CN110657208B - Transmission, power driving system and vehicle - Google Patents
Transmission, power driving system and vehicle Download PDFInfo
- Publication number
- CN110657208B CN110657208B CN201810714103.2A CN201810714103A CN110657208B CN 110657208 B CN110657208 B CN 110657208B CN 201810714103 A CN201810714103 A CN 201810714103A CN 110657208 B CN110657208 B CN 110657208B
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- China
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- gear
- transmission
- synchronizer
- sun gear
- planetary gear
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
- B60K17/08—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing of mechanical type
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
- B60K6/54—Transmission for changing ratio
- B60K6/547—Transmission for changing ratio the transmission being a stepped gearing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/78—Special adaptation of synchronisation mechanisms to these gearings
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
- H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2035—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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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/64—Electric machine technologies in electromobility
Abstract
The invention discloses a transmission, a power driving system and a vehicle, wherein the transmission comprises: the planetary gear set comprises three rows of planetary gears, an input shaft, an intermediate shaft, a first synchronizer and a second synchronizer, wherein a first gear ring of a first planetary gear mechanism is fixedly connected with a shell of a transmission, a second gear ring of a second planetary gear mechanism is fixedly connected with a first planet carrier, a third planet carrier of a third planetary gear mechanism is fixedly connected with an output end of the transmission, the input shaft is connected with a first sun gear and a second sun gear, the intermediate shaft is connected with a third sun gear, the first synchronizer connects the third sun gear with the second planet carrier or the third sun gear with the second sun gear, and the second synchronizer fixes the third gear ring with the shell of the transmission or connects the third gear ring with the third sun gear. According to the transmission, the three-planet-row three-synchronizer structure is arranged, so that the gear can be shifted quickly, smoothly and reliably, and the transmission is simple in structure and convenient to maintain.
Description
Technical Field
The invention belongs to the technical field of vehicle manufacturing, and particularly relates to a transmission, a power driving system and a vehicle.
Background
Hybrid drive automobiles, electric automobiles and extended range electric automobiles are the development direction of future automobiles and are also the main form of new energy automobiles. In the related technology, the structure of the power transmission system is complex, the working mode is complex, the control strategy is complicated, the energy conversion efficiency needs to be improved, the motive energy of the engine and the electric energy of the battery can not be fully utilized, and the problems of secondary energy conversion, complex control and low efficiency exist. Specifically, in the related art, a plate clutch and a plate brake of a vehicle control shifting, but when these two components are not operated, drag torque exists due to lubrication, resulting in inefficiency of the entire transmission.
In addition, in the multi-gear transmission in the related art, gears are mostly selected by a shifting fork and a sliding sleeve when the clutch cuts off power, the number of pairs of gears is large, the occupied space is large, and the structure is complex, so that the improvement space exists.
Disclosure of Invention
The present invention is directed to solving at least one of the problems of the prior art. Therefore, an object of the present invention is to provide a transmission with high efficiency, simple structure and smooth gear shifting.
The invention also provides a power driving system with the transmission.
The invention also provides a vehicle with the power driving system.
The transmission according to the present invention includes: a first planetary gear mechanism comprising a first sun gear, a first planet carrier, and a first ring gear, the first ring gear being fixedly connected to the transmission housing; the second planetary gear mechanism comprises a second sun gear, a second planet carrier and a second gear ring, and the second gear ring is fixedly connected with the first planet carrier; a third planetary gear mechanism comprising a third sun gear, a third planet carrier and a third ring gear, wherein the third planet carrier is fixedly connected with the output end of the transmission; an input shaft connected to the first sun gear and the second sun gear; an intermediate shaft connected to the third sun gear; a first synchronizer connecting the third sun gear with the second carrier or the second sun gear (first sun gear); a second synchronizer that fixes the third ring gear with the case of the transmission or connects the third ring gear with the third sun gear.
According to the transmission, the three-planet-row three-synchronizer structure is arranged, so that the gear can be shifted quickly, smoothly and reliably, and the transmission is simple in structure and convenient to maintain.
In some embodiments, the axis of the input shaft and the axis of the intermediate shaft are collinear, and the first planetary gear mechanism, the second planetary gear mechanism, and the third planetary gear mechanism are arranged in sequence along the axial direction.
In some embodiments, the first synchronizer is disposed between the second planetary gear mechanism and the third planetary gear mechanism, and the third planetary gear mechanism is disposed between the second synchronizer and the first synchronizer.
In some embodiments, the transmission according to the present invention further comprises: the first planetary gear mechanism, the second planetary gear mechanism, the output gear and the third planetary gear mechanism are sequentially arranged along the axial direction, and the output gear is sleeved outside the intermediate shaft in an empty mode.
In some embodiments, the transmission is engaged in first gear, the first synchronizer connects the third sun gear with the second carrier, and the second synchronizer fixes the third ring gear with a housing of the transmission.
In some embodiments, the transmission is in second gear, the first synchronizer connects the third sun gear with the second carrier, and the second synchronizer connects the third ring gear with the third sun gear.
In some embodiments, the transmission is in third gear, the first synchronizer connects the second sun gear with the third sun gear, and the second synchronizer fixes the third ring gear with the housing of the transmission.
In some embodiments, the transmission is in fourth gear, the first synchronizer connects the second sun gear with the third sun gear, and the second synchronizer connects the third ring gear with the third sun gear.
The power drive system according to the present invention includes: the transmission according to the invention comprises a drive motor which is connected in a power-coupling manner to the input shaft.
The power driving system of the invention has corresponding advantages by arranging the speed changer of the invention, and the detailed description is omitted.
In some embodiments, the drive motor is arranged on a side of the first planetary gear mechanism facing away from the second planetary gear mechanism.
The vehicle according to the invention comprises the power drive system according to the invention.
The vehicle provided by the invention has the same advantages compared with the prior art by arranging the power driving system provided by the invention, and the detailed description is omitted.
Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.
Drawings
The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:
fig. 1 is a schematic structural diagram of a transmission according to an embodiment of the present invention.
Reference numerals:
a transmission 100; a housing 10;
a first planetary gear mechanism 1; a first sun gear 11; a first ring gear 12; a first carrier 13; a first planet 14;
a second planetary gear mechanism 2; a second sun gear 21; a second ring gear 22; a second carrier 23; a second planet wheel 24;
a third planetary gear mechanism 3; the third sun gear 31; the third ring gear 32; a third carrier 33; a third planet wheel 34;
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 1, a second planetary gear mechanism 2, a third planetary gear mechanism 3, an input shaft 4, an intermediate shaft 5, a first synchronizer 7, and a second synchronizer 8.
Torque of the vehicle can be input to the transmission 100 through the input shaft 4, and torque can be finally output from the output end of the output gear 6 in the transmission 100 through the first planetary gear mechanism 1, the second planetary gear mechanism 2, and the third planetary gear mechanism 3. The synchronizer is used to connect the various components within the transmission 100 to effect a gear shift.
The first planetary gear mechanism 1 may include a plurality of first planet gears 14, the plurality of first planet gears 14 may be connected to the first carrier 13, the second planetary gear mechanism 2 may include a plurality of second planet gears 24, the plurality of second planet gears 24 may be connected to the second carrier 23, the third planetary gear mechanism 3 may include a plurality of third planet gears 34, and the plurality of third planet gears 34 may be connected to the third carrier 33. When the sun gear of each planetary gear mechanism rotates, each sun gear can drive the corresponding planet gear to rotate, and the planet carrier corresponding to the planet gear can selectively rotate. When the gear ring is fixed and the planet carrier is not fixed, the sun gear is input, and the planet gear rotates and drives the planet carrier to output; when the planet carrier is fixed and the gear ring is not fixed, the sun gear inputs, and the planet gear rotates and drives the gear ring to output; when the planet carrier and the gear ring are not fixed, the sun gear and the gear ring are input, and the planet gear rotates and drives the planet carrier to output; when the planet carrier and the gear ring are not fixed, the sun gear and the planet carrier input, and the planet gear rotates and drives the gear ring to output.
The first planetary gear set 1 includes a first sun gear 11, a first planetary gear 14, a first carrier 13, and a first ring gear 12, and the first ring gear 12 is fixedly connected to the housing 10 of the transmission 100, so that when torque is transmitted in the first planetary gear set 1, torque can be input into the first planetary gear set 1 from the first sun gear 11, output from the first planetary gear set 1 to a second ring gear 22 of the second planetary gear set 2 by the first carrier 13, and output from the first planetary gear set 1 to a second sun gear 21 of the second planetary gear set 2 by the first sun gear 11.
The second planetary gear mechanism 2 includes a second sun gear 21, a second planetary gear 24, a second planet carrier 23, and a second ring gear 22, and the second ring gear 22 is fixedly connected to the first planet carrier 13, so that when torque is transmitted in the second planetary gear mechanism 2, torque can be input to the second planetary gear mechanism 2 from the second ring gear 22 and the second sun gear 21, and transmitted to the third planetary gear mechanism 3 from the second sun gear 21 or the second planet carrier 23 via the intermediate shaft 5.
The third planetary gear set 3 includes a third sun gear 31, a third planet gear 34, a third planet carrier 33 and a third ring gear 32, and the third planet carrier 33 is fixedly connected to the output of the transmission 100, so that when torque is transmitted in the third planetary gear set 3, torque can be input by the third sun gear 31 and/or the third ring gear 32 and output by the third planet carrier 33 to the output of the transmission 100, and finally transmitted out of the transmission 100.
The input shaft 4 is connected to the first sun gear 11 and the second sun gear 21, the intermediate shaft 5 is connected to the third sun gear 31, torque can be transmitted from the input shaft 4 to the first planetary gear mechanism 1 through the first sun gear 11 and to the second planetary gear mechanism 2 through the second sun gear 21, and torque can be input to the third planetary gear mechanism 3 through the intermediate shaft 5 and from the third sun gear 31.
The first synchronizer 7 connects the third sun gear 31 with the second carrier 23 or the third sun gear 31 with the second sun gear 21 (first sun gear 11): when the first synchronizer 7 connects the third sun gear 31 with the second carrier 23, torque can be transmitted from the second carrier 23 to the third planetary gear mechanism 3 by the third sun gear 31; when the first synchronizer 7 connects the third sun gear 31 with the second sun gear 21 (first sun gear 11), torque can be transmitted from the second sun gear 21 to the third planetary gear mechanism 3 by the third sun gear 31.
The second synchronizer 8 fixes the third ring gear 32 to the housing 10 of the transmission 100 or connects the third ring gear 32 with the third sun gear 31: when the second synchronizer 8 fixes the third ring gear 32 to the housing 10 of the transmission 100, in the third planetary gear mechanism 3, torque is input by the third sun gear 31 and is transmitted out of the transmission 100 by the third carrier 33 through the output end of the transmission 100; when the second synchronizer 8 connects the third ring gear 32 with the third sun gear 31, torque is input from the third sun gear 31 and the third ring gear 32 in the third planetary gear mechanism 3, and is transmitted from the third carrier 33 out of the transmission 100 through the output end of the transmission 100
According to the transmission 100 provided by the embodiment of the invention, the first synchronizer 7 and the second synchronizer 8 are arranged, and the three-planetary-row double synchronizer structure is adopted, so that the gear shifting mode of the motor control synchronizer is realized, 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 is solved. 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 three-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 and the axis of the intermediate shaft 5 are collinear, and the first planetary gear mechanism 1, the second planetary gear mechanism 2 and the third planetary gear mechanism 3 are arranged in sequence along the axial direction, so that the arrangement of the input shaft 4 and the intermediate shaft 5 can be facilitated, and the torque can be transmitted from the first planetary gear, the second planetary gear mechanism 2 and the third planetary gear mechanism 3.
In some embodiments, as shown in fig. 1, the first synchronizer 7 is disposed between the second planetary gear mechanism 2 and the third planetary gear mechanism 3, and the third planetary gear mechanism 2 is disposed between the second synchronizer 8 and the first synchronizer 7. In some examples, the first synchronizer 7 is disposed between the second planetary gear mechanism 2 and the third planetary gear mechanism 3, the second synchronizer 8 is disposed on the side of the third planetary gear mechanism 3 facing away from the second planetary gear mechanism 2, so that the disposition of the first synchronizer 7 can be facilitated, and the disposition position of the first synchronizer 7 can be such that the distance between the second planetary gear mechanism 2 and the third planetary gear mechanism 3 is short, so that the length of the intermediate shaft 5 can be short, improving the stability of the transmission 100, the second synchronizer 8 is disposed on the side of the third planetary gear mechanism 3 facing away from the second planetary gear mechanism 2, so that the disposition of the second synchronizer 8 can be facilitated, and the length of the intermediate shaft 5 can be short, improving the stability of the transmission 100, in some examples, the second synchronizer 8 can be disposed radially outside the second planetary gear mechanism 2, the second synchronizer 8 is arranged on the side of the third planetary gear mechanism 3 facing away from the third planetary gear mechanism 3, so that the space in the radial direction of the transmission 100 can be utilized, the length of the transmission 100 in the axial direction can be saved, and the structure of the transmission 100 can be more compact.
In some embodiments, as shown in fig. 1, the output end of the transmission 100 includes the output gear 6, the first planetary gear mechanism 1, the second planetary gear mechanism 2, the output gear 6 and the third planetary gear mechanism 3 are sequentially arranged along the axial direction, and the output gear 6 is freely sleeved 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 the torque from the input shaft 4 to the output gear 6 can be changed, the size of the transmission 100 in the axial direction of the input shaft 4 can be reduced, the transmission 100 can be arranged on the vehicle more conveniently, and the output position can be adjusted to the middle position of the transmission 100, so that the width of the power driving device of the vehicle can be smaller than the width of the axle.
In some embodiments, the output of the transmission 100 may further comprise an output shaft connected to the third carrier 33, the axis of the output shaft being collinear with the axis of the intermediate shaft 5. In some embodiments, the first planetary gear mechanism 1, the second planetary gear mechanism 2, and the third planetary gear mechanism 3 are single-stage planetary gear mechanisms, i.e., the sun gear reaches the first-stage planetary gear mechanism, i.e., the planetary gear mechanism that can 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 invention may have 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 are arranged, so that the transmission 100 can have a four-gear shifting structure, and for medium and heavy trucks, due to the large torque requirement range, uncertain load and complex working condition, a six-gear structure is adopted, the motor is ensured to run 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 side (i.e., the output gear 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.
Torque is input from the first sun gear 11 to the first planetary gear mechanism 1 by the input shaft 4 and is transmitted from the first carrier 13 to the second ring gear 22, and torque may also be input from the second sun gear 21 to the second planetary gear mechanism 2, whereby, when torque is transmitted in the second planetary gear mechanism 2, input by the second sun gear 21 and the second ring gear 22, and output by the second sun gear 21 or the second carrier 23 to the intermediate shaft 5, when the transmission 100 is engaged in each gear, torque is the same in the transmission path from the first planetary gear mechanism 1 to the second planetary gear mechanism 2, and the transmission path of torque when each gear is described below is not described in detail.
When the transmission 100 is in first gear, the first synchronizer 7 connects the third sun gear 31 with the second carrier 23, and the second synchronizer 8 fixes the third ring gear 32 with the casing 10 of the transmission 100.
In this way, in the first gear of the transmission 100, torque is transmitted from the second carrier 23 to the third sun gear 31 via the intermediate shaft 5 in the second planetary gear mechanism 2, and torque is input from the third sun gear 31, transmitted to the output gear 6 by the third carrier 33 in the third planetary gear mechanism 3, and finally transmitted out of the transmission 100.
Accordingly, in the first gear of the transmission 100, the torque is input from the second sun gear 21 and the second ring gear 22 in the second planetary gear mechanism 2, is output from the second carrier 23 to the third sun gear 31, the torque is input from the third sun gear 31 and is output from the third carrier 33 to the output gear 6, the torque is input from the third planetary gear mechanism 3, is output from the third carrier 23 to the third sun gear 31, is reduced in speed again through the same rotational direction of the third planetary gear mechanism 3 with respect to the input shaft 4, and is transmitted out of the transmission 100 through the reduction of the first planetary gear mechanism 1, the second planetary gear mechanism 2, and the third planetary gear mechanism 3 after the torque is transmitted from the input shaft 4 to the transmission 100 in the first gear, and the torque transmission directions of the input shaft 4 and the output gear 6 are not changed.
When the transmission 100 is in second gear, the first synchronizer 7 connects the third sun gear 31 with the second carrier 23, and the second synchronizer 8 connects the third ring gear 32 with the third sun gear 31.
In this way, when the transmission 100 is in the second gear, torque is transmitted from the second carrier 23 to the third sun gear 31 via the intermediate shaft 5 in the second planetary gear mechanism 2, and torque is input from the third sun gear 31 and the third ring gear 32 in the third planetary gear mechanism 3, output to the output gear 6 by the third carrier 33, and finally transmitted out of the transmission 100.
Thus, in the second gear of the transmission 100, the torque is input from the second sun gear 21 and the second ring gear 22 in the second planetary gear mechanism 2, is output from the second carrier 23 to the third sun gear 31, the torque is input from the third sun gear 31 and is output from the third carrier 33 to the output gear 6, the torque passes through the third planetary gear mechanism 3, is output from the input shaft 4 to the output gear 31, is in the same rotational direction as the input shaft 4, and is reduced in speed again, in the second gear, the torque is transmitted from the input shaft 4 to the transmission 100, is transmitted out of the transmission 100 through the reduction of the speed of the first planetary gear mechanism 1, the second planetary gear mechanism 2, and the third planetary gear mechanism 3, and the torque transmission directions of the input shaft 4 and the output gear 6 are not changed, in the first gear, the input end of the third planetary gear mechanism 3 is the third sun gear 31, in the second gear, the input of the third planetary gear mechanism 3 is the third sun gear 31 and the third ring gear 32, so that the rotational speed output from the transmission 100 in the second gear is higher than that in the first gear when the rotational speed of the input shaft 4 is constant, and the speed ratio u1 in the first gear is larger than the speed ratio u2 in the second gear.
When the transmission 100 is in the third gear, the first synchronizer 7 connects the second sun gear 21 with the third sun gear 31, and the second synchronizer 8 fixes the third ring gear 32 with the case 10 of the transmission 100.
In this way, when the transmission 100 is in the third gear, torque is transmitted from the second sun gear 21 to the third sun gear 31 via the intermediate shaft 5 in the second planetary gear mechanism 2, and torque is input from the third sun gear 31, output to the output gear 6 by the third carrier 33 in the third planetary gear mechanism 3, and finally transmitted out of the transmission 100.
Thus, in the third gear of the transmission 100, the torque is input from the second sun gear 21 to the third sun gear 31 in the second planetary gear mechanism 2 and is output from the second sun gear 21 to the third sun gear 31, while the torque is not changed in the rotational direction of the input shaft 4, in the third planetary gear mechanism 3, the torque is input from the third sun gear 31 and is output from the third carrier 33 to the output gear 6, the torque is transmitted to the transmission 100 through the third planetary gear mechanism 3 in the same rotational direction as the input shaft 4 and is reduced in speed, in the third gear, the torque is transmitted from the input shaft 4 to the transmission 100, and is then transmitted to the transmission 100 through the reduction in speed of the first planetary gear mechanism 1, the second planetary gear mechanism 2 and the third planetary gear mechanism 3, while the torque transmission directions of the input shaft 4 and the output gear 6 are not changed, in the third gear, the torque is reduced in the transmission 100 only through the third planetary gear mechanism 3, in the second gear, the torque is reduced by the first planetary gear mechanism 1, the second planetary gear mechanism 2 and the third planetary gear mechanism 3, 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 third sun gear 31, and the second synchronizer 8 connects the third ring gear 32 with the third sun gear 31.
In this way, when the transmission 100 is in the third gear, torque is transmitted from the second sun gear 21 to the third sun gear 31 via the intermediate shaft 5 in the second planetary gear mechanism 2, and torque is input from the third sun gear 31 and the third ring gear 32 in the third planetary gear mechanism 3, is output to the output gear 6 by the third carrier 33, and is finally transmitted out of the transmission 100.
Thus, in the third gear of the transmission 100, torque is input from the second sun gear 21 to the second sun gear 21 in the second planetary gear mechanism 2 and is output from the second sun gear 21 to the third sun gear 31, while the torque is not changed in the rotational direction of the input shaft 4, in the third planetary gear mechanism 3, torque is input from the third sun gear 31 and is output from the third carrier 33 to the output gear 6 in the third planetary gear mechanism 3, torque is transmitted to the transmission 100 through the third planetary gear mechanism 3 in the same rotational direction as the input shaft 4 and is decelerated again, in the second gear, torque is transmitted from the input shaft 4 to the transmission 100, and is transmitted out of the transmission 100 through the deceleration of the first planetary gear mechanism 1, the second planetary gear mechanism 2 and the third planetary gear mechanism 3, while the torque transmission directions of the input shaft 4 and the output gear 6 are not changed, in the third gear, the input end of the third planetary gear mechanism 3 is the third sun gear 31, in the fourth gear, the input end of the third planetary gear mechanism 3 is the third sun gear 31 and the third ring gear 32, so that when the rotation speed of the input shaft 4 is constant relative to the third gear, the rotation speed output by the transmission 100 in the fourth gear is greater, and 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 three-planetary-row dual 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 some embodiments, the driving motor is disposed on a side of the first planetary gear mechanism 1 facing away from the second planetary gear mechanism 2, so that various components of the power driving system can be disposed along an axis of the input shaft 4, thereby facilitating the arrangement of the power driving system and 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 (11)
1. A transmission, comprising: a first planetary gear mechanism comprising a first sun gear, a first planet wheel, a first planet carrier and a first ring gear, a second planetary gear mechanism comprising a second sun gear, a second planet wheel, a second planet carrier and a second ring gear, a third planetary gear mechanism comprising a third sun gear, a third planet wheel, a third planet carrier and a third ring gear, characterized in that the first ring gear is fixedly connected with the housing of the transmission; the second gear ring is fixedly connected with the first planet carrier; the third planet carrier is fixedly connected with the output end of the transmission;
the transmission further includes:
an input shaft connected to the first sun gear and the second sun gear;
an intermediate shaft connected to the third sun gear;
a first synchronizer connecting the third sun gear with the second planet carrier or the third sun gear with the second sun gear;
a second synchronizer that fixes the third ring gear with the case of the transmission or connects the third ring gear with the third sun gear.
2. The transmission of claim 1, wherein an axis of the input shaft and an axis of the intermediate shaft are collinear, and the first planetary gear mechanism, the second planetary gear mechanism, and the third planetary gear mechanism are arranged in axial sequence.
3. The transmission of claim 2, wherein the first synchronizer is disposed between the second planetary gear mechanism and the third planetary gear mechanism, the third planetary gear mechanism being disposed between the second synchronizer and the first synchronizer.
4. The transmission of claim 2, further comprising: the first planetary gear mechanism, the second planetary gear mechanism, the output gear and the third planetary gear mechanism are sequentially arranged along the axial direction, and the output gear is sleeved outside the intermediate shaft in an empty mode.
5. The transmission of any of claims 1-4, wherein the transmission is engaged in first gear, the first synchronizer connects the third sun gear with the second carrier, and the second synchronizer fixes the third ring gear with a housing of the transmission.
6. The transmission of any one of claims 1-4, wherein the transmission is in second gear, the first synchronizer connects the third sun gear with the second carrier, and the second synchronizer connects the third ring gear with the third sun gear.
7. The transmission of any of claims 1-4, wherein the transmission is in third gear, the first synchronizer connects the second sun gear with the third sun gear, and the second synchronizer fixes the third ring gear with the housing of the transmission.
8. The transmission of any one of claims 1-4, wherein the transmission is in fourth gear, the first synchronizer connects the second sun gear with the third sun gear, and the second synchronizer connects the third ring gear with the third sun gear.
9. A powertrain system, comprising:
a drive motor;
the transmission of any one of claims 1-8, said drive motor being in power-coupled connection with said input shaft.
10. The powertrain system according to claim 9, wherein the drive motor is disposed on a side of the first planetary gear mechanism facing away from the second planetary gear mechanism.
11. A vehicle, characterized by comprising: a drivetrain as claimed in claim 9 or claim 10.
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| CN201810714103.2A CN110657208B (en) | 2018-06-29 | 2018-06-29 | Transmission, power driving system and vehicle |
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| CN201810714103.2A CN110657208B (en) | 2018-06-29 | 2018-06-29 | Transmission, power driving system and vehicle |
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| CN110657208A CN110657208A (en) | 2020-01-07 |
| CN110657208B true CN110657208B (en) | 2021-10-22 |
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| CN115465084B (en) * | 2022-09-26 | 2023-08-15 | 浙江吉利控股集团有限公司 | Multi-speed transmission, power drive system and vehicle |
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| CN110657208A (en) | 2020-01-07 |
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