Power assembly of automatic transmission

Abstract

The present invention provides a power train for an automatic transmission, characterized in that a first carrier is integrated with a single pinion which meshes with a first sun gear and a first ring gear, a second carrier is integrated with the single pinion which meshes with a second sun gear and a second ring gear, and a third carrier is integrated with the single pinion which meshes with a second sun gear and a second ring gear. The third carrier and the single pinion are integrated, the single pinion is meshed with the third sun gear and the third inner gear ring, the fourth carrier and the single pinion are integrated, and the single pinion is meshed with the fourth sun gear and the fourth inner gear ring. A power assembly of an automatic transmission of the present invention transmits reverse drive of a motor through an input shaft in the same transmission path as a first gear to realize a reverse gear.

Description

Technical Field

[0001] The invention relates to a power assembly of an automatic transmission, which can realize eight forward gear shifts and one reverse gear shift. Background Art

[0002] Generally, an automatic transmission includes various types of structures, which adapt to the driving load by changing the power of the engine, and includes a gear train with planetary gears and a hydraulic control device for operating the gear train. Since the gear train forms a specific gear by the working combination of friction elements such as clutches or brakes operated by the hydraulic control device, when the hydraulic control device is automatically operated according to the driving conditions of the vehicle and the operation of the driver, the gear can be changed according to the desired gear. In order to form multiple gears of the automatic transmission, the power output from the engine can be transmitted to the drive wheels with higher efficiency, thereby improving fuel efficiency, acceleration performance and shifting quality.

[0003] Figure 1 FIG. 1 is a diagram showing a powertrain of a conventional automatic transmission. Figure 2 The following is an operation table showing the operation of a powertrain of a conventional automatic transmission according to each gear stage.

[0004] Reference Figure 1 and Figure 2 The powertrain of the existing automatic transmission includes: a first planetary gear set PG1, including a first transmission element CL1, a second transmission element CL2, a third transmission element CL3, a fourth transmission element B1, a fifth transmission element B2, a first sun gear S1, a first carrier C1, and a first inner ring gear R1; a second planetary gear set PG2, including a second sun gear S2, a second carrier C2, and a second inner ring gear R2; a third planetary gear set PG3, including a third sun gear S3, a third carrier C3, and a third inner ring gear R3; and a fourth planetary gear set PG4, including a fourth sun gear S4, a fourth carrier C4, and a fourth inner ring gear R4.

[0005] The powertrain of the existing automatic transmission also includes: a first rotating element N1, which connects the first sun gear S1 with the second sun gear S2; a second rotating element N2, which connects the first carrier C1, the third carrier C3, and the fourth inner ring gear R4; a third rotating element N3, which connects the first inner ring gear R1; a fourth rotating element N4, which connects the second carrier C2 with the input shaft IN; a fifth rotating element N5, which connects the second inner ring gear R2; a sixth rotating element N6, which connects the third inner ring gear R3 with the output shaft OUT; a seventh rotating element N7, which connects the fourth sun gear S4; and an eighth rotating element N8, which connects the third sun gear S3 with the fourth carrier C4.

[0006] However, in the powertrain of the existing automatic transmission, since the fourth planetary gear set is a double pinion structure, it is not conducive to gear efficiency.

[0007] Prior art literature

[0008] Patent Literature

[0009] Patent Document 1: Korean Patent Publication No. 10-2014-0120478 (Publication Date: October 14, 2014) Summary of the invention

[0010] Technical issues

[0011] In order to solve the above problems, the object of the present invention is to provide a powertrain of an automatic transmission, wherein the plurality of planetary gear sets are all single pinion structures, thereby achieving a reverse gear by transmitting the reverse drive of the motor to the same transmission path as the first gear.

[0012] Technical Solution

[0013] In order to achieve the above-mentioned purpose, the powertrain of the automatic transmission provided by the present invention includes: a first planetary gear set, including a first sun gear, a first carrier and a first inner gear ring, the first sun gear is selectively fixed to the housing by a first brake, and the first inner gear ring is selectively fixed to the housing by a second brake; a second planetary gear set, connected to the first planetary gear set, including a second sun gear connected to the first sun gear, a second carrier and a second inner gear ring; a third planetary gear set, connected to the second planetary gear set, including a third sun gear, a third carrier and a third inner gear ring; and a fourth planetary gear set, connected to the third planetary gear set, including a fourth A sun gear, a fourth carrier and a fourth inner gear ring, the first carrier and a single pinion are integrated, the single pinion is meshed with the first sun gear and the first inner gear ring, the second carrier and a single pinion are integrated, the single pinion is meshed with the second sun gear and the second inner gear ring, the third carrier and a single pinion are integrated, the single pinion is meshed with the third sun gear and the third inner gear ring, the fourth carrier and a single pinion are integrated, the single pinion is meshed with the fourth sun gear and the fourth inner gear ring, the powertrain of the automatic transmission of the present invention realizes reverse gear by transmitting the reverse drive of the motor through the transmission path that is the same as the first gear through the input shaft.

[0014] Furthermore, when in the reverse gear, the power generated by the reverse drive of the motor is transmitted to the input shaft, the power transmitted to the input shaft is transmitted to the third star gear via the second carrier through the engagement of the third clutch, the power transmitted to the third star gear is transmitted to the fourth star gear via the third internal ring gear, and the power transmitted to the fourth star gear is output to the output shaft via the fourth internal ring gear.

[0015] Furthermore, when the fourth sun gear is connected to the third internal gear ring, the fourth sun gear is variably connected to the second internal gear ring through the first clutch.

[0016] Furthermore, the second internal gear ring is variably connected to the third sun gear via a second clutch.

[0017] Furthermore, when the second carrier is connected to the input shaft, the second carrier is variably connected to the third sun gear via the third clutch.

[0018] Furthermore, the first carrier is connected to the third carrier and the fourth carrier.

[0019] Furthermore, the fourth internal gear ring is connected to the output shaft.

[0020] Furthermore, the first clutch is engaged in the 4th gear, the 5th gear, the 6th gear, the 7th gear, and the 8th gear.

[0021] Furthermore, the second clutch is engaged in the 2nd, 3rd, 4th, 6th, and 8th gears.

[0022] Furthermore, the third clutch is engaged in the 1st gear, the 3rd gear, the 5th gear, the 6th gear, the 7th gear, and the reverse gear.

[0023] Furthermore, the first brake is engaged in the 1st gear, the 2nd gear, the 7th gear, the 8th gear, and the reverse gear.

[0024] Furthermore, the second brake is engaged in the first gear, the second gear, the third gear, the fourth gear, the fifth gear, and the reverse gear.

[0025] Furthermore, the motor is located between the engine and the transmission, and the power of the engine is variably connected to the input shaft via a fourth clutch.

[0026] Effects of the Invention

[0027] The present invention has the following effect: since the plurality of planetary gear sets are all single pinion structures, the reverse gear (R gear) can be realized by transmitting the reverse drive of the motor to the same transmission path as the first gear.

[0028] Moreover, compared with the prior art, the present invention can increase the gear ratio of the reverse gear.

[0029] Furthermore, the present invention can provide a vehicle transmission device that is most suitable for a hybrid structure by realizing a reverse gear by reverse driving of the motor. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] Figure 1 The diagram shows a powertrain of a conventional automatic transmission.

[0031] Figure 2 The following is an operation table showing the operation of a powertrain of a conventional automatic transmission according to each gear stage.

[0032] Figure 3 The figure is a diagram showing a powertrain of an automatic transmission according to a preferred embodiment of the present invention.

[0033] Figure 4 A diagram showing a speed diagram during reverse gear shifting according to a preferred embodiment of the present invention.

[0034] Figure 5 The following is an operation table showing the operation of the powertrain of the automatic transmission according to each gear stage in a preferred embodiment of the present invention.

[0035] Figure 6 A diagram showing the power flow of a powertrain of an automatic transmission according to a preferred embodiment of the present invention during reverse gear shifting.

[0036] Description of Reference Numerals

[0037] 1: Shell

[0038] S1: First sun gear C1: First carrier R1: First ring gear

[0039] S2: Second sun gear C2: Second carrier R2: Second inner ring gear

[0040] S3: Third sun gear C3: Third carrier R3: Third ring gear

[0041] S4: Fourth sun gear C4: Fourth carrier R4: Fourth ring gear

[0042] CL1: First clutch CL2: Second clutch CL3: Third clutch

[0043] CL4: Fourth clutch B1: First brake B2: Second brake

[0044] IN: Input shaft OUT: Output shaft

[0045] E: Engine M: Motor T: Transmission DETAILED DESCRIPTION

[0046] Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. First, in the process of assigning figure marks to the structural elements of each figure, it should be noted that even if the same structural elements are represented on different figures, the same figure marks are assigned as much as possible. Also, in the process of describing the present invention, when it is determined that the specific description of the known structure or function may unnecessarily confuse the main purpose of the present invention, its detailed description will be omitted. Furthermore, although the preferred embodiments of the present invention are described below, the technical idea of ​​the present invention is not limited to this, and a person of ordinary skill in the technical field to which the present invention belongs can realize a variety of implementation methods through deformation.

[0047] Figure 3 A diagram showing a powertrain of an automatic transmission according to a preferred embodiment of the present invention is shown in FIG. Figure 4 A diagram showing a speed diagram of a reverse gear according to a preferred embodiment of the present invention. Figure 5 The following is an operation table showing the operation of the powertrain of the automatic transmission according to each gear stage in a preferred embodiment of the present invention.

[0048] like Figures 3 to 5 As shown, the present invention includes: a first planetary gear set; a second planetary gear set connected to the first planetary gear set; a third planetary gear set connected to the second planetary gear set; and a fourth planetary gear set connected to the third planetary gear set.

[0049] The first planetary gear set includes a first sun gear S1, a first carrier C1, and a first inner ring gear R1 connected to each other. The second planetary gear set includes a second sun gear S2, a second carrier C2, and a second inner ring gear R2 connected to each other. The third planetary gear set includes a third sun gear S3, a third carrier C3, and a third inner ring gear R3 connected to each other. The fourth planetary gear set includes a fourth sun gear S4, a fourth carrier C4, and a fourth inner ring gear R4 connected to each other.

[0050] The first sun gear S1 can be selectively fixed to the housing 1 of the transmission T by a first brake B1. The first ring gear R1 can be selectively fixed to the housing 1 of the transmission T by a second brake B2.

[0051] In the present invention, the first planetary gear set, the second planetary gear set, the third planetary gear set and the fourth planetary gear set may constitute a single pinion structure to improve transmission efficiency.

[0052] Specifically, the first carrier C1 may be formed as a whole with a single pinion (not shown). The single pinion is located between the first sun gear S1 and the first inner gear ring R1 and may mesh with the first sun gear S1 and the first inner gear ring R1.

[0053] The second carrier C2 may be formed integrally with a single pinion (not shown). The single pinion is located between the second sun gear S2 and the second inner gear ring R2 and may mesh with the second sun gear S2 and the second inner gear ring R2.

[0054] The third carrier C3 may be formed as a whole with a single pinion (not shown). The single pinion is located between the third sun gear S3 and the third inner gear ring R3 and may mesh with the third sun gear S3 and the third inner gear ring R3.

[0055] The fourth carrier C4 may be formed as a whole with a single pinion (not shown). The single pinion is located between the fourth sun gear S4 and the fourth inner gear ring R4 and may mesh with the fourth sun gear S4 and the fourth inner gear ring R4.

[0056] In the existing fourth planetary gear set, since the fourth carrier and the double pinion are formed into a double pinion structure as one body, it is not conducive to transmission efficiency. However, in the present invention, since the first planetary gear set, the second planetary gear set, the third planetary gear set and the fourth planetary gear set form a single pinion structure, the transmission efficiency can be improved compared with the existing double pinion structure.

[0057] The reverse gear (R gear) can be realized by transmitting the reverse driving of the motor M to the same transmission path as the first gear through the input shaft IN. The motor M can be located between the engine E and the transmission T. In the engagement operation of the fourth clutch CL4, the power of the engine E can be connected to the input shaft IN.

[0058] When in reverse gear, the power generated by the reverse driving of the motor M may be transmitted to the input shaft IN. The power transmitted to the input shaft IN may be transmitted to the third sun gear S3 via the second carrier C2 by the engagement operation of the third clutch CL3. The power transmitted to the third sun gear S3 may be transmitted to the fourth sun gear S4 via the third ring gear R3. The power transmitted to the fourth sun gear S4 may be output to the output shaft OUT via the fourth ring gear R4.

[0059] The fourth sun gear S4 may be connected to the third ring gear R3 via a rotation element. The fourth sun gear S4 may be variably connected to the second ring gear R2 via a first clutch CL1.

[0060] The second ring gear R2 can be variably connected to the third sun gear S3 via the second clutch CL2.

[0061] The second carrier C2 may be connected to the input shaft IN via a rotation element. The second carrier C2 may be variably connected to the third sun gear S3 via a third clutch CL3.

[0062] The first carrier C1 may be connected to the third carrier C3 and the fourth carrier C4 via a rotating element.

[0063] The fourth ring gear R4 may be connected to the output shaft OUT via a rotation element.

[0064] The first clutch CL1 can be engaged in the 4th, 5th, 6th, 7th and 8th gears. The second clutch CL2 can be engaged in the 2nd, 3rd, 4th, 6th and 8th gears. The third clutch CL3 can be engaged in the 1st, 3rd, 5th, 6th, 7th and reverse gears. The first brake B1 can be engaged in the 1st, 2nd, 7th, 8th and reverse gears. The second brake B2 can be engaged in the 1st, 2nd, 3rd, 4th, 5th and reverse gears.

[0065] Next, the power flow during the reverse gear shift of the present invention will be described.

[0066] Figure 6 A diagram showing the power flow of a powertrain of an automatic transmission according to a preferred embodiment of the present invention during reverse gear shifting.

[0067] like Figures 4 to 6 As shown, when in the reverse gear, the power generated by the reverse driving of the motor M is input to the input shaft IN. The power input to the input shaft IN is transmitted to the second carrier C2.

[0068] The power transmitted to the second carrier C2 is transmitted to the third sun gear S3 by the engagement operation of the third clutch CL3. In this case, the first sun gear S1 can be used as a fixed element fixed to the housing 1 by the engagement operation of the first brake B1, and the first ring gear R1 can be used as a fixed element fixed to the housing 1 by the engagement operation of the second brake B2.

[0069] The power transmitted to the third sun gear S3 can be transmitted to the fourth sun gear S4 via the third inner ring gear R3. The power transmitted to the fourth sun gear S4 can be output to the output shaft OUT via the fourth inner ring gear R4 so that the reverse rotation power is output.

[0070] On the other hand, in the case of the first gear, the power of the engine E is input to the input shaft IN. At this time, as the rotation of the engine E and the motor M is synchronized by the engagement operation of the fourth clutch CL4, the power of the engine E can be transmitted to the input shaft IN.

[0071] The power input to the input shaft IN is transmitted to the second carrier C2. The power transmitted to the second carrier C2 can be transmitted to the third sun gear S3 by the engagement operation of the third clutch CL3. In this case, the first sun gear S1 is fixed to the housing 1 by the engagement operation of the first brake B1, and the first ring gear R1 is fixed to the housing 1 by the engagement operation of the second brake B2.

[0072] The power transmitted to the third sun gear S3 may be transmitted to the fourth sun gear S4 via the third ring gear R3. The power transmitted to the fourth sun gear S4 may be output to the output shaft OUT via the fourth ring gear R4.

[0073] The above description is only an illustrative description of the technical idea of ​​the present invention. Ordinary technicians in the technical field to which the present invention belongs can make various modifications, changes and substitutions without departing from the basic features of the present invention. Therefore, the embodiments and drawings disclosed in the present invention are only for illustration and do not limit the technical idea of ​​the present invention. The scope of the technical idea of ​​the present invention is not limited to the above embodiments and drawings. The protection scope of the present invention should be interpreted based on the protection scope of the invention claims, and all technical ideas within the equivalent scope thereof belong to the protection scope of the present invention claims.

Claims

1. A powertrain of an automatic transmission, characterized in that: include: A first planetary gear set, comprising a first sun gear, a first carrier and a first inner gear ring, wherein the first sun gear is selectively fixed to the housing through a first brake, and the first inner gear ring is selectively fixed to the housing through a second brake; A second planetary gear set connected to the first planetary gear set, comprising a second sun gear connected to the first sun gear, a second carrier and a second inner ring gear; a third planetary gear set connected to the second planetary gear set, comprising a third sun gear, a third carrier and a third inner ring gear; and a fourth planetary gear set, connected to the third planetary gear set, comprising a fourth sun gear, a fourth carrier and a fourth inner gear ring, The first carrier is integrally formed with a single pinion, and the single pinion is meshed with the first sun gear and the first inner gear ring. The second carrier is integrally formed with a single pinion, and the single pinion is meshed with the second sun gear and the second inner gear ring. The third carrier is integrally formed with a single pinion, and the single pinion is meshed with the third sun gear and the third inner gear ring. The fourth carrier is integrally formed with a single pinion, and the single pinion is meshed with the fourth sun gear and the fourth inner gear ring. Reverse gearing is achieved by transmitting the reverse drive of the motor through the same transmission path as the first gear through the input shaft.

2. The powertrain of the automatic transmission according to claim 1, characterized in that: When in the reverse gear, the power generated by the reverse drive of the motor is transmitted to the input shaft, the power transmitted to the input shaft is transmitted to the third sun gear via the second carrier through the engagement of the third clutch, the power transmitted to the third sun gear is transmitted to the fourth sun gear via the third internal gear ring, and the power transmitted to the fourth sun gear is output to the output shaft via the fourth internal gear ring.

3. The powertrain of the automatic transmission according to claim 1, characterized in that: When the fourth sun gear is connected to the third internal gear ring, the fourth sun gear is variably connected to the second internal gear ring via the first clutch.

4. The powertrain of the automatic transmission according to claim 1, characterized in that: The second internal gear ring is variably connected to the third sun gear via a second clutch.

5. The powertrain of the automatic transmission according to claim 1, characterized in that: In a case where the second carrier is connected to the input shaft, the second carrier is variably connected to the third sun gear via a third clutch.

6. The powertrain of the automatic transmission according to claim 1, characterized in that: The first carrier is connected to the third carrier and the fourth carrier.

7. The powertrain of the automatic transmission according to claim 1, characterized in that: The fourth internal gear ring is connected to the output shaft.

8. The powertrain of the automatic transmission according to claim 3, characterized in that: The first clutch is engaged in the 4th gear, the 5th gear, the 6th gear, the 7th gear, and the 8th gear.

9. The powertrain of the automatic transmission according to claim 4, characterized in that: The second clutch is engaged in the 2nd, 3rd, 4th, 6th and 8th gears.

10. The powertrain of the automatic transmission according to claim 5, characterized in that: The third clutch is engaged in the 1st gear, the 3rd gear, the 5th gear, the 6th gear, the 7th gear and the reverse gear.

11. The powertrain of the automatic transmission according to claim 1, characterized in that: The first brake is engaged in the 1st gear, the 2nd gear, the 7th gear, the 8th gear, and the reverse gear.

12. The powertrain of the automatic transmission according to claim 1, characterized in that: The second brake is engaged in the 1st gear, the 2nd gear, the 3rd gear, the 4th gear, the 5th gear, and the reverse gear.

13. The powertrain of the automatic transmission according to claim 2, characterized in that: The motor is located between the engine and the transmission, and the power of the engine is variably connected to the input shaft through a fourth clutch.

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