CN110657200B - Transmission, power driving system and vehicle - Google Patents
Transmission, power driving system and vehicle Download PDFInfo
- Publication number
- CN110657200B CN110657200B CN201810713124.2A CN201810713124A CN110657200B CN 110657200 B CN110657200 B CN 110657200B CN 201810713124 A CN201810713124 A CN 201810713124A CN 110657200 B CN110657200 B CN 110657200B
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- gear
- transmission
- sun gear
- synchronizer
- torque
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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, the second planetary gear mechanism, the input shaft, the intermediate shaft, the first synchronizer and the second synchronizer, the first gear ring is fixedly connected with a shell of the transmission, the second planet carrier is connected with the output end of the transmission, the input shaft is connected with the first sun gear, the intermediate shaft is connected with the second sun gear, the first synchronizer connects the second sun gear with the first planet carrier or connects the intermediate shaft with the first sun gear, and the second synchronizer fixes the second gear ring with the shell of the transmission or connects the second gear ring 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 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 planet carrier is connected with the output end of the transmission; an input shaft connected with the first sun gear; an intermediate shaft connected to the second sun gear; a first synchronizer connecting the second sun gear with the first carrier or the intermediate shaft with the first sun gear; a second synchronizer that fixes the second ring gear with a housing of the transmission or connects the second ring gear 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 includes an output gear connected to the second carrier.
In some embodiments, the axis of the input shaft is collinear with the axis of the intermediate shaft, the output gear is located between the first planetary gear mechanism and the second planetary gear mechanism, and the output gear is hollow outside the intermediate shaft.
In some embodiments, the first synchronizer is located between the first planetary gear mechanism and the output gear.
In some embodiments, the transmission is in first gear, the first synchronizer connects the second sun gear with the first carrier, and the second synchronizer fixes the second ring gear with a housing of the transmission.
In some embodiments, the transmission is in second gear, the first synchronizer connects the second sun gear with the first sun gear, and the second ring gear is fixed with a housing of the transmission.
In some embodiments, the transmission is in the third gear, the first synchronizer connects the second sun gear with the first carrier, and the second synchronizer connects the second ring gear with the second sun gear.
In some embodiments, the first synchronizer connects the second sun gear with the first sun gear and the second synchronizer connects the second ring gear with the second sun gear when the transmission is in the fourth 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.
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 gear 6;
a first synchronizer 7; a second synchronizer 8;
a differential 200.
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 through the input shaft 4, and the torque can be finally output from the output end of the transmission 100 through the first planetary gear mechanism and the second planetary gear mechanism in the transmission 100. 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 includes a first sun gear 11, a first planetary gear 14, a first carrier 13 and a first ring gear 12, 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, torque can be input into the first planetary gear set from the first carrier 13 or the first sun gear 11 and output from the first planetary gear set to the intermediate shaft 5 from the first carrier 13.
The second planetary gear mechanism comprises a second sun gear 21, a second planet gear 24, a second planet carrier 23 and a second ring gear 22, wherein the second planet carrier 23 is connected with the output end of the transmission 100, so that when torque is transmitted in the second planetary gear mechanism, the torque can be input by the second sun gear 21 and/or the second ring gear 22, output by the second planet carrier 23 to the output end of the transmission 100 and finally transmitted out of the transmission 100.
The input shaft 4 is connected to the first sun gear 11, the intermediate shaft 5 is connected to the second sun gear 21, torque can be transmitted from the input shaft 4 to the first sun gear 11 to transmit torque to the first planetary gear mechanism, and torque can be transmitted from the intermediate shaft 5 to the second sun gear 21 to transmit torque to the second planetary gear mechanism.
The first synchronizer 7 connects the second sun gear 21 to the first carrier 13 or the countershaft 5 to the first sun gear 11: when the first synchronizer 7 connects the second sun gear 21 with the first carrier 13, the torque input from the first sun gear 11 to the first planetary gear mechanism is output from the first planetary gear mechanism from the first carrier 13, and the first carrier 13 transmits the torque to the intermediate shaft 5; when the first synchronizer 7 is to connect the intermediate shaft 5 with the first sun gear 11, torque can be transferred from the input shaft 4 to the first sun gear 11, torque being transferred from the first sun gear 11 to the intermediate shaft 5.
The second synchronizer 8 fixes the second ring gear 22 to the housing 10 of the transmission 100 or connects the second ring gear 22 to the second sun gear 21: when the second synchronizer 8 fixes the second ring gear 22 with the housing 10 of the transmission 100, torque is transmitted from the second sun gear 21 to the second planetary gear mechanism, and is output from the second planetary gear mechanism by the second carrier 23; when the second synchronizer 8 connects the second ring gear 22 with the second sun gear 21, torque is input from the second sun gear 21 and the second ring gear 22 in the second planetary gear mechanism, and is output from the second planetary gear mechanism by the second carrier 23.
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 output end of the transmission 100 includes the output gear 6, the output gear 6 is connected to the second carrier 23, the torque output from the second planetary gear mechanism is transmitted to the output gear 6, the transmission 100 is transmitted out through the output gear 6, and the transmission direction of the output torque can be changed by connecting the second carrier 23 to the output gear 6, 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 the vehicle.
In some embodiments, as shown in fig. 1, the axis of the input shaft 4 is collinear with the axis of the intermediate shaft 5, the output gear 6 is located between the first planetary gear mechanism and the second planetary gear mechanism, and the output gear 6 is hollow outside the intermediate shaft 5, so that the arrangement of the input shaft 4 and the output gear 6 can be facilitated, the transmission direction of torque from the input shaft 4 to the output gear 6 can be changed, the size of the transmission 100 in the axis direction of the input shaft 4 can be reduced, and the transmission 100 can be arranged on a vehicle more conveniently.
In some embodiments, as shown in fig. 1, the first synchronizer 7 is located between the first planetary gear mechanism and the output gear 6, the first synchronizer 7 can be disposed in a position to effectively utilize the space of the transmission 100 in the axial direction of the input shaft 4, and the second synchronizer 8 can be disposed in a position to utilize the space of the transmission 100 in the axial direction perpendicular to the input shaft 4, so as to reduce the volume of the transmission 100 in the axial direction of the input shaft 4, thereby making the structure of the transmission 100 more compact, and further saving the space for disposing the transmission 100 on the vehicle.
In some embodiments, the first planetary gear mechanism and the second planetary gear mechanism are single-stage planetary gear mechanisms, namely, the sun gear reaches the first planetary gear to drive the ring gear, and the single-stage planetary gear mechanisms are simple in structure and can effectively enhance the torque transmission efficiency of the transmission 100.
In some embodiments, the transmission 100 according to the embodiment of the present invention may have a plurality of gears, i.e., first, second, third, and fourth gears, in which the speed ratio of the first gear to the fourth gear 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 u3 of the third gear > the speed ratio u4 of the fourth gear.
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.
The operation states of the first synchronizer 7 and the second synchronizer 8 for 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 gear 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 engaged in the first gear, the first synchronizer 7 connects the second sun gear 21 with the first carrier 13, and the second synchronizer 8 fixes the second ring gear 22 with the housing 10 of said 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, torque is output from the first carrier 13 of the first planetary gear mechanism to the second sun gear 21 because the first ring gear 12 is fixed to the case 10 of the transmission 100, and the first synchronizer 7 connects the second sun gear 21 to the first carrier 13, torque is transmitted from the first carrier 13 of the first planetary gear mechanism to the second sun gear 21, torque is transmitted from the second sun gear 21 to the second planetary gear mechanism, and the second ring gear 22 is fixed to the case 10 of the transmission 100, and torque is transmitted from the second carrier 23 to the output gear 6 in the second planetary gear mechanism.
Thus, when the transmission 100 is in the first gear, torque is input from the first sun gear 11 in the first planetary gear mechanism and is output from the first carrier 13 to the second sun gear 21, at this time, the torque decreases with respect to the rotation speed of the input shaft 4, the torque is transmitted to the second planetary gear mechanism via the intermediate shaft 5 and is input from the second sun gear 21, the torque is output from the second carrier 23 to the output gear 6, the torque is decelerated again with respect to the input shaft 4 via the second planetary gear mechanism, and when the torque is transmitted from the input shaft 4 to the transmission 100 in the first gear, the torque is transmitted to the transmission 100 via the two-stage deceleration of the first planetary gear mechanism and the second planetary gear mechanism.
When the transmission 100 is in the second gear, the first synchronizer 7 connects the second sun gear 21 with the first sun gear 11, and the second ring gear 22 is fixed 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, the second sun gear 21 outputs torque from the first sun gear 11 of the first planetary gear mechanism to the second sun gear 21 because the first synchronizer 7 connects the second sun gear 21 with the first sun gear 11, the second sun gear 21 transmits torque to the second planetary gear mechanism, the second ring gear 22 is fixed to the housing 10 of the transmission 100, and torque is transmitted from the second carrier 23 to the output gear 6 in the second planetary gear mechanism.
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 sun gear 11 to the second sun gear 21, at which time the torque is not changed with respect to the rotation speed of the input shaft 4, the torque is transmitted to the second planetary gear mechanism through the intermediate shaft 5 and input from the second sun gear 21, the torque is output from the second carrier 23 to the output gear 6, the torque is decelerated with respect to the input shaft 4 through the second planetary gear mechanism, 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 deceleration of the first planetary gear mechanism and the second planetary gear mechanism, in the second gear, the torque is decelerated with respect to the input shaft 4 only through the one stage of the second planetary gear mechanism, so that when the rotation speed of the input shaft 4 is constant with respect to the first gear, the output rotation speed of the second carrier 23 in the second gear is larger, thus, the speed ratio u1 of the first gear is larger than the speed ratio u2 of the second gear.
When the transmission 100 is in third gear, the first synchronizer 7 connects the second sun gear 21 with the first carrier 13, and the second synchronizer 8 connects the second ring gear 22 with the second sun gear 21.
Thus, torque is transmitted from the input shaft 4 to the transmission 100, the input shaft 4 transmits the torque to the first sun gear 11, the torque is output from the first carrier 13 of the first planetary gear mechanism to the second sun gear 21 because the first ring gear 12 is fixed to the transmission 100 housing 10, and the first synchronizer 7 connects the second sun gear 21 to the first carrier 13, the torque is transmitted from the first carrier 13 of the first planetary gear mechanism to the second sun gear 21, the torque is transmitted from the second sun gear 21 to the second planetary gear mechanism, the second synchronizer 8 connects the second ring gear 22 to the second sun gear 21, and the torque is input from the second sun gear 21 to the second planetary gear mechanism and is transmitted from the second carrier 23 to the output gear 6.
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 carrier 13 to the second sun gear 21, the torque is reduced with respect to the rotation speed of the input shaft 4, the torque is transmitted to the second planetary gear mechanism via the intermediate shaft 5 and input from the second sun gear 21 and the second ring gear 22, the torque is output from the second carrier 23 to the output gear 6, and the torque is reduced again with respect to the input shaft 4 via the second planetary gear mechanism. With respect to 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 gear 6 of the third gear rotates at a speed faster than that of the output gear 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 second sun gear 21 with the first sun gear 11, and the second synchronizer 8 connects the second ring gear 22 with the second sun gear 21.
Thus, torque is transmitted from the input shaft 4 to the transmission 100, the input shaft 4 transmits the torque to the first sun gear 11, the torque is output from the first sun gear 11 of the first planetary gear mechanism to the second sun gear 21 because the first synchronizer 7 connects the second sun gear 21 with the first sun gear 11, the torque is transmitted from the second sun gear 21 to the second planetary gear mechanism, the second synchronizer 8 connects the second ring gear 22 with the second sun gear 21, and the torque is input from the second sun gear 21 and the second ring gear 22 to the second planetary gear mechanism and is transmitted from the second carrier 23 to the output gear 6.
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 sun gear 11 to the second sun gear 21, while the torque is unchanged with respect to the rotation speed of the input shaft 4, the torque is transmitted to the second planetary gear mechanism via the intermediate shaft 5 and input from the second sun gear 21 and the second ring gear 22, the torque is output from the second carrier 23 to the output gear 6, the torque is decelerated with respect to the input shaft 4 via the second planetary gear mechanism, in the third 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 deceleration of the first planetary gear mechanism and the second planetary gear mechanism, in the fourth gear, the torque is decelerated only via the one-stage deceleration of the second planetary gear mechanism with respect to the input shaft 4, so that, with respect to the third gear, when the rotation speed of the input shaft 4 is constant, in the fourth gear, the output speed of the second carrier 23 is higher, so that the speed ratio u3 of the third gear is higher than the speed ratio u4 of the fourth gear.
In summary, the transmission 100 of the present invention can be a 4-gear synchronizer transmission for a heavy pure electric vehicle, and has the advantages of simple and reliable structure, large output torque, strong climbing capability, and strong power when being matched with a driving motor even though road conditions are complicated. And the synchronizer is adopted for shifting, and a clutch is not needed, so that the structure is simple and compact, the shifting process is smooth, and the cost is lower.
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, through the combination of the first planetary gear mechanism and the second planetary gear mechanism, the two synchronizers reasonably utilize the space between the two planetary rows, the design is more compact on the whole, the gear load balancing effect is better, and the requirements of the vehicle on the aspects of the durability, the power transmission efficiency, the size, the cost and the like of the transmission 100 are well met.
In some embodiments, the driving motor is arranged coaxially with the input shaft 4, and the driving motor is arranged at a side of the first planetary gear mechanism facing away from the second planetary gear mechanism, so that the arrangement of the power driving system can be facilitated, and the extra gears and the like are not needed to change the route of torque transmission between the driving motor and the input shaft 4, 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 some examples, as shown in fig. 1, the vehicle may further include a differential 200, and an input end of the differential 200 is connected to the output gear 6, so that the torque output by the transmission 100 can be input into the differential 200 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 (7)
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 planet carrier is connected with the output end of the transmission;
an input shaft connected with the first sun gear;
an intermediate shaft connected to the second sun gear;
a first synchronizer connecting the second sun gear with the first carrier or the intermediate shaft with the first sun gear;
a second synchronizer that fixes the second ring gear with a housing of the transmission or connects the second ring gear with the second sun gear;
the output end of the speed changer comprises an output gear, and the output gear is connected with the second planet carrier;
the axis of the input shaft is collinear with the axis of the intermediate shaft, the output gear is positioned between the first planetary gear mechanism and the second planetary gear mechanism, and the output gear is idly sleeved outside the intermediate shaft;
the first synchronizer is located between the first planetary gear mechanism and the output gear.
2. The transmission of claim 1, wherein the transmission is in first gear, the first synchronizer connects the second sun gear with the first carrier, and the second synchronizer fixes the second ring gear with a housing of the transmission.
3. The transmission of claim 1, wherein the transmission is in second gear, the first synchronizer connects the second sun gear with the first sun gear, and the second ring gear is fixed with a housing of the transmission.
4. The transmission of claim 1, wherein the transmission is in third gear, the first synchronizer connects the second sun gear with the first carrier, and the second synchronizer connects the second ring gear with the second sun gear.
5. The transmission of claim 1, wherein the first synchronizer connects the second sun gear with the first sun gear and the second synchronizer connects the second ring gear with the second sun gear when the transmission is in fourth gear.
6. A powertrain system, comprising:
a drive motor;
the transmission of any one of claims 1-5, said drive motor being in power-coupled connection with said input shaft.
7. A vehicle, characterized by comprising: the drivetrain of claim 6.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810713124.2A CN110657200B (en) | 2018-06-29 | 2018-06-29 | Transmission, power driving system and vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810713124.2A CN110657200B (en) | 2018-06-29 | 2018-06-29 | Transmission, power driving system and vehicle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110657200A CN110657200A (en) | 2020-01-07 |
| CN110657200B true CN110657200B (en) | 2021-12-07 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810713124.2A Active CN110657200B (en) | 2018-06-29 | 2018-06-29 | Transmission, power driving system and vehicle |
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| CN (1) | CN110657200B (en) |
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