JP3116630B2 - Gearbox for automatic transmission - Google Patents

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 more particularly, to a main shaft to which torque is input from an engine and a sub-shaft to output torque to a drive shaft or the like. And a gear transmission for shifting gears by transmitting torque from the main shaft to the sub shaft via a planetary gear mechanism and two pairs of counter gears.

[0002]

2. Description of the Related Art A gear transmission of this kind can reduce the shaft length, so that engines such as FF vehicles (front engine / front drive vehicle) and RR vehicles (rear engine / rear drive vehicle) are mounted on the vehicle body. It is suitable for automatic transmissions mounted on vehicles that are placed sideways. For example, Japanese Patent Application Laid-Open No. 60-188645 discloses a gear transmission for an automatic transmission having the following configuration.

That is, in the device described in Japanese Patent Application Laid-Open No. 60-188645, a first planetary gear mechanism is arranged on the same axis as an input shaft, and clutches are respectively provided between the sun gear and ring gear and the input shaft. Placed,
A first drive gear is connected to the sun gear, and a 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. Further, clutches are provided between the sun gear and the first driven gear and between the carrier and the first driven gear, respectively, and a brake for selectively stopping the rotation of the sun gear and a brake for selectively stopping the rotation of the carrier are provided. Have been.

[0004]

As is well known, a planetary gear mechanism performs a speed increasing action, a deceleration action, and a reversing action by appropriately changing its input element, fixed element, and output element. In the gear train of the machine, the switching of those elements in each planetary gear mechanism is performed by a clutch or a brake to execute a gear shift. On the other hand, in a gear train using the above-described counter gear pair, even if the gear ratio of the plurality of counter gear pairs is made different, torque can be transmitted from the input shaft to the output shaft via only the counter gear pair. A predetermined gear position can be executed, and power transmission efficiency is improved in such a case.

Therefore, in the conventional gear transmission described above, the gear ratio of one counter gear pair is made larger than "1" and the other gear ratio is made smaller than "1".
In the third forward speed and the fourth forward speed, the shift is performed by only one of the counter gear pairs. Therefore, of the five forward speeds, the power transmission efficiency at the third speed and the fourth speed at which the planetary gear mechanism does not operate is good. However, in the above-mentioned conventional apparatus, when setting the second speed, the sun gear of the planetary gear mechanism disposed 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, and accordingly, the ring gear is rotated. The torque is transmitted from the carrier rotating at a lower speed to the output shaft via the pair of counter gears. Therefore, in the second speed, the relative rotation speed of each rotating element of the planetary gear mechanism on the input shaft side becomes a high rotation speed, and as a result, power transmission efficiency is poor.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and has as its object to provide a gear transmission that has a good power transmission efficiency and is advantageous in reducing the size of an automatic transmission.

[0007]

In order to achieve the above object, according to the first aspect of the present invention, a torque is input.
Out a main shaft for the torque which is arranged parallel to the main axis
A countershaft for applying force, a single pinion type planetary gear mechanism arranged on the same axis as the main shaft, a first counter gear pair including a drive gear and a driven gear meshed with the drive gear, and another drive gear. A driven gear meshed with another drive gear, and a second counter gear pair having a different gear ratio from the first counter gear pair, wherein a carrier of the planetary gear mechanism 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 of the drive gears is rotatable with a main shaft, and each of the driven gears is a sub shaft. When the four forward speeds are set by being connected via the clutch means or directly,
Also, it is configured to output torque from the countershaft.

According to the second aspect of the present invention, a torque is input.
A main shaft of the order, the torque is arranged parallel to the major axis thereof
A sub- shaft for outputting, a single pinion type planetary gear mechanism arranged on the same axis as the main shaft, another planetary gear mechanism arranged on the same axis as the sub-shaft, a drive gear and the drive gear and the drive gear meshed therewith. 1st with driven gear
The single pinion type planetary gear comprising a counter gear pair, a second counter gear pair having another drive gear and a driven gear meshed with the other drive gear, and having a gear ratio different from that of the first counter gear pair; The carrier of the gear mechanism is rotatable with the main shaft, the sun gear of the single pinion type planetary gear mechanism is rotatable with any of the drive gears, and the ring gear of the single pinion type planetary gear mechanism is rotated with the other drive gears. Each drive gear is rotatable together with a main shaft, and any one of the driven gears is connected to any one of the rotating elements and the countershaft of the other planetary gear mechanism, and Another driven gear is connected to another rotating element in the gear mechanism, and further to the other planetary gear mechanism. A clutch hand stage to integrally rotate the entirety of the planetary gear mechanism connects the two rotating elements that, before
Brake means for setting another planetary gear mechanism to a deceleration operation state
Doo is provided, that is capable of setting five forward stages.

[0009]

According to a third aspect of the present invention, in the first aspect of the present invention, the planetary gear mechanism on the same axis as the main shaft is replaced with a double pinion type planetary gear mechanism. Is rotatable with the ring gear, and the sun gear and the carrier are each rotatable with one of the drive gears.

According to a fourth aspect of the present invention, in addition to the configuration of the third aspect, another planetary gear mechanism is provided on the same axis as the sub shaft, and each driven gear is connected to the sub shaft.
Instead of connecting directly or via clutch means,
While any of the rotating elements and the countershaft in the other planetary gear mechanism are connected to any of the driven gears,
The other is connected the other of the driven gear to the other rotating elements in the planetary gear mechanism, a clutch hand stage to integrally rotate the entirety of the planetary gear mechanism further connecting two rotating elements in the other planetary gear mechanism, The planetary gear mechanism
And a brake means for setting a deceleration operation state .

[0012]

[0013]

According to the first or third aspect of the present invention, since the planetary gear mechanism is not provided on the countershaft side, four forward gears are required.
A compact and compact gear transmission can be set.

According to the second or fourth aspect of the present invention, the second speed and the fourth speed are selected from among the five forward speeds.
To eliminate relative rotation of each rotating element of the planetary gear mechanism
Of the planetary gear mechanism that operates in the third speed.
It is possible to reduce the relative rotation speed of each rotating element.
Therefore, power transmission efficiency is improved. In addition, since five forward gears and one reverse gear can be set with the configuration of three clutches and three brakes, the required number of friction engagement devices is small, and as a result, the automatic transmission is downsized.

Furthermore, in the invention described in claim 3 or claim 6, since the planetary gear mechanism is not provided on the countershaft side,
A compact gear transmission that can set four forward speeds is provided.

[0016]

Next, the present invention will be described more specifically based on embodiments. 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 torque is input to the first planetary gear mechanism 1. The second planetary gear mechanism 2 is arranged on the same axis as the main shaft 3 and on the same axis as the sub shaft 4 which is arranged parallel to the main shaft 3 and outputs torque to a drive shaft (not shown). It is an example. These planetary gear mechanisms 1 and 2 include sun gears 1S and 2S, ring gears 1R and 2R as internal gears, and sun gears 1S and 2S.
And carriers 1C and 2C holding 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 (eg, casing) 5, and a second brake B2 for stopping the rotation of the carrier 1C is provided on 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 countershaft 4 so as to rotate integrally therewith. A third clutch K3 for integrally rotating the entire 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 pairs of counter gears 6,
7 is performed. That is, these counter gear pairs 6, 7 are composed of drive gears 6a, 7a and driven gears 6b, 7b meshing therewith, respectively.
The drive gears 6a, 7a are provided on the same axis as the main shaft 3, and the driven gears 6b, 7b are provided on the same axis as the sub 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 therewith, and the drive gear 7a of the second counter gear pair 7 is connected to the first planetary gear The sun gear 1S of the mechanism 1 is connected so as to rotate integrally. Further, the driven gear 6b of the first counter gear pair 6 is connected to the carrier 2C of the second planetary gear mechanism 2 so as to rotate integrally therewith, 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. It is connected so that it may 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 larger than "1". .

In the transmission having the above-described structure, any one of the two
By engaging the two friction engagement devices, five forward speeds and one reverse speed can be set, 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 any of the main shaft 3 and the casing 5, so that the first planetary gear mechanism 1 does not perform the shifting operation. That is, the drive gear 7a of the second counter gear pair 7 rotates together with the main shaft 3,
Through the second counter gear pair 7, the second planetary gear mechanism 2
Ring gear 2R 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 countershaft 4 connected thereto rotate at a lower speed than the ring gear 2R. That is, the sub 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 speed ratio is expressed by the following equation. In the following description, ρ1 indicates the gear ratio of the first planetary gear mechanism 1, and ρ2 indicates the gear ratio of the second planetary gear mechanism 2.

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

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 are connected to the counter gear pair 6,
7, the second planetary gear mechanism 2 is rotated by being restrained by the second planetary gear mechanism 2 side, but the whole of the second planetary gear mechanism 2 is integrally rotated by 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 first
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 each of the counter gear pairs 6 and 7 performing a speed change action, and the speed ratio is expressed by (i1 + i2 ・ ρ1) / (1 + ρ1). Is 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 whole thereof rotates integrally. On the other hand, in the second planetary gear mechanism 2, the sun gear 2S is not connected to either the ring gear 2R or the casing 5, so that the second planetary gear mechanism 2 does not perform the shifting operation. Therefore, torque is directly transmitted to the countershaft 4 via the first counter gear pair 6, and as a result, the rotation speed is reduced only by the first counter gear pair 6 with respect to the rotation speed of the main shaft 3. The number of rotations. That is, the speed 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, the carrier 1C rotates together with the main shaft 3 while the sun gear 1S is fixed by the first brake B1, so that 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 shifting operation as in the case of the above-described fourth speed, the countershaft 4 moves from the ring gear 1R of the first planetary gear mechanism 1 to the first counter gear pair 6
It rotates by receiving a torque through. Therefore, the rotation speed of the sub shaft 4 is larger than the rotation speed 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 fifth speed, the sun gear 1S rotates together with the main shaft 3 with the carrier 1C of the first planetary gear mechanism 1 fixed, so that the ring gear 1R moves with respect to the main shaft 3. The ring gear 1
The torque is transmitted from R to the countershaft 4 via the first counter gear pair 6. Therefore, the rotation speed of the sub-shaft 4 is reduced in reverse rotation by the first planetary gear mechanism 1 with respect to the rotation speed of the
The rotation speed is increased by the counter gear pair 6, and the speed ratio 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 gear transmission described above.
Is replaced by a double pinion type planetary gear mechanism, 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, and a drive gear 6a of the first counter gear pair 6 is connected to the carrier 1C. The other structure is the same as that shown in FIG.

Even with the structure shown in FIG. 3, the gears of five forward steps and one reverse step can be set by engaging and disengaging the friction engagement devices as shown in FIG. .

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, in conjunction with this or Instead, the second planetary gear mechanism 2 may be of a double pinion type. The clutch for integrally rotating the entire second planetary gear mechanism 2 only needs to connect at least one of the two rotating elements. The clutch for connecting the ring gear 2R and the sun gear 2S is not required. Not limited.

In the gear transmission shown in FIG. 1 or FIG. 3, as can be seen from the operation table of FIG. In this case, the second planetary gear mechanism 2 does not particularly perform the speed change operation. Therefore, by removing the second planetary gear mechanism 2 from the configuration shown in FIG. 1 and making a slight change accordingly, a gear transmission capable of setting four forward speeds and one reverse speed can be provided.

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

In the gear transmission shown in FIG. 4, each of the four forward speeds and one reverse speed is set by engaging and disengaging the friction engagement devices as shown in the operation chart of FIG. Can be. The operation table of FIG. 5 is the same as the operation table of FIG. 2 except that the row of the first speed and the column of B3 are omitted. Each shift speed is set in the same manner as the second to fifth speeds 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, by setting the friction engagement devices to engage as shown in the operation table of FIG. 5, it is possible to set the four forward speeds and one reverse speed. In the configuration shown in FIG. 4 or FIG. 6, the third clutch K3 may be provided between the driven gear 7b of the second counter gear pair 7 and the countershaft 4.

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

Note that the present invention is not limited to the above-described embodiments, and a one-way clutch can be used in combination with the above-described clutch and brake.

[0036]

As described above, in the gear transmission according to the present invention, the planetary gear mechanism is provided on each of the main shaft side and the counter shaft side, so that the power transmission efficiency is improved as compared with the conventional case, and the vehicle transmission is improved. Fuel efficiency can be improved. Also advance 5
In order to provide a configuration capable of setting one gear and one reverse, the required friction engagement device may be three clutches and three brakes, so that a compact gear transmission can be provided.

Further, in a configuration in which a planetary gear mechanism is provided only on the main shaft side, three clutches, two brakes, four forward steps, and one reverse step
The gear transmission can be set in stages, and the size of the automatic transmission can be reduced by reducing the number of planetary gear mechanisms and friction engagement devices.

[Brief description of the drawings]

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

FIG. 2 is an engagement operation table of the gear transmission shown in FIG. 1;

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.

FIG. 5 is an engagement operation table of the gear transmission shown in FIG. 4;

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 sub shaft 5 casing 6,7 counter gear pair

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int.Cl. ⁷ , DB name) F16H 3/62 F16H 3/66

Claims (4)

(57) [Claims] And 1. A for inputting the torque main axis, a minor axis for outputting a torque disposed parallel to its main axis,
A single pinion type planetary gear mechanism arranged on the same axis as the main shaft, a first counter gear pair including a drive gear and a driven gear meshed with the drive gear, and another drive gear and a driven gear meshed with the other drive gear And a second counter gear pair having a different gear ratio from the first counter gear pair, wherein the carrier of the planetary gear mechanism is rotatable together with the main shaft, and the sun gear of the planetary gear mechanism is one of Are rotatable together with the drive gear, and the ring gear is rotatable with the other drive gears, each of the drive gears is rotatable with the main shaft, and each of the driven gears is the sub shaft, via a clutch means, Or directly, linked ,
Four forward gears are set, and the
A gear transmission for an automatic transmission, which is configured to output a torque. 2. A for inputting the torque main axis, a minor axis for outputting a torque disposed parallel to its main axis,
A first counter gear including a single-pinion type planetary gear mechanism arranged on the same axis as the main shaft, another planetary gear mechanism arranged on the same axis as the sub-shaft, a drive gear and a driven gear meshed with the drive gear. The single-pinion type planetary gear mechanism, comprising: a pair of gears; and a second counter gear pair having a different drive gear and a driven gear meshed with the other drive gear and having a different gear ratio from the first counter gear pair. Carrier is rotatable with the main shaft, the sun gear of the single pinion type planetary gear mechanism is rotatable with any of the drive gears,
And the ring gear of the single pinion type planetary gear mechanism is rotatable with other drive gears, and each of the drive gears is rotatable with the main shaft, and any one of the rotating element and the sub shaft in the other planetary gear mechanism is used. To
One of the driven gears is connected, another driven gear is connected to another rotating element of the other planetary gear mechanism, and the other driven gear is connected to the other planetary gear mechanism.
A clutch hand stage to integrally rotate the entirety of the planetary gear mechanism connecting the One rotary element, reducing the other planetary gear mechanism
Brake means for setting a fast acting state, and a forward 5
Automatic transmission speed change gear according to claim that you have been configured to set the. 3. A for inputting torque main axis, a minor axis for outputting a torque disposed parallel to its main axis,
A double pinion type planetary gear mechanism disposed on the same axis as the main shaft, a first counter gear pair including a drive gear and a driven gear meshed with the drive gear, and 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, wherein a ring gear of the planetary gear mechanism is rotatable together with the main shaft, and a sun gear of the planetary gear mechanism is one of And the carrier is rotatable with another drive gear, and each of the drive gears is rotatable with the main shaft and each of the driven gears is on the sub shaft, via a clutch means, or Directly linked , forward 4
The gear stage is set and the torque is
A gear transmission for an automatic transmission characterized by being configured to output . 4. A for inputting the torque main axis, a minor axis for outputting a torque disposed parallel to its main axis,
A first counter gear including a double pinion type planetary gear mechanism arranged on the same axis as the main shaft, another planetary gear mechanism arranged on the same axis as the sub-shaft, a drive gear and a driven gear meshed with the drive gear. A double-pinion type planetary gear mechanism, comprising a pair, a second counter gear pair having another drive gear and a driven gear meshed with the other drive gear and having a different gear ratio from the first counter gear pair. Ring gear is rotatable with the main shaft, the sun gear of the double pinion type planetary gear mechanism is rotatable with any drive gear, and the carrier of the double pinion type planetary gear mechanism is rotatable with other drive gears. And each of the drive gears is rotatable together with the main shaft, and the other planetary gear mechanism One of the driven gears is connected to one of the rotating elements and the countershaft, and another driven gear is connected to another rotating element of the other planetary gear mechanism. a clutch hand stage to integrally rotate the entirety of the planetary gear mechanism connects the rotary element, the other planetary gear mechanism decelerating operation
And a brake means for operating the vehicle.
Automatic transmission speed change gear according to claim that you have been constant capable constructed.