JPH06221387A - Gear speed change device for automatic transmission - Google Patents

Abstract

PURPOSE:To improve motive power transmission efficiency in the case of the above gear speed shift device for a vehicle automatic transmission by arranging a main shaft and an auxiliary shaft in parallel with each other, conducting connection between each through planetary gear devices and pairs of counter gears, and making constitution so that the relative rotation of each rotary element of the planetary gear mechanisms may be prevented at a second speed and a fourth speed and a relative rotation number may be made small at a third speed. CONSTITUTION:A first planetary gear mechanism 1 is arranged coaxially with a main shaft 3 into which torque is inputted, and a second planetary gear mechanism 2 is arranged coaxially with an auxiliary shaft 4 that is arranged in parallel with the main shaft 3 and from which torque is outputted to a drive shaft. Also, pairs of counter gears 6, 7 are provided between both planetary gear mechanisms 1, 2, and torque transmission is carried out. The sun gear 1S of the planetary gear mechanism 1 is made rotatable together with either drive gear 6a, and a ring gear 1R is made rotatable togeth with each drive gear 7a. Also, respective drive gears 6a, 7a are made rotatable together with the main shaft 3, and driven gears 6b, 7b are made rotatable together with the auxiliary shaft 4.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gear transmission used in an automatic transmission for a vehicle, and in particular, a main shaft to which torque is input from an engine and a sub shaft for outputting torque to a drive shaft and the like are parallel to each other. The present invention relates to a gear transmission device which is arranged at a main shaft and transmits a torque from its main shaft to a sub shaft through a planetary gear mechanism and two pairs of counter gears.

[0002]

2. Description of the Related Art This type of gear transmission is capable of shortening the shaft length, so that an engine such as an FF vehicle (front engine / front drive vehicle) or an RR vehicle (rear engine / rear drive vehicle) is mounted on the vehicle body. In contrast, it is suitable for an automatic transmission mounted on a vehicle that is placed sideways. For example, Japanese Patent Laid-Open No. 60-188645 discloses a gear transmission for an automatic transmission having the following structure.

That is, in the device disclosed in Japanese Unexamined Patent Publication No. 60-188645, the first planetary gear mechanism is arranged on the same axis as the input shaft, and the clutch is provided between the sun gear and the ring gear and the input shaft. Placed,
The first drive gear is connected to the sun gear and the second drive gear is connected to the carrier.
On the other hand, the output shaft parallel to the input shaft is directly connected to the ring gear of the second planetary gear mechanism arranged on the same axis as the output shaft,
A second driven gear is attached to the ring gear. A clutch is provided between the sun gear and the first driven gear and between the carrier and the first driven gear, and a brake that selectively stops rotation of the sun gear and a brake that selectively stops rotation of the carrier are provided. Has been.

[0004]

As is well known, in a planetary gear mechanism, the input element, the fixed element, and the output element are appropriately changed to perform a speed-up action, a deceleration action, and a reversal action. In the gear train of the machine, those elements in each planetary gear mechanism are switched by a clutch or a brake to execute gear shifting. On the other hand, in the gear train using the counter gear pair described above, even if the gear ratios of the plurality of counter gear pairs are made different, and the torque is transmitted from the input shaft to the output shaft via only the counter gear pair. It is possible to execute a predetermined shift speed, which improves the power transmission efficiency.

Therefore, also in the above-described conventional gear transmission, the gear ratio of one counter gear pair is made larger than "1" and the gear ratio of the other is made smaller than "1".
In the third forward speed and the fourth forward speed, gear shifting is performed by only one of the counter gear pairs. Therefore, among the five forward speeds, the power transmission efficiency is good at the third speed and the fourth speed at which the planetary gear mechanism does not operate. However, in the above-mentioned conventional device, when the second speed is set, the sun gear of the planetary gear mechanism arranged on the same axis as the input shaft is fixed and the ring gear of the planetary gear mechanism is rotated together with the input shaft. Torque is transmitted from the carrier rotating at a lower speed to the output shaft via the counter gear pair. For this reason, at the second speed, the relative rotational speed of the rotary elements of the planetary gear mechanism on the input shaft side becomes high, resulting in inconvenience such as poor power transmission efficiency.

The present invention has been made in view of the above circumstances, and it is an object of the present invention to provide a gear transmission that has good power transmission efficiency and is advantageous for downsizing an automatic transmission.

[0007]

In order to achieve the above object, the invention described in claim 1 has a main shaft, a sub shaft arranged in parallel to the main shaft, and a main shaft arranged on the same axis. A single pinion type planetary gear mechanism, a first counter gear pair having a drive gear and a driven gear meshing with the drive gear, another drive gear, and a driven gear meshing with the other drive gear.
A second counter gear pair having a gear ratio different from that of the counter gear pair, the carrier of the planetary gear mechanism is rotatable with the main shaft, and the sun gear of the planetary gear mechanism is rotatable with any drive gear. And the ring gear is rotatable with other drive gears, the drive gears are rotatable with the main shaft, and the driven gears are rotatable with the auxiliary shaft.

According to the second aspect of the present invention, another planetary gear mechanism is provided on the same axis as the sub shaft, and any driven element is provided on any one of the rotary element and the sub shaft of the other planetary gear mechanism. Is connected, another driven gear is connected to another rotating element in the other planetary gear mechanism, and two rotating elements in the other planetary gear mechanism are connected to integrally rotate the entire planetary gear mechanism. Clutch means is provided for causing the movement.

Further, according to the invention of claim 3, in the structure described in claim 1, each driven gear and the sub shaft are connected to each other via the clutch means or directly.

On the other hand, according to the invention described in claim 4, in the invention described in claim 1, the planetary gear mechanism on the same axis as the main shaft is replaced with a double pinion type planetary gear mechanism, and accordingly, the main shaft is replaced. Is rotatable with the ring gear, and the sun gear and the carrier are rotatable with any one of the drive gears.

According to a fifth aspect of the present invention, in addition to the structure of the fourth aspect, another planetary gear mechanism is provided on the same axis as the sub shaft, and any rotating element and sub shaft of the other planetary gear mechanism are provided. And any one of the driven gears is connected to the other planetary gear mechanism, the other driven gear is connected to the other rotary element of the other planetary gear mechanism, and the two rotary elements of the other planetary gear mechanism are connected to the planetary gear. Clutch means for integrally rotating the entire gear mechanism is provided.

According to the invention of claim 6, in the construction of the invention of claim 4, each driven gear and the counter shaft are connected to each other via the clutch means or directly.

[0013]

In the invention described in claim 1 or 4, it is possible to eliminate the relative rotation of each rotary element of the planetary gear mechanism in the second speed and the fourth speed of the five forward speed stages. Further, it is possible to reduce the relative rotational speed of each rotary element of the planetary gear mechanism that operates at the third speed, and thus the power transmission efficiency is improved.

Further, in the invention described in claim 2 or 5, it is possible to set 5 forward gears and 1 reverse gear with the structure of 3 clutches and 3 brakes, so that the number of friction engagement devices required is small. As a result, the automatic transmission is downsized.

Further, in the invention described in claim 3 or 6, since the planetary gear mechanism is not provided on the auxiliary shaft side,
It is a compact gear transmission that can set four forward speeds.

[0016]

EXAMPLES Next, the present invention will be described more specifically based on examples. FIG. 1 is a skeleton diagram showing an embodiment of the present invention, in which a single pinion type first planetary gear mechanism 1 and a second planetary gear mechanism 2 are used, and the first planetary gear mechanism 1 receives a torque input. The second planetary gear mechanism 2 is arranged on the same axis as the main shaft 3, and is arranged parallel to the main shaft 3 and on the same axis as the auxiliary shaft 4 that outputs torque to a drive shaft (not shown) or the like. Here is an example. These planetary gear mechanisms 1 and 2 include sun gears 1S and 2S, ring gears 1R and 2R that are internal gears, and sun gears 1S and 2S.
And the carriers 1C and 2C holding the pinion gears meshing with the ring gears 1R and 2R are used as rotating elements.

The sun gear 1 of the first planetary gear mechanism 1
A first clutch K1 is provided between S and the main shaft 3, and a second clutch K2 is provided between the carrier 1C and the main shaft 3. A first brake B1 for stopping the rotation of the sun gear 1S is provided between the sun gear 1S and a predetermined fixed portion (for example, a casing) 5, and a second brake B2 for stopping the rotation of the carrier 1C is provided in the carrier 1C. And the casing 5.

On the other hand, the carrier 2C of the second planetary gear mechanism 2 is connected to the auxiliary shaft 4 so as to rotate integrally therewith. A third clutch K3 for integrally rotating the second planetary gear mechanism 2 is provided between the ring gear 2R and the sun gear 2S. Further, a third brake B3 for stopping the rotation of the sun gear 2S is provided between the sun gear 2S and the casing 5.

The torque transmission between the first planetary gear mechanism 1 and the second planetary gear mechanism 2 is performed by two counter gear pairs 6,
Performed by 7. That is, these counter gear pairs 6 and 7 are respectively composed of drive gears 6a and 7a and driven gears 6b and 7b which mesh with them.
The drive gears 6a and 7a are provided on the same axis as the main shaft 3, and the driven gears 6b and 7b are provided on the same axis as the auxiliary shaft 4. The drive gear 6a of the first counter gear pair 6 is connected to the ring gear 1R of the first planetary gear mechanism 1 so as to rotate integrally, and the drive gear 7a of the second counter gear pair 7 is connected to the first planetary gear set. It is connected to the sun gear 1S of the mechanism 1 so as to rotate integrally. Further, the driven gear 6b of the first counter gear pair 6 is coupled to the carrier 2C of the second planetary gear mechanism 2 so as to rotate integrally, and the driven gear 7b of the second counter gear pair 7 is connected to the ring gear 2R of the second planetary gear mechanism 2. Is connected so as to rotate integrally. In the example shown in FIG. 1, the gear ratio i1 of the first counter gear pair 6 is set smaller than "1", and the gear ratio i2 of the second counter gear pair 7 is set to a value larger than "1". .

In the transmission having the above-mentioned structure, any one of
By engaging one of the friction engagement devices, it is possible to set a shift speed of five forward gears and one reverse gear, and the engagement operation table is shown in FIG. Hereinafter, each shift speed will be described.

First, in the first forward speed, the first clutch K1 and the third brake B3 are engaged. Therefore, in the first planetary gear mechanism 1, the carrier 1C is not connected to both the main shaft 3 and the casing 5, so that the first planetary gear mechanism 1 does not perform the gear shifting action. That is, the drive gear 7a of the second counter gear pair 7 rotates together with the main shaft 3,
The second planetary gear mechanism 2 is connected via the second counter gear pair 7.
The ring gear 2R of is rotated at a reduced speed with respect to the main shaft 3. In the second planetary gear mechanism 2, the sun gear 2S is fixed by the third brake B3, so that the carrier 2C and the sub shaft 4 connected thereto rotate at a lower speed than the ring gear 2R. That is, the counter shaft 4 rotates at a rotational speed reduced by the second counter gear pair 7 and the second planetary gear mechanism 2 with respect to the main shaft 3, and the gear ratio thereof is represented by the following formula. In the following description, ρ1 is the gear ratio of the first planetary gear mechanism 1 and ρ2 is the gear ratio of the second planetary gear mechanism 2.

I2 (1 + ρ2) The second forward speed is set by engaging the first clutch K1 and the third clutch K3. In this case as well, the carrier 1C of the first planetary gear mechanism 1 is not constrained to either the main shaft 3 or the casing 5, so that the first planetary gear mechanism 1 does not perform a gear shifting action. Further, since the ring gear 2R and the sun gear 2S are integrally connected by the third clutch K3, the second planetary gear mechanism 2 rotates as a whole. Therefore, the counter shaft 4 is second with respect to the main shaft 3.
The counter gear pair 7 rotates at a reduced rotation speed only, and its gear ratio is "i2" which is the gear ratio of the second counter gear pair 7.
It is represented by ".

The third speed is set by engaging the second clutch K2 and the third clutch K3. In this case, the carrier 1C of the first planetary gear mechanism 1 rotates together with the main shaft 3, and the sun gear 1S and the ring gear 1R of the carrier 1C and the counter gear pair 6,
The second planetary gear mechanism 2 rotates by being restrained from the side of the second planetary gear mechanism 2 via 7, but the second planetary gear mechanism 2 rotates as a whole due to the engagement of the third clutch K3. Since the gear ratio i1 of the first counter gear pair 6 is smaller than the gear ratio i2 of the second counter gear pair 7,
The sun gear 1S of the planetary gear mechanism 1 rotates at a higher speed than the ring gear 1R. That is, the third speed is set by the first planetary gear mechanism 1 and the counter gear pairs 6, 7 performing a gear shifting action, and the gear ratio is represented by (i1 + i2 · ρ1) / (1 + ρ1). To be done.

The fourth speed is set by engaging the first clutch K1 and the second clutch K2. Therefore, in the first planetary gear mechanism 1, the sun gear 1S rotates integrally with the main shaft 3 together with the carrier 1C, so that the entire sun gear 1S integrally rotates. On the other hand, in the second planetary gear mechanism 2, since the sun gear 2S thereof is not connected to either the ring gear 2R or the casing 5, the second planetary gear mechanism 2 does not perform the gear shifting action. Therefore, torque is directly transmitted to the counter shaft 4 through the first counter gear pair 6, and as a result, the rotation speed of the main shaft 3 is reduced only by the first counter gear pair 6. It becomes the number of rotations. That is, the gear ratio of the fourth speed is represented by "i1" which is the gear ratio of the first counter gear pair 6.

The fifth speed is set by engaging the second clutch K2 and the first brake B1. In the first planetary gear mechanism 1, since the carrier 1C rotates together with the main shaft 3 while the sun gear 1S is fixed by the first brake B1, the ring gear 1R rotates at an increased speed with respect to the main shaft 3. On the other hand, since the second planetary gear mechanism 2 does not perform the gear shifting operation as in the case of the above-described fourth speed, the sub shaft 4 includes the ring gear 1R to the first counter gear pair 6 of the first planetary gear mechanism 1.
It receives torque via and rotates. Therefore, the rotation speed of the sub shaft 4 is larger than that of the main shaft 3 by the first planetary gear mechanism 1
And the rotation speed increased by the first counter gear pair 6,
The gear ratio is represented by i1 / (1 + ρ1).

The reverse speed is set by engaging the first clutch K1 and the second brake B2. In this case, contrary to the case of the above fifth speed, since the sun gear 1S is rotated together with the main shaft 3 with the carrier 1C of the first planetary gear mechanism 1 fixed, the ring gear 1R is rotated relative to the main shaft 3. This ring gear 1
Torque is transmitted from R to the counter shaft 4 via the first counter gear pair 6. Therefore, the rotation speed of the counter shaft 4 is reversely reduced by the first planetary gear mechanism 1 with respect to the rotation speed of the main shaft 3, and
The counter gear pair 6 increases the rotational speed, and the speed ratio thereof is represented by i1 / ρ1.

Next, another embodiment of the present invention will be described.
FIG. 3 shows the first planetary gear mechanism 1 of the above-described gear transmission.
To a double pinion type planetary gear mechanism, and accordingly, a second clutch K2 is provided between the ring gear 1R and the main shaft 3, and a second clutch K2 is provided between the ring gear 1R and the casing 5.
A brake B2 is provided, the drive gear 6a of the first counter gear pair 6 is further connected to the carrier 1C, and the other structure is the same as that shown in FIG.

Even with the configuration shown in FIG. 3, by engaging and disengaging each frictional engagement device as shown in FIG. 2, it is possible to set a shift speed of 5 forward gears and 1 reverse gear. .

The example shown in FIG. 3 is an example in which the first planetary gear mechanism 1 of the configuration shown in FIG. 1 is replaced with a double pinion type, but in the present invention, together with this or this Instead of this, the second planetary gear mechanism 2 may be of the double pinion type. Further, the clutch for integrally rotating the entire second planetary gear mechanism 2 is only required to connect at least any two rotating elements, and not to connect the ring gear 2R and the sun gear 2S. Not limited.

By the way, in the gear transmission shown in FIG. 1 or FIG. 3, as is known from the operation table of FIG. 2, the second planetary gear mechanism 2 performs the gear shifting operation only at the first speed, and any other gear stage. Also in the above, the second planetary gear mechanism 2 does not particularly perform the speed change action. Therefore, by removing the second planetary gear mechanism 2 from the configuration shown in FIG. 1 and making some changes accordingly, it is possible to provide a gear transmission that can set four forward gears and one reverse gear.

An example thereof is shown in FIG. 4, in which the driven gears 6b and 7b are directly connected to the counter shaft 4, and the sun gear 1S and the drive gear of the second counter gear pair 7 are connected. A third clutch K3 is provided between the second clutch 7a and the motor 7a, and the other structure is the same as that shown in FIG.

In the gear transmission shown in FIG. 4, each of the friction engagement devices is engaged / released as shown in the operation table of FIG. 5 to set each of four forward gears and one reverse gear. You can The operation table of FIG. 5 is the same as the operation table of FIG. 2 except that the first speed row and the B3 column are omitted. Then, the respective shift speeds are set in the same manner as the second speed to the fifth speed and the reverse speed described in the embodiment shown in FIG.

Further, in the gear transmission shown in FIG. 4, the planetary gear mechanism 1 can be changed from a single pinion type to a double pinion type.
An example is shown in FIG. Even with the configuration shown in FIG. 6, it is possible to set four forward gears and one reverse gear by engaging the friction engagement devices as shown in the operation table of FIG. In the configuration shown in FIG. 4 or 6, the third clutch K3 may be provided between the driven gear 7b of the second counter gear pair 7 and the sub shaft 4.

In the gear transmissions shown in FIGS. 4 and 6, only one set of planetary gear mechanism and five friction engagement devices are required, so that the gear transmission can be made compact.

The present invention is not limited to the above-mentioned embodiments, and the one-way clutch can be used together with the above-mentioned clutch and brake.

[0036]

As described above, in the gear transmission of the present invention in which the planetary gear mechanism is provided on each of the main shaft side and the sub shaft side, the power transmission efficiency is improved as compared with the prior art, and the vehicle transmission is improved. Fuel efficiency can be improved. Again 5
The frictional engagement device required for the configuration capable of setting one speed and one reverse speed may be three clutches and three brakes, and thus a compact gear transmission can be realized.

Further, in the construction in which the planetary gear mechanism is provided only on the main shaft side, there are 3 clutches and 2 brakes, 4 forward gears and 1 reverse gear.
The gear transmission is capable of setting the number of stages, and the reduction of the planetary gear mechanism and the friction engagement device can reduce the size of the automatic transmission.

[Brief description of drawings]

FIG. 1 is a skeleton diagram showing an embodiment of the present invention.

FIG. 2 is an engagement operation table of the gear transmission shown in FIG.

FIG. 3 is a skeleton diagram showing another embodiment of the present invention.

FIG. 4 is a skeleton diagram showing still another embodiment of the present invention.

5 is an engagement operation table of the gear transmission shown in FIG.

FIG. 6 is a skeleton diagram showing another embodiment of the present invention.

[Explanation of symbols] 1, 2 Planetary gear mechanism 1S, 2S Sun gear 1C, 2C Carrier 1R, 2R Ring gear 3 Main shaft 4 Secondary shaft 5 Casing 6,7 Counter gear pair

Claims (6)

[Claims] 1. A first shaft comprising a main shaft, a counter shaft arranged in parallel with the main shaft, a single pinion type planetary gear mechanism arranged on the same axis as the main shaft, a drive gear and a driven gear meshing with the drive gear. The planetary gear mechanism includes one counter gear pair, another drive gear, and a driven gear meshed with the other drive gear, and a second counter gear pair having a gear ratio different from that of the first counter gear pair. Carrier is rotatable with the main shaft,
The sun gear of the planetary gear mechanism is rotatable with any drive gear, the ring gear is rotatable with another drive gear, each drive gear is rotatable with the main shaft, and each driven gear is a sub gear. A gear transmission for an automatic transmission, which is configured to be rotatable together with a shaft. 2. Another planetary gear mechanism is provided on the same axis as the counter shaft, and any driven gear is connected to any one of the rotating elements and the counter shaft in the other planetary gear mechanism. Another driven gear is connected to another rotating element in the other planetary gear mechanism, and clutch means for connecting two rotating elements in the other planetary gear mechanism to integrally rotate the entire planetary gear mechanism is provided. The gear transmission for an automatic transmission according to claim 1, wherein: 3. The gear transmission for an automatic transmission according to claim 1, wherein each of the driven gears is connected to the counter shaft via clutch means or directly. 4. A first shaft comprising a main shaft, a sub-shaft arranged parallel to the main shaft, a double pinion type planetary gear mechanism arranged on the same axis as the main shaft, a drive gear and a driven gear meshing with the drive gear. 1 counter gear pair,
A second counter gear pair having another drive gear and a driven gear meshing with the other drive gear and having a gear ratio different from that of the first counter gear pair, and the ring gear of the planetary gear mechanism together with the main shaft. Is rotatable, the sun gear of the planetary gear mechanism is rotatable with any of the drive gears, the carrier is rotatable with other drive gears, and each of the drive gears is rotatable with the main shaft, and A gear transmission for an automatic transmission, wherein each driven gear is configured to be rotatable together with a sub shaft. 5. Another planetary gear mechanism is provided on the same axis as the sub shaft, and any one of the trivial gears is connected to any one of the rotating elements and the sub shaft of the other planetary gear mechanism, Another driven gear is connected to another rotating element of the other planetary gear mechanism, and clutch means for connecting two rotating elements of the other planetary gear mechanism to integrally rotate the entire planetary gear mechanism is provided. The gear transmission for an automatic transmission according to claim 4, wherein: 6. The gear transmission for an automatic transmission according to claim 4, wherein each of the driven gears is connected to the counter shaft via clutch means or directly.