CN209164506U - Speed changer, power drive system and vehicle - Google Patents
Speed changer, power drive system and vehicle Download PDFInfo
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- CN209164506U CN209164506U CN201821049005.3U CN201821049005U CN209164506U CN 209164506 U CN209164506 U CN 209164506U CN 201821049005 U CN201821049005 U CN 201821049005U CN 209164506 U CN209164506 U CN 209164506U
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Abstract
The utility model discloses a kind of speed changer, power drive system and vehicles, speed changer includes: planetary gear mechanism, input shaft, output shaft and synchronizer, the planetary gear mechanism includes first element, second element and third element, the input shaft is connected with the first element, the output shaft is connected with the third element, and the second element is fixed with the shell of the speed changer or connect the second element with the first element by the synchronizer；Wherein, the first element is sun gear, and one in the second element and third element is planet carrier, another is gear ring.According to the speed changer of the utility model embodiment, by setting double pinions mechanism and synchronizer structure, may be implemented it is quick, smooth, reliably shift gears, and the structure of speed changer is simple, convenient for safeguarding.
Description
Technical Field
The utility model belongs to the technical field of the vehicle manufacturing, particularly, relate to a derailleur, power transmission system and 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.
SUMMERY OF THE UTILITY MODEL
The utility model discloses aim at solving one of the technical problem that exists among the prior art at least. Therefore, an object of the utility model is to provide an efficient and simple structure shifts steady derailleur.
The utility model discloses still provide a power transmission system who has above-mentioned derailleur.
The utility model discloses still provide a vehicle that has above-mentioned power transmission system.
According to the utility model discloses a derailleur includes: a planetary gear mechanism that is a dual stage planetary gear mechanism that includes a first element, a second element, and a third element; an input shaft connected to the first element; an output shaft connected to the third element; a synchronizer that fixes the second element with a case of the transmission or connects the second element with the first element; the first element is a sun gear, the second element is a planet carrier, and the third element is a gear ring.
According to the utility model discloses derailleur is through setting up the synchronous ware, and its mode of shifting makes the motor control synchronous ware shift, and simple structure, shift fast, bearing capacity is strong, efficient, do not have the drag torque problem of multiplate clutch and multiplate stopper. Meanwhile, the cost is lower, the maintenance is simpler and more convenient, the synchronizer 4 is adopted for shifting, and the structure of the transmission is simplified without a clutch.
In some embodiments, the dual stage planetary gear mechanism comprises: sun gear, first planet wheel, second planet wheel, ring gear and planet carrier, the sun gear with first planet wheel meshing, first planet wheel with second planet wheel meshing, the second planet wheel with the ring gear meshing, first planet wheel the second planet wheel all rotationally install in the planet carrier.
In some embodiments, the synchronizer comprises: a stationary hub connected to the second element; a first engaging portion connected to a housing of the transmission; a second engagement portion connected to the first element; an engagement sleeve for connecting the stationary hub with the first engagement portion or connecting the stationary hub with the second engagement portion.
In some embodiments, the axis of the input shaft is collinear with the axis of the output shaft.
According to the utility model discloses a power transmission system, include: driving motor and according to the utility model discloses a derailleur, driving motor with input shaft power coupling connects.
Power transmission system is through setting up the utility model thereby the derailleur have corresponding advantage, no longer describe here.
In some embodiments, the drive motor is arranged coaxially with the input shaft.
According to the utility model discloses a vehicle includes the utility model discloses a power transmission system.
Vehicle is through setting up the utility model power transmission system to the advantage that has for prior art is the same, no longer gives unnecessary details here.
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 element 11; a second element 12; a third element 13; the first planetary gear 141; the second planet wheel 142;
an input shaft 2; an output shaft 3; a synchronizer 4; a fixed hub 41; a first engaging portion 42, a second engaging portion 43, an engaging sleeve 44;
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 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 drawings are exemplary only for the purpose of explaining the present invention, and should not 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 planetary gear mechanism, an input shaft 2, an output shaft 3, and a synchronizer 4.
The torque of the vehicle can be input to the transmission 100 through the input shaft 2, and the torque can be finally output from the output shaft 3 through the planetary gear mechanism in the transmission 100. The synchronizer 4 is used to connect various components within the transmission 100 to achieve gear shifting.
The planetary gear mechanism is a double-stage planetary gear mechanism, the double-stage planetary gear mechanism can obtain a speed ratio of about 2, compared with the planetary gear mechanism with two single planet wheels, the double-stage planetary gear mechanism has the advantages that the number of parts is reduced, the size and the weight of the transmission 100 are further reduced, the cost is reduced, the input and output directions of each gear are consistent due to the double stages, and reverse gear cannot be generated.
The double-stage planetary gear mechanism includes: sun gear, first planet wheel, second planet wheel, ring gear and planet carrier, sun gear and the meshing of first planet wheel, first planet wheel and the meshing of second planet wheel, second planet wheel and the meshing of ring gear, first planet wheel, second planet wheel all rotationally install in the planet carrier.
The planetary gear mechanism comprises a first element 11, a second element 12 and a third element 13, the first element 11 being a sun gear, the second element 12 being a planet carrier and the third element 13 being a ring gear. The planetary gear mechanism further comprises a first planetary gear and a second planetary gear which are meshed with each other in the radial direction, the first planetary gear and the second planetary gear are connected with the planetary carrier, the first planetary gear is meshed with the sun gear, and the second planetary gear is meshed with the gear ring.
When the sun gear of the planetary gear mechanism rotates, the sun gear can drive the planet gear to rotate, and the planet carrier connected with 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 input shaft 2 is connected to the first element 11, i.e. the input shaft 2 is connected to the sun gear, and torque can be input from the sun gear to the planetary gear mechanism via the input shaft 2, and the output shaft 3 is connected to the third element 13, so that in the planetary gear mechanism, torque is input from the sun gear to the planetary gear mechanism and is output from the ring gear, thereby completing the transmission of torque in the transmission 100.
In some embodiments, the synchronizer 4 includes: a stationary hub 41, a first engaging portion 42, a second engaging portion 43, and an engaging sleeve 44, the stationary hub 41 being connected to the second element 12, the first engaging portion 42 being connected to the case 10 of the transmission 10, the second engaging portion 43 being connected to the first element 11, the engaging sleeve 44 being used to connect the stationary hub 41 to the first engaging portion 42 or to connect the stationary hub 41 to the second engaging portion 43. When the synchronizer 4 fixes the second element 12 with the housing 10 of the transmission 100, torque can be transmitted from the input shaft 2 to the planetary gear mechanism via the first element 11, and torque is transmitted from the third element 13 to the output shaft 3; when the synchronizer 4 connects the second element 12 with the first element 11, torque can be transmitted from the input shaft 2 to the planetary gear mechanism through the first element 11 and the second element 12, and torque is transmitted from the third element 13 to the output shaft 3, the synchronizer 4 can be arranged to enable the transmission to be switched between two speed ratios, and when the planet carrier and the sun gear are selected to be combined, namely the speed ratio is 1, the planetary gear mechanism rotates integrally, gears are not meshed in the planetary gear mechanism, the efficiency is improved, and noise of the transmission 100 can be reduced.
According to the utility model discloses derailleur 100 is through setting up synchronous ware 4, and its mode of shifting makes motor control synchronous ware 4 shift, and simple structure, shift fast, bearing capacity are strong, efficient, do not have the drag torque problem of multiplate clutch and multiplate brake. Meanwhile, the cost is lower, the maintenance is simpler and more convenient, the synchronizer 4 is adopted for shifting, and the structure of the transmission 100 is simplified without a clutch.
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 second member 12 may be a planetary carrier, and the third member 13 may be a ring gear, such that the ring gear is connected to the output shaft 3, the planetary carrier is selectively connected to the housing 10 or the sun gear of the transmission 100 through the synchronizer 4, and the output end of the planetary gear mechanism is the ring gear, so that the transmission 100 can have higher motion stability and shifting comfort.
In some embodiments, as shown in FIG. 1, the planetary gear mechanism is a double-pinion planetary gear mechanism, i.e., a planetary gear mechanism having double-pinion planets, with the sun gear going 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 less, and the rotation directions of the sun gear and the ring gear are the same when the planet carrier is fixed.
When the planetary gear is a double-stage planetary gear mechanism, the second element 12 may be a planet carrier, so that the ring gear may be used as the output end 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 may be in the same direction, so that the rotation direction of the input shaft 2 is the same as the rotation direction of the output shaft 3, and the complexity of the operation of the transmission 100 is solved.
In some embodiments, the transmission 100 according to embodiments of the present invention may have 2 gears, i.e. a first gear and a second gear, wherein the speed ratio u1 of the first gear > the speed ratio u2 of the second gear.
The operation state of the synchronizer 4 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 2 to the output shaft 3 in the transmission 100 when the planetary gear mechanism in the transmission 100 is a double-pinion planetary gear mechanism, the first element 11 is a sun gear, the second element 12 is a carrier, and the third element 13 is a ring gear will be described below with reference to fig. 1.
When the transmission 100 is in first gear, the synchronizer 4 fixes the second element 12 (i.e., the carrier) to the housing 10 of the transmission 100, so that torque is transmitted from the input shaft 2 to the transmission 100, the input shaft 2 transmits torque to the sun gear, torque is input from the sun gear in the planetary gear mechanism and is output from the ring gear, and the ring gear transmits torque to the output shaft 3.
When the transmission 100 is in second gear, the synchronizer 4 connects the second element 12 (i.e., carrier) with the first element 11 (i.e., sun gear) so that torque is transmitted from the input shaft 2 into the transmission 100, the input shaft 2 transmits torque to the sun gear and carrier, torque is input from the sun gear and carrier in the planetary gear mechanism and output from the ring gear, and the ring gear transmits torque to the output shaft 3.
Thus, in the first gear, the input of the planetary gear mechanism is the sun gear, and in the second gear, the input of the planetary gear mechanism is the sun gear and the carrier, so that the output rotation speed of the ring gear is greater in the second gear than in the first gear when the rotation speed of the input shaft 2 is constant, so that the speed ratio u1 of the first gear is greater than the speed ratio u2 of the second gear.
When the planetary gear mechanism in the transmission 100 is a single-stage planetary gear mechanism, the first element 11 is a sun gear, the second element 12 is a ring gear, and the third element 13 is a carrier, the operating state of the synchronizer 4 of each gear of the transmission 100, and the torque transmission path in which torque is transmitted from the input shaft 2 to the output shaft 3 in the transmission 100.
When the transmission 100 is in first gear, the synchronizer 4 fixes the second element 12 (i.e., the ring gear) to the housing 10 of the transmission 100, so that torque is transmitted from the input shaft 2 to the transmission 100, the input shaft 2 transmits torque to the sun gear, the torque is input from the sun gear in the planetary gear mechanism and is output from the carrier, and the carrier transmits torque to the output shaft 3.
When the transmission 100 is in second gear, the synchronizer 4 connects the second element 12 (i.e., the ring gear) with the first element 11 (i.e., the sun gear), so that torque is transmitted from the input shaft 2 into the transmission 100, the input shaft 2 transmits torque to the sun gear and the ring gear, torque is input from the sun gear and the ring gear in the planetary gear mechanism and is output from the carrier, and the carrier transmits torque to the output shaft 3.
Thus, in the first gear, the input of the planetary gear mechanism is the sun gear, and in the second gear, the input of the planetary gear mechanism is the sun gear and the ring gear, so that the output rotation speed of the carrier is greater in the second gear at a constant rotation speed of the input shaft 2 with respect to the first gear, so that the speed ratio u1 of the first gear is greater than the speed ratio u2 of the second gear.
To sum up, the utility model discloses a derailleur 100 belongs to a horizontal formula derailleur 100, adopts 4 structures of doublestage planet wheel single synchronizer, and its mode of shifting can be that motor control synchronizer 4 shifts, has simple structure, shifts fast, advantage that the moment of torsion transmission is efficient, and does not have the drag torque problem of multiplate clutch and multiplate brake. At the same time, transmission 100 is less expensive to manufacture and easier to maintain.
The synchronizer 4 is adopted for gear shifting, a clutch is not needed, the structure is simplified, and the transmission 100 adopts a two-gear speed change structure, so that the electric energy can be saved when the motor operates in a high-efficiency area.
In some embodiments, as shown in fig. 1, the axis of the input shaft 2 is collinear with the axis of the output shaft 3, so that the arrangement of the input shaft 2 and the output shaft 3 can be facilitated and the transmission direction of the torque from the input shaft 2 to the output shaft 3 is unchanged.
According to the utility model discloses power transmission system 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 2. Thus, according to the utility model discloses power transmission system is through setting up according to the utility model discloses thereby derailleur 100 of embodiment has the advantage that the shift is fast, torque transmission efficiency is high, the shift is smooth-going, and power transmission system's simple structure.
In some embodiments, the driving motor is disposed coaxially with the input shaft 2, so that various components of the power transmission system can be disposed along the axis of the input shaft 2, thereby facilitating the disposition of the power transmission system, and the route of torque transmission does not need to be changed by redundant gears, etc., thereby improving the torque transmission efficiency of the power transmission system.
According to the utility model discloses vehicle, include: the power transmission system of above-mentioned embodiment, the vehicle is through setting up above-mentioned power transmission system to make the vehicle have shift steady, shift the advantage that the transmission of torque is efficient rapidly and, and can make the output torque scope of vehicle big, the load is stable, can deal with complicated road conditions, has the advantage of the energy can be saved, in some examples, according to the utility model discloses a vehicle can be electric vehicle or hybrid vehicle etc..
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 shaft 3, 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 driving of the vehicle.
In the description of the present invention, it is to be understood that the terms "center", "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, indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for convenience of description and simplicity of description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore, should not be construed as limiting the present 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 present 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 present 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 planetary gear mechanism that is a dual stage planetary gear mechanism that includes a first element, a second element, and a third element;
an input shaft connected to the first element;
an output shaft connected to the third element;
a synchronizer that fixes the second element with a case of the transmission or connects the second element with the first element; wherein,
the first element is a sun gear, the second element is a planet carrier, and the third element is a gear ring.
2. The transmission of claim 1, wherein the dual-stage planetary gear mechanism comprises: sun gear, first planet wheel, second planet wheel, ring gear and planet carrier, the sun gear with first planet wheel meshing, first planet wheel with second planet wheel meshing, the second planet wheel with the ring gear meshing, first planet wheel the second planet wheel all rotationally install in the planet carrier.
3. The transmission of claim 1, wherein the synchronizer comprises:
a stationary hub connected to the second element;
a first engaging portion connected to a housing of the transmission;
a second engagement portion connected to the first element;
an engagement sleeve for connecting the stationary hub with the first engagement portion or connecting the stationary hub with the second engagement portion.
4. A transmission as claimed in any one of claims 1 to 3, characterised in that the axis of the input shaft is collinear with the axis of the output shaft.
5. A powertrain system, comprising:
a drive motor;
the transmission of any one of claims 1-3, said drive motor being in power-coupled connection with said input shaft.
6. The powertrain system of claim 5, wherein the drive motor is disposed coaxially with the input shaft.
7. A vehicle, characterized by comprising: the drivetrain of claim 5.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821049005.3U CN209164506U (en) | 2018-06-29 | 2018-06-29 | Speed changer, power drive system and vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821049005.3U CN209164506U (en) | 2018-06-29 | 2018-06-29 | Speed changer, power drive system and vehicle |
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| Publication Number | Publication Date |
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| CN209164506U true CN209164506U (en) | 2019-07-26 |
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| CN201821049005.3U Active CN209164506U (en) | 2018-06-29 | 2018-06-29 | Speed changer, power drive system and vehicle |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110784065A (en) * | 2019-09-26 | 2020-02-11 | 曾浩文 | Electric drive device |
| CN112128321A (en) * | 2020-09-04 | 2020-12-25 | 绿传(北京)汽车科技股份有限公司 | Planetary row type two-gear electric drive transmission device and operation method thereof |
| CN114017475A (en) * | 2021-11-10 | 2022-02-08 | 一汽解放汽车有限公司 | Speed change device, transmission and vehicle |
| CN115234641A (en) * | 2022-08-10 | 2022-10-25 | 一汽解放汽车有限公司 | Speed reducer assembly and drive axle assembly |
| CN115257334A (en) * | 2022-08-01 | 2022-11-01 | 一汽解放汽车有限公司 | Double-motor multi-gear parallel shaft drive axle and automobile |
-
2018
- 2018-06-29 CN CN201821049005.3U patent/CN209164506U/en active Active
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110784065A (en) * | 2019-09-26 | 2020-02-11 | 曾浩文 | Electric drive device |
| CN112128321A (en) * | 2020-09-04 | 2020-12-25 | 绿传(北京)汽车科技股份有限公司 | Planetary row type two-gear electric drive transmission device and operation method thereof |
| CN114017475A (en) * | 2021-11-10 | 2022-02-08 | 一汽解放汽车有限公司 | Speed change device, transmission and vehicle |
| CN114017475B (en) * | 2021-11-10 | 2023-11-21 | 一汽解放汽车有限公司 | Speed change device, speed changer and vehicle |
| CN115257334A (en) * | 2022-08-01 | 2022-11-01 | 一汽解放汽车有限公司 | Double-motor multi-gear parallel shaft drive axle and automobile |
| CN115234641A (en) * | 2022-08-10 | 2022-10-25 | 一汽解放汽车有限公司 | Speed reducer assembly and drive axle assembly |
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