JPS6118062B2 - - Google Patents

Description

[Detailed description of the invention]

The present invention relates to a transmission used in automobiles and the like, and more particularly to an automatic transmission for a vehicle in which a transmission mechanism includes a planetary gear mechanism to obtain multi-speed gear ratios including overdrive. In recent years, as automobile roads have improved, there has been a demand for adding an overdrive stage to general-purpose multi-speed transmissions in order to reduce fuel consumption during high-speed driving. Conventionally, few overdrive devices have been proposed that meet these demands because their internal structures are complicated and impractical. An object of the present invention is to include a planetary gear mechanism that can be easily added to a general-purpose multi-speed transmission,
It is an object of the present invention to obtain a compact, highly efficient, highly reliable transmission with a multi-stage gear ratio including a practically satisfactory overdrive gear ratio. Still another object of the present invention is to provide a one-way clutch between the sun gear and ring gear of the planetary gear mechanism to obtain an overdrive ratio. An embodiment of the present invention will be described with reference to the drawings.
In Fig. 1, 100 is a torque converter, 2
00 is an automatic transmission with 3 forward speeds and 1 reverse speed, 300 is an overdrive device, and torque converter 1
00 and the overdrive device 300 are connected via an input shaft 6. Overdrive device 300
and automatic transmission 200 are connected via shaft 7. The shaft 7 is also the output shaft of the overdrive device 300 and the input shaft of the automatic transmission 200. A torque converter 100 includes a pump impeller 2 and a turbine runner 3 connected to an output shaft 1 of a prime mover.
It consists of a one-way clutch 5 and a stator 4 supported by the one-way clutch 5. When the speed difference between the pump impeller 2 and the turbine runner 3 is large, the stator 4 rectifies the fluid flow to generate a large torque that is greater than the input torque to the turbine runner 3. Outputs torque. The automatic transmission 200 has an input shaft 7 (output shaft of the overdrive device 300), intermediate shafts 8 and 9, and a first
The second planetary gear mechanism 30 and 40 and the output shaft 10 are arranged concentrically, and two clutch devices 11, 12, three brake devices 14,
15, 16, and two one-way clutches 18, 19. The first planetary gear mechanism 30 has a sun gear 31 and a ring gear 33.
1 and 33, and a carrier 34 that rotatably supports the planetary pinion 32. carrier 34
When the sun gear 31 is rotated in the right direction while being fixed, the ring gear 33 rotates in the opposite direction to the sun gear 31 via the planetary pinion 32. The second planetary gear mechanism 40 has a sun gear 41 and a ring gear 4.
3, a planetary pinion 42 that meshes with both gears 41 and 43, and a carrier 44 that rotatably supports the planetary pinion 42. When the sun gear 41 is fixed and the ring gear 43 is rotated in the right direction, the carrier 44 is rotated to the ring gear 43 via the planetary pinion 42.
rotate in the same direction. A clutch device 11 is provided between the input shaft 7 and the intermediate shaft 8, and a clutch device 12 is provided between the input shaft 7 and the intermediate shaft 9.
is connected to the ring gear 43 of the second planetary gear mechanism 40, and the intermediate shaft 9 is connected to the sun gears 31 and 41 of the first and second planetary gear mechanisms to connect the brake device 14 and the brake device 15 via the one-way clutch 18. It is equipped with The ring gear 33 of the first planetary gear mechanism 30 and the carrier 44 of the second planetary gear mechanism 40 are connected to the output shaft 10 . The carrier 34 of the first planetary gear mechanism 30 is equipped with a one-way clutch 19 and a brake device 16. Here, the clutch devices 11 and 12 detachably connect the input shaft 7 and the intermediate shaft 8, and the input shaft 7 and the intermediate shaft 9, respectively, by means of a pressure oil operating mechanism. brake device 14,
Reference numerals 15 and 16 stop the rotation of each component of the first and second planetary gear mechanisms 30 and 40 by means of a hydraulic hydraulic mechanism. The overdrive device 300 has an input shaft 6 connected to the turbine runner 3 of the torque converter 100, a third planetary gear mechanism 50, and an output shaft 7 (input shaft of the automatic transmission 200) arranged concentrically. The clutch device 13 includes one clutch device 13, one brake device 17, and one one-way clutch 20. The third planetary gear mechanism 50 has a sun gear 51 and a ring gear 53, a planetary pinion 52 that meshes with these gears 51 and 53, and a carrier 54 that rotatably supports the planetary pinion 52. . When the sun gear 51 is fixed and the carrier 54 is rotated in the right direction, the ring gear 53 rotates in the same direction as the carrier 54 via the planetary pinion 52. In Figure 2,
The input shaft 6 connected to the turbine runner 3 of the torque converter 100 is connected to the carrier 54 of the third planetary gear mechanism 50, and the ring gear 53 is connected to the hub 61 which is spline-fitted to the friction plate 60 of the clutch device 13. There is. The sun gear 51 is connected to a cylinder 62, which is connected at one end to a hub 65 which is spline-fitted with a pressure plate 63 of the clutch device 13 and a friction plate 64 of the brake device 17. Also, inside the cylinder 62 is a piston 66 for actuating the clutch device 13.
is installed. A pressure plate 68 of the brake device 17 is spline-fitted to the transmission case 67, and a cylinder 69 is formed therein. Further, a piston 70 for operating the brake device 17 is disposed within the cylinder 69. A flange 71 connected to the ring gear 53 is connected to the output shaft 7 (input shaft of the automatic transmission 200). The one-way clutch 20 disposed between the sun gear 51 and the carrier 54 is connected to the sun gear 51 and is composed of an inner race 72 and an outer race 73 provided on the hub 61. The operation of automatic transmission 200 and overdrive device 300 with the above configuration will be explained. The operation of the automatic transmission 200 is as shown in Table 1.

[Table] In this Table 1, the mark ◯ indicates that it is operating by a hydraulic oil operating mechanism. The symbol △ indicates that the engine brake is being operated by the pressurized oil operating mechanism when necessary. The * mark indicates that the one-way clutch is locked only when the engine is driving. Next, the operation of each gear stage will be explained. In the case of the first forward speed, the clutch device 11 and the one-way clutch 19 are operated, and the intermediate shaft 9 is in a free state. Therefore, the input rotation from the input shaft 7 is transmitted to the intermediate shaft 8 by the clutch device 11 to rotate the ring gear 43 of the second planetary gear mechanism 40. Therefore, the carrier 34 of the first planetary gear mechanism 30 is connected to the planetary pinion 42 and the sun gear 4 of the second planetary gear mechanism 40 by the ring gear 43.
1. Rotation in the opposite direction is transmitted through the sun gear 31 and planetary pinion 32 of the first planetary gear mechanism 30, but the carrier 34 is connected to the one-way clutch 19.
Since rotation in the opposite direction is restrained by
The ring gear 33 is rotated in the same direction by the sun gear 31 via the planetary pinion 32, and further rotates the carrier 44 of the second planetary gear mechanism 40 connected to the ring gear 33 in the same direction, and the combined rotation is output. is transmitted to the shaft 10. When it is desired to apply the engine brake when traveling downhill, the one-way clutch 19 alone allows the carrier 34 to rotate in the same direction, so the brake device 16 is applied to restrain the rotation of the carrier 34. In the case of the second forward speed, the clutch device 11, the brake device 15 and the one-way clutch 18 are in operation. The input rotation from the input shaft 7 is transmitted by the clutch device 11 to the ring gear 43 of the second planetary gear mechanism 40 via the intermediate shaft 8. Therefore, rotation in the opposite direction is transmitted to the sun gear 41 by the ring gear 43 via the planetary pinion 42, but at this time, since the sun gear 41 is restrained from rotating in the opposite direction by the brake device 15 and the one-way clutch 18, the planetary pinion 42 is caused to revolve in the same direction along the sun gear 41 by the ring gear 43, and as a result, the carrier 44 rotates in the same direction and is transmitted to the output shaft 10. When it is desired to apply engine braking, such as when traveling downhill, the one-way clutch 18 allows the sun gear 41 to rotate in the same direction, so the brake device 14 is actuated to restrain the rotation of the sun gear 41. In the case of the third forward speed, the clutch device 11 and the clutch device 12 are in operation. The input rotation from the input shaft 7 is transmitted by the clutch device 11 to the ring gear 43 of the second planetary gear mechanism 40 via the intermediate shaft 8.
At the same time, it is transmitted to the sun gear 41 of the second planetary gear mechanism 40 by the clutch device 12 via the intermediate shaft 9. Therefore, in the second planetary gear mechanism 40, due to the rotation of the ring gear 43 and the sun gear 41 in the same direction, the planetary pinion 42 is rotated integrally with the ring gear 43 and the sun gear 41 without relative movement.
is transmitted to the output shaft 10. In the case of reverse movement, the clutch device 12 and the brake device 16 are activated and the intermediate shaft 8 is in a free state. The input rotation from the input shaft 7 is transmitted to the sun gear 31 of the first planetary gear mechanism 30 via the intermediate shaft 9 by the clutch device 12 . Therefore, rotation in the same direction is transmitted to the carrier 34, but at this time, since the rotation of the carrier 34 is restrained by the brake device 16, the ring gear 33 is rotated in the opposite direction by the sun gear 31 via the planetary pinion 32, and the output shaft 10 can be conveyed to. The operation of the overdrive device 300 is as shown in Table 2.

[Table] In this second table, the mark ◯ indicates that the hydraulic oil operating mechanism is in operation. The * mark indicates that the one-way clutch is locked only when the engine is driving. Next, the operation of each gear stage will be explained. In the case of direct coupling, the clutch device 13 and the one-way clutch 20 are activated. Therefore, in the third planetary gear mechanism 50, the sun gear 51 and the ring gear 53 are integrally connected, and the input rotation from the input shaft 6 is transmitted to the carrier 54, and the ring gear 53 moves relative to the planetary pinion 52 and the sun gear 51. The output shaft 7 is rotated and transmitted to the output shaft 7 without being integrated. When it is desired to apply engine braking, such as when driving downhill, the one-way clutch 20 becomes free, but the clutch device 13 causes the sun gear 51, planetary pinion 52, and ring gear 53 to rotate integrally. In this manner, power is transmitted through both the clutch device 13 and the one-way clutch 20 during engine drive, and power is transmitted through the clutch device 13 during engine braking. In the case of overdrive, input rotation from the input shaft 6 is transmitted to the carrier 54. At this time,
Since the brake device 17 is operating, the sun gear 5
1 is fixed, and the planetary pinion 52 revolves along the sun gear 51 and is accelerated to the ring gear 53.
and is transmitted to the output shaft 7. FIG. 3 is a schematic diagram showing a power transmission mechanism of an automatic transmission according to another embodiment of the present invention. The layout has been changed. The operation is the same as that shown in FIG. As explained above, the present invention relates to a vehicle automatic transmission in which an overdrive device is disposed between a torque converter and a general-purpose multi-stage automatic transmission. The driving connection between a torque converter and a general-purpose multi-stage automatic transmission is such that an input gear of the multi-stage automatic transmission is normally connected to the rear end of a turbine shaft, which is an output shaft of the torque converter. Therefore, when installing an overdrive device between a torque converter and a multi-stage automatic transmission, the output shaft of the torque converter is connected to the input gear of the overdrive device, and the output shaft of the overdrive device is connected to the input gear of the overdrive device. By forming the rear end portion in the same manner as the rear end portion of the turbine shaft when the torque converter is connected to a general-purpose multi-stage automatic transmission, driving connection can be easily made and an overdrive device can be formed. The engine power that is transmitted via the torque converter is always transmitted from the output shaft of the multi-speed automatic transmission, whether the multi-speed automatic transmission is shifted to a low forward gear or a reverse gear. Only increased engine power or rotational torque in the opposite direction to the forward gear is output, and the magnitude and direction of the power transmitted from the torque converter to the overdrive device does not affect the shifting of the multi-speed automatic transmission. never be done. Further, there is no need for any design change in the driving connection between the output shaft of the multi-stage automatic transmission and the drive axle or the differential gear on the output side of the general-purpose multi-stage automatic transmission. On the other hand, in a vehicle automatic transmission system consisting of a torque converter and a general-purpose multi-stage automatic transmission,
When installing an overdrive device on the output side of a multi-speed automatic transmission, the drive connection between the torque converter and the input side of the multi-speed automatic transmission does not require any design changes; Significant design changes are required for the drive connection between the output shaft and the drive axle or differential gearing. In other words, a governor valve is usually installed on the output side of a general-purpose multi-stage automatic transmission to detect the rotational speed of the output shaft.
Furthermore, a constant velocity joint to be connected to the drive axle or a gear to drive a differential gear device is usually attached. Additionally, if the overdrive device is installed on the output side of the multi-speed automatic transmission, when the multi-speed automatic transmission is shifted to a low forward gear, a torque greater than the input torque of the multi-speed automatic transmission will be transmitted to the overdrive device. In addition, when the multi-stage automatic transmission is shifted to the reverse gear, torque is transmitted to the overdrive device in the rotation direction opposite to the forward rotation direction and larger than the input torque of the multi-stage automatic transmission. Therefore, the overdrive device must be a gear mechanism that can withstand torque, and in the case of an overdrive device that has a planetary gear mechanism with a one-way clutch, when the one-way clutch is transmitted with rotation in the opposite direction, is in a free rotation state, so
A clutch device with a capacity corresponding to the above-mentioned large torque must also be provided. If the overdrive device is placed between the torque converter and the automatic transmission in this way, there will be significant benefits in terms of structure and effectiveness compared to when the overdrive device is placed on the output side of the automatic transmission. In addition, in the present invention, an overdrive device that should achieve an overdrive ratio and direct connection,
A planetary gear mechanism comprising a sun gear, a ring gear, a planetary pinion meshing with the sun gear and the ring gear, and a carrier rotatably supporting the planetary pinion, an input shaft connected to the carrier, and an input shaft connected to the ring gear and the automatic transmission. The machine consists of an output shaft that also serves as the input shaft of the machine, a brake device for braking the sun gear, and a clutch device that removably connects the sun gear and ring gear. To achieve a driving connection between a transmission and a general-purpose torque converter and an automatic transmission without requiring major design changes, and to minimize the axial dimension of an overdrive device. As a vehicle automatic transmission system, it is possible to improve engine durability and fuel efficiency due to the effect of overdrive, and it is sufficient to have a clutch capacity that corresponds to the engine traction. . Furthermore, in the present invention, by disposing the overdrive device between the torque converter and the main transmission of the automatic transmission, the overdrive device is disposed on the output side of the main transmission. The input torque to the drive device is small, and the rotational direction of the engine power transmitted to the overdrive device is always in one direction, so the overdrive device can be constructed with a small capacity and compact. When the overdrive device achieves a direct coupling ratio, the input torque is shared by the clutch device and the one-way clutch, and the capacity distribution of the one-way clutch can be reduced. In addition, since the one-way clutch is disposed between the sun gear and ring gear of the planetary gear mechanism, the effective diameter of the one-way clutch can be selected from a wide range. The capacity of the one-way clutch can be arbitrarily selected, and since the capacity of the one-way clutch is determined by the input torque x number of sun gear teeth/number of sun gear teeth + number of ring gear teeth, the one-way clutch can be connected to the input shaft and output of the overdrive device. Compared to the case where the one-way clutch is installed between the shaft and the shaft, the capacity of the one-way clutch is approximately 1/3 that in the torque direction, which improves its durability and makes it easy to make the one-way clutch more compact. shall be.

[Brief explanation of the drawing]

FIG. 1 is a schematic diagram showing the power transmission mechanism of an automatic transmission according to an embodiment of the present invention, FIG. 2 is a sectional view showing the structure of the overdrive device of the present invention in FIG. 1, and FIG. FIG. 3 is a schematic diagram showing a power transmission mechanism of an automatic transmission according to another embodiment of the invention. Explanation of symbols, 100...Torque converter, 2
00... Automatic transmission, 300... Overdrive device, 11, 12, 13... Clutch device, 1
4, 15, 16, 17...brake device, 18,
19, 20...One-way clutch, 30, 40, 5
0... Planetary gear mechanism.

Claims (1)

[Claims] 1. In a vehicle automatic transmission device in which an overdrive device is disposed between a torque converter and an automatic transmission, the overdrive device includes an input shaft connected to an output side of the torque converter, a planetary gear mechanism, and a planetary gear mechanism. An output shaft that also serves as an input shaft of an automatic transmission is arranged concentrically, the input shaft is connected to a carrier of the planetary gear mechanism, the output shaft is connected to a ring gear of the planetary gear mechanism, and the planetary gear a brake device for braking the sun gear of the mechanism; a clutch device for removably coupling the sun gear and the ring gear; and a clutch device disposed between the sun gear and the ring gear to connect the inner race to the sun gear and the outer race. An automatic transmission for a vehicle having an overdrive device, comprising a one-way clutch that connects each of the two ring gears to the ring gear.