CN110657204A - Transmission, power driving system and vehicle - Google Patents
Transmission, power driving system and vehicle Download PDFInfo
- Publication number
- CN110657204A CN110657204A CN201810713969.1A CN201810713969A CN110657204A CN 110657204 A CN110657204 A CN 110657204A CN 201810713969 A CN201810713969 A CN 201810713969A CN 110657204 A CN110657204 A CN 110657204A
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- gear
- transmission
- carrier
- synchronizer
- 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
- F16H3/46—Gearings having only two central gears, connected by orbital gears
- F16H3/58—Gearings having only two central gears, connected by orbital gears with sets of orbital gears, each consisting of two or more intermeshing 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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
- F16H61/0403—Synchronisation before shifting
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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, wherein a second gear ring of the second planetary gear mechanism is connected with the output end of the speed changer, the input shaft is connected with the first sun gear, the first gear ring is connected with the intermediate shaft, the intermediate shaft is connected with the second sun gear, the first synchronizer fixes the first planet carrier with a shell of the speed changer or connects the first planet carrier with the first sun gear, and the second synchronizer fixes the second planet carrier with the shell of the speed changer 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 gear ring is connected with the intermediate shaft, and the intermediate shaft is connected with the second sun gear; a first synchronizer that fixes the first carrier with a housing of the transmission or connects the first carrier with 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 includes an output gear connected to the second ring gear.
In some embodiments, the output gear is idler outside the countershaft.
In some embodiments, the output gear is located between the first planetary gear mechanism and the second planetary gear mechanism.
In some embodiments, the first planetary gear mechanism is disposed between the first synchronizer and the second planetary gear mechanism, and the second planetary gear mechanism is disposed between the second synchronizer and the first planetary gear mechanism. In some embodiments, the first planetary gear mechanism and the second planetary gear mechanism are both double-stage planetary gear mechanisms.
In some embodiments, the decelerator according to the present invention further comprises: the driving gear is meshed with the idler, the idler is meshed with the driven gear, and the driven gear is connected with the input shaft.
In some embodiments, the transmission is engaged in first gear, the first synchronizer fixes the first carrier 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 connects the first carrier with the first sun gear, and the second synchronizer fixes the second carrier with a housing of the transmission.
In some embodiments, the transmission is in third gear, the first synchronizer fixes the first carrier to a housing of the transmission, and the second synchronizer connects the second carrier to the second sun gear.
In some embodiments, the transmission is in fourth gear, the first synchronizer connects the first carrier with the first sun gear, and the second synchronizer connects the second carrier with the second 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 transmission is a transmission including a driving gear, an idler gear, and a driven gear, the driving motor is connected to the driving gear, and the driving motor and the first planetary gear mechanism are both disposed on the same side of the driving gear.
The vehicle according to the invention comprises the power drive system according to the invention.
The vehicle provided by the invention has the same advantages compared with the prior art by arranging the power driving system provided by the invention, and the detailed description is omitted.
Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.
Drawings
The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:
fig. 1 is a schematic structural diagram of a transmission according to an embodiment of the present invention.
Reference numerals:
a transmission 100; a housing 10;
a first sun gear 11; a first ring gear 12; a first carrier 13; a first planet 14;
a second sun gear 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 terminal 6;
a first synchronizer 7; a second synchronizer 8;
a drive gear 91; an idler pulley 92; a driven gear 93;
a driving motor 200; a differential 300.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the accompanying drawings are illustrative only for the purpose of explaining the present invention, and are not to be construed as limiting the present invention.
A transmission 100 according to an embodiment of the present invention is described below with reference to fig. 1.
As shown in fig. 1, a transmission 100 according to an embodiment of the present invention includes: 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 6 of the transmission 100 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 third planet carrier to the intermediate shaft 5.
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, and the second ring gear 22 is connected with the output end 6 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 planet carrier 22, output by the second planet carrier 23 to the output end 6 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 first ring gear 12 is connected to the intermediate shaft 5, the intermediate shaft 5 is connected to the second sun gear 21, torque can be transmitted into the first planetary gear mechanism via the input shaft 4, from the first ring gear 12 to the intermediate shaft 5, and torque is transmitted to the second sun gear 21 of the second planetary gear mechanism via the intermediate shaft 5.
The first synchronizer 7 fixes the first carrier 13 to the housing 10 of the transmission 100 or connects the first carrier 13 to the first sun gear 11: when the first synchronizer 7 fixes the first carrier 13 with the housing 10 of the transmission 100, torque can be transmitted from the first sun gear 11 via the input shaft 4 into the first planetary gear mechanism and from the first planetary gear mechanism by the first ring gear 12; when the first synchronizer 7 connects the first carrier 13 with the first sun gear 11, torque can be transmitted from the first sun gear 11 and the first carrier 13 via the input shaft 4 into the first planetary gear set and from the first ring gear 12 out of the first planetary gear set.
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 transmitted from the second sun gear 21 via the intermediate shaft 5 into the second planetary gear mechanism and from the second ring gear 22 out of the second planetary gear mechanism; when the second synchronizer 8 connects the second carrier 23 with the second sun gear 21, torque can be transmitted from the second sun gear 21 and the second carrier 23 to the second planetary gear mechanism via the intermediate shaft 5, and from the second ring gear 22 to the second planetary gear mechanism.
According to the transmission 100 provided by the embodiment of the invention, the first synchronizer 7 and the second synchronizer 8 are 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, and the structure of the transmission 100100 is simplified by adopting a synchronizer for shifting gears and not using 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 6 of the transmission 100 includes an output gear connected to the second ring gear 22, and torque output from the second planetary gear mechanism is transmitted to the output gear, and transmitted out of the transmission 100 through the output gear. Connecting the second ring gear 22 with the output gear can 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, thereby allowing the transmission 100 to be more conveniently arranged on the vehicle.
In some embodiments, the output of the transmission 100 may further comprise an output shaft connected to the second ring gear 22, the axis of the output shaft being collinear with the axis of the intermediate shaft 5.
In some embodiments, as shown in fig. 1, the output gear may be freely sleeved outside the intermediate shaft 5, so that the arrangement of the output gear may be facilitated, and a shaft is not required to be separately provided for the output gear, so that the size of the transmission 100 in the axial direction of the input shaft 4 may be reduced, thereby making the structure of the transmission 100 more compact, and enabling the transmission 100 to be more conveniently arranged on the vehicle.
In some embodiments, as shown in fig. 1, the output gear is located between the first planetary gear mechanism and the second planetary gear mechanism, so that the space of the transmission 100 in the axial direction can be saved, and the structure of the transmission 100 can be more compact.
The first planetary gear mechanism is disposed between the first synchronizer and the second planetary gear mechanism, and the second planetary gear mechanism is disposed between the second synchronizer and the first planetary gear mechanism. The first synchronizer 7 is located on the side of the first planetary gear mechanism facing away from the second planetary gear mechanism, and the second synchronizer 8 is located on the side of the second planetary gear mechanism facing away from the first planetary gear mechanism, so that the arrangement of the first synchronizer 7 and the second synchronizer 8 can be facilitated, the distance between the first planetary gear mechanism and the second planetary gear mechanism can be made to be short, the length of the intermediate shaft 5 can be made to be short, and the stability of the transmission 100 can be improved.
In some embodiments, as shown in fig. 1, the first and second planetary gear mechanisms are both double-pinion planetary gear mechanisms, i.e., planetary gear mechanisms having double-pinion planets, with the sun gear accessible to the double-pinion planets, i.e., driving the ring gear. The number of the planet carrier teeth of the double-stage planetary gear mechanism is small, and when the planet carrier is fixed, the rotation directions of the sun gear and the ring gear are the same, so that the ring gear can be used as the output end 6 of the planetary gear mechanism, and the torque input into the planetary gear mechanism from the sun gear and the torque output from the planetary gear mechanism from the ring gear can be in the same direction, so that the rotation direction of the input shaft 4 is consistent with the rotation direction of the output gear, and the complexity in operation of the transmission 100 is solved.
In some embodiments, as shown in fig. 1, the reducer according to the present invention further comprises: the driving gear 91, the idler gear 92 and the driven gear 93, the driving gear 91 is meshed with the idler gear 92, the idler gear 92 is meshed with the driven gear 93, the driven gear 93 is connected with the input shaft 4, torque can be transmitted to the input shaft 4 through the driving gear 91 and the idler gear 92 and the driven gear 93 in sequence at a motor or an engine of a vehicle, the torque is transmitted to the first planetary gear mechanism through the input shaft 4, the driving gear 91, the idler gear 92 and the driven gear 93 can change the torque transmission direction of the motor or the engine of the vehicle, and therefore the speed reducer and the motor or the engine of the vehicle can be arranged side by side. That is, the axis of the reduction gear is parallel to the axis of the motor or the engine, so that the length of the power drive system of the vehicle in the axial direction can be reduced, the space for arranging the power drive system on the vehicle can be saved, the idle gear 92 is added to the axis member of the input shaft 4 and the planetary gear set, and the output position is adjusted to the middle position of the transmission 100, so that the axial length of the driving motor 200 and the axial length of the reduction gear 100 at the planetary gear set are not overlapped, so that the width of the power drive device of the vehicle can be smaller than the width of the axle.
In some embodiments, the transmission 100 according to the embodiment of the invention may have four gears, i.e., a first gear, a second gear, a third gear, and a fourth gear, 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 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 6 of the transmission 100 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 the first gear, the first synchronizer 7 fixes the first carrier 13 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.
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, and since the first carrier 13 is fixed to the transmission 100 casing 10, torque is output from the first ring gear 12 of the first planetary gear mechanism 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 gear.
Thus, in the first gear of the transmission 100, in the first planetary gear mechanism, torque is input from the first sun gear 11 and output from the first ring gear 12 to the 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, 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 gear, torque is transmitted to the transmission 100 through the second planetary gear mechanism and reduced again, and in the first gear, after torque is transmitted from the input shaft 4 to the transmission 100, torque is transmitted to the transmission 100 through 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 gear are not changed.
When the transmission 100 is in the second gear, the first synchronizer 7 connects the first carrier 13 to the first sun gear 11, and the second synchronizer 8 fixes the second carrier 23 to the case 10 of the transmission 100.
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 and the first carrier 13, in the first planetary gear mechanism, is input by the first carrier 13 and the first sun gear 11, is output from the first ring gear 12, and transmits torque to the intermediate shaft 5, the intermediate shaft 5 transmits torque to the second sun gear 21, in the second planetary gear mechanism, torque transmitted to the second planetary gear mechanism is input by the second sun gear 21 and output by the second ring gear 22, and the second ring gear 22 transmits torque to the output gear.
Thus, in the second gear of the transmission 100, the torque is input from the first carrier 13 and the first sun gear 11 in the first planetary gear mechanism, is output from the first ring gear 12, and is transmitted to the intermediate shaft 5, the torque is transmitted to the second sun gear 21 of the second planetary gear mechanism via the intermediate shaft 5 while the torque is input from the first sun gear 21 and is output from the second ring gear 22 to the output gear while the torque is input from the first carrier 13 and the first sun gear 11 in the second gear, and the rotational speed is reduced while the torque is input to the output gear while the torque is input to the input shaft 4 in the second planetary gear mechanism. In the second 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 two-stage speed reduction of the first planetary gear mechanism and the second planetary gear mechanism, and the torque transmission direction of the input shaft 4 and the output gear is unchanged. However, in the first gear, the input of the first planetary gear mechanism is the first sun gear 11, and in the second gear, the input of the first planetary gear mechanism is the first sun gear 11 and the first carrier 13, so that the output rotation speed of the transmission 100 is greater in the second gear than in the first gear when the rotation speed of the input shaft 4 is constant, and 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 fixes the first carrier 13 to the case 10 of the transmission 100, and the second synchronizer 8 connects the second carrier 23 to the second sun gear 21.
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 ring gear 12 of the first planetary gear mechanism to the intermediate shaft 5 because the first carrier 13 is fixed to the transmission 100 casing 10, torque is transmitted to the second carrier 23 through the intermediate shaft 5 because the second synchronizer 8 connects the second sun gear 21 to the second carrier 23, torque transmitted to the second planetary gear mechanism is input from the second sun gear 21 and the second carrier 23 and output from the second ring gear 22, and torque is transmitted to the output gear by the second ring gear 22.
Thus, when the transmission 100 is in the third gear, in the first planetary gear mechanism, torque is input from the first sun gear 11 and output from the first ring gear 12 to the intermediate shaft 5, at which time torque is in the same direction as the rotation direction of the input shaft 4 and the rotation speed is reduced, torque is transmitted to the third planetary gear mechanism via the intermediate shaft 5, torque is transmitted to the second sun gear 21 and the second carrier 23 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, torque is output to the output gear via the second ring gear 22, torque is in the same direction as the rotation direction of the input shaft 4 via the second planetary gear mechanism and is reduced again, and 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 rotation speed of the input shaft 4 is constant, the rotation speed of the output gear of the third gear is faster than that of the output gear of the second gear, thus, the speed ratio u2 of the second gear is larger 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 carrier 13 with the first sun gear 11, and the second synchronizer 8 connects the second carrier 23 with the second sun gear 21.
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 the first carrier 13, in the first planetary gear mechanism, is input from the first carrier 13 and the first sun gear 11, is output from the first ring gear 12, and transmits torque to the intermediate shaft 5, in the second planetary gear mechanism, torque is transmitted to the second carrier 23 through the intermediate shaft 5 due to the second synchronizer 8 connecting the second sun gear with the second carrier 23, torque transmitted to the second planetary gear mechanism is input from the second sun gear 21 and the second carrier 23 and is output from the second ring gear 22, and the second ring gear 22 transmits torque to the output gear.
Thus, in the fourth gear of the transmission 100, in the first planetary gear mechanism, the torque is input from the first carrier 13 and the first sun gear 11, is output from the first ring gear 12, and is transmitted to the intermediate shaft 5, at which 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 and the second carrier 23 through the intermediate shaft 5, and is 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 gear 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 fourth gear, the torque is transmitted to the transmission 100 from the input shaft 4 after being transmitted to the transmission 100 through the two-stage speed 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 end 6 of the transmission 100 are unchanged, in the third gear, the input of the first planetary gear mechanism is the first sun gear 11, and in the fourth gear, the input of the first planetary gear mechanism is the first sun gear 11 and the first carrier 13, so that the output rotation speed of the second ring gear 22 is greater in the fourth gear than in the third gear when the rotation speed of the input shaft 4 is constant, 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 200 and the transmission 100 of any one of the above embodiments, wherein the driving motor 200 is in power coupling connection with the input shaft 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, as shown in fig. 1, when the transmission 100 is a transmission 100 including a driving gear 91, an idler gear 92 and a driven gear 93, the driving motor 200 is connected to the driving gear 91, the driving motor 200 and the first planetary gear mechanism are both disposed on the same side of the driving gear 91, and the axes of the driving motor 200 and the input shaft 4 may be arranged in parallel, that is, the driving motor 200 and the transmission 100 may be arranged side by side, so that the length of the power drive system in the axial direction may be reduced, and the space for disposing the power drive system on the vehicle may be saved.
A vehicle according to an embodiment of the present invention includes: in the power driving system of the embodiment, the vehicle is provided with the power driving system, so that the vehicle has the advantages of smooth gear shifting, quick gear shifting and high torque transmission efficiency, the output torque range of the vehicle is large, the load is stable, the vehicle can cope with complex road conditions, and the power driving system has the advantage of saving energy.
In some examples, as shown in fig. 1, the vehicle may further include a differential 300, and an input end of the differential 300 is connected to an output end 6 of the speed reducer, so that the torque output by the transmission 100 can be input into the differential 300 and finally drive wheels of the vehicle to rotate, thereby realizing the running of the vehicle.
In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the invention and to simplify the description, and are not intended to indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and are not to be considered limiting of the invention.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an illustrative embodiment," "an example," "a specific example," or "some examples" or the like mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
While embodiments of the invention have been shown and described, it will be understood by those of ordinary skill in the art that: various changes, modifications, substitutions and alterations can be made to the embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.
Claims (14)
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 gear ring is connected with the intermediate shaft, and the intermediate shaft is connected with the second sun gear;
a first synchronizer that fixes the first carrier with a housing of the transmission or connects the first carrier with 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.
2. The transmission of claim 1, wherein the output of the transmission includes an output gear connected with the second ring gear.
3. The transmission of claim 2 wherein said output gear is idler from said countershaft.
4. The transmission of claim 3, wherein the output gear is located between the first planetary gear mechanism and the second planetary gear mechanism.
5. The transmission of claim 1, wherein the first planetary gear mechanism is disposed between the first synchronizer and the second planetary gear mechanism, and the second planetary gear mechanism is disposed between the second synchronizer and the first planetary gear mechanism.
6. The transmission of claim 1, wherein the first planetary gear mechanism and the second planetary gear mechanism are both double-pinion planetary gear mechanisms.
7. The transmission of claim 1, further comprising: the driving gear is meshed with the idler, the idler is meshed with the driven gear, and the driven gear is connected with the input shaft.
8. The transmission of any of claims 1-7, wherein the transmission is in first gear, the first synchronizer fixes the first carrier to a housing of the transmission, and the second synchronizer fixes the second carrier to the housing of the transmission.
9. The transmission of any one of claims 1-7, wherein the transmission is in second gear, the first synchronizer connects the first carrier with the first sun gear, and the second synchronizer fixes the second carrier with a housing of the transmission.
10. The transmission of any one of claims 1-7, wherein the transmission is in third gear, the first synchronizer fixes the first carrier to a housing of the transmission, and the second synchronizer connects the second carrier to the second sun gear.
11. The transmission of any one of claims 1-7, wherein the transmission is in fourth gear, the first synchronizer connects the first carrier with the first sun gear, and the second synchronizer connects the second carrier with the second sun gear.
12. A power drive system, comprising:
a drive motor;
the transmission of any one of claims 1-11, said drive motor being in power-coupled connection with said input shaft.
13. A power drive system according to claim 12, wherein the transmission is according to claim 7, the drive motor is connected to the drive gear, and the drive motor and the first planetary gear mechanism are both arranged on the same side of the drive gear.
14. A vehicle, characterized by comprising: a power drive system according to claim 12 or 13.
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| CN110657204B (en) | 2022-04-15 |
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