JPS6127619B2 - - Google Patents

Description

[Detailed description of the invention]

A gear transmission that uses planetary gears has an input shaft, an output shaft, and a planetary gear arranged concentrically on one shaft.
By combining a clutch, a brake, and a one-way clutch, low-speed, high-speed, and reverse gear train configurations can be achieved, so it is commonly used as an automotive gear transmission in combination with a torque converter, and usually has two sets of planetary gears. This combination results in a gear train configuration with three forward stages and one reverse stage. Recently, due to demands for higher speeds, lighter weights, and resource conservation in automobiles, some vehicles have been combined with a set of overdrive planetary gears to form a gear train with four forward speeds and one reverse speed. In these gear transmissions, the gear train in the low speed range usually brakes the planetary carrier of a set of planetary gears, and transmits the rotational driving force transmitted to the input shaft of the gear transmission to the sun gear of the planetary gear. , the rotation of the sun gear is transmitted to the output shaft by rotationally driving the ring gear of the planetary gear through the rotation of the planetary pinion supported by the braked planetary carrier, thereby obtaining a large speed reduction. , and a one-way clutch is commonly used for braking the planetary carrier. By the way, in such a gear train configuration for a low speed range, the rotational speed to be transmitted to the output shaft is low, but the torque to be transmitted is required to be large, so the one-way clutch that brakes the planetary carrier is required to have a high speed. A one-way clutch is required to have a large braking effect on torque transmission, and the one-way clutch is frequently used when an automobile is running, and smooth operation is required. In response to such demands, the present invention increases the diameter of the one-way clutch that operates in the gear train configuration in the low speed range, and increases the braking load by increasing the shape and number of the combination of the taper and pawl or the sprag that is the braking member. In addition, the purpose is to prevent deformation, damage, and wear of the one-way clutch even if there is a dimensional error in the housing or each gear of the planetary gear. The outer race of the one-way clutch is connected to the carrier and has an appropriate floating gap in the diametrical and circumferential directions on a spline formed on the inner wall of the housing in the direction of the rotation center axis of the input shaft of the planetary gear. The outer race is supported in a non-rotatable manner, and an appropriate floating gap is provided between stoppers fixed to both sides of the outer race on the inner wall of the housing in the direction of the rotation center axis, so that the outer race is supported in a floating manner. In addition, the spline formed on the inner wall of the housing is also used for spline engagement with a friction plate of a brake disposed in relation to the planetary gear. FIG. 1 is an explanatory diagram of an automatic transmission for an automobile suitable for implementing the present invention, and FIG. 2 is an embodiment of the present invention applied to the transmission, in which 1 is a torque converter;
2 indicates a gear transmission, and the torque converter 1 is fixed by a pump connected to an output shaft 3 of an internal combustion engine (not shown), a turbine connected to an input shaft 4 of the gear transmission 2, and a one-way clutch. The gear transmission 2 consists of a stator connected to the input shaft 4, an output gear 5 as an output shaft, an intermediate shaft 6,
7, 8 and three sets of planetary gears 10, 20, 30 are arranged concentrically in a housing 9. The first planetary gear 10 among the three sets of planetary gears
consists of a sun gear 11, a planetary pinion 12, a ring gear 13, and a planetary carrier 14 that rotatably supports the planetary pinion 12. The sun gear 11 is integrally formed with the intermediate shaft 6, and the ring gear 13 is integrally formed with the intermediate shaft 7. A first one-way clutch 16 with the shaft 6 as an inner race is disposed on the circumferential surface of the intermediate shaft 6, and the outer race is engaged with and disengaged from the housing 9 by a first brake 17. The planetary carrier 14 has a second
The inner race of the one-way clutch 18 is connected, and the outer race of the one-way clutch 18 is supported on the inner wall of the housing 9 so as not to rotate in the circumferential direction. The inner race of the one-way clutch 18 is further releasably engaged with the housing 9 by a second brake 19. The second planetary gear 20 includes a sun gear 21, a planetary pinion 22, a ring gear 23, and a planetary carrier 24 that rotatably supports the planetary pinion 22, and the sun gear 21 is similar to the sun gear of the planetary gear 10. A planetary carrier 24 formed integrally with the intermediate shaft 6 is connected to the intermediate shaft 7 by a spline, a ring gear 23 is removably connected to the input shaft 4 by a first clutch 26, and the intermediate shaft 6 The input shaft 4
It is removably connected by a second clutch 27 and is removably locked by a third brake 28. The above planetary gears 10, 20, one-way clutch 1
6, 18, clutches 26, 27 and brake 1
7, 19, and 28 should constitute an underdrive gear ratio. On the other hand, the third planetary gear 30 includes a sun gear 31, a planetary pinion 32,
It consists of a planetary carrier 34 that rotatably supports a ring gear 33 and a planetary pinion 32, its sun gear is formed integrally with the intermediate shaft 8, and the ring gear 33 is connected to the output gear 5. The planetary carrier 34 of the planetary gear 30 is connected to the intermediate shaft 8 by a third one-way clutch 3.
6 is interposed therein and is detachably connected to the intermediate shaft 8 by a third clutch 37,
Further, the intermediate shaft 8 is detachably engaged with the housing 9 by a fourth brake 38. In addition, in FIG. 1, the output gear 5 is rotatably supported on an intermediate shaft 7, a gear 41 meshing with the gear 5, and a shaft 4 fixing the gear 41.
2. It is configured to transmit rotational driving force to a differential gear device 44 via a gear 43 fixed to the shaft 42 to drive the drive shafts 45 and 46 of the wheels. The following table shows the operating status of the automatic transmission configured as described above. In the table, the ○ mark indicates that the clutch or brake is in operation by the hydraulic operating mechanism, the △ mark indicates that the clutch is engaged during engine braking, and the * mark indicates that the one-way clutch is in operation.

[Table] As is clear from the above table, in the first speed gear train having the highest reduction ratio, the clutch 26 is engaged and the one-way clutch 18 is in the operating state. At this time, the planetary gear 30 for overdrive is rotated as one unit because the planetary carrier 34 and the sun gear 31 are engaged by the clutch 37, and the intermediate shaft 7 and the output gear 5 are rotated as one unit. The rotational drive of the internal combustion engine rotates the ring gear 23 of the planetary gear 20 via the input shaft 4, and the intermediate shaft 7
Since the rotation is low, the sun gear 21 is rotated. Therefore, in the first planetary gear 10, the sun gear 21
The rotational drive of the input shaft is transmitted to the sun gear 11 connected by the intermediate shaft 6 to the one-way clutch 18.
The ring gear 13 is driven to rotate at a low speed via the planetary pinion 12 on the planetary carrier 14 whose rotation is prevented by the rotation speed of the output gear 5 . However, when the first speed gear train is driven, the torque output to the output gear 5 is large, so the load acting on the one-way clutch 18 via the ring gear 13 is large. FIG. 2 shows an embodiment of the present invention implemented in the above-mentioned automatic transmission, in which a spline 51 is carved on the inner circumferential wall of the housing 9 of the transmission 2 in parallel with the central axis of rotation of the intermediate shafts 6 and 7. Furthermore, an outer race 52 of the one-way clutch 18 is engaged with the spline 51, and an inner race 53 of the one-way clutch 18 is engaged with the spline 51.
is fixed to the planetary carrier 14 and spline-fitted to the friction plate 57 of the brake 19, and a sprag 5 is connected between the races 52 and 53.
4 is interposed therebetween, and end bearings 55 are provided on both sides of the sprag 54. As shown in FIG. 2, on both sides of the outer race 52 of the one-way clutch 18 in the direction of the rotation center axis, stoppers 56, 56 formed by fixing snap rings to the inner circumferential wall of the housing 9 are provided.
An appropriate floating gap is formed between the outer race 52 and the side wall in the direction of the rotation center axis. Moreover, as shown in FIG.
An appropriate floating gap is formed between the spline 51 and the spline 51 to prevent rotation. Note that the spline 51 is connected to the pressure plate 58 of the brake 17, 19,
The end plates 49 connected to the planetary carrier 24 of the planetary gear 20 and the ring gear 13 of the planetary gear 10 are each spline-coupled to the intermediate shaft 7, and the clutch A frame 29 supporting the pressure plate 27 and forming an engaging cylindrical surface of the boot 28 is splined to the intermediate shaft 6. In the above structure, the outer race 52 of the one-way clutch 18 can be formed to have an outer diameter approximately equal to the dimension of the inner circumferential wall of the housing 9, so the one-way clutch as a whole can be formed with a large diameter, and the sprags 54 can be increased in size or inserted in large numbers. Since the one-way clutch 18 can be placed close to the inner circumferential wall of the housing 9, the one-way clutch 18 can withstand high loads and shocks. . By absorbing the whirling in the radial free gap between the outer race 52 and the spline 51, the outer race 52 can follow the whirling of the inner race 53 via the end bearing 55, which is a necessary condition for the one-way clutch to operate normally. This ensures concentricity between the inner race surface and the outer race surface. The present invention uses at least one set of planetary gears and a one-way clutch to transfer rotational driving force transmitted from an input shaft to a sun gear of the planetary gear to a planetary carrier whose rotation is prevented by the one-way clutch. In a gear transmission equipped with a gear train configuration that converts the rotation of a supported planetary pinion to rotationally drive a ring gear meshing therewith and outputs an output to an output shaft, the inner race of the one-way clutch is connected to the planetary carrier. The outer race is connected to a spline formed on the inner circumferential wall of the transmission housing in the axial direction of the planetary gear and the rotational center axis of the input shaft and output shaft to prevent the rotation thereof, and the outer race and the spline are fitted together. Since the outer race is fitted with an appropriate play gap in the diametrical and circumferential directions,
Even if misalignment occurs in the outer race of the one-way clutch during rotational drive due to the dimensional tolerances of the splines of the housing, the gears of the planetary gears and the planetary carrier, or the intermediate shaft that supports the planetary gears, the position of the outer race in the diametrical direction of the outer race Since the clutch moves freely within the range of its free movement gap, it absorbs the fluctuations of the outer race in the diametrical and circumferential directions due to the above-mentioned dimensional tolerances, prevents damage and wear on the one-way clutch, and follows the whirling of the inner race. The concentricity of the inner race surface and the outer race surface is maintained, and in the axial direction, a stopper such as a snap spring fixed to the inner wall of the housing is provided with an appropriate free space on both sides. Even if an axial force is generated due to dimensional tolerances, or an axial force acts on the inner race during brake operation through the friction plate of the brake supported by the inner race of the one-way clutch, The outer race of the -direction clutch moves within the range of the free movement gap provided in the axial direction to prevent damage such as deformation and wear of the sprag and end pairing, and furthermore, this free movement also impairs the braking effect. There's nothing wrong with that. Further, in the present invention, the pressure plate of the brake is supported by the inner race of the one-way clutch and allows the planetary carrier connected to the inner race to be freely engaged and detached from the transmission housing. Since the one-way clutch is non-rotatably fitted with the outer race of the one-way clutch, the planetary carrier is connected to the inner race of the one-way clutch, and the one-way clutch and brake are placed in close proximity to each other. Plines can be shared and arranged, reducing the axial dimension of the gear transmission and simplifying the structure. Further, according to the present invention, each includes a sun gear, a planetary pinion meshing with the sun gear,
First and second planetary gears comprising a ring gear meshing with the planetary pinion and a planetary carrier rotatably supporting the planetary pinion, an input shaft, an output shaft, and an intermediate shaft are concentrically disposed in a transmission housing. sun gears of the first and second planetary gears are fixedly provided on the intermediate shaft, and a first one-way clutch disposed on the circumferential surface of the intermediate shaft is freely engageable and detachable from the housing. a first brake for locking is provided, the planetary carrier of the first planetary gear and the housing are connected by a second one-way clutch disposed on the inner surface of the housing, and the carrier is connected to the housing; A second brake that can be engaged and disengaged is provided, and a ring gear of the first planetary gear and a planetary carrier of the second planetary gear are fixed to either the input shaft or the output shaft, and a second brake is provided to the other shaft. The ring gear of the second planetary gear is
In a gear transmission having three gear stages in one rotational direction of the output shaft and one gear stage in the opposite rotational direction, the gear transmission can be freely engaged and disengaged by a clutch. By non-rotatably engaging and supporting the outer race of the one-way clutch and the pressure plate of the second brake on splines formed on the inner wall of the transmission housing, the functions and effects described above with respect to the second planetary gear are obtained. and a pressure plate of a first brake that removably locks a first one-way clutch disposed on the circumferential surface of the intermediate shaft to the housing;
By being non-rotatably fitted to the spline formed on the inner wall of the housing, the spline of the housing is engaged with the outer race of the second one-way clutch and the pressure plate of the second brake. Since it is also used for the fitting of the pressure plate of the first brake, only one spline can be formed on the inner wall of the transmission housing to support the fitting of these elements without forming separate splines. In addition, the second one-way clutch is interposed between the first and second brakes, and the first one-way clutch is connected to the first and second planetary gears. a second brake, a second one-way clutch and a second planetary gear concentrically arranged with the first brake; and the first one-way clutch can be disposed diametrically outwardly and axially adjacent to the first one-way clutch, and the first and second planetary gears can be disposed concentrically with a reduced axial spacing. Therefore, the axial dimension of the gear transmission as a whole can be reduced, which is extremely effective in eliminating wasted space inside the transmission housing and making the transmission more compact. Moreover, in the one-way clutch according to the present invention that only allows rotation of the planetary carrier in one direction, the outer race of the one-way clutch is floatingly secured directly to the inner circumferential wall of the transmission housing. Since the rotation of the one-way clutch is prevented by contacting the spline of the towing over its entire axial length, even if an impact is applied to the one-way clutch, the outer race will not be deformed, and the one-way clutch will not be rotated within the housing. Since it is formed along the inner peripheral wall, the space near the intermediate shaft of the gear transmission can be used effectively, and the gear transmission can be made more compact by shortening the axial dimension. Since it can be constructed with a larger diameter than conventional ones, it is possible to improve the performance of the one-way clutch by increasing the size or number of rotational braking mechanisms such as sprags, and especially when operating as a one-way clutch. A great feature is that it is possible to ensure concentricity between the inner race surface and the outer race surface, which is a necessary condition for normal operation of a one-way clutch.

[Brief explanation of the drawing]

Fig. 1 is an explanatory diagram of an automatic transmission for an automobile most suitable for implementing the present invention, Fig. 2 is a side cross-sectional view of an embodiment of the present invention implemented in the above-mentioned transmission, and Fig. 3 is a front part thereof. FIG. In the figure, 1 is a torque converter, 2 is a gear transmission, 4 is an input shaft, 5 is an output gear, 6, 7, and 8 are intermediate shafts, 9 is a housing, 51 is its spline, and 10, 20, and 30 are planets. Gears, 11, 21,
31 is its sun gear, 12, 22, 32 are its planetary pinions, 13, 23, 33 are its ring gears, 14, 24, 34 are its planetary carriers, 16, 18 are one-way clutches, 17, 1
9, 28, and 38 are brakes, 26, 27, and 37 are clutches, 52 is an outer race of the one-way clutch 18, 53 is an inner race thereof, 54 is a sprag thereof, 55 is an end bearing thereof, and 56 is a stopper, respectively. It is.

Claims (1)

[Scope of Claims] 1. An input shaft, an output shaft, an intermediate shaft rotatably supported on either the input shaft or the output shaft, a sun gear disposed on the intermediate shaft, a planetary pinion, a ring gear, and the above. At least one set of planetary gears consisting of a planetary carrier rotatably supporting a planetary pinion and a one-way clutch that allows rotation of the planetary carrier in only one direction are disposed concentrically in the housing, and the planetary gear A gear transmission including a gear train configuration that includes a brake whose rear part can be freely engaged and detached from the housing, and outputs rotational drive transmitted from the input shaft to the sun gear to the output shaft via the ring gear. The inner race of the one-way clutch is connected to the planetary carrier, and the outer race of the one-way clutch is connected to a spline formed on the inner wall of the housing in the direction of the rotational center axis of the intermediate shaft, and has an appropriate amount of free movement in the diametrical and circumferential directions. The outer race is non-rotatably engaged and supported with a space between the outer race and the outer race, and is disposed in the axial direction of the rotational center shaft with an appropriate free movement space between stoppers formed on both sides of the outer race on the inner wall of the housing. A gear transmission characterized in that the outer race is supported in a floating manner by the housing, and the pressure plate of the brake is non-rotatably fitted to the spline formed on the inner wall of the housing. 2. The gear transmission according to claim 1, wherein the inner race of the one-way clutch is integrally formed with the planetary carrier. 3. First and second planetary gears each consisting of a sun gear, a planetary pinion that meshes with the sun gear, a ring gear that meshes with the planetary pinion, and a planetary carrier that rotatably supports the planetary pinion, and an input shaft; An output shaft and an intermediate shaft rotatably supported by either the input shaft or the output shaft are arranged concentrically in the housing, and sun gears of the first and second planetary gears are fixedly mounted on the intermediate shaft. and a first brake for detachably locking a first one-way clutch disposed on the circumferential surface of the intermediate shaft to the housing, the planetary carrier of the first planetary gear. and the housing by a second one-way clutch disposed on the inner surface of the housing, and a second brake that allows the carrier to be freely engaged with and detached from the housing; or on one axis,
The ring gear of the first planetary gear and the planetary carrier of the second planetary gear are fixed to the other shaft, and the ring gear of the second planetary gear is freely engaged and disengaged by a first clutch, and the intermediate The intermediate shaft is capable of being engaged and disengaged from the shaft by a second clutch, the second one-way clutch being interposed between the first and second brakes, and an outer race of the intermediate shaft being attached to an inner wall of the housing. A spline formed in the axial direction of the intermediate shaft is floating between stoppers formed in the housing in the axial direction of the intermediate shaft.
The intermediate shaft is provided with an appropriate floating distance between it and the housing in the radial and circumferential directions of the intermediate shaft.
and the pressure plates of the first brake and the second brake are each non-rotatably fitted to the spline formed on the inner wall of the housing. Transmission gear device. 4. The transmission gear device according to claim 3, wherein the inner race of the second one-way clutch is integrally formed with the planetary carrier of the first planetary gear.