CN113028006B - Speed variator - Google Patents
Speed variator Download PDFInfo
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- CN113028006B CN113028006B CN201911360113.1A CN201911360113A CN113028006B CN 113028006 B CN113028006 B CN 113028006B CN 201911360113 A CN201911360113 A CN 201911360113A CN 113028006 B CN113028006 B CN 113028006B
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- gear
- clutch
- transmission
- sun gear
- brake
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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
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
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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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- 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
- F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten 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 the field of vehicles, and provides a transmission, wherein the transmission comprises an input shaft, an output shaft, a shell, a plurality of brakes, a plurality of clutches, a first planetary gear set, a second planetary gear set, a third planetary gear set and a fourth planetary gear set which are coaxially arranged, the first planetary gear set comprises a first sun gear, a first planet carrier and a first ring gear, the second planetary gear set comprises a second sun gear, a second planet carrier and a second ring gear, the third planetary gear set comprises a third sun gear, a third planet carrier and a third ring gear, and the fourth planetary gear set comprises a fourth sun gear, a fourth planet carrier and a fourth ring gear. The transmission provided by the invention realizes transmission through the four planetary gear sets which are coaxially arranged, can reduce the size in the axial direction, is convenient for the space design inside the transmission shell, and reduces the space occupied by the whole transmission.
Description
Technical Field
The present invention relates to vehicle components, and more particularly to a transmission.
Background
The transmission is one of the important parts of the vehicle, on one hand, the shifting speed, the smoothness and the quietness of power connection of the transmission have important influence on the driving experience, and on the other hand, the compact structure, the light weight and the larger transmission ratio are also important factors in the design aspect of the vehicle
In a multi-gear transmission, in order to realize multiple gears, more gears and control elements need to be added, which brings difficulty to the structural design inside the transmission, which leads to the increase of the volume of the transmission and the difficulty in the arrangement of the whole transmission.
Disclosure of Invention
In view of this, the present invention provides a transmission to solve the problems of a transmission structure in the transmission that the volume is large and the space design difficulty is high.
In order to achieve the purpose, the technical scheme of the invention is realized as follows:
a transmission, wherein the transmission comprises an input shaft, an output shaft, a housing, a first planetary gear set, a second planetary gear set, a third planetary gear set, a fourth planetary gear set, coaxially arranged, the first planetary gear set comprising a first sun gear, a first planet carrier, and a first ring gear, the second planetary gear set comprising a second sun gear, a second planet carrier, and a second ring gear, the third planetary gear set comprising a third sun gear, a third planet carrier, and a third ring gear, the fourth planetary gear set comprising a fourth sun gear, a fourth planet carrier, and a fourth ring gear;
the first planet carrier is in transmission connection with the third planet carrier, the first sun gear is in transmission connection with the second sun gear, the second planet carrier is in transmission connection with the input shaft, the second gear ring is in transmission connection with the third sun gear, the third planet carrier is in transmission connection with the fourth gear ring, and the fourth planet carrier is in transmission connection with the output shaft;
the first sun gear is selectively connected to the housing through a first brake, the first ring gear is selectively connected to the housing through a second brake, the first carrier is selectively drivingly connected to the second ring gear through a first clutch, the third ring gear is selectively drivingly connected to the third sun gear through a second clutch and a third clutch, the third sun gear is selectively drivingly connected to the fourth sun gear through the third clutch, and the fourth sun gear is selectively drivingly connected to the input shaft through the fourth clutch.
Further, the first brake and the second brake are respectively braked, and the fourth clutch is engaged to realize a first-gear transmission ratio;
the first brake and the second brake respectively brake, and the third clutch is engaged to realize two-gear transmission ratio.
Further, the second brake is braked, and the third clutch and the fourth clutch are respectively engaged to realize a third gear transmission ratio.
Further, the second brake is braked, and the first clutch and the third clutch are respectively engaged to realize a fourth gear ratio.
Further, the second brake is braked, and the first clutch and the fourth clutch are respectively engaged to realize a fifth gear transmission ratio;
the second brake is braked, and the second clutch and the fourth clutch are respectively engaged to realize a six-gear transmission ratio.
Further, the first clutch, the second clutch and the fourth clutch are respectively engaged to achieve a seventh gear transmission ratio; alternatively, the second clutch, the third clutch, and the fourth clutch are engaged, respectively, to achieve a seven speed gear ratio.
Further, the first brake is braked, and the second clutch and the fourth clutch are respectively engaged to realize an eight-gear transmission ratio;
the first brake is braked, and the first clutch and the fourth clutch are respectively engaged to realize a nine-gear transmission ratio.
Further, the first brake is braked, and the first clutch and the second clutch are respectively engaged to realize a ten-gear transmission ratio; alternatively, the first brake is braked and the first clutch and the third clutch are respectively engaged to achieve a ten-speed gear ratio.
Further, the first brake and the second brake are respectively braked, and the second clutch is engaged to realize a reverse gear transmission ratio.
A transmission, wherein the transmission comprises an input shaft, an output shaft, a housing, a first planetary gear set, a second planetary gear set, a third planetary gear set, a fourth planetary gear set, an input shaft, a housing, which are coaxially arranged, the first planetary gear set comprising a first sun gear, a first planet carrier, and a first ring gear, the second planetary gear set comprising a second sun gear, a second planet carrier, and a second ring gear, the third planetary gear set comprising a third sun gear, a third planet carrier, and a third ring gear, the fourth planetary gear set comprising a fourth sun gear, a fourth planet carrier, and a fourth ring gear;
the first planet carrier is in transmission connection with the fourth gear ring, the first sun gear is in transmission connection with the second sun gear, the second planet carrier is in transmission connection with the input shaft, the second gear ring is in transmission connection with the third sun gear, the third gear ring is in transmission connection with the fourth sun gear, and the fourth planet carrier is in transmission connection with the output shaft;
the first sun gear is selectively drivingly connected to the housing by a first brake, the first ring gear is selectively drivingly connected to the housing by a second brake, the first carrier is selectively drivingly connected to the second ring gear by a first clutch, the first carrier is selectively drivingly connected to the third carrier by a second clutch, the third carrier is selectively drivingly connected to the fourth ring gear by the second clutch, the third ring gear is selectively drivingly connected to the third sun gear by a third clutch, the third sun gear is selectively drivingly connected to the fourth sun gear by the third clutch, and the fourth sun gear is selectively drivingly connected to the input shaft by the fourth clutch.
Compared with the prior art, the transmission disclosed by the invention has the following advantages:
the transmission provided by the invention realizes transmission through the four planetary gear sets which are coaxially arranged, can reduce the size in the axial direction, is convenient for the space design inside the transmission shell, and reduces the space occupied by the whole transmission.
Additional features and advantages of the invention will be set forth in the detailed description which follows.
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 transmission according to a first embodiment of the present invention;
fig. 2 is a transmission according to a second embodiment of the present invention.
Description of the reference numerals:
s1-first sun gear, S2-second sun gear, S3-third sun gear, S4-fourth sun gear, PC 1-first planet carrier, PC 2-second planet carrier, PC 3-third planet carrier, PC 4-fourth planet carrier, R1-first gear ring, R2-second gear ring, R3-third gear ring, R4-fourth gear ring, B1-first brake, B2-second brake, C1-first clutch, C2-second clutch, C3-third clutch, C4-fourth clutch, G-input shaft, H-housing, T-output shaft.
Detailed Description
In addition, the embodiments of the present invention and the 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 accompanying drawings in conjunction with embodiments.
According to a first embodiment of the present invention, referring to fig. 1, there is provided a transmission, wherein the transmission comprises an input shaft G, a housing H, a first planetary gear set, a second planetary gear set, a third planetary gear set and a fourth planetary gear set, which are coaxially arranged, the first planetary gear set comprising a first sun gear S1, a first planet carrier PC1 and a first ring gear R1, the second planetary gear set comprising a second sun gear S2, a second planet carrier PC2 and a second ring gear R2, the third planetary gear set comprising a third sun gear S3, a third planet carrier PC3 and a third ring gear R3, the fourth planetary gear set comprising a fourth sun gear S4, a fourth planet carrier PC4 and a fourth ring gear R4;
the first planet carrier PC1 is in driving connection with the third planet carrier PC3, the first sun gear S1 is in driving connection with the second sun gear S2, the second planet carrier PC2 is in driving connection with the input shaft G, the second ring gear R2 is in driving connection with the third sun gear S3, the third planet carrier PC3 is in driving connection with the fourth ring gear R4, and the fourth planet carrier PC4 is in driving connection with the output shaft T;
the first sun gear S1 is selectively connected to the housing H through a first brake B1, the first ring gear R1 is selectively connected to the housing H through a second brake B2, the first carrier PC1 is selectively drivingly connected to the second ring gear R2 through a first clutch C1, the third ring gear R3 is selectively drivingly connected to the third sun gear S3 through a second clutch C2 and a third clutch C3, the third sun gear S3 is selectively drivingly connected to the fourth sun gear S4 through a third clutch C3, and the fourth sun gear S4 is selectively drivingly connected to the input shaft G through a fourth clutch C4.
The main transmission structure of the transmission of the scheme is four planetary gear sets, and the planet carrier, the sun gear and the ring gear of each of the four planetary gear sets are partially in direct transmission connection, partially selectively in transmission connection through four clutches, partially in transmission connection with the input shaft G, and the first sun gear S1 and the first gear R1 are respectively selectively connected to the shell H through two brakes so as to change the transmission mode of the first planetary gear set.
The transmission realizes transmission through four planetary gear sets which are coaxially arranged, the size in the axial direction can be reduced, the space design inside the transmission shell is convenient to carry out, and the space occupied by the whole transmission is reduced.
Alternatively, the first brake B1 and the second brake B2 are braked respectively, and the fourth clutch C4 is engaged to realize a first gear transmission ratio;
the first brake B1 and the second brake B2 are respectively braked, and the third clutch C3 is engaged to achieve the two-gear transmission ratio.
In the first gear ratio, the first ring gear R1, the first sun gear S1 and the second sun gear S2 are fixed, and the transmission path is as follows: the input shaft G → the fourth sun gear S4 → the fourth planet carrier PC4 → the output shaft T;
in the second gear ratio, the first ring gear R1, the first sun gear S1 and the second sun gear S2 are fixed, and the transmission path is: the input shaft G → the second carrier PC2 → the second ring gear R2 → the third sun gear S3 → the fourth sun gear S4 → the fourth carrier PC4 → the output shaft T.
The speed ratio step difference of the first gear transmission ratio and the second gear transmission ratio is relatively reasonable, so that the gear shifting operation is smoother, and the gear shifting impact force is reduced.
Alternatively, the second brake B2 is braked and the third clutch C3 and the fourth clutch C4 are engaged, respectively, to achieve a third gear ratio.
In the third gear ratio, the first ring gear R1 is fixed and the second planet carrier PC2 is connected to the input shaft G by the following transmission path: first, the input shaft G → the second carrier PC2 → the second sun gear S2 → the first sun gear S1 → the first carrier PC1 → the fourth ring gear R4 → the fourth carrier PC4 → the output shaft T; input shaft G → second carrier PC2 → second ring gear R2 → third sun gear S3 → fourth sun gear S4 → fourth carrier PC4 → output shaft T; third, the input shaft G → the fourth sun gear S4 → the fourth planet carrier PC4 → the output shaft T. That is, in the third gear ratio, three transmission paths are present simultaneously.
Alternatively, the second brake B2 is braked and the first clutch C1 and the third clutch C3 are engaged, respectively, to achieve a fourth gear ratio. The second brake B2 is braked, the first clutch C1 and the third clutch C3 are respectively engaged, the first ring gear R1 is fixed, the second planet carrier PC2 is connected with the input shaft G, and the transmission path is as follows: first, the input shaft G → the second carrier PC2 → the second sun gear S2 → the first sun gear S1 → the first carrier PC1 → the fourth ring gear R4 → the fourth carrier PC4 → the output shaft T; input shaft G → second carrier PC2 → second ring gear R2 → fourth ring gear R4 → fourth carrier PC4 → output shaft T; third, the input shaft G → the second carrier PC2 → the second ring gear R2 → the third sun gear S3 → the fourth sun gear S4 → the fourth carrier PC4 → the output shaft T. In this mode, three transmission paths exist simultaneously.
Optionally, the second brake B2 is braked, and the first clutch C1 and the fourth clutch C4 are respectively engaged to realize a fifth gear transmission ratio;
the second brake B2 is applied, and the second clutch C2 and the fourth clutch C4 are engaged, respectively, to achieve a sixth gear ratio.
In the fifth gear ratio, the first ring gear R1 is fixed and the second planet carrier PC2 is connected to the input shaft G through the following transmission path: first, the input shaft G → the second carrier PC2 → the second sun gear S2 → the first sun gear S1 → the first carrier PC1 → the fourth ring gear R4 → the fourth carrier PC4 → the output shaft T; input shaft G → second carrier PC2 → second ring gear R2 → fourth ring gear R4 → fourth carrier PC4 → output shaft T; ③ the input shaft G → the fourth sun gear S4 → the fourth planet carrier PC4 → the output shaft T; wherein three transmission paths are present simultaneously.
In a sixth gear ratio, the first ring gear R1 is fixed and the second planet carrier PC2 is connected to the input shaft G by the following transmission path: first, the input shaft G → the second carrier PC2 → the second sun gear S2 → the first sun gear S1 → the first carrier PC1 → the fourth ring gear R4 → the fourth carrier PC4 → the output shaft T; the input shaft G → the second carrier PC2 → the second ring gear R2 → the third sun gear S3 → the third carrier PC3 → the third ring gear R3 → the fourth sun gear S4 → the fourth carrier PC4 → the output shaft T; ③ the input shaft G → the fourth sun gear S4 → the fourth planet carrier PC4 → the output shaft T; wherein three transmission paths are present simultaneously.
Optionally, the first clutch C1, the second clutch C2 and the fourth clutch C4 are engaged respectively to achieve a seven speed gear ratio; alternatively, the second clutch C2, the third clutch C3, and the fourth clutch C4 are engaged, respectively, to achieve a seven speed gear ratio.
Two operating modes for achieving a seven speed transmission ratio have been proposed above, wherein:
first, the first clutch C1, the second clutch C2 and the fourth clutch C4 are engaged, and the second planet carrier PC2 is connected with the input shaft G, and the transmission path is: (ii) input shaft G → fourth sun gear S4 → fourth planet carrier PC4 → output shaft T; the input shaft G → the third ring gear R3 → the third carrier PC3 → the fourth ring gear R4 → the fourth carrier PC4 → the output shaft T; in which two transmission paths are present simultaneously.
Second, the second clutch C2, the third clutch C3 and the fourth clutch C4 are engaged, and the second planet carrier PC2 is connected to the input shaft G, and the transmission path is: (ii) input shaft G → fourth sun gear S4 → fourth planet carrier PC4 → output shaft T; the input shaft G → the third ring gear R3, the third planet carrier PC3, the fourth ring gear R4 → the fourth planet carrier PC4 → the output shaft T; ③ the input shaft G → the third sun gear S3 → the third ring gear R3 → the fourth ring gear R4 → the fourth carrier PC4 → the output shaft T; wherein three transmission paths are present simultaneously.
Alternatively, the first brake B1 is braked and the second clutch C2 and the fourth clutch C4 are engaged respectively to achieve an eight speed gear ratio;
the first brake B1 is braked and the first clutch C1 and the fourth clutch C4 are engaged respectively to achieve a nine speed gear ratio.
In the eighth gear ratio, the first sun gear S1 and the second sun gear S2 are fixed, and the second planet carrier PC2 is connected with the input shaft G, and the transmission path is as follows: first, the input shaft G → the second carrier PC2 → the second ring gear R2 → the third sun gear S3 → the third carrier PC3 → the fourth ring gear R4 → the fourth carrier PC4 → the output shaft T; the input shaft G → the second carrier PC2 → the second ring gear R2 → the third sun gear S3 → the third carrier PC3 → the third ring gear R3 → the fourth sun gear S4 → the fourth carrier PC4 → the output shaft T; ③ the input shaft G → the fourth sun gear S4 → the fourth planet carrier PC4 → the output shaft T; wherein three transmission paths are present simultaneously.
In the ninth gear ratio, the first sun gear S1 and the second sun gear S2 are fixed, and the second planet carrier PC2 is connected to the input shaft G through the following transmission path: first, the input shaft G → the second carrier PC2 → the second ring gear R2 → the fourth ring gear R4 → the fourth carrier PC4 → the output shaft T; input shaft G → fourth sun gear S4 → fourth planet carrier PC4 → output shaft T; in which two transmission paths are present simultaneously.
Alternatively, the first brake B1 is applied, and the first clutch C1 and the second clutch C2 are engaged, respectively, to achieve a ten-speed gear ratio; alternatively, the first brake B1 is braked and the first clutch C1 and the third clutch C3 are engaged, respectively, to achieve a ten-speed gear ratio.
Two operating modes for achieving a ten speed transmission ratio have been proposed above, wherein:
first, the first brake B1 is braked, the first clutch C1 and the second clutch C2 are engaged, the first sun gear S1 and the second sun gear S2 are fixed, the second planet carrier PC2 is connected with the input shaft G, and the transmission path is as follows: first, the input shaft G → the second carrier PC2 → the second ring gear R2 → the fourth ring gear R4 → the fourth carrier PC4 → the output shaft T; input shaft G → second carrier PC2 → second ring gear R2 → third carrier PC3 → third ring gear R3 → fourth sun gear S4 → fourth carrier PC4 → output shaft T; in which two transmission paths are present simultaneously.
Second, the first brake B1 is braked, the first clutch C1 and the third clutch C3 are engaged, the first sun gear S1 and the second sun gear S2 are fixed, the second planet carrier PC2 is connected with the input shaft G, and the transmission path is as follows: first, the input shaft G → the second carrier PC2 → the second ring gear R2 → the fourth ring gear R4 → the fourth carrier PC4 → the output shaft T; input shaft G → second carrier PC2 → second ring gear R2 → third sun gear S3 → fourth sun gear S4 → fourth carrier PC4 → output shaft T; third, the input shaft G → the second carrier PC2 → the second ring gear R2 → the third carrier PC3 → the third sun gear S3 → the fourth sun gear S4 → the fourth carrier PC4 → the output shaft T; wherein three transmission paths are present simultaneously.
Alternatively, the first brake B1 and the second brake B2 are applied separately and the second clutch C2 is engaged to achieve the reverse gear ratio.
In the reverse gear ratio, the first sun gear S1, the second sun gear S2 and the first ring gear R1 are fixed, and the second planet carrier PC2 is connected with the input shaft G by the following transmission paths: first, the input shaft G → the second carrier PC2 → the second ring gear R2 → the third sun gear S3 → the third carrier PC3 → the fourth ring gear R4 → the fourth carrier PC4 → the output shaft T; the input shaft G → the second carrier PC2 → the second ring gear R2 → the third sun gear S3 → the third carrier PC3 → the third ring gear R3 → the fourth sun gear S4 → the fourth carrier PC4 → the output shaft T; in which two transmission paths are present simultaneously.
The following table is a control method of the transmission of the first embodiment.
According to a second embodiment of the present invention, referring to fig. 2, there is provided a transmission, wherein the transmission includes an input shaft G, an output shaft T, a housing H, a first planetary gear set including a first sun gear S1, a first carrier PC1, and a first ring gear R1, coaxially arranged, a second planetary gear set including a second sun gear S2, a second carrier PC2, and a second ring gear R2, a third planetary gear set including a third sun gear S3, a third carrier PC3, and a third ring gear R3, and a fourth planetary gear set including a fourth sun gear S4, a fourth carrier PC4, and a fourth ring gear R4;
the first planet carrier PC1 is in driving connection with the fourth ring gear R4, the first sun gear S1 is in driving connection with the second sun gear S2, the second planet carrier PC2 is in driving connection with the input shaft G, the second ring gear R2 is in driving connection with the third sun gear S3, the third ring gear R3 is in driving connection with the fourth sun gear S4, and the fourth planet carrier PC4 is in driving connection with the output shaft T;
the first sun gear S1 is selectively drivingly connected to the housing H through a first brake B1, the first ring gear R1 is selectively drivingly connected to the housing H through a second brake B2, the first planet carrier PC1 is selectively drivingly connected to the second ring gear R2 via a first clutch C1, the first planet carrier PC1 is selectively drivingly connected to the third planet carrier PC3 via a second clutch C2, the third planet carrier PC3 is selectively drivingly connected to the fourth ring gear R4 through the second clutch C2, the third ring gear R3 is selectively drivingly connected to the third sun gear S3 through a third clutch C3, the third sun gear S3 is selectively drivingly connected to the fourth sun gear S4 through the third clutch C3, the fourth sun gear S4 is selectively drivingly connected to the input shaft G through the fourth clutch C4.
Compared with the transmission of the first embodiment, the main structure (including the planetary gear sets, the input shaft and the output shaft) of the transmission of the second embodiment is basically the same as that of the transmission of the first embodiment, except for the positions of several clutches, and the transmission of the second embodiment can realize the same gear ratio and the same transmission path corresponding to each gear ratio as those of the transmission of the first embodiment.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and should not be taken as limiting the scope of the present invention, which is intended to cover any modifications, equivalents, improvements, etc. within the spirit and scope of the present invention.
Claims (9)
1. A transmission, characterized by comprising an input shaft (G), an output shaft (T), a housing (H), a first planetary gear set, a second planetary gear set, a third planetary gear set, a fourth planetary gear set, coaxially arranged, the first planetary gear set comprising a first sun gear (S1), a first planet carrier (PC1) and a first ring gear (R1), the second planetary gear set comprising a second sun gear (S2), a second planet carrier (PC2) and a second ring gear (R2), the third planetary gear set comprising a third sun gear (S3), a third planet carrier (PC3) and a third ring gear (R3), the fourth planetary gear set comprising a fourth sun gear (S4), a fourth planet carrier (PC4) and a fourth ring gear (R4);
the first planet carrier (PC1) is in driving connection with the third planet carrier (PC3), the first sun gear (S1) is in driving connection with the second sun gear (S2), the second planet carrier (PC2) is in driving connection with the input shaft (G), the second ring gear (R2) is in driving connection with the third sun gear (S3), the third planet carrier (PC3) is in driving connection with the fourth ring gear (R4), and the fourth planet carrier (PC4) is in driving connection with the output shaft (T);
the first sun gear (S1) is selectively connected to the housing (H) through a first brake (B1), the first ring gear (R1) is selectively connected to the housing (H) through a second brake (B2), the first carrier (PC1) is selectively drivingly connected to the second ring gear (R2) through a first clutch (C1), the third ring gear (R3) is selectively drivingly connected to the third sun gear (S3) through a second clutch (C2) and a third clutch (C3), the third sun gear (S3) is selectively drivingly connected to the fourth sun gear (S4) through the third clutch (C3), and the fourth sun gear (S4) is selectively drivingly connected to the input shaft (G) through a fourth clutch (C4).
2. The transmission of claim 1, wherein the first brake (B1) and the second brake (B2) are each braked and the fourth clutch (C4) is engaged to achieve a first gear ratio;
the first brake (B1) and the second brake (B2) are braked respectively, and the third clutch (C3) is engaged to realize a two-gear transmission ratio.
3. The transmission of claim 1, wherein said second brake (B2) is braked and said third clutch (C3) and said fourth clutch (C4) are engaged respectively to achieve a third gear ratio.
4. The transmission of claim 1, wherein said second brake (B2) is braked and said first clutch (C1) and said third clutch (C3) are engaged respectively to achieve a fourth gear ratio.
5. The transmission of claim 1, wherein the second brake (B2) is braked, and the first clutch (C1) and the fourth clutch (C4) are engaged, respectively, to achieve a fifth gear ratio;
the second brake (B2) is braked, and the second clutch (C2) and the fourth clutch (C4) are respectively engaged to realize a six-gear transmission ratio.
6. The transmission of claim 1, wherein the first clutch (C1), the second clutch (C2), and the fourth clutch (C4) are each engaged to achieve a seven speed gear ratio; alternatively, the second clutch (C2), the third clutch (C3), and the fourth clutch (C4) are engaged, respectively, to achieve a seven speed gear ratio.
7. The transmission of claim 1, wherein the first brake (B1) is braked, and the second clutch (C2) and the fourth clutch (C4) are respectively engaged to achieve an eight speed gear ratio;
the first brake (B1) is braked, and the first clutch (C1) and the fourth clutch (C4) are respectively engaged to realize a nine-gear transmission ratio.
8. The transmission of claim 1, wherein said first brake (B1) is braked and said first clutch (C1) and said second clutch (C2) are respectively engaged to achieve a ten speed gear ratio; alternatively, the first brake (B1) is braked and the first clutch (C1) and the third clutch (C3) are engaged, respectively, to achieve a ten-speed gear ratio.
9. The transmission of claim 1, wherein the first brake (B1) and the second brake (B2) are each braked and the second clutch (C2) is engaged to achieve a reverse gear ratio.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911360113.1A CN113028006B (en) | 2019-12-25 | 2019-12-25 | Speed variator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911360113.1A CN113028006B (en) | 2019-12-25 | 2019-12-25 | Speed variator |
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| Publication Number | Publication Date |
|---|---|
| CN113028006A CN113028006A (en) | 2021-06-25 |
| CN113028006B true CN113028006B (en) | 2022-08-12 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201911360113.1A Active CN113028006B (en) | 2019-12-25 | 2019-12-25 | Speed variator |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101896737A (en) * | 2007-12-14 | 2010-11-24 | 腓特烈斯港齿轮工厂股份公司 | 10-gear automatic transmission |
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| CN103727187A (en) * | 2012-10-12 | 2014-04-16 | 通用汽车环球科技运作有限责任公司 | Multi-speed transmission |
| CN103867663A (en) * | 2012-12-07 | 2014-06-18 | 通用汽车环球科技运作有限责任公司 | Multi-speed transmission |
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| DE102015102829A1 (en) * | 2014-03-07 | 2015-09-10 | GM Global Technology Operations LLC (n. d. Ges. d. Staates Delaware) | Multi-speed transmission |
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| US20160333973A1 (en) * | 2015-05-13 | 2016-11-17 | Hyundai Motor Company | Planetary gear train of automatic transmission for vehicles |
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| CN101896737A (en) * | 2007-12-14 | 2010-11-24 | 腓特烈斯港齿轮工厂股份公司 | 10-gear automatic transmission |
| JP2015505355A (en) * | 2011-12-29 | 2015-02-19 | ヒュンダイ パワーテック カンパニー、リミテッド | 10-speed powertrain for vehicle automatic transmission |
| CN103727183A (en) * | 2012-10-10 | 2014-04-16 | 通用汽车环球科技运作有限责任公司 | Multi-speed transmission |
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| DE102015102829A1 (en) * | 2014-03-07 | 2015-09-10 | GM Global Technology Operations LLC (n. d. Ges. d. Staates Delaware) | Multi-speed transmission |
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