JPS6323052A - Gear transmission device - Google Patents

Abstract

PURPOSE:To prohibit unnecessary high speed revolution of a simple planetary gear set by placing the third clutch between an output shaft and a carrier of the second simple planetary gear set, in a gear transmission device for automobiles. CONSTITUTION:The selective operation of 1st-3rd clutches 42, 44, 46 and 1st-3rd brakes 48, 50, 52 can provide four advance- and one reverse gearshifts, through the intermediary of 1st-2nd simple planetary gear sets 38, 40. Further, the second simple planetary gear set 40, when subjected to the unloaded condition without being involved in determining output revolution, releases the engagement of the carrier 64 of the second simple planetary gear set 40 with an output shaft 36 by the third clutch 46. Thus, each gear and so on of the second simple planetary gear set 40 can be prevented from developing its high revolution for determing the output revolution.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a gear transmission with four forward speeds and one reverse speed, which is suitable as a gear transmission for an automatic transmission for an automobile.

[Conventional technology]

As a gear transmission for an automatic transmission using a hydraulic torque converter, a gear transmission with 3 forward gears and 11 forward gears is known, which is configured using two simple planetary gear sets.

Furthermore, a gear transmission with four forward speeds and one reverse speed is constructed by adding one set of simple planetary gear sets to the above gear transmission and arranging three sets of simple planetary gear sets in series in the direction of the power transmission shaft. Are known.

In this gear transmission with 4 forward speeds and 1 reverse speed, the number of simple planetary gear sets and the accompanying increase in control elements such as clutch devices and hydraulic devices increases the shaft length of the gear transmission, which increases cost and weight. There was an inconvenience that caused an increase.

As the shaft length of a gear transmission becomes longer, it becomes difficult to install it in vehicles with narrow mounting space, especially in front-engine/front-drive vehicles with horizontally mounted engines, because the shaft direction must be aligned with the width of the vehicle. , the difficulties have become remarkable.

Therefore, JP-A-60-125444, JP-A No. 60-125
As disclosed in No. 445, a gear transmission device has been developed that can obtain four speeds of four forward speeds and one reverse speed using a 21JI simple planetary gear set.

In the gear transmission disclosed in JP-A-60-125444, the simple planetary gear set 21J1 has a ring gear of one simple planetary gear set and a carrier of the other simple planetary gear set both coupled to the output shaft. , the sun gear of one simple planetary gear set and the sun gear of the other simple planetary gear set are both coupled to the intermediate shaft, so that the two simple planetary gear sets are related to each other.

Therefore, even if the output rotation is determined by only one simple planetary gear set and the other simple planetary gear set is in a no-load state, the rotation of each gear etc. of the simple planetary gear set in the no-load state will be determined by itself. This may result in unnecessary high rotation.

Even when a simple planetary gear set is not involved in determining the output rotation and is in an unloaded state, high rotation will have a negative effect on durability, so it is preferable to reduce the rotation as much as possible.

[Problem that the invention seeks to solve]

In view of the above, the present invention prevents the rotation of each gear of the simple planetary gear set in an unloaded state from reaching an unnecessary high rotation speed when obtaining four forward speeds and one reverse speed with two simple planetary gear sets. The purpose is to provide a possible gear transmission.

[Means for solving problems]

In the gear transmission device according to the present invention, Japanese Patent Application Laid-Open No. 60-1254
The above object is achieved by adding a third clutch device to the gear transmission disclosed in No. 4 and interposing this third clutch device between the carrier and the output shaft of the second simple planetary gear set. are doing.

That is, the gear transmission according to the present invention includes input shafts arranged concentrically with each other and rotatably supported by the transmission case;
The first and second gears are provided with an intermediate shaft and an output shaft, and a pinion rotatably supported by a carrier is meshed between the sun gear and the ring gear to form a set, each of which has the axis of the input shaft as the center of rotation or the center of revolution. It includes two second simple planetary gear sets, and further includes three clutch devices, first to third, and three brake devices, first to third, and the sun gear of the first simple planetary gear set. The sun gears of the second simple planetary gear set are each coupled to the intermediate shaft, the ring gear of the first simple planetary gear set is coupled to the output shaft, and the first clutch device is arranged to be able to couple the input shaft and the intermediate shaft, A second clutch device is arranged so as to be able to couple the input shaft and the carrier of the first simple planetary gear set, and a third clutch device is arranged so as to be able to couple the carrier of the second simple planetary gear set and the output shaft, The first brake device is arranged so that the ring gear of the second simple planetary gear set can be restrained to the transmission case, the second brake device is arranged so that the intermediate shaft can be restrained to the transmission case,
A third braking device is arranged to be capable of restraining the carrier of the first simple planetary gear set to the transmission case.

[Effect]

In the gear transmission with the above configuration, by selectively operating the first to third clutch devices and the first to third brake devices, it is possible to obtain four speeds of four forward speeds and one reverse speed. .

Further, when the second simple planetary gear set is not involved in determining the output rotation and is in a no-load state, if the third clutch device releases the connection between the carrier of the second simple planetary gear set and the output shaft, Unnecessarily high rotation of each gear of the second simple planetary gear set is prevented.

〔Example〕

FIG. 1 shows an embodiment of a gear transmission according to the present invention, which is applied to a front engine/front drive vehicle with a transverse engine.

The output of the engine 10 is input to a gear transmission 14 via a three-element, one-stage, two-phase hydraulic torque converter 12.
After being decelerated by this gear transmission 14, it is further decelerated by the final deceleration [16] and output to the left and right axle shafts 18, -.

The hydraulic torque converter 12 includes a pump 20, a turbine 22, and a stator 24. The pump 20 is connected to the output shaft 26 of the engine 10, and the turbine 22 is connected to the output shaft 26.
The input shaft 28 of the gear transmission Z 14 extends coaxially with the gear transmission Z 6.
is connected to. Further, the stator 24 is connected to a transmission case 32 via a one-way clutch 30.

The gear transmission 14 includes the input shaft 28 as well as an intermediate shaft 34 and an output shaft concentrically therewith. 36 is the transmission case 32
is housed within. These three shafts 28, 34, 36 are all supported by the transmission case 32 so as to be able to rotate independently of each other, and the output shaft 36 is fitted to the outer periphery of the intermediate portion in the longitudinal direction of the intermediate shaft 34. It is fitted onto the outer periphery of the longitudinally intermediate portion of the input shaft 28 .

The gear transmission 14 also includes first and second simple planetary gear sets 38.40, first to third clutch devices 42.44.46, and first to third brake devices 48.50.52. are housed in the transmission case 32.

1st and 2nd simple planetary gear set 3rd, 4th
0 is sun gear 54.56, ring gear 58.60,
They are each composed of a carrier 62, 64 and a pinion 66, 68. Four pinions 66.68 are provided in the first and second simple planetary gear sets 38.40, and the sun gear 54.56 and ring gear 58.60
It is arranged between the two so that they mesh with each other. The binions 66, 68 are each rotatably supported on a carrier 62, 64. These sun gears 54, 56, ring gears 58, 60, and carriers 62, 64 are all arranged with the axis of the input shaft 28 as the center of rotation. Furthermore, the pinions 66 and 68 are arranged with the axis of the input shaft 28 as the center of revolution.

The first to third clutch devices 42, 44, 46 and the first
The brake device 4 is of a known friction multi-plate type, and the second and third brake devices 50 and 52 are of a known brake band type, and these are individually controlled by a hydraulic control device (not shown). be done.

Each of the above-mentioned shafts 28.34.36, the first and second simple planetary gear sets 38.40, the first to third clutch devices 42.44.46, and the first to third brake devices 48.5o , 52 are arranged and related to each other as follows.

That is, the sun gear 54 of the first non-pull planetary gear set 38 and the sun gear 56 of the second dual planetary gear set 40 are each coupled to the intermediate shaft 34, and the ring gear 58 of the first simple planetary gear set 38 is coupled to the output shaft 36. ing.

Further, the first clutch device 42 is actuated and arranged to couple the input shaft 2 and the intermediate shaft 34, and the second clutch device 44 is actuated to connect the input shaft 2 and the first simple planetary gear set. The third clutch device 46 is arranged to couple the carrier 64 of the second simple planetary gear set 40 and the output shaft 36 when activated.

Further, the first braking device 48 is actuated and arranged to restrain the ring gear 60 of the second simple planetary gear set 40 to the transmission case 32, and the second braking device 50 is actuated to form the ring gear 60 of the second simple planetary gear set 40 on the intermediate shaft 34. The brake band is attached to the transmission case 3 so as to restrain the drum part that has been
2, the third braking device 52 is actuated to stop the carrier 62 of the first simple planetary gear set 38.
A brake band is arranged on the transmission case 32 so as to restrain the drum portion formed in the transmission case 32.

An output gear 70 is concentrically coupled to the output shaft 36 . This output gear 70 meshes with a transmission gear 74 coupled to one end of a transmission shaft 72. An output gear 76 is coupled to the other end of the transmission shaft 72, and this output gear 76 meshes with the final reduction gear 78 of the final reduction gear a16. The axle shafts 18 are taken out from the final reducer 16 on the left and right sides of the vehicle, and the front wheels (not shown) are attached to the axle shafts 18.Next, the operation of this embodiment will be explained.

The output rotation of the engine 10 is determined by the hydraulic torque converter 1
2, the torque is increased to the input shaft 2 of the gear transmission 14.
8, and the gear transmission 14 provides 4 forward gears and 1 reverse gear.
The gears are changed and the output is taken out to the output shaft 36. The drive rotation taken out to the output shaft 36 is transmitted from the output gear 70 to the transmission gear 74, and then transmitted to the output gear 76 via the transmission shaft 72.
transmitted to. Output gear 76 is the final 'lii! The final speed gear 78 of the machine 16 is rotated to rotate the front wheels (not shown) via the axle shafts 18,H.

The gear transmission 14 has four forward speeds and one reverse speed.
This is accomplished by controlling the three clutch devices 42, 44, and 46 and the three brake devices Z4B and 50.52 by a hydraulic control device (not shown). The clutch devices 42, 44, 46 are actuated and controlled to the clutch connected state, and the brake devices 48, 50, 52 are actuated and controlled to the braking state.

Table 1 shows clutch devices 42,44.
46 and brake equipment 48, 50, and 52 are shown, and the operating state is indicated by 'OJ' in the table.
Unmarked indicates inactive state. Table 2 also shows the reduction ratio (rotational speed of the input shaft 28/rotational speed of the output shaft 36) for each of the four gears.

Table 3 shows the rotation ratios between the gears of the first and second simple planetary gear sets 38 and 40 at each shift 4 when the input shaft rotation speed on the 2nd day is 1. In addition, Table 4 shows a case where the third clutch device 46 is controlled to be in a constantly operating state (as disclosed in Japanese Patent Application Laid-open No. 125444/1989 mentioned in the section of the prior art), in correspondence with Table 3. (This corresponds to a gear transmission with a similar configuration.)

In Table 1 and Table 2, the operation of the gear transmission in which the clutch device and brake device are controlled as shown in Table 1 will be explained.

(First series) At the first speed, the first clutch device 42, the third clutch device 46, and the first brake device 48 are operated. By actuating the first clutch device 42, the input shaft 28 and the intermediate shaft 34 are brought into a power connected state, and the second rotation of the input shaft is caused by the first simple planetary gear set 38 coupled to the intermediate shaft 34. It is transmitted to sun gear 54 and sun gear 56 of second simple planetary gear set 40 .

By actuating the third clutch device 46, the carrier 64 of the second simple planetary gear set 40 and the output shaft 36 are brought into a connected state. When the first brake device 4 is operated, the ring gear 60 of the second simple planetary gear set 40 is restrained by the transmission case 32 and prevented from rotating.

As a result, the rotation transmitted from the input shaft 28 to the sun gear 56 of the second simple planetary gear set 40 is transmitted to the pinion 68 meshed with the sun gear 56, causing the pinion 68 to rotate.

Pinion 68 is the second simple planetary gear set 4
Since the ring gear 60 of 0 is prevented from rotating,
The ring gear 60 rotates and revolves around its own axis along the internal teeth of the ring gear 60, and this revolution is outputted to the output shaft 36 as normal rotation and deceleration rotation via the carrier 64 of the second simple planetary gear set 40.

Note that in the first speed, rotation is also transmitted to the sun gear 54 of the first simple planetary gear set 38, but the second clutch device 44 and the third brake device 52 that engage the carrier 62 that supports the pinion 66 are Since both of them are in a non-operating state and the carrier 62 is in a free state, the pinion 66 freely rotates between the sun gear 54 and the ring gear 58, and the pinion 66 rotates freely between the sun gear 54 and the ring gear 58, and the first gear by the second simple planetary gear set 40 described above is shifted. It does not affect the ratio settings.

(Second Speed) In the second speed, the second clutch device 44, the third clutch device 46, and the first brake device 48 are operated.

By operating the second clutch device 44, the input shaft 2
8 and the carrier 62 of the first simple planetary gear set 38 are in a power connected state, and the pinion 66 supported by the carrier 62 is rotated. Third clutch device
By actuating a46, the carrier 64 of the second simple planetary gear set 40 and the output shaft 36 are brought into a connected state. When the first brake device 48 is activated, the ring gear 60 of the second simple planetary gear set 40 is restrained by the transmission case 32 and prevented from rotating.

As a result, the first simple planetary gear set 38
The rotation of the input shaft 28 transmitted to the pinion 66 as the revolution rotation of the pinion 66 is transmitted to the sun gear 54 and the ring gear 58 that mesh with the pinion 66. The rotation of the sun gear 54 and the ring gear 58 is caused by the rotation of the intermediate shaft 3, respectively.
4 and the sun gear 5 of the second simple planetary gear set 40 coupled to these gears via the output shaft 36.
6 and the carrier 64, and the rotation of the carrier 64 causes the pinion 68 to revolve. This sun gear 56 and pinion 68 are connected to the second simple planetary gear set 40.
Since the ring gear 60 is prevented from rotating, it rotates under predetermined conditions in relation to the first simple planetary gear set 38, and at this time the pinion 68 of the second simple planetary gear set 40 revolves. rotation and first
Ring gear 58 of simple planetary gear set 38
The rotation is outputted to the output shaft 36 as normal rotation and deceleration rotation.

(Third Speed) In the third gear, the first clutch device W142 and the second clutch device 44 are operated. By actuating the first clutch device 42, the input shaft 28 and the intermediate shaft 34 are brought into a power connected state, and the rotation of the input shaft 28 is caused by the sun gear of the first simple planetary gear set 38 coupled to the intermediate shaft 34. 54 and the sun gear 56 of the second simple planetary gear set 40. By operating the second clutch device 44, the input shaft 28 and the carrier 62 of the first simple planetary gear set 38 are brought into a power connected state.

As a result, the sun gear 54 and the carrier 62 rotate integrally with each other, so that the ring gear 58 that meshes with the pinion 66 supported by the carrier 62 also rotates integrally with the same rotation. This rotation of the ring gear 58 is extracted to the output shaft 36. Therefore, the rotation initiated by the output shaft 36 is equal to the rotation of the input shaft 28, and its reduction ratio is l.

In the second simple planetary gear set 40, although the sun gear 56 is rotated, the third clutch device 46 is not activated and the carrier 64 is not connected to the output shaft 36, and the first brake device 48 made by IJ
Since the carrier 64 and the ring gear 60 are not rotated and the rotation of the ring gear 60 is not prevented, the carrier 64 and the ring gear 60 are in a free state. Therefore, the sun gear 56 of the second simple planetary gear set 40 rotates the same as the sun gear 54 of the first simple planetary gear set 38, but
Carrier 64 and ring gear 6o are at most sun gear 5
The rotation will not exceed 4 rotations.

The third speed of the conventional gear transmission device (hereinafter referred to as the conventional device) shown in Japanese Patent Application Laid-Open No. 60-125444 differs from the case where the third clutch device 46 is also operated in the third speed of this embodiment. However, in this case, as shown in Table 4, in the second simple planetary gear set 40, the carrier 64 and the ring gear 60 are driven to rotate at the same rotation as the sun gear 54.

(Fourth Speed) In the fourth speed, the second clutch device 44 and the second brake device 50 are operated. By actuating the second clutch device 44, the input shaft 28 and the carrier 62 of the first simple planetary gear set 38 are brought into a power connection state B. When the second brake device 50 is operated, the intermediate shaft 34 is restrained by the transmission case 32 and prevented from rotating, and the sun gear 54 of the first simple planetary gear set 38 coupled to the intermediate shaft 34 and the second The sun gear 56 of the simple planetary gear set 40 is also prevented from rotating.

As a result, the first simple planetary gear set 38
With the rotation of the carrier 62, the pinion 66 supported by the carrier 62 rotates and revolves because the sun gear 54 is prevented from rotating.

The rotation of this pinion 66 rotates the ring gear 58,
The rotation of the ring gear 58 is outputted to the output shaft 36 as stopped rotation and accelerated rotation.

Note that the carrier 64 of the second simple planetary gear set 40 is in a free state because the third clutch device 46 is not activated and is not connected to the output shaft 36. Therefore, in the second simple planetary gear set 40, since the sun gear 56 is prevented from rotating as described above, the pinion 68 and carrier 64 have stopped rotating. As a result, the ring gear 60 of the second simple planetary gear set 40 also stops rotating.

The fourth speed of the conventional device is the same as the case where the third clutch device 46 is also operated in the fourth speed of this embodiment, but
In this case, the carrier 40 of the second simple planetary gear set 40 will be rotated via the output shaft 36. In addition, 1. As a result, the pinion 68 rotates and revolves around the sun gear 56, which is prevented from rotating, and the ring gear 60 is also rotated by the rotation of the pinion 68.
At this time, the rotation of the carrier 64 and the ring gear 60, especially the rotation of the ring gear 60, becomes extremely high as shown in Table 4.

(Reverse Travel) In reverse travel, the first clutch device 42 and the third brake device 52 are operated. By actuating the first clutch device 42, the input shaft 28 and the intermediate shaft 34 are brought into a power-coupled state, and the rotation of the input shaft 28 is controlled by the first simple clutch gear set coupled to the intermediate shaft 34. 38 sun gear 54
and is transmitted to the sun gear 56 of the second simple planetary gear set 40. By actuating the third brake device 52, the first simple planetary gear set 38
The carrier 62 is restrained by the transmission case 32 and prevented from rotating.

As a result, the first simple planetary gear set 38
The rotation of the input shaft 28 transmitted to the sun gear 54 is transmitted to the ring gear 58 via a pinion 66 that is meshed with the sun gear 54 . Since the carrier 62 is prevented from rotating, the pinion 66 rotates while being prevented from revolutionizing. Therefore, the ring gear 58 rotates in the opposite direction to the sun gear 54, and the rotation of the ring gear 58 causes the output shaft 36 to rotate.
It is taken out as a deceleration rotation of reverse rotation.

In the second simple planetary gear set 40, although the sun gear 56 is rotated, the third clutch device 46 is not activated and the carrier 64 is not connected to the output shaft 36, and the first brake device 48 is not actuated and ring gear 60 is not prevented from rotating, carrier 64 and ring gear 60 are in a free state. Therefore, in the second simple planetary gear set 40, the sun gear 56 rotates the same as the sun gear 54 of the first simple planetary gear set 38, but the carrier 64 and the ring gear 60 rotate at the same time as the sun gear 54 at most.
The rotation will never exceed the rotation of .

The reverse movement of the conventional device is the same as the case where the third clutch device 46 is also operated in the reverse movement of the present embodiment, but in this case, the carrier 64 of the second simple planetary gear set 40 is operated via the output shaft 36. It gets rotated,
Further, the ring gear 60 of the second simple planetary gear set 40 is rotated by the rotation of the carrier 64, and is also rotated by the pinion 68, which is rotated in the same direction as the revolution direction by the rotation of the sun gear 56. As shown in Table 4, the rotation is extremely high compared to the output rotation.

[Effects of Examples]

As described above, in this embodiment, the third clutch device 46 is added to output the carrier 64 of the second simple planetary gear set 40 during the third speed, fourth speed, and reverse, which are not involved in setting the output rotation. Since they are separated from the shaft 36, the gears and carrier of the second simple planetary gear set 40 are prevented from rotating at a higher speed than the rotation of the sun gear 54 of the first simple planetary gear set 38. As a result, the gear transmission bag W14 has reduced wear on the bearings, friction members of the crofch devices 42, 44, 46, and brake devices 48, 50, 52, and has improved durability. Furthermore, the lubrication means can be simplified. It has become possible.

In addition, vibration and noise caused by high rotation are also reduced, and when shifting between 3rd and 4th speeds, each Since the difference in rotation between the gears has become smaller, shift shock has also been alleviated.

[Other Examples]

In the above embodiment, in the third gear, the fourth gear, and when moving backward, the third gear
In the third and fourth speeds, the third clutch device 46 is controlled only when the engine 10 exceeds a predetermined rotation speed. It is also possible to control it so that it is in a non-operating state.

When controlled in this way, when the engine 10 is at a predetermined rotation speed or lower, the sun gear 56 or ring gear 60 of the second simple planetary gear set 40 is rotated as shown in Table 4. However, since the absolute rotation of the gear is low in this engine rotation range, there is no substantial adverse effect.

Furthermore, the reason why the rotation of the engine 10 is not controlled during reverse travel is because the ring gear 60 of the second simple planetary gear set 40 rotates as high as about three times the output revolution during reverse travel. However, since the engine 10 generally does not rotate at a high speed when traveling in reverse, it is advantageous in the design of the control device to control the third clutch device W46 by the rotation of the engine 10 during reverse as well as in third and fourth speeds. In some cases, there is no problem in doing so.

〔Effect of the invention〕

As explained above, in the present invention, in a gear transmission that can obtain four forward speeds and one reverse speed with two simple planetary gear sets, the rotation of each gear, etc. of the simple planetary gear set in a no-load state is This has the effect of being able to prevent unnecessary high rotations.

[Brief explanation of the drawing]

FIG. 1 is a skeleton diagram showing an embodiment of a gear transmission according to the present invention. 14... Gear transmission, 28... Input shaft, 32... Transmission case, 34... Intermediate shaft, 36... Output shaft, 38... First simple planetary gear set, 40
...Second simple planetary gear set, 54.5
6... Sun gear, 58.60... Ring gear, 62.64... Carrier, 66.68... Pinion, 42... First clutch device, 44... Second clutch device, 46... Third clutch device, 48... First brake device, 50... Second brake device, 52... Third brake device.

Claims (1)

[Claims] (1) An input shaft, an intermediate shaft, and an output shaft are arranged concentrically with each other and rotatably supported by the four transmission cases, and a pinion rotatably supported by a carrier is engaged between the sun gear and the ring gear. The first and second parts are arranged in pairs, each having the axis of the input shaft as the center of rotation or the center of revolution.
It is equipped with two sets of simple planetary gear sets, and further includes three clutch devices, first to third, and three clutch devices, first to third.
The sun gear of the first simple planetary gear set and the sun gear of the second simple planetary gear set are respectively coupled to the intermediate shaft, the ring gear of the first simple planetary gear set is coupled to the output shaft, and the sun gear of the first simple planetary gear set is coupled to the output shaft. A first clutch device is arranged to connect the input shaft and the intermediate shaft, a second clutch device is arranged to connect the input shaft and the carrier of the first simple planetary gear set, and a third clutch device connects the input shaft to the carrier of the first simple planetary gear set. The carrier of the second simple planetary gear set is arranged so as to be able to couple with the output shaft, the first brake device is arranged so as to be able to bind the ring gear of the second simple planetary gear set to the transmission case, and the second brake device is arranged so that the carrier of the second simple planetary gear set can be coupled to the output shaft. A gear transmission characterized in that the shaft is arranged so as to be able to be restrained in the transmission case, and the third brake device is arranged so that the carrier of the first simple planetary gear set can be restrained in the transmission case.