CN111750047A - Multi-gear planetary row type automatic transmission, control method thereof and vehicle - Google Patents
Multi-gear planetary row type automatic transmission, control method thereof and vehicle Download PDFInfo
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- CN111750047A CN111750047A CN201910252402.3A CN201910252402A CN111750047A CN 111750047 A CN111750047 A CN 111750047A CN 201910252402 A CN201910252402 A CN 201910252402A CN 111750047 A CN111750047 A CN 111750047A
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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
- F16H3/64—Gearings having three or more central gears composed of a number of gear trains, the drive always passing through all the trains, each train having not more than one connection for driving another train
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four 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
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
Abstract
The invention relates to a multi-gear planet row type automatic transmission, a control method thereof and a vehicle, wherein the automatic transmission comprises a first planet row, a second planet row, a third planet row, a fourth planet row, a plurality of clutch mechanisms and brake mechanisms, wherein the first planet row, the second planet row, the third planet row and the fourth planet row are respectively provided with a sun gear, a planet carrier and a gear ring, the planet carrier of the first planet row is provided with the first brake mechanism, or the input end of the automatic transmission is also in transmission connection with a motor. The multi-gear planetary row type automatic transmission has high transmission efficiency and good driving smoothness.
Description
Technical Field
The invention relates to the technical field of transmissions, in particular to a multi-gear planetary row type automatic transmission, and meanwhile, the invention also relates to a control method of the multi-gear planetary row type automatic transmission.
Background
With the rapid development of the automobile industry and the increasing shortage of energy sources, the requirements of people on driving smoothness and engine fuel economy are higher and higher, so that the multi-gear transmission is more and more popular with consumers. In the prior art, in order to realize the switching among a plurality of gears, more gears and control elements are generally required to be added into the transmission, so that the control system of the transmission is more complex and the efficiency is lower. In addition, the existing multi-gear transmission is difficult to structurally modify, so that structural platformization is not facilitated, and the development cost of a new vehicle type is increased. In addition, because of structural design is unreasonable, current many gears derailleur shifts unsmooth, leads to driving to feel relatively poor.
Disclosure of Invention
In view of this, the present invention is directed to a multi-gear planetary-row type automatic transmission, which has high transmission efficiency and can reduce the oil consumption of the entire vehicle.
In order to achieve the purpose, the technical scheme of the invention is realized as follows:
a multi-gear planet row type automatic transmission at least comprises a first planet row, a second planet row, a third planet row and a fourth planet row, wherein the first planet row, the second planet row, the third planet row and the fourth planet row respectively comprise a sun gear, a planet carrier and a gear ring;
the sun gear of the first planet row is in transmission connection with the sun gear of the fourth planet row and is in transmission connection with the input end of the automatic transmission, the gear ring of the first planet row is in transmission connection with the sun gear of the second planet row, the planet carrier of the third planet row and the gear ring of the fourth planet row are in transmission connection, and the gear ring of the third planet row is in transmission connection with the output end of the automatic transmission;
the automatic transmission also comprises a first clutch mechanism which is in transmission connection between the planet carrier of the first planet row and the gear ring of the second planet row, a second clutch mechanism which is in transmission connection between the sun gear of the first planet row and the sun gear of the fourth planet row as well as the gear ring of the second planet row, a third clutch mechanism which is in transmission connection between the planet carrier of the fourth planet row and the gear ring of the third planet row as well as the output end of the automatic transmission, a second brake mechanism which is arranged at the gear ring of the first planet row, and a third brake mechanism which is arranged at the sun gear of the third planet row;
the input end of the automatic transmission is in transmission connection with the power output end of the engine, a first brake mechanism is arranged at the planet carrier of the first planet row, or the input end of the automatic transmission is also in transmission connection with a motor.
Further, when the input end of the automatic transmission is in transmission connection with a motor, the power output end of the engine and the motor are coaxially arranged.
Compared with the prior art, the invention has the following advantages:
the multi-gear planetary row type automatic transmission has the advantages of higher transmission efficiency, better driving smoothness and capability of effectively reducing oil consumption, so that the multi-gear planetary row type automatic transmission has a better using effect.
Meanwhile, the present invention also provides a control method of a multi-gear planetary automatic transmission, which is applied to the multi-gear planetary automatic transmission as described above, and in which a first brake mechanism is provided at a carrier of the first planetary gear, and the control method includes:
a. controlling the first clutch mechanism to be engaged, controlling the second brake mechanism and the third brake mechanism to brake, and entering a first gear mode; or the like, or, alternatively,
b. controlling the first clutch mechanism and the third clutch mechanism to be engaged, controlling the first brake mechanism to brake, and entering a two-gear mode; or the like, or, alternatively,
c. controlling the first clutch mechanism and the third clutch mechanism to be engaged, controlling the second brake mechanism to brake, and entering a third gear mode; or the like, or, alternatively,
d. controlling the third clutch mechanism to be engaged, braking the third brake mechanism, and entering a fourth gear mode; or the like, or, alternatively,
e. controlling the second clutch mechanism and the third clutch mechanism to be engaged, controlling the second brake mechanism to brake, and entering a fifth gear mode; or the like, or, alternatively,
f. controlling the first clutch mechanism, the second clutch mechanism and the third clutch mechanism to be engaged to enter a sixth gear mode; or the like, or, alternatively,
g. controlling the second clutch mechanism to be engaged, controlling the second brake mechanism and the third brake mechanism to brake, and entering a seven-gear mode; or the like, or, alternatively,
h. controlling the first clutch mechanism and the second clutch mechanism to be engaged, controlling the third brake mechanism to brake, and entering an eight-gear mode; or the like, or, alternatively,
i. and controlling the first clutch mechanism to be engaged, controlling the first brake mechanism and the third brake mechanism to brake, and entering a reverse gear mode.
In addition, the present invention further provides another control method for a multi-gear planetary automatic transmission, which is applied to the multi-gear planetary automatic transmission, wherein a motor is connected to an input end of the automatic transmission in a transmission manner, and the control method comprises:
a. controlling the first clutch mechanism to be engaged, controlling the second brake mechanism and the third brake mechanism to brake, and entering a first gear mode; or the like, or, alternatively,
b. controlling the first clutch mechanism and the third clutch mechanism to be jointed, controlling the second brake mechanism to brake, and entering a second gear mode; or the like, or, alternatively,
c. controlling the third clutch mechanism to be engaged, braking the third brake mechanism and entering a third gear mode; or the like, or, alternatively,
d. controlling the second clutch mechanism and the third clutch mechanism to be engaged, controlling the second brake mechanism to brake, and entering a fourth-gear mode; or the like, or, alternatively,
e. controlling the first clutch mechanism, the second clutch mechanism and the third clutch mechanism to be engaged to enter a fifth gear mode; or the like, or, alternatively,
f. controlling the second clutch mechanism to be engaged, controlling the second brake mechanism and the third brake mechanism to brake, and entering a six-gear mode; or the like, or, alternatively,
g. controlling the first clutch mechanism and the second clutch mechanism to be engaged, controlling the third brake mechanism to brake, and entering a seven-gear mode; or the like, or, alternatively,
h. and controlling the motor to rotate reversely to enter a reverse gear mode.
In addition, another objective of the present invention is to provide a vehicle, wherein the vehicle is provided with the multi-gear planetary automatic transmission, and when an input end of the automatic transmission is in transmission connection with a motor, the vehicle is further provided with a power battery unit electrically connected with the motor.
Compared with the prior art, the vehicle and the multi-gear planetary automatic transmission have the same beneficial effects, and the details are not repeated.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate an embodiment of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:
fig. 1 is a schematic view of a multi-speed planetary automatic transmission according to a first embodiment of the present invention;
fig. 2 is a control logic diagram of a multi-speed planetary automatic transmission according to a first embodiment of the present invention;
fig. 3 is a schematic view of a multi-speed planetary automatic transmission according to a second embodiment of the invention;
fig. 4 is a control logic diagram of a multi-speed planetary automatic transmission according to a second embodiment of the present invention;
description of reference numerals:
s1-first sun gear, PC 1-first planet carrier, R1-first ring gear;
s2-second sun gear, PC 2-second planet carrier, R2-second ring gear;
s3-third sun gear, PC 3-third planet carrier, R3-third ring gear;
s4-fourth sun gear, PC 4-fourth planet carrier, R4-fourth ring gear;
b1-first brake, B2-second brake, B3-third brake;
c1-first clutch, C2-second clutch, C3-third clutch.
Detailed Description
It should be noted that the embodiments and features of the embodiments may be combined with each other without conflict.
The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings.
Example one
The present embodiment relates to a multiple-speed planetary automatic transmission, which includes, as shown in fig. 1, a first planetary row, a second planetary row, a third planetary row, and a fourth planetary row, each having a sun gear, a carrier, and a ring gear, and arranged in this order in a power transmission direction of the automatic transmission. The sun gear of the first planet row is in transmission connection with the sun gear of the fourth planet row and is in transmission connection with the input end of the automatic transmission, namely the input shaft of the automatic transmission, and the gear ring of the first planet row is in transmission connection with the sun gear of the second planet row. In addition, the planet carrier of the second planet row, the planet carrier of the third planet row and the gear ring of the fourth planet row are in transmission connection, and the gear ring of the third planet row is in transmission connection with the output end of the automatic transmission, namely the output shaft of the automatic transmission. It should be noted that the specific structures of the sun gears, the ring gears and the planet carriers mentioned above can be referred to the prior art, and will not be described in detail herein. In addition, the number of the planet wheels on the planet carrier can also be three, four or other numbers according to specific conditions.
Still referring to fig. 1, in order to control the switching between the gears, the multi-gear planetary automatic transmission of the present embodiment further includes a first clutch mechanism drivingly connected between the carrier of the first planetary row and the ring gear of the second planetary row, a second clutch mechanism drivingly connected between the sun gear of the first planetary row and the sun gear of the fourth planetary row and the ring gear of the second planetary row, a third clutch mechanism drivingly connected between the carrier of the fourth planetary row and the ring gear of the third planetary row and the output end of the automatic transmission, a second brake mechanism provided at the ring gear of the first planetary row, and a third brake mechanism provided at the sun gear of the third planetary row.
The input end of the automatic transmission is in transmission connection with the power output end of the engine, namely, the input shaft of the automatic transmission is in transmission connection with the output shaft of the engine; and a first brake mechanism is arranged at the planet carrier of the first planet row. In addition, in order to improve the use effect, the first clutch C1, the second clutch C2 and the third clutch C3 are respectively adopted as the first clutch, the second clutch and the third clutch in the present embodiment, and the specific structure of each clutch can refer to the prior art. In addition, the first brake mechanism, the second brake mechanism and the third brake mechanism of the present embodiment respectively employ the first brake B1, the second brake B2 and the third brake B3, and the specific structure of each brake can refer to the prior art.
The control method of the multi-speed planetary automatic transmission of the present embodiment will be described in detail below with reference to fig. 1 and 2, and for convenience of description hereinafter, the sun gear, the ring gear, and the carrier of the first planetary row will be referred to as "first sun gear S1", "first ring gear R1", and "first carrier PC 1", respectively; similarly, the sun gear, the ring gear, and the carrier of the second planetary row are referred to as "second sun gear S2", "second ring gear R2", and "second carrier PC 2", respectively; and the sun gear, ring gear, and carrier of the third planetary row will be referred to as "third sun gear S3", "third ring gear R3", and "third carrier PC 3", respectively; and the sun gear, the ring gear, and the carrier of the fourth planetary row are referred to as "fourth sun gear S4", "fourth ring gear R4", and "fourth carrier PC 4", respectively.
The control method of the multi-gear planetary automatic transmission when the modes of the gears are pre-entered is respectively detailed as follows:
a. when the first gear mode is pre-entered: the first clutch C1 is controlled to be engaged, and the second brake B2 and the third brake B3 are controlled to brake. At this time, the first carrier PC1 and the second ring gear R2 are integrally connected and integrally rotated, and the first ring gear R1, the second sun gear S2 and the third sun gear S3 are all fixed and the fourth planetary row does not function as a transmission. Therefore, power is input only from the first sun gear S1, transmitted to the first planetary row and the second planetary row, transmitted to the third carrier PC3 via the second carrier PC2, and output from the third ring gear R3, so that the first gear mode can be achieved.
b. When entering the second-gear mode in advance: the first clutch C1 and the third clutch C3 are controlled to be engaged, and the first brake B1 is controlled to brake. At this time, the first carrier PC1 and the second ring gear R2 are stationary, and the fourth carrier PC4 and the third ring gear R3 are connected with the output shaft of the automatic transmission. Therefore, power is simultaneously input from the first sun gear S1 and the fourth sun gear S4, transmitted to the second planet carrier PC2 and the fourth ring gear R4 and the third planet carrier PC3 via the first planetary row and the second planetary row, and finally simultaneously output from the fourth planet carrier PC4 and the third ring gear R3, whereby the second gear mode can be entered.
c. When the three-gear mode is pre-entered: the first clutch C1 and the third clutch C3 are controlled to be engaged, and the second brake B2 is controlled to brake. At this time, the first carrier PC1 and the second ring gear R2 rotate integrally, the fourth carrier PC4, the third ring gear R3 and the output shaft of the automatic transmission are connected, and the first ring gear R1 and the second sun gear S2 are fixed. Therefore, power is input from the first sun gear S1 and the fourth sun gear S4, transmitted to the first planetary row and the second planetary row, transmitted to the fourth ring gear R4 and the third planet carrier PC3 via the second planet carrier PC2, and finally output from the fourth planet carrier PC4 and the third ring gear R3, so that the three-gear mode can be entered.
d. When the four-gear mode is pre-entered; the third clutch C3 is controlled to be engaged, and the third brake B3 is controlled to brake. At this time, the fourth planet carrier PC4, the third ring gear R3, and the output shaft of the automatic transmission rotate integrally, and the third sun gear S3 is fixed. Therefore, power is input from the fourth sun gear S4, transmitted to the third planetary row and the fourth planetary row, and finally simultaneously output from the fourth carrier PC4 and the third ring gear R3, whereby the fourth gear mode can be entered.
e. When a fifth gear mode is pre-entered; the second clutch C2 and the third clutch C3 are controlled to be engaged, and the second brake B2 is controlled to brake. At this time, the first sun gear S1, the second ring gear R2, the input shaft of the automatic transmission, and the fourth sun gear S4 rotate integrally, while the first ring gear R1 is fixed; further, the fourth planet carrier PC4, the third ring gear R3, and the output shaft of the automatic transmission rotate together. Therefore, power is input from the first sun gear S1, the second ring gear R2, and the fourth sun gear S4, transmitted to the second planet carrier PC2 through the first and second planet rows, then transmitted to the fourth ring gear R4, and finally output from the fourth planet carrier PC4, so that the fifth gear mode can be entered.
f. When entering a six-gear mode in advance: the first clutch C1, the second clutch C2, and the third clutch C3 are controlled to be engaged. At this time, the first carrier PC1, the second ring gear R2, and the input shaft of the automatic transmission rotate integrally with the fourth sun gear S4, and at the same time, the fourth carrier PC4, the third ring gear R3, and the output shaft of the automatic transmission rotate integrally. Therefore, power is input from the first carrier PC1, the second ring gear R2, and the fourth sun gear S4, and the first planetary row and the second planetary row operate together as a whole, and power is transmitted from the second carrier PC2 to the fourth ring gear R4 at the same speed as the input shaft of the automatic transmission, and finally output from the fourth carrier PC4, so that the six-speed mode can be entered.
g. When the seven-gear mode is pre-entered: the second clutch C2 is controlled to be engaged, and the second brake B2 and the third brake B3 are controlled to brake. At this time, the first sun gear S1, the second ring gear R2, and the input shaft of the automatic transmission and the fourth sun gear S4 rotate integrally, and the first ring gear R1 and the third sun gear S3 are fixed. Therefore, power is simultaneously input from the first sun gear S1, the second ring gear R2, and the fourth sun gear S4, transmitted to the first and second planetary rows, transmitted to the second and third carriers PC2 and PC3, and finally output from the third ring gear R3, so that the seven-gear mode can be entered.
h. When the eight-gear mode is pre-entered: the first clutch C1 and the second clutch C3 are controlled to be engaged, and the third brake B3 is controlled to brake. At this time, the first carrier PC1, the second ring gear R2, and the input shaft of the automatic transmission and the fourth sun gear S4 rotate integrally, and the third sun gear S3 is fixed. Therefore, power is input from the first sun gear S1 and the second ring gear R2, and at this time the first planetary row and the second planetary row operate as a whole, and power transmitted from the second planet carrier PC2 is transmitted to the third planet carrier PC3 at the same speed as the input shaft of the automatic transmission, and finally output from the third ring gear R3, whereby the eight speed mode can be entered.
i. When the reverse gear mode is pre-entered: the first clutch C1 is controlled to be engaged, and the first brake B1 and the third brake B3 are controlled to brake. At this time, the first carrier PC1 is fixed integrally with the second ring gear R2, and the third sun gear S3 is also fixed. Therefore, power is input from the first sun gear S1 and the fourth sun gear S4, transmitted to the second planet carrier PC2 and the third planet carrier via the first and second planet rows, and finally output from the third ring gear R3, whereby the reverse gear mode can be entered.
Based on the above overall description, the multi-gear planetary-row type automatic transmission described in this embodiment can realize the switching between nine gears only by three clutches and three brakes, and has higher transmission efficiency and better driving smoothness compared with the multi-gear automatic transmission in the prior art; in addition, the first clutch mechanism and the second clutch mechanism are arranged close to the second planet row, so that the first clutch mechanism and the second clutch mechanism are arranged at the front end of the automatic transmission, the loss of a lubricating oil path can be reduced, the oil consumption can be effectively reduced, and the multi-gear planet row type automatic transmission has a better using effect; in addition, the control method of the multi-gear planetary automatic transmission is simple and reliable.
Example two
The present embodiment relates to a multi-speed planetary automatic transmission, and as shown in fig. 3, the overall structure thereof is similar to that of the embodiment, except that a first brake mechanism is not provided at a carrier of a first planetary row, and a motor is driven at an input end of the automatic transmission.
Based on the above structure and with reference to fig. 4, a detailed description will be given of a control method of the multi-speed planetary automatic transmission when the respective speed modes are pre-entered:
a. when the first gear mode is pre-entered: the first clutch C1 is controlled to be engaged, and the second brake B2 and the third brake B3 are controlled to brake. At this time, the first carrier PC1 and the second ring gear R2 are integrally connected and integrally rotated, and the first ring gear R1, the second sun gear S2 and the third sun gear S3 are all fixed and the fourth planetary row does not function as a transmission. Therefore, power is input only from the first sun gear S1, transmitted to the first planetary row and the second planetary row, transmitted to the third carrier PC3 via the second carrier PC2, and output from the third ring gear R3, so that the first gear mode can be achieved.
b. When entering the second-gear mode in advance: the first clutch C1 and the third clutch C3 are controlled to be engaged, and the second brake B2 is controlled to brake. At this time, the first ring gear R1 and the second sun gear S2 are fixed, the first carrier PC1 and the second ring gear R2 rotate integrally, and the fourth carrier PC4 and the third ring gear R3 are connected to an output shaft of the automatic transmission. Therefore, power is simultaneously input from the first sun gear S1 and the fourth sun gear S4, transmitted to the first planetary row and the second planetary row, transmitted to the fourth ring gear R4 and the third carrier PC3 via the second carrier PC2, and finally output from the fourth carrier PC4 and the third ring gear R3, so that the second gear mode can be entered.
c. When the three-gear mode is pre-entered: the third clutch C3 is controlled to be engaged, and the third brake B3 is controlled to brake. At this time, the fourth planet carrier PC4, the third ring gear R3, and the output shaft of the automatic transmission rotate integrally, and the third sun gear S3 is fixed. Therefore, power is input from the fourth sun gear S4, transmitted to the third planetary row and the fourth planetary row, and finally simultaneously output from the fourth carrier PC4 and the third ring gear R3, whereby the three-speed mode can be entered.
d. When the four-gear mode is pre-entered: the second clutch C2 and the third clutch C3 are controlled to be engaged, and the second brake B2 is controlled to brake. At this time, the first sun gear S1, the second ring gear R2, the input shaft of the automatic transmission, and the fourth sun gear S4 rotate integrally, while the first ring gear R1 is fixed; further, the fourth planet carrier PC4, the third ring gear R3, and the output shaft of the automatic transmission rotate together. Therefore, power is input from the first sun gear S1, the second ring gear R2, and the fourth sun gear S4, transmitted to the second planet carrier PC2 via the first and second planet rows, then transmitted to the fourth ring gear R4, and finally output from the fourth planet carrier PC4, so that the four-gear mode can be entered.
e. When the five-gear mode is pre-entered: the first clutch C1, the second clutch C2, and the third clutch C3 are controlled to be engaged. At this time, the first carrier PC1, the second ring gear R2, and the input shaft of the automatic transmission rotate integrally with the fourth sun gear S4, and the fourth carrier PC4, the third ring gear R3, and the output shaft of the automatic transmission rotate integrally with each other. Therefore, power is input from the first carrier PC1, the second ring gear R2, and the fourth sun gear S4, and the first planetary row and the second planetary row operate together as a whole, and power is transmitted from the second carrier PC2 to the fourth ring gear R4 at the same speed as the input shaft of the automatic transmission, and finally output from the fourth carrier PC4, so that the fifth gear mode can be entered.
f. When entering a six-gear mode in advance: the second clutch C2 is controlled to be engaged while the second brake B2 and the third brake B3 are controlled to brake. At this time, the first sun gear S1, the second ring gear R2, and the input shaft of the automatic transmission and the fourth sun gear S4 rotate integrally, and the first ring gear R1 and the third sun gear S3 are fixed. Therefore, power is simultaneously input from the first sun gear S1, the second ring gear R2, and the fourth sun gear S4, transmitted to the first and second planetary rows, transmitted to the second and third carriers PC2 and PC3, and finally output from the third ring gear R3, so that the sixth gear mode can be entered.
g. When the eight-gear mode is pre-entered: the first clutch C1 and the second clutch C3 are controlled to be engaged, and the third brake B3 is controlled to brake. At this time, the first carrier PC1, the second ring gear R2, and the input shaft of the automatic transmission and the fourth sun gear S4 rotate integrally, and the third sun gear S3 is fixed. Therefore, power is input from the first sun gear S1 and the second ring gear R2, and at this time the first planetary row and the second planetary row operate as a whole, and power transmitted from the second planet carrier PC2 is transmitted to the third planet carrier PC3 at the same speed as the input shaft of the automatic transmission, and finally output from the third ring gear R3, whereby the seven-speed mode can be entered.
h. When the reverse gear mode is pre-entered: the motor is controlled to rotate reversely, and corresponding clutches and brakes are respectively controlled according to the control method of each gear mode, so that the reverse gear mode can be entered. Here, taking the pre-entry reverse mode as an example, the electric motor is controlled to rotate in the forward direction, the first clutch C1 is controlled to be engaged, and the second brake B2 and the third brake B3 are controlled to brake. At this time, the first carrier PC1 and the second ring gear R2 are integrally connected and integrally rotated, and the first ring gear R1, the second sun gear S2 and the third sun gear S3 are all fixed and the fourth planetary row does not function as a transmission. Therefore, power is input only from the first sun gear S1, transmitted to the first planetary row and the second planetary row, transmitted to the third planet carrier PC3 via the second planet carrier PC2, and output from the third ring gear R3, so that the first reverse gear mode can be entered. Similarly, when the reverse gear modes of the second gear, the third gear and the like are pre-entered, the control method is similar to that of the reverse gear mode of the first gear, and the detailed description is omitted here.
Based on the above overall description, the multi-gear planetary-row type automatic transmission described in this embodiment can realize the switching among multiple gears only by three clutches and two brakes, and has higher transmission efficiency and better driving smoothness compared with the multi-gear automatic transmission in the prior art; in addition, the first clutch C1 and the second clutch C2 are arranged at the front end of the automatic transmission close to the second planet row, so that the loss of a lubricating oil path can be reduced, the oil consumption can be effectively reduced, and the multi-gear planet row type automatic transmission has a better using effect; in addition, the control method of the multi-gear planetary automatic transmission is simple and reliable.
EXAMPLE III
The present embodiment relates to a vehicle, in which a multi-gear planetary-row automatic transmission as described in the first embodiment or the second embodiment is installed, and when an input end of the automatic transmission is in transmission connection with a motor, the vehicle further includes a power battery unit electrically connected to the motor.
The vehicle of the embodiment adopts the multi-gear planetary row type automatic transmission as described in the first embodiment or the second embodiment, so that the vehicle has a good gear shifting effect and driving smoothness, and meanwhile, the oil consumption is low, and the vehicle has a good using effect.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.
Claims (5)
1. The utility model provides a many gears planet row formula automatic gearbox which characterized in that: the planetary gear set at least comprises a first planetary row, a second planetary row, a third planetary row and a fourth planetary row, wherein the first planetary row, the second planetary row, the third planetary row and the fourth planetary row respectively comprise a sun gear, a planet carrier and a gear ring;
the sun gear of the first planet row is in transmission connection with the sun gear of the fourth planet row and is in transmission connection with the input end of the automatic transmission, the gear ring of the first planet row is in transmission connection with the sun gear of the second planet row, the planet carrier of the third planet row and the gear ring of the fourth planet row are in transmission connection, and the gear ring of the third planet row is in transmission connection with the output end of the automatic transmission;
the automatic transmission also comprises a first clutch mechanism which is in transmission connection between the planet carrier of the first planet row and the gear ring of the second planet row, a second clutch mechanism which is in transmission connection between the sun gear of the first planet row and the sun gear of the fourth planet row as well as the gear ring of the second planet row, a third clutch mechanism which is in transmission connection between the planet carrier of the fourth planet row and the gear ring of the third planet row as well as the output end of the automatic transmission, a second brake mechanism which is arranged at the gear ring of the first planet row, and a third brake mechanism which is arranged at the sun gear of the third planet row;
the input end of the automatic transmission is in transmission connection with the power output end of the engine, a first brake mechanism is arranged at the planet carrier of the first planet row, or the input end of the automatic transmission is also in transmission connection with a motor.
2. The multi-speed planetary automatic transmission according to claim 1, characterized in that: when the input end of the automatic transmission is in transmission connection with the motor, the power output end of the engine is coaxially arranged with the motor.
3. A control method of a multi-gear planetary row type automatic transmission is characterized in that: the multi-gear planetary automatic transmission is applied to the multi-gear planetary automatic transmission of claim 1; when a first brake mechanism is arranged at a planet carrier of a first planet row in the multi-gear planet row type automatic transmission, the control method comprises the following steps:
a. controlling the first clutch mechanism to be engaged, controlling the second brake mechanism and the third brake mechanism to brake, and entering a first gear mode; or the like, or, alternatively,
b. controlling the first clutch mechanism and the third clutch mechanism to be engaged, controlling the first brake mechanism to brake, and entering a two-gear mode; or the like, or, alternatively,
c. controlling the first clutch mechanism and the third clutch mechanism to be engaged, controlling the second brake mechanism to brake, and entering a third gear mode; or the like, or, alternatively,
d. controlling the third clutch mechanism to be engaged, braking the third brake mechanism, and entering a fourth gear mode; or the like, or, alternatively,
e. controlling the second clutch mechanism and the third clutch mechanism to be engaged, controlling the second brake mechanism to brake, and entering a fifth gear mode; or the like, or, alternatively,
f. controlling the first clutch mechanism, the second clutch mechanism and the third clutch mechanism to be engaged to enter a sixth gear mode; or the like, or, alternatively,
g. controlling the second clutch mechanism to be engaged, controlling the second brake mechanism and the third brake mechanism to brake, and entering a seven-gear mode; or the like, or, alternatively,
h. controlling the first clutch mechanism and the second clutch mechanism to be engaged, controlling the third brake mechanism to brake, and entering an eight-gear mode; or the like, or, alternatively,
i. and controlling the first clutch mechanism to be engaged, controlling the first brake mechanism and the third brake mechanism to brake, and entering a reverse gear mode.
4. A control method of a multi-gear planetary row type automatic transmission is characterized in that: the multi-gear planetary automatic transmission is applied to the multi-gear planetary automatic transmission of claim 1 or 2; when the input end of the multi-gear planetary automatic gearbox is in transmission connection with a motor, the control method comprises the following steps:
a. controlling the first clutch mechanism to be engaged, controlling the second brake mechanism and the third brake mechanism to brake, and entering a first gear mode; or the like, or, alternatively,
b. controlling the first clutch mechanism and the third clutch mechanism to be jointed, controlling the second brake mechanism to brake, and entering a second gear mode; or the like, or, alternatively,
c. controlling the third clutch mechanism to be engaged, braking the third brake mechanism and entering a third gear mode; or the like, or, alternatively,
d. controlling the second clutch mechanism and the third clutch mechanism to be engaged, controlling the second brake mechanism to brake, and entering a fourth-gear mode; or the like, or, alternatively,
e. controlling the first clutch mechanism, the second clutch mechanism and the third clutch mechanism to be engaged to enter a fifth gear mode; or the like, or, alternatively,
f. controlling the second clutch mechanism to be engaged, controlling the second brake mechanism and the third brake mechanism to brake, and entering a six-gear mode; or the like, or, alternatively,
g. controlling the first clutch mechanism and the second clutch mechanism to be engaged, controlling the third brake mechanism to brake, and entering a seven-gear mode; or the like, or, alternatively,
h. and controlling the motor to rotate reversely to enter a reverse gear mode.
5. A vehicle, characterized in that: the multi-gear planetary automatic transmission of claim 1 or 2 is mounted on the vehicle, and when the input end of the automatic transmission is in transmission connection with a motor, the vehicle is further provided with a power battery unit electrically connected with the motor.
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