WO2012092749A1

WO2012092749A1 - Multi-speed transmission

Info

Publication number: WO2012092749A1
Application number: PCT/CN2011/075263
Authority: WO
Inventors: 黄庆培
Original assignee: Huang Qingpei
Priority date: 2011-01-07
Filing date: 2011-06-03
Publication date: 2012-07-12
Also published as: CN102042372B; CN102042372A

Abstract

A multi-speed transmission for a front drive vehicle comprises an input shaft (1), an output part (2), a countershaft (3), two planetary gear sets (10,20), two fixed axis gear sets (30,40), and five gearshift parts (61,62,63,64,65). The driven wheel of the first fixed axis gear set is connected to the driving wheel of the second fixed axis gear set to form the countershaft. The sun gear and the planetary carrier of the second planetary gear set are connected to the input shaft and the output part, respectively. Respective ring gears of the first and the second planetary gear set are connected to the driving wheel of the first fixed axis gear set and the driven wheel of the second fixed axis gear set, respectively. The first and the third gearshift parts are connected in series between the sun gear and the planetary carrier of the first planetary gear set and the input shaft, respectively. The second gearshift part is connected in series between the sun gear of the first planetary gear set and the planetary carrier of the second planetary gear set. The fourth gearshift part selectively connects or drivingly connects the planetary carrier of the first planetary gear set to the ring gear of the second planetary gear set. The fifth gearshift part selectively brakes the planetary carrier of the first planetary gear set. The transmission has seven forward gear ratios and one reverse gear ratio.

Description

Multi-speed transmission

Technical field

The present invention relates to the field of multi-speed transmissions for automobiles, and more particularly to a multi-stage automatic transmission including a plurality of planetary gear sets and shifting elements.

Background technique

The gradual popularization of the five- and six-stage automatic transmissions will gradually replace the early three- and four-speed shifts. Existing six-speed transmissions typically include three planetary gear sets and five shifting elements (clutches and brakes), and a seven- or eight-speed transmission typically includes at least three planetary gear sets and six shifting elements, or four planetary gear sets. And five shifting elements, such as: Chinese Patent Publication No. CN1860314, CN1531634, CN1650119, CN101191535, CN101846160A, CN101235879, CN101275644, CN101103212, CN101354072, CN101275631 Wait. The planetary gear sets and shifting elements of these transmissions are all arranged on the same axis. The axial length of the transmission is long, which is not suitable for the front-premise, laterally-displaced vehicles, which hinders their widespread application.

'Power-shiftable multi-speed transmission' of Chinese Patent Publication No. CN101275630, CN101334094 'Eight speed transmission with planetary gear unit and countershaft gear unit', CN101392817, CN101392819 The 'eight-speed transmission' and the like include three planetary gear sets, five shifting elements and three fixed-shaft gear sets for front-mounted, laterally-displaced vehicles, but with a large volumetric weight. US patent application 'AUMATIC TRANSMISSION of US20100035718A1 'Includes two planetary gear sets, two fixed-shaft gear sets, five shifting elements for six-speed shifting, or one shifting element for eight-speed shifting. All planetary gear sets and shifting elements are placed On the spindle.

technical problem

The technical problem to be solved by the present invention is that a transmission including two planetary gear sets, five shifting elements, and two fixed-shaft gear sets has seven-stage forward and one-stage reverse shift, on the basis of The addition of a fixed-axis gear set improves the distribution of the gear ratio of each gear, optimizes the layout of the clutch shifting components, and further reduces the axial distance. With fewer components and shorter axial distances, more shift stages are achieved, which is beneficial for popular use in vehicles with front transversely arranged transmissions.

Technical solution

The technical solution of the present invention is: a multi-speed transmission including an input shaft, an output member, a counter shaft, a housing, first and second planetary gear sets of a single pinion type, and the first and outer mesh type a second fixed-axis gear set, first to fifth clutch shifting elements; the first and second planetary gear sets are disposed on an axis of the input shaft;

The first and second fixed-axis gear sets respectively have respective driving wheels and driven wheels, and the driving wheels of the first fixed-axis gear set and the driven wheels of the second fixed-axis gear set are arranged on the axis of the input shaft. The driven wheel of the first fixed-axis gear set and the driving wheel of the second fixed-axis gear set are connected to each other, and the connecting shaft constitutes a secondary shaft;

The sun gear and the carrier of the second planetary gear set are respectively connected to the input shaft and the output member;

a ring gear of the first planetary gear set is coupled to a driving wheel of the first fixed gear set, and a ring gear of the second planetary gear set is coupled to a driven wheel of the second fixed gear set;

The first clutch shifting element is serially coupled between the sun gear of the first planetary gear set and the input shaft; the second clutch shifting element is serially coupled to the first Selectively connecting the sun gear of the planetary gear set with the planet carrier of the second planetary gear set; the third clutch shifting element is coupled in series with the planet carrier of the first planetary gear set and Optionally connecting the two between the input shafts;

The fourth clutch shifting element has two arrangements: a first one, directly connecting between the carrier of the first planetary gear set and the ring gear of the second planetary gear set to selectively connect the two a ratio of a rotational speed of a carrier of the first planetary gear set to a ring gear of the second planetary gear set when the fourth clutch shifting element is coupled 1 In the second embodiment, the transmission further includes a third fixed shaft gear set on which the driving wheel and the driven wheel are respectively disposed on the input shaft and the countershaft axis, and the fourth clutch shifting element is serially connected to the planet of the first planetary gear set. The frame is selectively drivably coupled to the ring gear of the second planetary gear set via a countershaft, and the 'transmission path through the countershaft' passes through the third fixed shaft gear Transmission of the carrier of the first planetary gear set formed by the main and driven wheels of the group, the countershaft, the main and driven wheels of the second fixed-axis gear set to the ring gear of the second planetary gear set a fourth clutch shifting element or a driven wheel that is coupled between the carrier of the first planetary gear set and the drive wheel of the third fixed-shaft gear set and the third fixed-shaft gear set Connected to the countershaft, or serially connected between the driven wheel and the countershaft of the third fixed shaft gear set and the carrier of the first planetary gear set and the drive wheel of the third fixed shaft gear set Connection when the fourth clutch shifting element is combined The planet carrier of the first planetary gear set and the ring gear of the second planetary gear set speed ratio may not be equal 1. Although the second scheme is slightly complicated, it can improve the distribution of the gear ratio of each gear position of the transmission, so that the gear ratio (the ratio between the gear ratios of adjacent gears) is better, and the fourth clutch shifting element can also be arranged to On the secondary shaft;

The fifth clutch shifting element is connected in series between the planet carrier of the first planetary gear set and the housing, or in the second embodiment, the fifth clutch shifting element is serially connected to the third fixed shaft Between the driven wheel of the gear set and the housing, the third fixed shaft gear set and the fifth clutch shifting element form a transmission connection route between the carrier of the first planetary gear set to the housing, and the fifth clutch shifting element The planet carrier of the first planetary gear set is selectively braked.

In addition, a one-way clutch may be further included, which is connected in series between the carrier of the first planetary gear set and the housing, or in parallel with two of the fifth clutch shifting elements End, the function of which is to allow the carrier of the first planetary gear set to rotate in the same rotational direction of the input shaft, and the locking does not allow the planetary carrier of the first planetary gear set to rotate in the opposite direction to the input shaft Rotate.

Beneficial effect

The invention has the beneficial effects that the existing multi-speed transmission usually increases or decreases a set of key components (such as: one planetary gear set, or two fixed-axis gear sets, or one shifting component) to increase or decrease two shifting stages; for example The existing four-speed transmission generally includes at least two planetary gear sets and five shifting elements, and a six-speed transmission includes three planetary gear sets and five shifting elements, or two planetary gear sets, five The shifting element and the two fixed-axis gear sets have a seven-stage forward shifting compared to the present invention. Another example: compared with the eight-speed transmission including three planetary gear sets, five shifting components and three fixed-shaft gear sets, the present invention has one planetary gear set and has seven-stage forward and one-stage reverse shifting. , has a higher cost performance.

DRAWINGS

Figure 1 is a schematic diagram of the first embodiment

Figure 2 is a schematic diagram of the second embodiment

The reference numerals are as follows:

1 : Input shaft

2 : Output part

3 : secondary shaft

5 : housing

8: a transmission connection route between the carrier of the first planetary gear set and the ring gear of the second planetary gear set via a countershaft

9: a transmission connection route between the carrier of the first planetary gear set and the housing

10 : First planetary gear set

11 : The sun gear of the first planetary gear set

12: Planet carrier of the first planetary gear set

13 : The ring gear of the first planetary gear set

20 : Second planetary gear set

21 : The sun gear of the second planetary gear set

22 : Planetary carrier of the second planetary gear set

23 : Ring gear of the second planetary gear set

30 : The first axis gear set

31 : Drive wheel of the fixed shaft gear set

32 : Follower wheel of the fixed shaft gear set

40 : Second fixed shaft gear set

41 : Drive wheel of the second fixed-axis gear set

42 : Follower wheel of the second fixed-axis gear set

50 : Third fixed shaft gear set

51 : Drive wheel of the third fixed-axis gear set

52 : Follower wheel of the third fixed-axis gear set

61 to 65 : First to fifth clutch shifting elements

71 : One-way clutch.

BEST MODE FOR CARRYING OUT THE INVENTION

As shown in FIG. 1, the first planetary gear set 10 and the second planetary gear set 20 are single pinion type planetary gear sets, which are arranged on the input shaft. On the axis of 1;

The driving wheel 31 of the first fixed shaft gear set 30 and the driven wheel 42 of the second fixed shaft gear set 40 are arranged on the input shaft 1 On the axis, and connected to the ring gear 13 of the first planetary gear set 10 and the ring gear 23 of the second planetary gear set 20, respectively.

The driven wheel 32 of the first fixed shaft gear set 30 and the drive wheel 41 of the second fixed shaft gear set 40 They are connected to each other, and their connecting shafts constitute a countershaft 3 .

The sun gear 21 and the carrier 22 of the second planetary gear set 20 are respectively connected to the input shaft 1 and the output member 2 .

The first clutch shifting member 61 is coupled in series with the sun gear 11 of the first planetary gear set 10 and the input shaft 1 Both are selectively connectable; the second clutch shifting member 62 is coupled in series with the sun gear 11 of the first planetary gear set 10 and the planet carrier 22 of the second planetary gear set 20 Both are selectively connectable; the third clutch shifting member 63 is selectively coupled in series between the planet carrier 12 of the first planetary gear set 10 and the input shaft 1 .

The fourth clutch shifting member 64 is serially coupled to the planet carrier 12 of the first planetary gear set 10 and the second planetary gear set Two of the ring gears 23 of 20 are selectively connectable.

The fifth clutch shifting member 65 is serially connected to the carrier 12 of the first planetary gear set 10 and the housing 5 The planet carrier 12 of the first planetary gear set 10 is selectively braked between.

If the gear ratio between the ring gear 13 of the first planetary gear set 10 and the sun gear 11 is taken: K ₁₀ = 1.909, the gear ratio between the ring gear 23 of the second planetary gear set 20 and the sun gear 21: K ₂₀ = 2.048, the gear ratio of the main and driven wheels 31, 32 of the first fixed-axis gear set 30 is multiplied by the gear ratio of the main and driven wheels 41, 42 of the second fixed-axis gear set 40:

Z ₃₁ /Z ₃₂ × Z ₄₁ /Z ₄₂ =1.555 , the combination of the gears and shifting elements of the transmission, the gear ratio is as follows, the table '●' indicates the clutch shifting element combination, the blank indicates the separation:

In addition, a one-way clutch 71, a one-way clutch 71, may be connected to both ends of the fifth clutch shifting member 65. The carrier 12 of the first planetary gear set 10 is allowed to rotate in the same rotational direction of the input shaft 1, and the locking does not allow the carrier 12 to the input shaft 1 The opposite direction of rotation is rotated such that the first and second gears of the low speed do not have to be combined with the fifth clutch shifting member 65 when the vehicle is traveling on a city road. When the throttle is closed, the car slides, no engine brake is generated, and the frustration at low speed is eliminated; and in the engine braking mode, the first and second gears are combined with the fifth clutch shifting member 65. Engine braking can be used to improve the safety of downhill driving.

Embodiments of the invention

As shown in Fig. 2, the main difference from the first embodiment is that the third fixed shaft gear set 50 is added, and the driving wheel 51 and the driven wheel 52 are added. Arranged on the axes of the input shaft 1 and the counter shaft 3, respectively, the fourth clutch shifting member 64 is not directly coupled in series with the carrier 12 of the first planetary gear set 10 and the ring gear of the second planetary gear set 20 Between the transmissions of the carrier 12 and the ring gear 23 of the second planetary gear set 20 via the third fixed shaft gear set 50, the countershaft 3, and the second fixed shaft gear set 40 Above, FIG. 2 shows the fourth clutch shifting member 64 connected in series between the driven wheel 52 of the third fixed-axis gear set 50 and the countershaft 3, and the driving wheel of the carrier 12 and the third fixed-axis gear set 50. 51 is connected such that when the fourth clutch shifting member 64 is engaged, the rotational speed ratio between the carrier 12 and the ring gear 23 is no longer equal to one, which is different from the first embodiment; the fifth clutch shifting member 65 Also differs from the first embodiment in that it is connected in series between the driven wheel 52 of the third fixed-axis gear set 50 and the casing 5; the fourth and fifth

clutch shifting members

64, 65 are arranged to the secondary shaft 3 On the axis, it helps to optimize the layout of each component and further shorten the axial distance.

Taking the gear ratio between the ring gear 13 of the first planetary gear set 10 and the sun gear 11: K ₁₀ = 1.909, the gear ratio between the ring gear 23 of the second planetary gear set 20 and the sun gear 21: K ₂₀ = 2.048 The gear ratio of the main and driven wheels 31, 32 of the first fixed-axis gear set 30 is multiplied by the gear ratio of the main and driven wheels 41, 42 of the second fixed-axis gear set 40: Z ₃₁ /Z ₃₂ × Z ₄₁ /Z ₄₂ = 1.555, the gear ratio of the main and driven wheels 51, 52 of the third fixed-axis gear set 50 multiplied by the gear ratio of the main and driven wheels 41, 42 of the second fixed-axis gear set 40: Z ₅₁ /Z ₅₂ × Z ₄₁ / Z ₄₂ =1.0526, the combination of the gears and the shifting components of the transmission, the gear ratio is as follows:

Comparing the two embodiments, in the first and second planetary gear sets 10, 20, the first and second fixed-axis gear sets 30, 40 In the case where the tooth ratios are all the same, the total ratio between the gears of the two embodiments is also the same, but the second embodiment has a better gear ratio distribution.

A one-way clutch 71 can be added that is coupled between the planet carrier 12 of the first planetary gear set 10 and the housing 5 The effect is the same as that of the first embodiment.

Claims

A multi-speed transmission includes an input shaft (1), an output member (2), a countershaft (3), a housing (5), first and second planetary gear sets (10, 20), first and second fixed shaft gear sets (30, 40), first to fifth clutch shifting elements (61, 62, 63, 64, 65) The first and second planetary gear sets (10, 20) are single pinion type planetary gear sets, and have respective sun gears (11, 21) and gear carriers (12, 22) ), the ring gear ( 13 , 23 ), and arranged on the axis of the input shaft ( 1 );

The first and second fixed-axis gear sets (30, 40) are externally-engaged gear sets, and have respective drive wheels (31, 41) and driven wheels ( 32, 42), the driving wheel (31) of the first fixed-axis gear set (30) and the driven wheel (42) of the second fixed-axis gear set (40) are arranged on the input shaft (1) On the axis of the axis, the driven wheel (32) of the first fixed-axis gear set (30) and the driving wheel (41) of the second fixed-axis gear set (40) are connected to each other, and the connecting shaft constitutes a secondary shaft (3) );

a sun gear (21) and a planet carrier (22) of the second planetary gear set (20) and the input shaft (1) and an output member (2) Connected;

a ring gear (13) of the first planetary gear set (10) and a drive wheel of the first fixed-axis gear set (30) (31) Interconnected; the ring gear (23) of the second planetary gear set (20) and the driven wheel (42) of the second fixed gear set (40) are interconnected;

The first clutch shifting member (61) is coupled in series with the sun gear (11) of the first planetary gear set (10) and the input shaft (1) Optionally connecting the two; the second clutch shifting element (62) is coupled in series with the sun gear (11) of the first planetary gear set (10) and the second planetary gear set (20) Planet carrier 22) selectively connecting the two; the third clutch shifting element (63) is coupled in series with the planet carrier (12) of the first planetary gear set (10) and the input shaft (1) Optionally connecting the two;

The fourth clutch shifting element (64) or the planet carrier (12) and the second planetary gear set (20) connected in series with the first planetary gear set (10) The ring gears (23) are selectively connectable between them, or alternatively connected in series between the two via the transmission connection path (8) of the countershaft (3);

The fifth clutch shifting element (65) or the planet carrier (12) and the housing (5) connected in series with the first planetary gear set (10) The planet carrier (12) of the first planetary gear set (10) is selectively braked between, or in series with, a transmission connection path (9) therebetween.
The multi-speed transmission of claim 1 further comprising a third fixed-axis gear set (50); wherein: said third fixed-axis gear set (50 Is an externally engaged gear set, the driving wheel (51) and the driven wheel (52) are respectively arranged on the axes of the input shaft (1) and the counter shaft (3); the first planetary gear set (10) Planetary frame 12) interconnecting with a driving wheel (51) of the third fixed-axis gear set (50), the fourth clutch shifting element (64) being serially connected to the slave of the third fixed-axis gear set (50) Moving wheel (52 Selectively connecting the two to the countershaft (3), the third fixed shaft gear set (50), the fourth clutch shifting element (64), the countershaft (3) and the second fixed axle Gear set ( 40 a transmission connection route between the carrier (12) of the first planetary gear set (10) and the ring gear (23) of the second planetary gear set (20) (8) The fifth clutch shifting member (65) is serially connected between the driven wheel (52) of the third fixed-axis gear set (50) and the housing (5), the third fixed shaft Gear set ( 50 a fifth clutch shifting member (65) constituting a transmission connection path (9) between the carrier (12) of the first planetary gear set (10) to the housing (5), the fifth clutch changing Gear element 65) selectively braking the planet carrier (12) of the first planetary gear set (10).
A multi-speed transmission according to claim 1 or 2, further comprising a one-way clutch (71); characterized by: said one-way clutch (71) Or connected in series between the planet carrier (12) of the first planetary gear set (10) and the housing (5), or in parallel with the fifth clutch shifting element (65) Both ends of the first planetary gear set (10) allow the planet carrier (12) to rotate in the same direction as the input shaft (1), locking the planets of the first planetary gear set (10) Rack (12 ) rotating in the opposite direction of rotation of the input shaft ( 1 ).