JPS587154Y2 - Hagurumahensokuuchi - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a gear transmission that achieves overdrive, and particularly to a gear transmission that is suitable for use in combination with a torque converter used in automobiles and the like.

Planetary gear mechanisms are often used as gear transmissions used in combination with torque converters, and for automobiles, two sets of planetary gear mechanisms are usually arranged concentrically, and a carrier or ring gear is selected to support the sun gear or planetary pinion. By engaging the clutch or applying the brake, a gear train with three forward speeds and one reverse speed is obtained.

The gear ratios of these gear transmission trains are conventionally set to 1-j or greater than 1.

This type of gear transmission, especially automatic transmissions used in automobiles, uses a drive mode that requires low torque on the driven shaft and rotates at high speed, such as when a car drives at high speed for a long time on a flat road. In this case, in order to save the energy consumed by the prime mover, a transmission gear train with a transmission ratio smaller than 1, in other words, an overdrive is required.

This invention is one of the planetary gear mechanisms to be incorporated into gear transmissions.
One gear ratio has a value smaller than 1, and is designed to achieve overdrive without adversely affecting other transmission gear trains of the gear transmission, and the planetary gear mechanism has a clutch and a brake. When configuring an overdrive device by incorporating a one-way clutch, a forcing force is generated between the elements due to accuracy errors when transmitting torque between the components of the planetary gear mechanism, and the one-way clutch races between these elements. If directly connected, this forcing force will deteriorate the operability and durability of the one-way clutch, so one of the races of the one-way clutch is spline-coupled to the element to prevent dimensional errors between each element. Even if there is misalignment of the one-way clutch due to installation error, this is absorbed by the spline, and the purpose is to improve operability and durability.It is especially used in combination with a torque converter that has a planetary gear mechanism. It is suitable for application to a gear transmission device of a conventional automatic transmission.

That is, the present invention includes a planetary gear mechanism consisting of a sun gear, a planetary pinion, and a ring gear, an input shaft concentrically connected to a carrier that supports the planetary pinion,
an output shaft concentrically connected to the ring gear; a friction plate type clutch that removably connects the sun gear and the carrier; a friction plate type brake that brakes the sun gear; and a friction plate type brake that brakes the sun gear; A one-way clutch is disposed between the carrier and the carrier and causes the carrier to overrun when the sun gear is braked,
The outer race of the one-way clutch is concentrically connected to the carrier and is integrally provided with one clutch hub of the clutch, and the inner race of the one-way clutch is integrally formed with an element to support the one-way clutch. The clutch is configured between the clutch cylinder and the clutch hub, which is rotated integrally with the sun gear, and the brake is connected between the clutch cylinder and the gear transmission.・・・
It is characterized by being configured between the cylinder and the planetary gear mechanism, and increases durability by absorbing misalignment and vibration caused by dimensional errors and installation errors of each element of the planetary gear mechanism, and also increases the axial dimension of the entire device. This relates to a compact overdrive device with a smaller size.

FIG. 1 shows a torque converter 2 in which an overdrive transmission according to the present invention is coupled to a prime mover output shaft 1, and a transmission gear device 100 with three forward speeds and one reverse speed, in which two sets of planetary gear mechanisms are arranged concentrically. FIG. 2 is a schematic diagram of an automatic transmission inserted as an auxiliary transmission 200 between a torque converter 2 and the transmission gear device 100 in an automatic transmission connected to the automatic transmission.

In FIG. 1, the input shaft 3 and output shaft 4 of the sub-transmission 200 are connected to the sun gear 21. It is arranged concentrically with a planetary gear mechanism 8 consisting of a planetary pinion 22 and a ring gear 23, the input shaft 3 is connected to a carrier 24 of the planetary pinion 22, the output shaft 4 is connected to the ring gear 23, and the sun gear 21. The carrier 24 is detachably connected to the clutch 11, and the sun gear 21 is configured to be braked by the brake 14.
A one-way clutch 20 is provided between the carrier 20 and the sun gear 21, and the carrier 24 is configured to overrun the sun gear 21 when the sun gear 21 is braked by the brake 14.

The variable speed gear device 100 has two sets of planetary gear mechanisms 9 and 10 arranged concentrically with the planetary gear mechanism 8, and the output shaft (
Intermediate shaft) 4 is used as its input shaft, clutches 12, 13, brakes 15, 16.17 and one-way clutch 18.1.
9 selectively switches output shaft 1 at a gear ratio of 3 forward stages and 1 reverse stage.
This is a conventionally known mechanism for outputting power to the output shaft (intermediate shaft) 4 and the intermediate shaft 5 by means of a clutch 12, which is detachably connected to the shaft 4 and the sun gear 91 of one of the planetary gear mechanisms 10. A clutch 13 is used to connect and remove the common shaft 6, and the shaft 6 is braked by a brake 15. An outer race of a one-way clutch 18 provided on the shaft 6 is braked by a brake 16. carrier 84 of the planetary pinion 82 of the planetary gear mechanism 9
is braked by a brake 17, and a one-way clutch 19 is formed between it and the fixed part, and its ring gear 83 is connected to the carrier 94 of the planetary pinion 92 of the other planetary gear mechanism 10 and the output shaft 7. is,
A ring gear 93 of the planetary gear mechanism 10 is connected to the intermediate shaft 5.

FIG. 2 is a cross-sectional view of the main parts of the sub-transmission 200 according to the present invention, in which seven flange 42 are formed in the radial direction at the rear end of the input shaft 3 to accommodate the carrier 24 of the planetary pinion 22. The outer race 37 of the one-way clutch 20 is integrally formed with the clutch hub 26, and the sun gear 21 is fixed to one clutch hub 26 of the clutch 11 in the axial direction of the carrier 24. 20 inner races 38 are spline-coupled, and a piston 34 for operating the clutch 11 is disposed inside the clutch cylinder 25, and
One end of the cylinder 25 is spline-fitted to the outer peripheral edge of each brake hub 29 with a pressure plate 28 of the clutch 11, and its movement is prevented by fastening members 43 and 44. A friction plate 27 fitted with a spline is inserted between a piston 34 and a pressure plate 28, so that the clutch 11 can be engaged and disengaged as the piston 34 moves back and forth.

The friction plate 30 of the outer brake 14 is spline-fitted to the cylindrical portion of the other end of the brake hub 29,
A pressure plate 46 spline-fitted to the inner periphery of the mission case 32 and locked by a fastening member 45, and a movable pressure plate 31.
．． The friction plate 30 is inserted between the transmission case 32 and the transmission case 32, and the brake 14 is activated or released by moving the cylinder 35 disposed in the cylinder 33 formed in the transmission case 32 forward or backward.

The inner race 38 of the one-way clutch 20 is the sun gear 21
A clutch member (sprag) 39 is disposed between the inner race 38 and the outer race 37, which are spline-coupled with each other, and allow overrun rotation of the carrier 24 when the sun gear 21 is braked by the brake 14. The purpose is to prevent overrun rotation.

An end bearing 40 is provided axially rearward of the inner race 38, and is supported in the axial direction by a snap ring 41.

The ring gear 23 of the planetary gear mechanism 8 is connected to the outer periphery of a flange 36 spline-coupled to the output shaft 4 whose tip is supported in the shaft hole 48 of the input shaft 3, and is connected to the output shaft 4.

Note that the small hole 49 drilled in the inner race 38 of the one-way clutch 20 is connected to the oil supply passages so, si, etc. from the oil supply pump driven by the prime mover by the same means as when refueling a normal planetary gear mechanism 8°9.10. One-way clutch 2
This hole was drilled to supply oil to the 0.

In the automatic transmission configured as described above, since the rotation of the input shaft 1 transmitted to the input shaft 3 via the torque converter 2 is transmitted to the carrier 24 of the planetary pinion 22, the clutch 11 is operated. When the sun gear 21 and the carrier 24 are made to rotate together, the planetary gear unit 8 rotates together and does not perform a speed change action, and the input shaft 3 is rotated via the ring gear 23 at a gear ratio of 1 to the output shaft (intermediate axis) 4.

Therefore, the clutch 11 is operated to connect the output shaft 4 and the intermediate shaft, and the clutch 12.13 and the brake 15.16 are
．． 17 selectively engages and disengages, a gear train with three forward speeds and one reverse speed similar to the conventional one can be obtained. When the clutch 11 is released and the brake 14 is applied to the sun gear 21, the input shaft of the carrier 24 3 drives the ring gear 23 and the output shaft (intermediate shaft) 4 that connects the ring gear 23 at higher speed than the rotation of the input shaft 3. Therefore, the sub-transmission 200
A smaller reduction ratio can be obtained and overdrive of the output shaft T can be achieved.

The operation of the automatic transmission having the configuration shown in FIG. 1 is as shown in the following table.

In this table, the ○ mark indicates that the clutch and brake are operating by the hydraulic oil operating mechanism.

The Δ mark indicates that the brake is being operated by the hydraulic oil operating mechanism during engine braking.

* indicates that the one-way clutch is locked only when the engine is driving.

Note that the explanation of the operation for each gear stage is well known, and there is no need to explain it.

The present invention connects the carrier of the planetary pinion that constitutes the planetary gear mechanism to the input shaft, and its ring gear to the output shaft, and connects and disconnects the sun gear and carrier of the planetary gear mechanism using a friction plate type clutch. At the same time, the sun gear can be freely engaged with the housing of the gear transmission by a friction plate type brake, and a one-way clutch is constructed between the sun gear and the carrier that causes the carrier to overrun when the sun gear is braked. When braking the sun gear to lock it to the housing, the output shaft is rotated at an increased speed compared to the input shaft, and the output shaft is overdriven by a reduction ratio smaller than the desired l, and when the brake is released, the output shaft is rotated at a speed higher than that of the input shaft. Since the directional clutch locks the sun gear and carrier, it can smoothly transition to direct coupling operation, and when the clutch is engaged, each element of the planetary gear mechanism is coupled together, and the input shaft and output shaft are directly coupled. Torque is transmitted without using gears.

In the present invention, when the one-way clutch is disposed between the sun gear and the carrier, the outer race of the one-way clutch is integrally provided with one clutch hub concentrically connected to the carrier, and the inner Since the race is constructed without being integrally formed with the element to carry it and splined to said element, it is concentrically and axially connected to the planetary gear mechanism that achieves the overdrive gear ratio. The one-way clutch can be configured in a position extremely close to the planetary gear mechanism, and the concentric arrangement with the planetary gear mechanism is extremely good. Even in cases where the inner race of a one-way clutch is not formed integrally with the element that is to support it, and the inner race is spline-fitted with the element, the spline-fitting portion is It absorbs misalignment and vibration, suppressing the generation of vibration and heat. Furthermore, oil supply to the one-way clutch can be done extremely easily and reliably by drilling oil holes in the inner race.
Significantly improves the durability of one-way clutches.

In other words, the outer race of the one-way clutch is provided integrally with one of the clutch hubs concentrically connected to the carrier of the planetary gear mechanism, and the inner race is configured without being integrally formed with the element that supports it. When this is spline-coupled to the above-mentioned element, the one-way clutch is disposed concentrically and axially parallel to the planetary gear mechanism, making the gear transmission compact and shortening the torque transmission path, and as described below. This has the advantage of reducing the load on the one-way clutch.

However, on the other hand, when the input shaft is driven with the sun gear of the planetary gear mechanism being braked, the planetary binion engages with the sun gear and ring gear through the carrier connected to the input shaft and rotates around the axis of the sun gear. The planetary gear mechanism attempts to revolve around the axis of the sun gear and center itself around the axis of the sun gear, but the torque acting on the surface that meshes with the sun gear and the planetary binion at this time is a dog, so there is a dimensional error in each element of the planetary gear mechanism. If there is a problem or there is an installation error in the assembly, the force acting on the meshing surface will be partially excessive, causing the axis of the sun gear to vibrate or the rotating shaft of the carrier that supports the planetary pinion to vibrate. do.

Therefore, when the inner race of the one-way clutch is fixed to the element to be carried, the rotation of the inner race will include a large eccentric runout relative to the outer race formed integrally with the carrier. become.

By the way, the sprags of a one-way clutch slide along with the outer race on the inner surface of the inner race in metal contact at the rotational speed of the input shaft, and when the relatively large eccentric runout occurs, the sprag comes into contact with each race. This accelerates the wear of the cam surface, causing early damage to the one-way clutch.

This is because the action of the sprag lug meshing with the inner race and the outer race is performed by the shape of the cam surface at the contact point between the cam surface of the sprag and the inner surface of each race and the torque received by the sprag lug. Wear on the surfaces can cause hopping, which causes the sprag to bounce out of engagement, hop-out, which causes the sprag to bite into the cage that holds it between the races, and even rollover, which causes the sprag to go too far in the direction of engagement and reverse the sprag. This causes damage to the one-way clutch.

However, in the present invention, since the inner race of the one-way clutch is spline-coupled to the element that supports it, the inner race between the carrier and the sun gear, that is, the inner race connecting the inner race and the outer race of the one-way clutch is Even if eccentric runout occurs in the relative rotation between the race and the element that should carry it, the runout is removed by the spline connection between the inner race of the one-way clutch and the element that should carry it, and the inner race Since concentricity with respect to the outer race of the sprag is maintained, there is no risk of wear on the cam surface of the sprag due to the runout, thereby maintaining accurate operation of the one-way clutch and increasing its durability.

This configuration enables forced lubrication by supplying oil from the shaft hole of the input shaft or output shaft through the oil hole formed in the inner race of the one-way clutch, which improves the durability of the one-way clutch. It can be said.

The clutch is configured between a clutch hub integrally formed with the carrier and another clutch hub that is rotated integrally with the sun gear, and the brake is configured between the other clutch hub and the housing of the gear transmission. Therefore, these clutches and brakes can be constructed on the outer periphery of the one-way clutch, and the outer diameter and engagement area of the frictional engagement part are large, resulting in good efficiency and space saving. To effectively utilize the overdrive gear transmission without increasing the axial dimension of the overdrive gear transmission.

When constructing the brake, if a brake hub is connected to the other end of the other clutch hub in the axial direction and the brake is constructed between the brake hub and the housing, the structure of the clutch cylinder can be simplified and the brake installation location can be reduced. You can expand your freedom.

Therefore, when the present invention is combined with a torque converter and a conventional gear transmission to form an automatic transmission, an overdrive gear train can be added without impairing the performance of the conventional gear transmission. The clutch and brake can be controlled using the control pressure oil of the hydraulic control circuit of the automatic transmission, and the increase in the axial dimension of the automatic transmission is kept as small as possible, and an overdrive gear ratio can be added. This makes it possible to construct an automatic transmission extremely easily.

Furthermore, in the present invention, the clutch is constructed between one clutch hub that is formed integrally with the carrier and the other clutch hub that rotates integrally with the sun gear, so that the sun gear is stopped by the brake and is locked to the housing. When the clutch is released and an overdrive ratio is achieved, one clutch hub integrally formed with the carrier rotates idly and its rotational speed becomes equal to the input rotational speed, but one clutch hub is connected to the ring gear. When overdrive is achieved, the ring gear's input rotational speed increases by the speed increase, so the rotation speed of the clutch hub connected to the ring gear also increases by the speed increase.

This reduces power loss due to a reduction in the agitation resistance of the hydraulic oil inside the transmission as the clutch hub and friction plates rotate, and prevents adverse effects on the transmission due to an increase in the temperature of the hydraulic oil caused by this agitation. Furthermore, it has a great effect on reducing the drag resistance that occurs between the friction plate and the pressure plate, and the torque required on the driven shaft is low and high speeds are required, especially when a car runs at high speed on a flat road for a long time. In the case of a rotary drive mode, in order to achieve the purpose of saving energy consumed by the prime mover, it is highly effective in an overdrive gear transmission that constitutes a gear train with a gear ratio smaller than 1. .

[Brief explanation of the drawing]

FIG. 1 is a schematic diagram of an automatic transmission in which the present invention is implemented as an auxiliary transmission, and FIG. 2 is a partial sectional view of an embodiment of the present invention. In the figure, 1... Output shaft of the prime mover, 2...
...Torque converter, 100...Gear transmission device of automatic transmission, 200...Sub-transmission, 8,9
, 10... Planetary gear transmission, 21.81.9
1...Sun gear, 22.82,92...
・Planetary pinion, 24°84.94...
Carrier, 23, 83, 93... Ring gear, 11, 12, 13... Clutch, 14.1
5, 16, 17... Brake, 20, 18゜1
9 shows a one-way clutch, 37 shows an outer race, and 38 shows an inner race.

Claims (1)

[Scope of utility model registration request] a planetary gear mechanism including a sun gear, a planetary binion, and a ring gear; an input shaft concentrically connected to a carrier that supports the planetary binion; an output shaft concentrically connected to the ring gear; and the sun gear and the carrier. a friction plate type clutch that freely engages and disengages the
The outer race of the one-way clutch includes a friction plate type brake that brakes the sun gear, and a one-way clutch that is disposed between the sun gear and the carrier and causes the carrier to overrun when the sun gear is braked. is integrally provided on one clutch hub concentrically connected to the carrier, the inner race of the one-way clutch is splined to the element to carry the inner race, and the clutch is connected to the one clutch hub. and another clutch hub that rotates integrally with the sun gear, and the brake is configured between the other clutch hub and the housing of the gear transmission. Drive gear transmission.