657201B (en) | 2018-06-29 | 2018-06-29 | Transmission, power driving system and vehicle |
| PCT/CN2019/093561 WO2020001589A1 (en) | 2018-06-29 | 2019-06-28 | Transmission, power drive system and vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810713252.7A CN110657201B (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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| CN110657201A CN110657201A (en) | 2020-01-07 |
| CN110657201B true CN110657201B (en) | 2022-03-18 |
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| CN201810713252.7A Active CN110657201B (en) | 2018-06-29 | 2018-06-29 | Transmission, power driving system and vehicle |
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| WO (1) | WO2020001589A1 (en) |
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| CN112810435A (en) * | 2020-07-19 | 2021-05-18 | 清研华科新能源研究院(南京)有限公司 | Coaxial electric drive axle based on tower planet row |
| CN112744038A (en) * | 2021-01-28 | 2021-05-04 | 江西科技学院 | Flying automobile driving system and flying automobile |
| CN113232501B (en) * | 2021-05-12 | 2022-12-27 | 东风汽车集团股份有限公司 | Hybrid power driving system |
| CN113650488B (en) * | 2021-08-20 | 2023-11-21 | 北方汤臣传动科技有限公司 | Transmission system with double-motor power coupling function |
| CN114017475B (en) * | 2021-11-10 | 2023-11-21 | 一汽解放汽车有限公司 | Speed change device, speed changer and vehicle |
| CN115214337B (en) * | 2022-06-09 | 2024-06-04 | 一汽解放汽车有限公司 | Hybrid power system |
| CN115366655B (en) * | 2022-09-26 | 2023-06-27 | 浙江吉利控股集团有限公司 | Multi-speed transmission, power drive system and vehicle |
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| Publication number | Publication date |
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| WO2020001589A1 (en) | 2020-01-02 |
| CN110657201A (en) | 2020-01-07 |
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