Nine-speed automatic transmission

Abstract

The present invention belongs to the technical field of automobile transmission, and relates to a nine-speed automatic transmission, including an input member, an output member, a transmission housing, a first planetary gear, a second planetary gear, a third planetary gear, a first clutch, a second clutch, a third clutch, a fourth clutch, a first brake, a second brake and a third brake. The nine-speed automatic transmission of the present invention realizes further concentration of the distribution of clutches and brakes by rationally combining and arranging four clutches and three brakes, so that the clutches and brakes can be fully nested, so that the arrangement of clutches and brakes can be highly integrated and the axial space of the entire planetary gear mechanism (composed of the first planetary gear, the second planetary gear and the third planetary gear) can be compressed to the maximum extent possible, so that the entire planetary gear mechanism is more compact.

Description

Technical Field

[0001] The invention belongs to the technical field of automobile transmission, and in particular relates to a nine-speed automatic transmission. Background Art

[0002] The mechanism for achieving speed change in the transmission system of an electronically controlled hydraulic automatic transmission generally includes multiple planetary gears. The power of the engine is transmitted to the planetary gear transmission mechanism after passing through the hydraulic torque converter for speed change and output. The size, weight, efficiency and load-bearing capacity of the automatic transmission are directly related to the planetary gear transmission mechanism. The more gears the automatic transmission transmission system has, the lower the fuel consumption of the car and the better the economy. However, as the number of gears increases, the number of planetary gears and the number of operating elements (clutches and brakes) also increase, and the design that meets the theoretical level ratio is even more difficult to achieve. People have been seeking to combine a planetary gear transmission mechanism with a smaller number of planetary gears, clutches and brakes to meet the performance requirements of the car, with a compact structure, greater strength and higher efficiency.

[0003] At present, there are three main 9AT (9-speed automatic transmission) products for passenger cars, namely ZF 9HP, Mercedes-Benz 9G-Tronic and GM 9T50.

[0004] ZF 9HP adopts a scheme of four simple planetary gears, four clutches and two brakes, of which there are two dog-tooth clutches, which have high control requirements. Mercedes-Benz 9G-Tronic adopts a longitudinal scheme of four simple planetary gears, three clutches and three brakes. In this scheme, the clutches and brakes each account for half of the operating elements. The dispersed positions are not easy to nest and are only suitable for longitudinal arrangements that do not require high axial space. GM 9T50 adopts a scheme of three planetary gears, three clutches and four brakes, one of which is a composite gear. The clutches and brakes of this scheme are relatively concentrated, which is suitable for highly nested compression integrated arrangements. One brake is a multi-mode clutch. This scheme has excellent axial arrangement space and is suitable for lateral arrangements.

[0005] The ZF 9HP solution and the Mercedes-Benz 9G-Tronic solution are 4-DOF systems. Each working gear requires three operating elements to be closed, which places high demands on the hydraulic system. In addition, as mentioned above, the ZF 9HP uses two dog-type clutches, which have very high control requirements. The Mercedes-Benz 9G-Tronic solution is more suitable for the longitudinal solution. The GM 9T50 solution uses three clutches and four brakes, one of which is far away from the other clutches. The distribution of clutches and brakes is relatively scattered, so that the clutches and brakes cannot be fully nested, and the layout of clutches and brakes cannot be highly integrated, which makes the axial space of the entire transmission larger and the structure is not compact, which is not conducive to lightweight design and cost reduction. Summary of the invention

[0006] The technical problem to be solved by the present invention is to provide a nine-speed automatic transmission in view of the defects of the existing nine-speed automatic transmission, that is, the axial space is large and the structure is not compact.

[0007] In order to solve the above technical problems, an embodiment of the present invention provides a nine-speed automatic transmission, comprising:

[0008] Input components;

[0009] Output component;

[0010] Transmission housing;

[0011] The first planet row, the second planet row and the third planet row; the first planet row includes a first compound sun gear, a second compound sun gear, a first planetary gear set, a first ring gear and a first planet carrier; the first compound sun gear and the second compound sun gear are externally meshed with the first planetary gear set, the first planetary gear set is internally meshed with the first ring gear, and the first planetary gear set is rotatably supported on the first planet carrier; the second planet row includes a second sun gear, a second planetary gear, a second ring gear and a second planet carrier; the second sun gear is externally meshed with the second planetary gear, and the second planetary gear is internally meshed with the second ring gear. The third planetary gear is internally meshed and driven, and the second planetary gear is rotatably supported on the second planetary carrier; the third planetary gear row includes a third sun gear, a third planetary gear, a third ring gear and a third planetary carrier; the third sun gear is externally meshed and driven with the third planetary gear, the third planetary gear is internally meshed and driven with the third ring gear, and the third planetary gear is rotatably supported on the third planetary carrier; the first ring gear is fixedly connected to the third planetary carrier, the third planetary carrier is fixedly connected to the output member, the second planetary carrier is fixedly connected to the third ring gear, the second sun gear is fixedly connected to the input member, and the third sun gear is fixedly connected to the transmission housing;

[0012] a first clutch, a second clutch, a third clutch, a fourth clutch, a first brake, a second brake and a third brake, wherein the input member is connected to the second sun gear of the compound row through the first clutch, the input member is connected to the first planet carrier through the second clutch, the first planet carrier is connected to the second ring gear through the third clutch, the second sun gear of the compound row is connected to the transmission case through the first brake, the first sun gear of the compound row is connected to the transmission case through the second brake, the first planet carrier is connected to the transmission case through the third brake, and the fourth clutch is connected between any two of the first sun gear of the compound row, the second sun gear of the compound row, the first planet carrier and the first ring gear;

[0013] The first clutch, the second clutch, the third clutch, the fourth clutch, the first brake, the second brake, and the third brake are selectively engaged or disengaged to produce nine forward speed ratios and one reverse speed ratio between the input member and the output member.

[0014] The nine-speed automatic transmission of the embodiment of the present invention is provided with three planetary gears and seven operating elements (four clutches and three brakes). By selectively engaging or disengaging the seven operating elements, nine forward gear ratios and one reverse gear ratio can be generated between the input member and the output member, thereby realizing nine forward gears and one reverse gear of the nine-speed transmission. Compared with the existing 4-DOF 9AT automatic transmission composed of four planetary gears, the number of planetary gears and the number of degrees of freedom are reduced by one, which simplifies the transmission system of the nine-speed automatic transmission and reduces the difficulty of developing the hydraulic control system.

[0015] Compared with the general 9T50 solution, one clutch is added (one brake is reduced), and the distribution of clutches and brakes is further concentrated by rationally combining and arranging four clutches and three brakes, so that the clutches and brakes can be fully nested, so that the arrangement of clutches and brakes is highly integrated and the axial space of the entire planetary gear mechanism (composed of the first planetary row, the second planetary row and the third planetary row) is compressed to the maximum extent possible, making the entire planetary gear mechanism more compact. In addition, compared with the general 9T50 solution, the present invention uses more clutches (fewer brakes) which will be more conducive to multi-speed expansion by adding planetary rows or adding more operating parts in the future.

[0016] The third sun gear is directly connected to the transmission housing, thereby avoiding direct impact on the transmission housing caused by the third sun gear being connected to the transmission housing via a brake in the prior art, thereby improving the load condition of the transmission housing.

[0017] In addition, compared with the 4-planet row scheme of ZF ZF 9HP and Mercedes-Benz 9G-Tronic, this patent adopts a 3-planet row structure, in which the first planet row is a composite row including two sun gears and sharing a planet carrier, which has a more compact structure and can better achieve lightweight in addition to the axial size advantage. In addition, compared with the 4-simple planet row scheme of ZF ZF 9HP and Mercedes-Benz 9G-Tronic, the present invention also saves a gear ring, which not only has the advantage of lightweight but also significantly reduces the cost. Moreover, the composite row used by the first planet row is not a Lavinia composite row. Compared with the Lavinia composite row, the first planet row of the present invention has one less set of inner planetary gears, which has the advantages of lightweight and low cost.

[0018] Optionally, only two of the first clutch, the second clutch, the third clutch, the fourth clutch, the first brake, the second brake and the third brake are selectively engaged during each shift operation.

[0019] Optionally, by engaging the third clutch and the third brake, the first clutch, the second clutch, the fourth clutch, the first brake and the second brake are disengaged to produce a first gear ratio between the input member and the output member;

[0020] by engaging the third clutch and the second brake, and disengaging the first clutch, the second clutch, the fourth clutch, the first brake, and the third brake to produce a second speed ratio between the input member and the output member;

[0021] by engaging the third clutch and the first brake, and disengaging the first clutch, the second clutch, the second brake, and the third brake to produce a 3rd speed ratio between the input member and the output member;

[0022] By engaging the third clutch and the fourth clutch, disengaging the first clutch, the second clutch, the first brake, the second brake, and the third brake, a 4th speed ratio is generated between the input member and the output member;

[0023] by engaging the first clutch and the third clutch, and disengaging the second clutch, the fourth clutch, the first brake, the second brake, and the third brake to produce a fifth speed ratio between the input member and the output member;

[0024] engaging the second clutch and the third clutch and disengaging the first clutch, the fourth clutch, the first brake, the second brake, and the third brake to produce a 6th speed ratio between the input member and the output member;

[0025] by engaging the first clutch and the second clutch, and disengaging the third clutch, the fourth clutch, the first brake, the second brake, and the third brake to produce a 7th speed ratio between the input member and the output member;

[0026] by engaging the second clutch and the first brake, and disengaging the first clutch, the third clutch, the fourth clutch, the second brake, and the third brake to produce an 8th speed ratio between the input member and the output member;

[0027] A 9th speed ratio is generated between the input member and the output member by engaging the second clutch and the second brake and disengaging the first clutch, the third clutch, the fourth clutch, the first brake, and the third brake.

[0028] Optionally, a reverse speed ratio is established between the input member and the output member by engaging the first clutch and the third brake and disengaging the second clutch, the third clutch, the fourth clutch, the first brake, and the second brake.

[0029] Optionally, the first planetary gear, the second planetary gear and the third planetary gear are coaxially arranged.

[0030] Optionally, the second planetary gear row is axially arranged between the first planetary gear row and the third planetary gear row.

[0031] Optionally, the first clutch, the second clutch, the third clutch and the fourth clutch are multi-plate wet clutches or dog clutches.

[0032] Optionally, the first brake, the second brake and the third brake are drum brakes, multi-plate wet brakes, multi-mode clutches or one-way clutches.

[0033] Optionally, the first gear ring is spline-connected, welded or integrally formed with the third planet carrier;

[0034] The third planet carrier is spline-connected, welded or integrally formed with the output member;

[0035] The second planet carrier is spline-connected, welded or integrally formed with the third ring gear;

[0036] The second sun gear is spline-connected, welded or integrally formed with the input member;

[0037] The third sun gear is spline-connected, welded or integrally formed with the transmission housing.

[0038] Optionally, the first planetary gear set includes a first compound row of planetary gears and a second compound row of planetary gears, the first compound row of sun gear is externally meshed with the first compound row of planetary gears for transmission, the second compound row of sun gear is externally meshed with the second compound row of planetary gears for transmission, the second compound row of planetary gears is internally meshed with the first gear ring for transmission, and the first compound row of planetary gears and the second compound row of planetary gears are rotatably supported on the first planet carrier. BRIEF DESCRIPTION OF THE DRAWINGS

[0039] Figure 1 is a simplified structural diagram of a nine-speed automatic transmission provided by a first embodiment of the present invention;

[0040] Figure 2 This is a schematic diagram of power transmission of the first gear of a nine-speed automatic transmission provided by the first embodiment of the present invention;

[0041] Figure 3 This is a schematic diagram of the second gear power transmission of a nine-speed automatic transmission provided by the first embodiment of the present invention;

[0042] Figure 4 It is a schematic diagram of power transmission of 3 gears of a nine-speed automatic transmission provided by the first embodiment of the present invention;

[0043] Figure 5 It is a schematic diagram of power transmission of 4 gears of a nine-speed automatic transmission provided by the first embodiment of the present invention;

[0044] Figure 6 It is a schematic diagram of 5-speed power transmission of a nine-speed automatic transmission provided by the first embodiment of the present invention;

[0045] Figure 7 It is a schematic diagram of 6-speed power transmission of a 9-speed automatic transmission provided by the first embodiment of the present invention;

[0046] Figure 8 It is a schematic diagram of power transmission of 7 gears of a nine-speed automatic transmission provided by the first embodiment of the present invention;

[0047] Fig. 9 It is a schematic diagram of 8-speed power transmission of a nine-speed automatic transmission provided by the first embodiment of the present invention;

[0048] Fig.10 It is a schematic diagram of 9-speed power transmission of a 9-speed automatic transmission provided by the first embodiment of the present invention;

[0049] Fig.11 It is a schematic diagram of reverse power transmission of a nine-speed automatic transmission provided by the first embodiment of the present invention;

[0050] Fig.12 is a simplified structural diagram of a nine-speed automatic transmission provided by a second embodiment of the present invention;

[0051] Fig.13 is a simplified structural diagram of a nine-speed automatic transmission provided by a third embodiment of the present invention;

[0052] Fig.14 1 is a simplified structural diagram of a nine-speed automatic transmission provided in a fourth embodiment of the present invention.

[0053] The reference numerals in the specification are as follows:

[0054] 1. Input member; 2. Output member; 3. First brake; 4. Second brake; 5. Third brake; 6. First clutch; 7. Second clutch; 8. Third clutch; 9. Fourth clutch; 10. First sun gear of compound row; 11. First planetary carrier; 12. First planetary gear set; 13. Second sun gear of compound row; 14. First ring gear; 15. Second ring gear; 16. Second planetary gear; 17. Second sun gear; 18. Second planetary carrier; 19. Third sun gear; 20. Third planetary gear; 21. Third planetary carrier; 22. Third ring gear; 23. Transmission case. DETAILED DESCRIPTION

[0055] In order to make the technical problems, technical solutions and beneficial effects solved by the present invention more clearly understood, the present invention is further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not used to limit the present invention.

[0056] like Figure 1 As shown, the nine-speed automatic transmission provided by the first embodiment of the present invention includes an input member 1, an output member 2, a transmission housing 23, a first planetary gear, a second planetary gear, a third planetary gear, a first clutch 6, a second clutch 7, a third clutch 8, a fourth clutch 9, a first brake 3, a second brake 4 and a third brake 5. In addition, the first clutch 6, the second clutch 7, the third clutch 8 and the fourth clutch 9 are also represented by C1, C2, C3 and C4 respectively in the figure, and the first brake 3, the second brake 4 and the third brake 5 are also represented by B1, B2 and B3 respectively in the figure.

[0057] In this embodiment, the first planetary row is a compound planetary row, and the second planetary row and the third planetary row are single planetary rows (simple planetary rows). Preferably, the first planetary row, the second planetary row and the third planetary row are coaxially arranged. The second planetary row is axially arranged between the first planetary row and the third planetary row.

[0058] The first planetary gear set includes a first compound sun gear 10, a second compound sun gear 13, a first planetary gear set 12, a first ring gear 14 and a first planetary carrier 11. The first compound sun gear 10 and the second compound sun gear 13 are externally meshed with the first planetary gear set 12 for transmission, the first planetary gear set 12 is internally meshed with the first ring gear 14 for transmission, and the first planetary gear set 12 is rotatably supported on the first planetary carrier 11 through rolling or sliding bearings. Preferably, the first planetary gear set 12 includes a first compound planetary gear and a second compound planetary gear, the first compound sun gear 10 is externally meshed with the first compound planetary gear, the second compound sun gear 13 is externally meshed with the second compound planetary gear, the second compound planetary gear is internally meshed with the first ring gear 14 for transmission, and the first compound planetary gear and the second compound planetary gear are rotatably supported on the first planetary carrier 11.

[0059] The second planetary gear set includes a second sun gear 17, a second planetary gear 16, a second ring gear 15 and a second planet carrier 18. The second sun gear 17 is externally meshed with the second planetary gear 16, the second planetary gear 16 is internally meshed with the second ring gear 15, and the second planetary gear 16 is rotatably supported on the second planet carrier 18 via rolling or sliding bearings.

[0060] The third planetary gear includes a third sun gear 19, a third planetary gear 20, a third ring gear 22 and a third planet carrier 21; the third sun gear 19 and the third planetary gear 20 are externally meshed for transmission, the third planetary gear 20 and the third ring gear 22 are internally meshed for transmission, and the third planetary gear 20 is rotatably supported on the third planet carrier 21 by rolling or sliding bearings.

[0061] like Figure 1 As shown, the first ring gear 14 is fixedly connected to the third planetary carrier 21, the third planetary carrier 21 is fixedly connected to the output member 2, the second planetary carrier 18 is fixedly connected to the third ring gear 22, the second sun gear 17 is fixedly connected to the input member 1, and the third sun gear 19 is fixedly connected to the transmission housing 23. The fixed connection here can be spline connection, welding or integral formation. That is, the first ring gear 14 is spline connected, welded or integrally formed with the third planetary carrier 21, the third planetary carrier 21 is spline connected, welded or integrally formed with the output member 2, the second planetary carrier 18 is spline connected, welded or integrally formed with the third ring gear 22, the second sun gear 17 is spline connected, welded or integrally formed with the input member 1, and the third sun gear 19 is spline connected, welded or integrally formed with the transmission housing 23.

[0062] like Figure 1 As shown, the input member 1 is connected to the second sun gear 13 of the compound row through the first clutch 6, the input member 1 is connected to the first planetary carrier 11 through the second clutch 7, the first planetary carrier 11 is connected to the second ring gear 15 through the third clutch 8, the second sun gear 13 of the compound row is connected to the transmission housing 23 through the first brake 3, the first sun gear 10 of the compound row is connected to the transmission housing 23 through the second brake 4, the first planetary carrier 11 is connected to the transmission housing 23 through the third brake 5, and the fourth clutch 9 is connected between the second sun gear 13 of the compound row and the first planetary carrier 11.

[0063] The function of the clutch is to achieve fixed connection and separation between two components by engagement or separation. In this embodiment, a multi-plate wet clutch or a dog clutch can be used. That is, the first clutch 6, the second clutch 7, the third clutch 8 and the fourth clutch 9 are multi-plate wet clutches or dog clutches.

[0064] The function of the brake is to achieve the connection or separation of the component and the transmission housing 23 by engaging or disengaging, so as to brake or separate the component. In this embodiment, a drum brake, a multi-plate wet brake, a multi-mode clutch or a one-way clutch can be used. That is, the first brake 3, the second brake 4 and the third brake 5 are drum brakes, multi-plate wet brakes, multi-mode clutches or one-way clutches.

[0065] In this embodiment, the first clutch 6, the second clutch 7, the third clutch 8, the fourth clutch 9, the first brake 3, the second brake 4 and the third brake 5 are selectively engaged or disengaged to generate nine forward speed ratios and one reverse speed ratio between the input member 1 and the output member 2.

[0066] The nine-speed automatic transmission of this embodiment is composed of three planetary gears to form a three-degree-of-freedom system. Only two operating elements need to be closed for each gear shift operation. That is, only two of the first clutch 6, the second clutch 7, the third clutch 8, the fourth clutch 9, the first brake 3, the second brake 4 and the third brake 5 are selectively engaged for each gear shift operation. In this way, compared with other four-degree-of-freedom 9AT systems that require three operating elements to be engaged at the same time for each gear position, this embodiment is a three-degree-of-freedom system, and only two operating elements need to be engaged at the same time for each gear shift operation, which reduces the difficulty of developing and designing the hydraulic control system.

[0067] In this embodiment, the operation logic of the first clutch 6, the second clutch 7, the third clutch 8, the fourth clutch 9, the first brake 3, the second brake 4 and the third brake 5 is shown in the following Table 1:

[0068] Table 1

[0069]

[0070]

[0071] In Table 1, ● Indicates that the operating element is engaged, and a blank indicates that the operating element is disengaged. K0 is the ratio of the number of teeth of the first gear ring 14 to the first sun gear 10 of the compound row, K1 is the ratio of the number of teeth of the first gear ring 14 to the second sun gear 13 of the compound row. k2 is the ratio of the number of teeth of the second gear ring 15 to the second sun gear 17, and k3 is the ratio of the number of teeth of the third gear ring 22 to the third sun gear 19.

[0072] See also Figures 2 to 11 Under the operating logic of Table 1, the power transmission routes of each gear of the nine-speed automatic transmission are as follows (the lines on the transmission routes are bolded).

[0073] (1) 1st gear

[0074] like Figure 2As shown, when the third clutch 8 and the third brake 5 are engaged (other brakes and clutches are disengaged), the first gear is realized, and the speed ratio of the first gear is: i1 = [(1+K2)*(1+K3)] / K3. When the third clutch 8 is engaged, the engagement of the third brake 5 causes the first planetary carrier 11 and the second ring gear 15 to brake simultaneously, and the third sun gear 19 is in a constant braking state, so that the second planetary gear and the third planetary gear both achieve single-degree-of-freedom output, and the power is decelerated by the second planetary gear and then connected to the third planetary gear for secondary deceleration.

[0075] The specific power transmission route is: input from the input member 1 → second sun gear 17 → second planetary gear 16 → second planetary carrier 18 → third ring gear 22 → third planetary gear 20 → third planetary carrier 21 → output from the output member 2 .

[0076] (2) 2nd gear

[0077] like Figure 3 As shown, when the third clutch 8 and the second brake 4 are engaged (other brakes and clutches are disengaged), the second gear is realized, and the speed ratio of the second gear is: i2 = [(1+K0)*(1+K2)+K3*(1+K0+K2)] / [K3*(1+K0)]. The engagement of the second brake 4 causes the first sun gear 10 of the compound row to brake, and the third sun gear 19 is in a normal braking state. When the third clutch 8 is engaged, the power transmission route is divided into two:

[0078] ① Input from input member 1 → second sun gear 17 → second planetary gear 16 → second planetary carrier 18 → third ring gear 22 → third planetary gear 20 → third planetary carrier 21 → output member 2 for output.

[0079] ② Input from input member 1 → second sun gear 17 → second planetary gear 16 → second ring gear 15 → third clutch 8 → first planetary carrier 11 → first planetary gear set 12 → first ring gear 14 → third planetary carrier 21 → output member 2 for output.

[0080] (3) 3rd gear

[0081] like Figure 4 As shown, when the third clutch 8 and the first brake 3 are engaged (other brakes and clutches are disengaged), the third gear is realized, and the speed ratio of the third gear is: i3 = [(1+K1)*(1+K2)+K3*(1+K1+K2)] / [K3*(1+K1)]. The engagement of the first brake 3 causes the second sun gear 13 of the compound row to brake, and the third sun gear 19 is in a normal braking state. When the third clutch 8 is engaged, the power transmission route is divided into two:

[0082] ① Input from input member 1 → second sun gear 17 → second planetary gear 16 → second planetary carrier 18 → third ring gear 22 → third planetary gear 20 → third planetary carrier 21 → output member 2 for output.

[0083] ② Input from input member 1 → second sun gear 17 → second planetary gear 16 → second ring gear 15 → third clutch 8 → first planetary carrier 11 → first planetary gear set 12 → first ring gear 14 → third planetary carrier 21 → output member 2 for output.

[0084] (4) 4th gear

[0085] like Figure 5 As shown, when the third clutch 8 and the fourth clutch 9 are engaged (other brakes and clutches are disengaged), the 4th gear is realized, and the speed ratio of the 4th gear is: i4 = (1 + K2 + K3) / K3. The engagement of the fourth clutch 9 enables the first planetary gear to rotate as a whole, and the engagement of the third clutch 8 enables the second ring gear 15 to be connected with the third ring gear 22 through the first rotation as a whole, thereby realizing single-degree-of-freedom output. There are two power transmission routes under this gear, namely:

[0086] ① Input from input member 1 → second sun gear 17 → second planetary gear 16 → second planetary carrier 18 → third ring gear 22 → third planetary gear 20 → third planetary carrier 21 → output member 2 for output.

[0087] ② Input from input member 1 → second sun gear 17 → second planetary gear 16 → second ring gear 15 → third clutch 8 → first planetary gear rotation as a whole → third planetary carrier 21 → output member 2 for output.

[0088] (5) 5th gear

[0089] like Figure 6 As shown, when the first clutch 6 and the third clutch 8 are engaged (other brakes and clutches are disengaged), the fifth gear is realized, and the speed ratio of the fifth gear is: I5 = [(1+K1)*(1+K2)+K3*(1+K1+K2)] / [K3*(1+K1+K2)]. The third sun gear 19 is in a normal braking state, and the engagement of the first clutch 6 and the third clutch 8 enables three power transmission routes:

[0090] ① Input from input member 1 → second sun gear 17 → second planetary gear 16 → second planetary carrier 18 → third ring gear 22 → third planetary gear 20 → third planetary carrier 21 → output member 2 for output.

[0091] ② Input from input member 1 → second sun gear 17 → second planetary gear 16 → second ring gear 15 → third clutch 8 → first planetary carrier 11 → first planetary gear set 12 → first ring gear 14 → third planetary carrier 21 → output member 2 for output.

[0092] ③ Input from input member 1 → first clutch 6 → second compound sun gear 13 → first planetary gear set 12 → first ring gear 14 → third planetary carrier 21 → output member 2 for output.

[0093] (6) 6th gear

[0094] like Figure 7 As shown, when the second clutch 7 and the third clutch 8 are engaged (other brakes and clutches are disengaged), the 6th gear is realized, and the 6th gear speed ratio is i6=(1+K3) / K3. The second clutch 7 and the third clutch 8 are engaged at the same time to make the second planetary gear achieve overall rotation, and the third sun gear 19 is in a constant braking state to make the third planetary gear achieve single-degree-of-freedom output. The power is input by the second planetary gear rotation as a whole, and is output after single-stage reduction through the third planetary gear.

[0095] The specific power transmission route is: input from the input member 1 → the second planetary gear set rotates as a whole → the third ring gear 22 → the third planetary gear 20 → the third planetary carrier 21 → the output member 2 for output.

[0096] (7) 7th gear

[0097] like Figure 8 As shown, when the first clutch 6 and the second clutch 7 are engaged (other brakes and clutches are disengaged), the 7th gear is realized, and the 7th gear is a direct gear with a speed ratio of i7 = 1. When the first clutch 6 and the second clutch 7 are engaged at the same time, the first planetary gear rotates as a whole.

[0098] The specific power transmission route is: input from input member 1 → first planetary gear rotates at a constant speed as a whole → first planetary carrier 11 outputs at a constant speed → output member 2 outputs. Output member 2, third planetary carrier 21 and first planetary carrier 11 are fixed as one body, so output member 2 and input member 1 have the same speed.

[0099] (8) 8th gear

[0100] like Fig. 9 As shown, when the second clutch 7 and the first brake 3 are engaged (other brakes and clutches are disengaged), the 8th gear is realized, and the 8th gear speed ratio is i8=K1 / (1+K1). The engagement of the second clutch 7 allows the power to be input from the first planetary gear carrier, and the engagement of the first brake 3 allows the second sun gear 13 of the compound gear to be braked, so that the first planetary gear achieves the first single-degree-of-freedom speed increase output.

[0101] The specific power transmission route is: input from the input member 1 → the second clutch 7 → the first planetary carrier 11 → the first planetary gear set 12 element → the first planetary carrier 11 → the third planetary carrier 21 → the output member 2 for output.

[0102] (9) 9th gear

[0103] like Fig.10 As shown, when the second clutch 7 and the second brake 4 are engaged (other brakes and clutches are disengaged), the 9th gear is realized, and the speed ratio of the 9th gear is i9=K0 / (1+K0). The engagement of the second clutch 7 allows the power to be input from the first planetary gear carrier, and the engagement of the second brake 4 allows the first sun gear 10 of the compound gear to be braked, so that the first planetary gear can achieve the second single degree of freedom speed increase output.

[0104] The specific power transmission route is: input from the input member 1 → the second clutch 7 → the first planetary carrier 11 → the first planetary gear set 12 → the first planetary carrier 11 → the third planetary carrier 21 → the output member 2 for output.

[0105] (10) Reverse gear

[0106] like Fig.11 As shown, when the first clutch 6 and the third brake 5 are engaged (other brakes and clutches are disengaged), the reverse gear is realized, and the reverse gear speed ratio is iR=-K1. The engagement of the first clutch 6 allows the power to be input from the second sun gear 13 of the compound row, and the engagement of the third brake 5 allows the first planetary carrier 11 to brake, so that the first planetary row achieves a single degree of freedom negative deceleration output.

[0107] The specific power transmission route is: input from the input member 1 → first clutch 6 → second compound sun gear 13 → first planetary gear set 12 → first ring gear 14 → third planetary carrier 21 → output member 2 for output.

[0108] The nine-speed automatic transmission of the embodiment of the present invention is provided with three planetary gears and seven operating elements (four clutches and three brakes). By selectively engaging or disengaging the seven operating elements, nine forward gear ratios and one reverse gear ratio can be generated between the input member 1 and the output member 2, thereby realizing nine forward gears and one reverse gear of the nine-speed transmission. Compared with the existing 4-DOF 9AT automatic transmission composed of four planetary gears, the number of planetary gears and the number of degrees of freedom are reduced by one, which simplifies the transmission system of the nine-speed automatic transmission and reduces the difficulty of developing the hydraulic control system.

[0109] Compared with the general 9T50 solution, one clutch is added (one brake is reduced), and the distribution of clutches and brakes is further concentrated by rationally combining and arranging four clutches and three brakes, so that the clutches and brakes can be fully nested, so that the arrangement of clutches and brakes is highly integrated and the axial space of the entire planetary gear mechanism (composed of the first planetary row, the second planetary row and the third planetary row) is compressed to the maximum extent possible, making the entire planetary gear mechanism more compact. In addition, compared with the general 9T50 solution, the present invention uses more clutches (fewer brakes) which will be more conducive to multi-speed expansion by adding planetary rows or adding more operating parts in the future.

[0110] The third sun gear 19 is directly connected to the transmission housing 23 , which avoids direct impact on the transmission housing 23 caused by the third sun gear 19 being connected to the transmission housing 23 via a brake in the prior art, thereby improving the load condition of the transmission housing 23 .

[0111] In addition, compared with the 4-planet row scheme of ZF ZF 9HP and Mercedes-Benz 9G-Tronic, this patent adopts a 3-planet row structure, in which the first planet row is a composite row including two sun gears and sharing a planet carrier, which has a more compact structure and can better achieve lightweight in addition to the axial size advantage. In addition, compared with the 4-simple planet row scheme of ZF ZF 9HP and Mercedes-Benz 9G-Tronic, the present invention also saves a gear ring, which not only has the advantage of lightweight but also significantly reduces the cost. Moreover, the composite row used for the first planet row is not a Lavinia composite row. Compared with the Lavinia composite row, the first planet of the present invention has one less set of inner planetary gears, which has the advantages of lightweight and low cost.

[0112] Fig.12 A schematic diagram of a nine-speed automatic transmission provided in accordance with a second embodiment of the present invention. Figure 1 The first embodiment shown is different in that the fourth clutch 9 is connected between the first ring gear 14 and the first planet carrier 11 .

[0113] Fig.13 A schematic diagram of a nine-speed automatic transmission provided in accordance with a third embodiment of the present invention. Figure 1 The first embodiment shown is different in that the fourth clutch 9 is connected between the first composite sun gear 10 and the first planet carrier 11 .

[0114] Fig.14 A schematic diagram of a nine-speed automatic transmission provided in accordance with a fourth embodiment of the present invention. Figure 1 The difference of the first embodiment shown is that the fourth clutch 9 is connected between the first compound sun gear 10 and the second compound sun gear 13 .

[0115] exist Figure 12 to Figure 14 In the embodiment shown, the shift operation logic and Figure 1 The embodiments shown are identical.

[0116] In fact, the fourth clutch 9 can be connected between any two of the first compound sun gear 10, the second compound sun gear 13, the first planet carrier 11 and the first ring gear 14. The function of the fourth clutch 9 is to enable the first planet gear to rotate as a whole.

[0117] Therefore, in another embodiment not shown in the figure, the fourth clutch may also be connected between the first sun gear and the first ring gear of the compound row.

[0118] In another embodiment not shown in the figure, the fourth clutch may also be connected between the second sun gear of the compound row and the first ring gear.

[0119] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present invention should be included in the protection scope of the present invention.

Claims

1. A nine-speed automatic transmission, characterized in that: include: Input components; Output component; Transmission housing; The first planet row, the second planet row and the third planet row; the first planet row includes a first compound sun gear, a second compound sun gear, a first planetary gear set, a first ring gear and a first planet carrier; the first compound sun gear and the second compound sun gear are externally meshed with the first planetary gear set, the first planetary gear set is internally meshed with the first ring gear, and the first planetary gear set is rotatably supported on the first planet carrier; the second planet row includes a second sun gear, a second planetary gear, a second ring gear and a second planet carrier; the second sun gear is externally meshed with the second planetary gear, and the second planetary gear is internally meshed with the second ring gear. The third planetary gear is internally meshed and driven, and the second planetary gear is rotatably supported on the second planetary carrier; the third planetary gear row includes a third sun gear, a third planetary gear, a third ring gear and a third planetary carrier; the third sun gear is externally meshed and driven with the third planetary gear, the third planetary gear is internally meshed and driven with the third ring gear, and the third planetary gear is rotatably supported on the third planetary carrier; the first ring gear is fixedly connected to the third planetary carrier, the third planetary carrier is fixedly connected to the output member, the second planetary carrier is fixedly connected to the third ring gear, the second sun gear is fixedly connected to the input member, and the third sun gear is fixedly connected to the transmission housing; a first clutch, a second clutch, a third clutch, a fourth clutch, a first brake, a second brake and a third brake, wherein the input member is connected to the second sun gear of the compound row through the first clutch, the input member is connected to the first planet carrier through the second clutch, the first planet carrier is connected to the second ring gear through the third clutch, the second sun gear of the compound row is connected to the transmission case through the first brake, the first sun gear of the compound row is connected to the transmission case through the second brake, the first planet carrier is connected to the transmission case through the third brake, and the fourth clutch is connected between any two of the first sun gear of the compound row, the second sun gear of the compound row, the first planet carrier and the first ring gear; The first clutch, the second clutch, the third clutch, the fourth clutch, the first brake, the second brake, and the third brake are selectively engaged or disengaged to produce nine forward speed ratios and one reverse speed ratio between the input member and the output member.

2. The nine-speed automatic transmission according to claim 1, characterized in that: Only two of the first clutch, the second clutch, the third clutch, the fourth clutch, the first brake, the second brake, and the third brake are selectively engaged in each shift operation.

3. The nine-speed automatic transmission according to claim 2, characterized in that: By engaging the third clutch and the third brake, the first clutch, the second clutch, the fourth clutch, the first brake and the second brake are disengaged to produce a first gear ratio between the input member and the output member; by engaging the third clutch and the second brake, and disengaging the first clutch, the second clutch, the fourth clutch, the first brake, and the third brake to produce a second speed ratio between the input member and the output member; by engaging the third clutch and the first brake, and disengaging the first clutch, the second clutch, the second brake, and the third brake to produce a 3rd speed ratio between the input member and the output member; By engaging the third clutch and the fourth clutch, disengaging the first clutch, the second clutch, the first brake, the second brake, and the third brake, a 4th speed ratio is generated between the input member and the output member; by engaging the first clutch and the third clutch, and disengaging the second clutch, the fourth clutch, the first brake, the second brake, and the third brake to produce a fifth speed ratio between the input member and the output member; engaging the second clutch and the third clutch and disengaging the first clutch, the fourth clutch, the first brake, the second brake, and the third brake to produce a 6th speed ratio between the input member and the output member; by engaging the first clutch and the second clutch, and disengaging the third clutch, the fourth clutch, the first brake, the second brake, and the third brake to produce a 7th speed ratio between the input member and the output member; by engaging the second clutch and the first brake, and disengaging the first clutch, the third clutch, the fourth clutch, the second brake, and the third brake to produce an 8th speed ratio between the input member and the output member; A 9th speed ratio is generated between the input member and the output member by engaging the second clutch and the second brake and disengaging the first clutch, the third clutch, the fourth clutch, the first brake, and the third brake.

4. The nine-speed automatic transmission according to claim 2 or 3, characterized in that: A reverse speed ratio is established between the input member and the output member by engaging the first clutch and the third brake and disengaging the second clutch, the third clutch, the fourth clutch, the first brake, and the second brake.

5. The nine-speed automatic transmission according to claim 1, characterized in that: The first planetary gear, the second planetary gear and the third planetary gear are coaxially arranged.

6. The nine-speed automatic transmission according to claim 5, characterized in that: The second planetary gear is arranged between the first planetary gear and the third planetary gear in the axial direction.

7. The nine-speed automatic transmission according to claim 1, characterized in that: The first clutch, the second clutch, the third clutch and the fourth clutch are multi-plate wet clutches or dog clutches.

8. The nine-speed automatic transmission according to claim 1, characterized in that: The first brake, the second brake and the third brake are drum brakes, multi-plate wet brakes, multi-mode clutches or one-way clutches.

9. The nine-speed automatic transmission according to claim 1, characterized in that: The first ring gear is spline-connected, welded or integrally formed with the third planet carrier; The third planet carrier is spline-connected, welded or integrally formed with the output member; The second planet carrier is spline-connected, welded or integrally formed with the third ring gear; The second sun gear is spline-connected, welded or integrally formed with the input member; The third sun gear is spline-connected, welded or integrally formed with the transmission housing.

10. The nine-speed automatic transmission according to claim 1, characterized in that: The first planetary gear set includes a first compound row planetary gear and a second compound row planetary gear, the first compound row sun gear is externally meshed with the first compound row planetary gear for transmission, the second compound row sun gear is externally meshed with the second compound row planetary gear for transmission, the second compound row planetary gear is internally meshed with the first gear ring for transmission, and the first compound row planetary gear and the second compound row planetary gear are rotatably supported on the first planet carrier.

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