JP6802744B2 - transmission - Google Patents

Description

The present invention relates to a transmission.

Conventionally, in vehicles and the like, a transmission capable of shifting and outputting the input power has been used. A conventional transmission is provided with a plurality of planetary gear mechanisms including a sun gear, a carrier and a ring gear as rotating elements, and a plurality of connecting mechanisms capable of switching the connection state between the rotating element of the planetary gear mechanism and other elements, and has multiple stages. There are some that can realize the gears of.

For example, Patent Document 1 discloses a transmission having four planetary gear mechanisms and six connecting mechanisms and capable of realizing eight forward gears and one reverse gear.

U.S. Patent Application Publication No. 2014/0128199

By the way, in a vehicle equipped with a transmission, it is considered desirable to further increase the number of gears and increase the gear ratio range (ratio coverage) in order to improve fuel efficiency and drivability. By increasing the number of gears, the engine can always be operated in a fuel-efficient region, so that fuel efficiency can be improved. Further, by expanding the ratio coverage, it is possible to improve the acceleration performance of the low gear stage without impairing the fuel efficiency performance of the high gear stage, so that the drivability can be improved. However, when the number of gears is increased, the number of parts constituting the transmission may increase, which may increase the size of the transmission.

Therefore, the present invention has been made in view of the above problems, and an object of the present invention is a new and improved method capable of further increasing the number of gears while suppressing an increase in the size of the transmission. Is to provide the transmission.

In order to solve the above problems, according to a certain viewpoint of the present invention, the first planetary gear mechanism and the second planetary gear mechanism, which are planetary gear mechanisms provided in a case and provided with a sun gear, a carrier and a ring gear as rotating elements, The first connecting mechanism, the second connecting mechanism, and the third connecting mechanism, which are the connecting states of the third planetary gear mechanism and the fourth planetary gear mechanism, and the rotating element of the planetary gear mechanism and other elements can be switched. A transmission including a mechanism, a fourth connecting mechanism, a fifth connecting mechanism, and a sixth connecting mechanism, wherein the sun gear of the first planetary gear mechanism is connected to the case and is a carrier of the first planetary gear mechanism. Is connected to the carrier of the fourth planetary gear mechanism, the ring gear of the second planetary gear mechanism is connected to the carrier of the third planetary gear mechanism, and power is input to the sun gear of the third planetary gear mechanism. The ring gear of the third planetary gear mechanism is connected to the sun gear of the fourth planetary gear mechanism, and the ring gear of the fourth planetary gear mechanism is connected to the output shaft that outputs the transmitted power. The first connecting mechanism is capable of switching the connection state between the carrier of the second planetary gear mechanism and the case, and the second connecting mechanism is a sun gear of the second planetary gear mechanism and the case. The connection state can be switched, and the third connection mechanism switches the connection state between the sun gear of the third planetary gear mechanism, the input shaft, the carrier of the first planetary gear mechanism, and the carrier of the fourth planetary gear mechanism. It is possible, and the fourth connecting mechanism can switch the connection state between the carrier of the second planetary gear mechanism, the ring gear of the third planetary gear mechanism, and the sun gear of the fourth planetary gear mechanism, and the fifth The connecting mechanism can switch the connection state between the ring gear of the first planetary gear mechanism and the carrier of the second planetary gear mechanism, and the sixth connecting mechanism is the ring gear of the first planetary gear mechanism and the second. Provided is a transmission capable of switching the connection state of the planetary gear mechanism with the sun gear.

In the case, the four planetary gear mechanisms may be arranged concentrically in the order of the first planetary gear mechanism, the second planetary gear mechanism, the third planetary gear mechanism, and the fourth planetary gear mechanism.

The input shaft is inserted into the inner peripheral side of the sun gear of the first planetary gear mechanism, the second planetary gear mechanism, the third planetary gear mechanism, and the fourth planetary gear mechanism, and the output shaft is the fourth. It is arranged on the opposite side of the third planetary gear mechanism with respect to the planetary gear mechanism, and the sun gear of the first planetary gear mechanism passes through the opposite side of the second planetary gear mechanism with respect to the first planetary gear mechanism. On the opposite side of the carrier of the first planetary gear mechanism to the second planetary gear mechanism, the ring gears of the first planetary gear mechanism, the second planetary gear mechanism, and the third planetary gear mechanism are connected to the case. It is connected to the third planetary gear mechanism side of the carrier of the fourth planetary gear mechanism via the outer peripheral side, and the ring gear of the first planetary gear mechanism is of the first planetary gear mechanism and the second planetary gear mechanism. The sun gear of the second planetary gear mechanism is connected to the sun gear of the second planetary gear mechanism via the sixth connecting mechanism, and the sun gear of the second planetary gear mechanism is on the inner peripheral side of the sun gear of the first planetary gear mechanism and the said. The first planetary gear of the carrier of the second planetary gear mechanism is connected to the first planetary gear mechanism via the case and the second connecting mechanism via the opposite side to the second planetary gear mechanism. The mechanism side is the fourth planetary gear mechanism via between the outer peripheral side of the ring gears of the second planetary gear mechanism and the third planetary gear mechanism and between the third planetary gear mechanism and the fourth planetary gear mechanism. The sun gear is connected to the sun gear via the fourth connecting mechanism, and the side of the carrier of the second planetary gear mechanism opposite to the first planetary gear mechanism is the sun gear of the second planetary gear mechanism and the first planetary gear mechanism. The ring gear of the second planetary gear mechanism is connected to the inner peripheral side via the case and the first connecting mechanism via the second planetary gear mechanism and the opposite side to the first planetary gear mechanism. Is connected to the second planetary gear mechanism side of the carrier of the third planetary gear mechanism, and the opposite side of the carrier of the fourth planetary gear mechanism to the third planetary gear mechanism is connected to the input shaft and the third connection. The ring gear of the fourth planetary gear mechanism may be connected to the output shaft of the fourth planetary gear mechanism via a side opposite to the third planetary gear mechanism.

In the case, the four planetary gear mechanisms may be arranged concentrically in the order of the third planetary gear mechanism, the second planetary gear mechanism, the first planetary gear mechanism, and the fourth planetary gear mechanism.

The input shaft is inserted into the inner peripheral side of the sun gear of the third planetary gear mechanism, the second planetary gear mechanism, the first planetary gear mechanism, and the fourth planetary gear mechanism, and the output shaft is the fourth. It is arranged on the side opposite to the first planetary gear mechanism with respect to the planetary gear mechanism, and the side opposite to the second planetary gear mechanism of the carrier of the third planetary gear mechanism is the outer peripheral side of the ring gear of the third planetary gear mechanism. It is connected to the ring gear of the second planetary gear mechanism via the above, and the ring gear of the third planetary gear mechanism is between the third planetary gear mechanism and the second planetary gear mechanism, and the second planetary gear mechanism and the ring gear. It is connected to the sun gear of the fourth planetary gear mechanism via the inner peripheral side of the sun gear of the first planetary gear mechanism, and the sun gear of the second planetary gear mechanism is the second planetary gear mechanism and the first planetary gear. The case is connected to the case via the second connecting mechanism via between the mechanisms, and the first planetary gear mechanism side of the carrier of the second planetary gear mechanism is connected to the case via the first connecting mechanism. The third planetary gear mechanism side of the carrier of the second planetary gear mechanism is connected to the inner peripheral side of the sun gear of the second planetary gear mechanism and the first planetary gear mechanism, and the first planetary gear mechanism and the said. The ring gear of the first planetary gear mechanism is connected to the ring gear of the first planetary gear mechanism via the fourth planetary gear mechanism, and the sun gear of the first planetary gear mechanism is the second planetary gear mechanism and the said. It is connected to the case via between the first planetary gear mechanisms, and the second planetary gear mechanism side of the carrier of the first planetary gear mechanism passes through the outer peripheral side of the ring gear of the first planetary gear mechanism. The carrier of the fourth planetary gear mechanism is connected to the first planetary gear mechanism side, and the side of the carrier of the fourth planetary gear mechanism opposite to the first planetary gear mechanism has the input shaft and the third connecting mechanism. The ring gear of the fourth planetary gear mechanism may be connected to the output shaft of the fourth planetary gear mechanism via the opposite side to the first planetary gear mechanism.

The fifth coupling mechanism may be a dog clutch.

As described above, according to the present invention, it is possible to further increase the number of gears while suppressing the increase in size of the transmission.

It is a skeleton figure which shows an example of the schematic structure of the transmission which concerns on 1st Embodiment of this invention. It is a collinear diagram which shows the relationship of the rotation speed of a sun gear, a carrier and a ring gear in a planetary gear mechanism. It is explanatory drawing which shows the fastening state of each connection mechanism for each shift stage in the transmission which concerns on this embodiment. It is explanatory drawing which shows an example of the gear ratio for each shift stage in the transmission which concerns on this embodiment. It is explanatory drawing which shows an example of the step ratio between each shift stage in the transmission which concerns on this embodiment. It is a skeleton figure which shows an example of the schematic structure of the transmission which concerns on 2nd Embodiment of this invention.

Preferred embodiments of the present invention will be described in detail below with reference to the accompanying drawings. In the present specification and the drawings, components having substantially the same functional configuration are designated by the same reference numerals, so that duplicate description will be omitted.

<1. First Embodiment>
The transmission 1 according to the first embodiment of the present invention will be described.

[1-1. Transmission configuration]
First, the configuration of the transmission 1 according to the present embodiment will be described with reference to FIGS. 1 and 2. FIG. 1 is a skeleton diagram showing an example of a schematic configuration of a transmission 1 according to the present embodiment. FIG. 2 is a collinear diagram showing the relationship between the rotation speeds of the sun gear, the carrier, and the ring gear in the planetary gear mechanism.

As shown in FIG. 1, for example, the transmission 1 includes an input shaft A1, an output shaft A2, a first planetary gear mechanism PG1, a second planetary gear mechanism PG2, a third planetary gear mechanism PG3, and a third. The four planetary gear mechanism PG4, the first brake B1, the second brake B2, the first clutch C1, the second clutch C2, the third clutch C3, and the fourth clutch C4 are provided. The transmission 1 is mounted on a vehicle, for example, and shifts the power output from a drive source such as an engine at a gear ratio corresponding to each shift stage and outputs the power to the drive wheels.

The input shaft A1 is a shaft to which power is input. For example, the input shaft A1 is connected to a drive source such as an engine via a torque converter, and the power output from the drive source is input to the input shaft A1.

The output shaft A2 is a shaft that outputs the transmitted power. For example, the output shaft A2 is connected to the drive wheels via a differential device, and the power output from the output shaft A2 is transmitted to the drive wheels.

The first planetary gear mechanism PG1, the second planetary gear mechanism PG2, the third planetary gear mechanism PG3, and the fourth planetary gear mechanism PG4 are planetary gear mechanisms provided in the case 9 and provided with a sun gear, a carrier, and a ring gear as rotating elements. is there. As described above, the transmission 1 includes four planetary gear mechanisms. In the case 9, the four planetary gear mechanisms are arranged concentrically in the order of the first planetary gear mechanism PG1, the second planetary gear mechanism PG2, the third planetary gear mechanism PG3, and the fourth planetary gear mechanism PG4.

Specifically, each planetary gear mechanism is a single pinion type planetary gear mechanism. As shown in FIG. 2, the rotation speeds of the sun gear, the carrier, and the ring gear of each planetary gear mechanism are arranged in a straight line on the collinear diagram. The ratio of the distance D1 on each vertical axis indicating the rotation speeds of the sun gear and the carrier to the distance D2 on each vertical axis indicating the rotation speeds of the carrier and the ring gear matches the ratio of the number of teeth of the ring gear to the number of teeth of the sun gear. .. Therefore, when the ratio of the rotation speed of the ring gear to the rotation speed of the sun gear when the carrier is fixed is taken as the gear ratio of the planetary gear mechanism, the gear ratio of the planetary gear mechanism is the number of teeth of the sun gear divided by the number of teeth of the ring gear. It becomes the value obtained by. In each planetary gear mechanism, the gear ratio of each planetary gear mechanism can be set to a desired gear ratio by appropriately setting the number of teeth of the ring gear and the number of teeth of the sun gear.

The first planetary gear mechanism PG1 rotates and revolves the sun gear S1, the ring gear R1 arranged concentrically with respect to the sun gear S1, the plurality of pinion gears P1 meshing with the sun gear S1 and the ring gear R1, and the plurality of pinion gears P1. It is provided with a carrier CA1 that freely supports it. The gear ratio of the first planetary gear mechanism PG1 is set to, for example, 0.57.

The second planetary gear mechanism PG2 rotates and revolves the sun gear S2, the ring gear R2 arranged concentrically with respect to the sun gear S2, the plurality of pinion gears P2 meshing with the sun gear S2 and the ring gear R2, and the plurality of pinion gears P2. It is provided with a carrier CA2 that freely supports it. The gear ratio of the second planetary gear mechanism PG2 is set to, for example, 0.24.

The third planetary gear mechanism PG3 rotates and revolves the sun gear S3, the ring gear R3 arranged concentrically with respect to the sun gear S3, the plurality of pinion gears P3 that mesh with the sun gear S3 and the ring gear R3, and the plurality of pinion gears P3. It is provided with a carrier CA3 that freely supports it. The gear ratio of the third planetary gear mechanism PG3 is set to, for example, 0.67.

The fourth planetary gear mechanism PG4 rotates and revolves the sun gear S4, the ring gear R4 arranged concentrically with respect to the sun gear S4, the plurality of pinion gears P4 that mesh with the sun gear S4 and the ring gear R4, and the plurality of pinion gears P4. It is provided with a carrier CA4 that freely supports it. The gear ratio of the fourth planetary gear mechanism PG4 is set to, for example, 0.30.

In the transmission 1, some of the rotating elements of the planetary gear mechanism are connected to other elements. The other elements may include an input shaft A1, an output shaft A2, and a case 9 in addition to the rotating elements of the planetary gear mechanism.

The sun gear S1 of the first planetary gear mechanism PG1 is connected to the case 9. Therefore, the sun gear S1 of the first planetary gear mechanism PG1 is fixed to the case 9.

The carrier CA1 of the first planetary gear mechanism PG1 is connected to the carrier CA4 of the fourth planetary gear mechanism PG4. Therefore, the rotation speeds of the carrier CA1 of the first planetary gear mechanism PG1 and the carrier CA4 of the fourth planetary gear mechanism PG4 are the same.

The ring gear R2 of the second planetary gear mechanism PG2 is connected to the carrier CA3 of the third planetary gear mechanism PG3. Therefore, the rotation speeds of the ring gear R2 of the second planetary gear mechanism PG2 and the carrier CA3 of the third planetary gear mechanism PG3 are the same.

The sun gear S3 of the third planetary gear mechanism PG3 is connected to the input shaft A1. Therefore, the rotation speeds of the sun gear S3 and the input shaft A1 of the third planetary gear mechanism PG3 are the same.

The ring gear R3 of the third planetary gear mechanism PG3 is connected to the sun gear S4 of the fourth planetary gear mechanism PG4. Therefore, the rotation speeds of the ring gear R3 of the third planetary gear mechanism PG3 and the sun gear S4 of the fourth planetary gear mechanism PG4 are the same.

The ring gear R4 of the fourth planetary gear mechanism PG4 is connected to the output shaft A2. Therefore, the rotation speeds of the ring gear R4 and the output shaft A2 of the fourth planetary gear mechanism PG4 are the same.

The first brake B1, the second brake B2, the first clutch C1, the second clutch C2, the third clutch C3, and the fourth clutch C4 can switch the connection state between the rotating element of the planetary gear mechanism and other elements. It is a connecting mechanism. As described above, the transmission 1 includes six connecting mechanisms. The first brake B1, the second brake B2, the first clutch C1, the second clutch C2, the third clutch C3, and the fourth clutch C4 are the first coupling mechanism, the second coupling mechanism, and the third coupling mechanism according to the present invention. , 4th connecting mechanism, 5th connecting mechanism and 6th connecting mechanism, respectively.

Each brake can switch the connection state between the rotating element of the planetary gear mechanism and the case 9. As each brake, for example, a wet multi-plate brake is used. By controlling the oil supply to each brake, each brake is engaged or released. When the brake is fastened, the rotating element of the planetary gear mechanism and the case 9 are connected to each other, and the rotating element of the planetary gear mechanism is fixed to the case 9. On the other hand, when the brake is released, the connection between the rotating element of the planetary gear mechanism and the case 9 is released, and the fixing of the rotating element of the planetary gear mechanism to the case 9 is released.

The first brake B1 can switch the connection state between the carrier CA2 of the second planetary gear mechanism PG2 and the case 9. By fastening the first brake B1, the carrier CA2 of the second planetary gear mechanism PG2 is fixed to the case 9. On the other hand, when the first brake B1 is released, the fixing of the carrier CA2 of the second planetary gear mechanism PG2 to the case 9 is released.

The second brake B2 can switch the connection state between the sun gear S2 of the second planetary gear mechanism PG2 and the case 9. By fastening the second brake B2, the sun gear S2 of the second planetary gear mechanism PG2 is fixed to the case 9. On the other hand, when the second brake B2 is released, the fixing of the second planetary gear mechanism PG2 to the case 9 of the sun gear S2 is released.

Each clutch can switch the connection state between the rotating element of the planetary gear mechanism and other rotating elements. The other rotating elements may include the input shaft A1 and the output shaft A2 in addition to the rotating elements of the planetary gear mechanism. As each clutch, for example, a wet multi-plate clutch is used. By controlling the oil supply to each clutch, each clutch is engaged or released. When the clutch is engaged, the rotating element of the planetary gear mechanism and other rotating elements are connected to each other, and the rotation speeds of the rotating element of the planetary gear mechanism and the other rotating elements match. On the other hand, when the clutch is released, the connection between the rotating element of the planetary gear mechanism and the other rotating elements is released, and the power is transmitted between the rotating element of the planetary gear mechanism and the other rotating elements. Is blocked.

The first clutch C1 can switch the connection state between the sun gear S3 of the third planetary gear mechanism PG3 and the input shaft A1 and the carrier CA1 of the first planetary gear mechanism PG1 and the carrier CA4 of the fourth planetary gear mechanism PG4. By engaging the first clutch C1, the number of rotations between the sun gear S3 and the input shaft A1 of the third planetary gear mechanism PG3 and the carrier CA1 of the first planetary gear mechanism PG1 and the carrier CA4 of the fourth planetary gear mechanism PG4. Match. On the other hand, when the first clutch C1 is released, the sun gear S3 and the input shaft A1 of the third planetary gear mechanism PG3 and the carrier CA1 of the first planetary gear mechanism PG1 and the carrier CA4 of the fourth planetary gear mechanism PG4 Power transmission is cut off.

The second clutch C2 can switch the connection state between the carrier CA2 of the second planetary gear mechanism PG2, the ring gear R3 of the third planetary gear mechanism PG3, and the sun gear S4 of the fourth planetary gear mechanism PG4. When the second clutch C2 is engaged, the rotation speeds of the carrier CA2 of the second planetary gear mechanism PG2 coincide with the ring gear R3 of the third planetary gear mechanism PG3 and the sun gear S4 of the fourth planetary gear mechanism PG4. On the other hand, when the second clutch C2 is released, power is transmitted between the carrier CA2 of the second planetary gear mechanism PG2, the ring gear R3 of the third planetary gear mechanism PG3, and the sun gear S4 of the fourth planetary gear mechanism PG4. Is blocked.

The third clutch C3 can switch the connection state between the ring gear R1 of the first planetary gear mechanism PG1 and the carrier CA2 of the second planetary gear mechanism PG2. By engaging the third clutch C3, the rotation speeds of the ring gear R1 of the first planetary gear mechanism PG1 and the carrier CA2 of the second planetary gear mechanism PG2 match. On the other hand, when the third clutch C3 is released, the transmission of power between the ring gear R1 of the first planetary gear mechanism PG1 and the carrier CA2 of the second planetary gear mechanism PG2 is cut off.

Further, the third clutch C3 may be a dog clutch. Here, as will be described later, the engaged state of the third clutch C3 is before and after switching between the reverse stage (Rev) and the forward first speed stage (1st), or the forward fifth speed stage (5th) and the forward sixth speed. It is switched before and after switching to the stage (6th). Torque generated in the 3rd clutch C3 before and after switching between the reverse speed (Rev) and the forward 1st speed (1st) and before and after switching between the forward 5th speed (5th) and the forward 6th speed (6th). Since the direction of the third clutch C3 is reversed, even when the dog clutch is used as the third clutch C3, the engaged state of the third clutch C3 can be smoothly switched.

The fourth clutch C4 can switch the connection state between the ring gear R1 of the first planetary gear mechanism PG1 and the sun gear S2 of the second planetary gear mechanism PG2. By engaging the fourth clutch C4, the rotation speeds of the ring gear R1 of the first planetary gear mechanism PG1 and the sun gear S2 of the second planetary gear mechanism PG2 match. On the other hand, when the fourth clutch C4 is released, the transmission of power between the ring gear R1 of the first planetary gear mechanism PG1 and the sun gear S2 of the second planetary gear mechanism PG2 is cut off.

Hereinafter, an example of a connection path between the rotating element of the planetary gear mechanism and other elements in the transmission 1 will be described. In the following, the axial direction of each planetary gear mechanism is simply referred to as an axial direction, and the radial direction of each planetary gear mechanism is simply referred to as a radial direction.

The input shaft A1 is the inner circumference of the sun gears S1, sun gear S2, sun gear S3 and sun gear S4, which are the sun gears of the first planetary gear mechanism PG1, the second planetary gear mechanism PG2, the third planetary gear mechanism PG3 and the fourth planetary gear mechanism PG4. It is inserted to the side. The input shaft A1 may be arranged concentrically with each planetary gear mechanism. The input shaft A1 is connected to the drive source on the side opposite to the second planetary gear mechanism PG2 with respect to the first planetary gear mechanism PG1. Therefore, power is input to the input shaft A1 from the side opposite to the second planetary gear mechanism PG2 with respect to the first planetary gear mechanism PG1.

The output shaft A2 is arranged on the side opposite to the third planetary gear mechanism PG3 with respect to the fourth planetary gear mechanism PG4. The output shaft A2 may be arranged concentrically with each planetary gear mechanism. The side of the output shaft A2 opposite to the fourth planetary gear mechanism PG4 is connected to the drive wheels. Therefore, power is output from the output shaft A2 toward the side opposite to the third planetary gear mechanism PG3 with respect to the fourth planetary gear mechanism PG4.

The sun gear S1 of the first planetary gear mechanism PG1 is connected to the case 9 with respect to the first planetary gear mechanism PG1 via the opposite side to the second planetary gear mechanism PG2. Therefore, the connecting portion connecting the sun gear S1 of the first planetary gear mechanism PG1 and the case 9 extends radially with respect to the first planetary gear mechanism PG1 on the opposite side of the second planetary gear mechanism PG2. It may have an existing portion 101 and an inner peripheral extending portion 126 extending axially from the side opposite to the second planetary gear mechanism PG2 to the inner peripheral side of the sun gear S1 with respect to the inner peripheral side of the sun gear S1.

The side opposite to the second planetary gear mechanism PG2 of the carrier CA1 of the first planetary gear mechanism PG1 passes through the outer peripheral side of the ring gear of the first planetary gear mechanism PG1, the second planetary gear mechanism PG2, and the third planetary gear mechanism PG3. It is connected to the third planetary gear mechanism PG3 side of the carrier CA4 of the fourth planetary gear mechanism PG4. Therefore, the connecting portion that connects the carrier CA1 of the first planetary gear mechanism PG1 and the carrier CA4 of the fourth planetary gear mechanism PG4 is radially opposite to the second planetary gear mechanism PG2 with respect to the first planetary gear mechanism PG1. The radial extending portion 102 extending in the axial direction extends from the side opposite to the second planetary gear mechanism PG2 to the outer peripheral side of the ring gear R1 to the fourth planetary gear mechanism PG4 side with respect to the outer peripheral side of the ring gear R3. It may have an outer peripheral extending portion 121 and a radial extending portion 108 extending in the radial direction between the third planetary gear mechanism PG3 and the fourth planetary gear mechanism PG4.

The ring gear R1 of the first planetary gear mechanism PG1 is connected via the sun gear S2 of the second planetary gear mechanism PG2 and the fourth clutch C4 via between the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2. .. Therefore, the connecting portion connecting the ring gear R1 of the first planetary gear mechanism PG1 and the sun gear S2 of the second planetary gear mechanism PG2 extends axially from the outer peripheral side of the ring gear R1 to the second planetary gear mechanism PG2 side. The circumferential extending portion 122, the radial extending portion 103 extending in the radial direction between the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2, and the first planetary gear mechanism PG1 side from the inner peripheral side of the sun gear S2. It may have an inner peripheral extending portion 128 extending in the axial direction.

The sun gear S2 of the second planetary gear mechanism PG2 is a case via the inner peripheral side of the sun gear S1 of the first planetary gear mechanism PG1 and the side opposite to the second planetary gear mechanism PG2 with respect to the first planetary gear mechanism PG1. It is connected to 9 via the second brake B2. Therefore, the connecting portion connecting the sun gear S2 of the second planetary gear mechanism PG2 and the case 9 extends radially with respect to the first planetary gear mechanism PG1 on the opposite side of the second planetary gear mechanism PG2. It may have an existing portion 111 and an inner peripheral extending portion 129 extending axially from the side opposite to the second planetary gear mechanism PG2 to the inner peripheral side of the sun gear S2 with respect to the inner peripheral side of the sun gear S1.

The first planetary gear mechanism PG1 side of the carrier CA2 of the second planetary gear mechanism PG2 is the outer peripheral side of the ring gears of the second planetary gear mechanism PG2 and the third planetary gear mechanism PG3, and the third planetary gear mechanism PG3 and the fourth planetary gear. It is connected to the sun gear S4 of the fourth planetary gear mechanism PG4 via the mechanism PG4 and the second clutch C2. Therefore, the connecting portion connecting the carrier CA2 of the second planetary gear mechanism PG2 and the sun gear S4 of the fourth planetary gear mechanism PG4 extends radially between the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2. The radial extending portion 104 extends axially from the first planetary gear mechanism PG1 side to the outer peripheral side of the ring gear R2 to the fourth planetary gear mechanism PG4 side with respect to the outer peripheral side of the ring gear R3. A radial extending portion 107 extending in the radial direction between the portion 123, the third planetary gear mechanism PG3 and the fourth planetary gear mechanism PG4, and a shaft from the inner peripheral side of the sun gear S4 to the third planetary gear mechanism PG3 side. It may have an inner peripheral extending portion 127 extending in the direction.

The opposite side of the carrier CA2 of the second planetary gear mechanism PG2 to the first planetary gear mechanism PG1 is relative to the inner peripheral side of the sun gear of the second planetary gear mechanism PG2 and the first planetary gear mechanism PG1 and the first planetary gear mechanism PG1. It is connected to the case 9 via the second planetary gear mechanism PG2 and the opposite side via the first brake B1. Therefore, the connecting portion connecting the carrier CA2 of the second planetary gear mechanism PG2 and the case 9 extends radially on the opposite side of the first planetary gear mechanism PG1 from the second planetary gear mechanism PG2. The existing portion 112 and the inner peripheral extension extending axially from the side opposite to the second planetary gear mechanism PG2 to the inner peripheral side of the sun gear S1 to the third planetary gear mechanism PG3 side with respect to the inner peripheral side of the sun gear S2. It may have a portion 130 and a radial extending portion 105 extending radially between the second planetary gear mechanism PG2 and the third planetary gear mechanism PG3.

The ring gear R2 of the second planetary gear mechanism PG2 is connected to the second planetary gear mechanism PG2 side of the carrier CA3 of the third planetary gear mechanism PG3. Therefore, the connecting portion connecting the ring gear R2 of the second planetary gear mechanism PG2 and the carrier CA3 of the third planetary gear mechanism PG3 extends axially from the outer peripheral side of the ring gear R2 to the third planetary gear mechanism PG3 side. It may have a circumferential extending portion 124 and a radial extending portion 106 extending radially between the second planetary gear mechanism PG2 and the third planetary gear mechanism PG3.

The side of the carrier CA4 of the fourth planetary gear mechanism PG4 opposite to the third planetary gear mechanism PG3 is connected via the input shaft A1 and the first clutch C1. Therefore, the connecting portion connecting the carrier CA4 of the 4th planetary gear mechanism PG4 and the input shaft A1 extends radially on the opposite side of the 4th planetary gear mechanism PG4 from the 3rd planetary gear mechanism PG3. It may have an extension 109.

The ring gear R4 of the fourth planetary gear mechanism PG4 is connected to the output shaft A2 of the fourth planetary gear mechanism PG4 via the opposite side to the third planetary gear mechanism PG3. Therefore, the connecting portion for connecting the ring gear R4 of the fourth planetary gear mechanism PG4 and the output shaft A2 is an outer peripheral extending portion 125 extending axially from the outer peripheral side of the ring gear R4 to the opposite side to the third planetary gear mechanism PG3. And the fourth planetary gear mechanism PG4 may have a radial extending portion 110 extending in the radial direction on the opposite side of the third planetary gear mechanism PG3.

As described above, in the transmission 1, twelve radial extending portions extending in the radial direction can be provided at positions different from the four planetary gear mechanisms along the axial direction.

Further, in the transmission 1, the outer peripheral extending portion 121 may be provided so as to cover the outer peripheral portion of the outer peripheral extending portion 122. Therefore, a double structure can be formed by the outer peripheral extending portion 122 and the outer peripheral extending portion 121.

Further, in the transmission 1, the outer peripheral extending portion 123 may be provided so as to cover the outer peripheral portion of the outer peripheral extending portion 124. Further, the outer peripheral extending portion 121 may be provided so as to cover the outer peripheral portion of the outer peripheral extending portion 123. Therefore, a triple structure can be formed by the outer peripheral extending portion 124, the outer peripheral extending portion 123, and the outer peripheral extending portion 121.

Further, in the transmission 1, the inner peripheral extending portion 130 may be provided so as to cover the outer peripheral portion of the input shaft A1. Further, the inner peripheral extending portion 129 may be provided so as to cover the outer peripheral portion of the inner peripheral extending portion 130. Further, the inner peripheral extending portion 126 and the inner peripheral extending portion 128 may be provided so as to cover the outer peripheral portion of the inner peripheral extending portion 129. Therefore, a quadruple structure can be formed by the input shaft A1, the inner peripheral extending portion 130, the inner peripheral extending portion 129, and the inner peripheral extending portion 126. Further, a quadruple structure can be formed by the input shaft A1, the inner peripheral extending portion 130, the inner peripheral extending portion 129, and the inner peripheral extending portion 128.

Further, in the transmission 1, the inner peripheral extending portion 127 may be provided so as to cover the outer peripheral portion of the input shaft A1. Therefore, a double structure can be formed by the input shaft A1 and the inner peripheral extending portion 127.

Here, an oil passage may be formed in the input shaft A1. The oil pressure for driving the first clutch C1 can be supplied from the oil passage formed in the input shaft A1 via the radial extending portion 109. Further, the oil pressure for driving the second clutch C2 can be supplied from the oil passage formed in the input shaft A1 via the inner peripheral extending portion 127, the radial extending portion 107, and the outer peripheral extending portion 123. Further, the hydraulic pressure for driving the third clutch C3 is the inner peripheral extending portion 130, the radial extending portion 105, the carrier CA2 of the second planetary gear mechanism PG2, and the radial extending portion from the oil passage formed in the input shaft A1. It can be supplied via the existing part 104. Further, the oil pressure for driving the fourth clutch C4 can be supplied from the oil passage formed in the input shaft A1 via the inner peripheral extending portion 130 and the inner peripheral extending portion 129.

Further, an oil passage may be formed in the case 9. The hydraulic pressure for driving the first brake B1 and the second brake B2 may be supplied through the oil passage formed in the case 9.

Further, in the transmission 1, for example, the rotation speeds of the outer peripheral extending portion 121 and the outer peripheral extending portion 125 are detected by using a sensor capable of detecting the rotation speed of the member, and the rotation speed of the input shaft A1 is detected based on the detection result. Can be calculated. The calculation result of the rotation speed of the input shaft A1 can be used for controlling the switching of the shift stage of the transmission 1. The detection result of the rotation speed of the outer peripheral extending portion 125 can be used for various controls as the detection result of the rotation speed of the output shaft A2.

[1-2. Transmission operation]
Subsequently, the operation of the transmission 1 according to the present embodiment will be described with reference to FIGS. 3 to 5. FIG. 3 is an explanatory diagram showing a fastening state of each connecting mechanism for each transmission stage in the transmission 1 according to the present embodiment. FIG. 4 is an explanatory diagram showing an example of a gear ratio for each shift stage in the transmission 1 according to the present embodiment. The gear ratio in the transmission 1 shown in FIG. 4 is the ratio of the rotation speed of the input shaft A1 to the rotation speed of the output shaft A2 for each transmission stage. FIG. 5 is an explanatory diagram showing an example of a step ratio between each transmission stage in the transmission 1 according to the present embodiment. The step ratio in the transmission 1 shown in FIG. 5 is a ratio of the gear ratio for the low gear side gear ratio to the gear ratio for the high gear side gear ratio in the adjacent transmission gears. As described above, the gear ratio and the step ratio in the transmission 1 shown in FIGS. 4 and 5 are the first planetary gear mechanism PG1, the second planetary gear mechanism PG2, the third planetary gear mechanism PG3, and the fourth planet. It is a value when the gear ratio of the gear mechanism PG4 is 0.57, 0.24, 0.67 and 0.30, respectively.

In the transmission 1, the transmission stage is switched by switching the fastening state of each connecting mechanism. As a result, the gear ratio of the transmission 1 is switched to the gear ratio according to the shift stage. The fastening state of each connecting mechanism is controlled by, for example, a control device mounted on the vehicle according to the traveling state of the vehicle. Each shift stage is realized by fastening three connecting mechanisms out of the six connecting mechanisms and opening the other three connecting mechanisms.

The first forward speed stage (1st) is realized by engaging the second brake B2, the third clutch C3, and the fourth clutch C4. The gear ratio for the first forward gear (1st) is 4.95.

The second forward speed stage (2nd) is realized by engaging the second brake B2, the second clutch C2, and the third clutch C3. The gear ratio for the second forward gear (2nd) is 3.03. Further, the step ratio between the first forward speed stage (1st) and the second forward speed stage (2nd) is 1.63.

The forward third speed stage (3rd) is realized by engaging the second clutch C2, the third clutch C3, and the fourth clutch C4. The gear ratio for the third forward gear (3rd) is 1.90. The step ratio between the 2nd forward speed stage (2nd) and the 3rd forward speed stage (3rd) is 1.60.

The forward fourth speed stage (4th) is realized by engaging the first clutch C1, the third clutch C3, and the fourth clutch C4. The gear ratio for the fourth forward gear (4th) is 1.41. The step ratio between the 3rd forward speed stage (3rd) and the 4th forward speed stage (4th) is 1.35.

The fifth forward speed (5th) is realized by engaging the first clutch C1, the second clutch C2, and the third clutch C3. The gear ratio for the fifth forward gear (5th) is 1.21. The step ratio between the 4th forward speed (4th) and the 5th forward speed (5th) is 1.16.

The sixth forward speed (6th) is realized by engaging the first clutch C1, the second clutch C2, and the fourth clutch C4. The gear ratio for the 6th forward gear (6th) is 1.07. The step ratio between the 5th forward speed (5th) and the 6th forward speed (6th) is 1.13.

The 7th forward speed (7th) is realized by engaging the second brake B2, the first clutch C1 and the second clutch C2. The gear ratio for the 7th forward gear (7th) is 0.90. The step ratio between the 6th forward speed (6th) and the 7th forward speed (7th) is 1.19.

The forward eighth speed stage (8th) is realized by engaging the first brake B1, the first clutch C1 and the second clutch C2. The gear ratio for the 8th forward gear (8th) is 0.77. The step ratio between the 7th forward speed (7th) and the 8th forward speed (8th) is 1.17.

The 9th forward speed stage (9th) is realized by engaging the first brake B1, the second brake B2, and the first clutch C1. The gear ratio for the 9th forward gear (9th) is 0.66. The step ratio between the 8th forward speed (8th) and the 9th forward speed (9th) is 1.16.

The 10th forward speed stage (10th) is realized by engaging the first brake B1, the first clutch C1 and the fourth clutch C4. The gear ratio for the 10th forward gear (10th) is 0.59. The step ratio between the 9th forward speed (9th) and the 10th forward speed (10th) is 1.13.

The reverse stage (Rev) is realized by engaging the second brake B2, the second clutch C2, and the fourth clutch C4. The gear ratio for the reverse stage (Rev) is −5.26.

In this way, the transmission 1 can realize 10 forward speeds and 1 reverse speed. Further, in the transmission 1, two of the three connecting mechanisms to be fastened between the adjacent transmission stages are common. Thereby, by switching one of the three connecting mechanisms to be fastened, the shift gear can be switched to the adjacent shift gear. Therefore, the shift gear can be switched smoothly.

[1-3. Effect of transmission]
Subsequently, the effect of the transmission 1 according to the present embodiment will be described.

In the transmission 1, the sun gear S1 of the first planetary gear mechanism PG1 is connected to the case 9. Further, the carrier CA1 of the first planetary gear mechanism PG1 is connected to the carrier CA4 of the fourth planetary gear mechanism PG4. Further, the ring gear R2 of the second planetary gear mechanism PG2 is connected to the carrier CA3 of the third planetary gear mechanism PG3. Further, the sun gear S3 of the third planetary gear mechanism PG3 is connected to the input shaft A1. Further, the ring gear R3 of the third planetary gear mechanism PG3 is connected to the sun gear S4 of the fourth planetary gear mechanism PG4. Further, the ring gear R4 of the fourth planetary gear mechanism PG4 is connected to the output shaft A2. Further, the first brake B1 can switch the connection state between the carrier CA2 of the second planetary gear mechanism PG2 and the case 9. Further, the second brake B2 can switch the connection state between the sun gear S2 of the second planetary gear mechanism PG2 and the case 9. Further, the first clutch C1 can switch the connection state between the sun gear S3 of the third planetary gear mechanism PG3 and the input shaft A1 and the carrier CA1 of the first planetary gear mechanism PG1 and the carrier CA4 of the fourth planetary gear mechanism PG4. .. Further, the second clutch C2 can switch the connection state between the carrier CA2 of the second planetary gear mechanism PG2, the ring gear R3 of the third planetary gear mechanism PG3, and the sun gear S4 of the fourth planetary gear mechanism PG4. Further, the third clutch C3 can switch the connection state between the ring gear R1 of the first planetary gear mechanism PG1 and the carrier CA2 of the second planetary gear mechanism PG2. Further, the fourth clutch C4 can switch the connection state between the ring gear R1 of the first planetary gear mechanism PG1 and the sun gear S2 of the second planetary gear mechanism PG2.

As a result, 10 forward stages and 1 reverse stage can be realized by providing four planetary gear mechanisms and six connecting mechanisms. Therefore, for example, the number of gears can be increased without increasing the number of planetary gears and coupling mechanisms as compared with a transmission having four planetary gears and six connecting mechanisms and capable of achieving eight forward gears and one reverse gear. Can be increased. Therefore, it is possible to further increase the number of gears while suppressing the increase in size of the transmission. As a result, it is possible to improve fuel efficiency and driveability.

Further, in the transmission 1, in the case 9, the four planetary gear mechanisms are concentrically arranged in the order of the first planetary gear mechanism PG1, the second planetary gear mechanism PG2, the third planetary gear mechanism PG3, and the fourth planetary gear mechanism PG4. Be placed. Specifically, the input shaft A1 includes sun gears S1, sun gears S2, sun gears S3, which are sun gears of the first planetary gear mechanism PG1, the second planetary gear mechanism PG2, the third planetary gear mechanism PG3, and the fourth planetary gear mechanism PG4. It is inserted on the inner peripheral side of the sun gear S4. Further, the output shaft A2 is arranged on the side opposite to the third planetary gear mechanism PG3 with respect to the fourth planetary gear mechanism PG4. Further, the sun gear S1 of the first planetary gear mechanism PG1 is connected to the case 9 with respect to the first planetary gear mechanism PG1 via the opposite side to the second planetary gear mechanism PG2. Further, the side opposite to the second planetary gear mechanism PG2 of the carrier CA1 of the first planetary gear mechanism PG1 passes through the outer peripheral side of the ring gear of the first planetary gear mechanism PG1, the second planetary gear mechanism PG2, and the third planetary gear mechanism PG3. Then, it is connected to the third planetary gear mechanism PG3 side of the carrier CA4 of the fourth planetary gear mechanism PG4. Further, the ring gear R1 of the first planetary gear mechanism PG1 is connected via the sun gear S2 of the second planetary gear mechanism PG2 and the fourth clutch C4 via between the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2. Will be done. Further, the sun gear S2 of the second planetary gear mechanism PG2 passes through the inner peripheral side of the sun gear S1 of the first planetary gear mechanism PG1 and the side opposite to the second planetary gear mechanism PG2 with respect to the first planetary gear mechanism PG1. It is connected to the case 9 via the second brake B2. Further, the first planetary gear mechanism PG1 side of the carrier CA2 of the second planetary gear mechanism PG2 is the outer peripheral side of the ring gears of the second planetary gear mechanism PG2 and the third planetary gear mechanism PG3, and the third planetary gear mechanism PG3 and the fourth. It is connected via the sun gear S4 of the fourth planetary gear mechanism PG4 and the second clutch C2 via between the planetary gear mechanism PG4. Further, the opposite side of the carrier CA2 of the second planetary gear mechanism PG2 to the first planetary gear mechanism PG1 is the inner peripheral side of the sun gears of the second planetary gear mechanism PG2 and the first planetary gear mechanism PG1 and the first planetary gear mechanism PG1. The case 9 and the first brake B1 are connected to each other via the second planetary gear mechanism PG2 and the opposite side. Further, the ring gear R2 of the second planetary gear mechanism PG2 is connected to the second planetary gear mechanism PG2 side of the carrier CA3 of the third planetary gear mechanism PG3. Further, the side of the carrier CA4 of the fourth planetary gear mechanism PG4 opposite to the third planetary gear mechanism PG3 is connected via the input shaft A1 and the first clutch C1. Further, the ring gear R4 of the fourth planetary gear mechanism PG4 is connected to the output shaft A2 of the fourth planetary gear mechanism PG4 via the opposite side to the third planetary gear mechanism PG3.

As a result, the number of inner peripheral extending portions interposed between the connecting mechanism to which the oil pressure is supplied from the oil passage formed in the input shaft A1 and the input shaft A1 can be set to at most two. Therefore, as compared with the case where the positional relationship of the four planetary gear mechanisms is different from that of the transmission 1, the interposition between the connecting mechanism and the input shaft A1 in which the oil supply is supplied from the oil passage formed in the input shaft A1. The number of extending inner circumferences can be relatively reduced. Therefore, it is possible to suppress an increase in energy loss with respect to the supply of hydraulic pressure.

Further, in the transmission 1, the third clutch C3 may be a dog clutch. As a result, it is possible to suppress an increase in friction loss that occurs in the third clutch C3 when the third clutch C3 is released.

<2. Second embodiment>
Next, the transmission 2 according to the second embodiment of the present invention will be described.

[2-1. Transmission configuration]
First, the configuration of the transmission 2 according to the present embodiment will be described with reference to FIG. FIG. 6 is a skeleton diagram showing an example of a schematic configuration of the transmission 2 according to the present embodiment.

In the transmission 2, the positional relationship of the four planetary gear mechanisms in the case 9 is different from that in the transmission 1 described above. Along with this, the transmission 2 has a different connection path between the rotating element of the planetary gear mechanism and other elements as compared with the transmission 1 described above.

In the transmission 2, the combination of the rotating elements of the planetary gear mechanisms connected to each other and other elements is the same as that of the transmission 1 described above. Further, in the transmission 2, the combination of the rotating element of the planetary gear mechanism, which is the target of switching the connection state of each connecting mechanism, and other rotating elements is the same as that of the transmission 1 described above. Further, in the transmission 2, the fastening state of each connecting mechanism for each transmission stage is the same as that of the transmission 1 described above. Further, in the transmission 2, when the gear ratio of each planetary gear mechanism is the same as that of the transmission 1 described above, the gear ratio for each transmission stage and the step ratio between each transmission stage are the same as those of the transmission 1 described above. The same is true. Further, in the transmission 2, the third clutch C3 may be a dog clutch, similarly to the transmission 1 described above.

In the transmission 2, the four planetary gear mechanisms are arranged concentrically in the case 9 in the order of the third planetary gear mechanism PG3, the second planetary gear mechanism PG2, the first planetary gear mechanism PG1 and the fourth planetary gear mechanism PG4. To.

Hereinafter, an example of a connection path between the rotating element of the planetary gear mechanism and other elements in the transmission 2 will be described.

The input shaft A1 is the inner circumference of the sun gears S3, sun gear S2, sun gear S1 and sun gear S4, which are the sun gears of the third planetary gear mechanism PG3, the second planetary gear mechanism PG2, the first planetary gear mechanism PG1 and the fourth planetary gear mechanism PG4. It is inserted to the side. The input shaft A1 may be arranged concentrically with each planetary gear mechanism, similarly to the transmission 1 described above. Further, power is input to the input shaft A1 from the side opposite to the second planetary gear mechanism PG2 with respect to the third planetary gear mechanism PG3.

The output shaft A2 is arranged on the side opposite to the first planetary gear mechanism PG1 with respect to the fourth planetary gear mechanism PG4. The output shaft A2 may be arranged concentrically with each planetary gear mechanism, similarly to the transmission 1 described above. Further, power is output from the output shaft A2 to the fourth planetary gear mechanism PG4 toward the opposite side of the first planetary gear mechanism PG1.

The side of the carrier CA3 of the third planetary gear mechanism PG3 opposite to the second planetary gear mechanism PG2 is connected to the ring gear R2 of the second planetary gear mechanism PG2 via the outer peripheral side of the ring gear R3 of the third planetary gear mechanism PG3. .. Therefore, the connecting portion that connects the carrier CA3 of the third planetary gear mechanism PG3 and the ring gear R2 of the second planetary gear mechanism PG2 is radially opposite to the second planetary gear mechanism PG2 with respect to the third planetary gear mechanism PG3. It has a radial extending portion 201 extending in the axial direction and an outer peripheral extending portion 221 extending axially from the side opposite to the second planetary gear mechanism PG2 to the outer peripheral side of the ring gear R2 with respect to the outer peripheral side of the ring gear R3. Can be.

The ring gear R3 of the third planetary gear mechanism PG3 passes between the third planetary gear mechanism PG3 and the second planetary gear mechanism PG2 and the inner peripheral side of the sun gear of the second planetary gear mechanism PG2 and the first planetary gear mechanism PG1. It is connected to the sun gear S4 of the fourth planetary gear mechanism PG4. Therefore, the connecting portion connecting the ring gear R3 of the third planetary gear mechanism PG3 and the sun gear S4 of the fourth planetary gear mechanism PG4 extends axially from the outer peripheral side of the ring gear R3 to the second planetary gear mechanism PG2 side. A radial extending portion 202 extending in the radial direction between the peripheral extending portion 222, the third planetary gear mechanism PG3 and the second planetary gear mechanism PG2, and a third planetary gear mechanism with respect to the inner peripheral side of the sun gear S2. It may have an inner peripheral extending portion 226 extending axially from the PG3 side to the inner peripheral side of the sun gear S4.

The sun gear S2 of the second planetary gear mechanism PG2 is connected via the case 9 and the second brake B2 via between the second planetary gear mechanism PG2 and the first planetary gear mechanism PG1. Therefore, the connecting portion connecting the sun gear S2 of the second planetary gear mechanism PG2 and the case 9 includes an inner peripheral extending portion 230 extending axially from the inner peripheral side of the sun gear S2 to the first planetary gear mechanism PG1 side. It may have a radially extending portion 211 extending radially between the second planetary gear mechanism PG2 and the first planetary gear mechanism PG1.

The first planetary gear mechanism PG1 side of the carrier CA2 of the second planetary gear mechanism PG2 is connected to the case 9 via the first brake B1. Therefore, the connecting portion connecting the carrier CA2 of the second planetary gear mechanism PG2 and the case 9 is a radially extending portion 204 extending in the radial direction between the second planetary gear mechanism PG2 and the first planetary gear mechanism PG1. Can have.

The third planetary gear mechanism PG3 side of the carrier CA2 of the second planetary gear mechanism PG2 is the inner peripheral side of the sun gear of the second planetary gear mechanism PG2 and the first planetary gear mechanism PG1, and the first planetary gear mechanism PG1 and the fourth planet. It is connected via the ring gear R1 of the first planetary gear mechanism PG1 and the third clutch C3 via between the gear mechanism PG4. Therefore, the connecting portion connecting the carrier CA2 of the second planetary gear mechanism PG2 and the ring gear R1 of the first planetary gear mechanism PG1 extends radially between the third planetary gear mechanism PG3 and the second planetary gear mechanism PG2. The radial extending portion 203 extends axially from the third planetary gear mechanism PG3 side to the inner peripheral side of the sun gear S2 to the fourth planetary gear mechanism PG4 side with respect to the inner peripheral side of the sun gear S1. The circumferential extending portion 227, the radial extending portion 207 extending in the radial direction between the first planetary gear mechanism PG1 and the fourth planetary gear mechanism PG4, and the fourth planetary gear mechanism PG4 with respect to the outer peripheral side of the ring gear R1. It may have an outer peripheral extending portion 224 extending axially from the side to the outer peripheral side of the ring gear R1.

The sun gear S1 of the first planetary gear mechanism PG1 is connected to the case 9 via between the second planetary gear mechanism PG2 and the first planetary gear mechanism PG1. Therefore, the connecting portion connecting the sun gear S1 and the case 9 of the first planetary gear mechanism PG1 is an inner peripheral extending portion 228 extending axially from the inner peripheral side of the sun gear S1 to the second planetary gear mechanism PG2 side. It may have a radially extending portion 205 extending radially between the second planetary gear mechanism PG2 and the first planetary gear mechanism PG1.

The second planetary gear mechanism PG2 side of the carrier CA1 of the first planetary gear mechanism PG1 passes through the outer peripheral side of the ring gear R1 of the first planetary gear mechanism PG1 and the first planetary gear mechanism of the carrier CA4 of the fourth planetary gear mechanism PG4. It is connected to the PG1 side. Therefore, the connecting portion connecting the carrier CA1 of the first planetary gear mechanism PG1 and the carrier CA4 of the fourth planetary gear mechanism PG4 extends radially between the second planetary gear mechanism PG2 and the first planetary gear mechanism PG1. The radial extending portion 206, the outer peripheral extending portion 223 extending axially from the second planetary gear mechanism PG2 side to the fourth planetary gear mechanism PG4 side with respect to the outer peripheral side of the ring gear R1, and the first planetary gear. It may have a radially extending portion 208 extending radially between the mechanism PG1 and the fourth planetary gear mechanism PG4.

The side of the carrier CA4 of the fourth planetary gear mechanism PG4 opposite to the first planetary gear mechanism PG1 is connected via the input shaft A1 and the first clutch C1. Therefore, the connecting portion that connects the carrier CA4 of the fourth planetary gear mechanism PG4 and the input shaft A1 extends in the radial direction on the opposite side of the fourth planetary gear mechanism PG4 from the first planetary gear mechanism PG1. It may have an extension 209.

The ring gear R4 of the fourth planetary gear mechanism PG4 is connected to the output shaft A2 of the fourth planetary gear mechanism PG4 via the opposite side to the first planetary gear mechanism PG1. Therefore, the connecting portion connecting the ring gear R4 of the fourth planetary gear mechanism PG4 and the output shaft A2 is an outer peripheral extending portion 225 extending in the axial direction from the outer peripheral side of the ring gear R4 to the opposite side to the first planetary gear mechanism PG1. And the fourth planetary gear mechanism PG4 may have a radial extending portion 210 extending in the radial direction on the opposite side of the first planetary gear mechanism PG1.

As described above, in the transmission 2, eleven radial extending portions extending in the radial direction can be provided at positions different from those of the four planetary gear mechanisms along the axial direction.

Further, in the transmission 2, the outer peripheral extending portion 221 may be provided so as to cover the outer peripheral portion of the outer peripheral extending portion 222. Therefore, a double structure can be formed by the outer peripheral extending portion 222 and the outer peripheral extending portion 221.

Further, in the transmission 2, the outer peripheral extending portion 223 may be provided so as to cover the outer peripheral portion of the outer peripheral extending portion 224. Therefore, a double structure can be formed by the outer peripheral extending portion 224 and the outer peripheral extending portion 223.
Further, in the transmission 2, the inner peripheral extending portion 226 may be provided so as to cover the outer peripheral portion of the input shaft A1. Further, the inner peripheral extending portion 227 may be provided so as to cover the outer peripheral portion of the inner peripheral extending portion 226. Further, the inner peripheral extending portion 228 may be provided so as to cover the outer peripheral portion of the inner peripheral extending portion 227. Therefore, a quadruple structure can be formed by the input shaft A1, the inner peripheral extending portion 226, the inner peripheral extending portion 227, and the inner peripheral extending portion 228.

Here, an oil passage may be formed in the input shaft A1. The oil pressure for driving the first clutch C1 can be supplied from the oil passage formed in the input shaft A1 via the radial extending portion 209. Further, the oil pressure for driving the second clutch C2 can be supplied from the oil passage formed in the input shaft A1 via the inner peripheral extending portion 226. Further, the oil pressure for driving the third clutch C3 and the fourth clutch C4 can be supplied from the oil passage formed in the input shaft A1 via the inner peripheral extending portion 226 and the inner peripheral extending portion 227.

Further, an oil passage may be formed in the case 9. The hydraulic pressure for driving the first brake B1 and the second brake B2 may be supplied through the oil passage formed in the case 9.

Further, in the transmission 2, for example, the rotation speeds of the outer peripheral extending portion 223 and the outer peripheral extending portion 225 are detected by using a sensor capable of detecting the rotation speed of the member, and the rotation speed of the input shaft A1 is detected based on the detection result. Can be calculated. The calculation result of the rotation speed of the input shaft A1 can be used for controlling the switching of the shift stage of the transmission 2. The detection result of the rotation speed of the outer peripheral extending portion 225 can be used for various controls as the detection result of the rotation speed of the output shaft A2.

[2-2. Effect of transmission]
Subsequently, the effect of the transmission 2 according to the present embodiment will be described.

In the transmission 2, the combination of the rotating element of the planetary gear mechanism connected to each other and other elements, and the combination of the rotating element of the planetary gear mechanism to be switched the connection state of each connecting mechanism and the other rotating element. Is the same as that of the transmission 1. Therefore, similarly to the transmission 1, the transmission 2 can realize 10 forward speeds and 1 reverse speed by providing four planetary gear mechanisms and six connecting mechanisms.

Further, in the transmission 2, in the case 9, the four planetary gear mechanisms are concentric in the order of the third planetary gear mechanism PG3, the second planetary gear mechanism PG2, the first planetary gear mechanism PG1 and the fourth planetary gear mechanism PG4. Be placed. Specifically, the input shaft A1 includes sun gears S3, sun gears S2, sun gears S1 and sun gears of the third planetary gear mechanism PG3, the second planetary gear mechanism PG2, the first planetary gear mechanism PG1 and the fourth planetary gear mechanism PG4. It is inserted on the inner peripheral side of the sun gear S4. Further, the output shaft A2 is arranged on the side opposite to the first planetary gear mechanism PG1 with respect to the fourth planetary gear mechanism PG4. Further, the side opposite to the second planetary gear mechanism PG2 of the carrier CA3 of the third planetary gear mechanism PG3 is connected to the ring gear R2 of the second planetary gear mechanism PG2 via the outer peripheral side of the ring gear R3 of the third planetary gear mechanism PG3. Will be done. Further, the ring gear R3 of the third planetary gear mechanism PG3 is located between the third planetary gear mechanism PG3 and the second planetary gear mechanism PG2 and on the inner peripheral side of the sun gear of the second planetary gear mechanism PG2 and the first planetary gear mechanism PG1. It is connected to the sun gear S4 of the fourth planetary gear mechanism PG4 via. Further, the sun gear S2 of the second planetary gear mechanism PG2 is connected via the case 9 and the second brake B2 via between the second planetary gear mechanism PG2 and the first planetary gear mechanism PG1. Further, the first planetary gear mechanism PG1 side of the carrier CA2 of the second planetary gear mechanism PG2 is connected to the case 9 via the first brake B1. Further, the third planetary gear mechanism PG3 side of the carrier CA2 of the second planetary gear mechanism PG2 is the inner peripheral side of the sun gears of the second planetary gear mechanism PG2 and the first planetary gear mechanism PG1, and the first planetary gear mechanism PG1 and the first. 4 It is connected via the ring gear R1 of the first planetary gear mechanism PG1 and the third clutch C3 via between the planetary gear mechanism PG4. Further, the sun gear S1 of the first planetary gear mechanism PG1 is connected to the case 9 via between the second planetary gear mechanism PG2 and the first planetary gear mechanism PG1. Further, the second planetary gear mechanism PG2 side of the carrier CA1 of the first planetary gear mechanism PG1 passes through the outer peripheral side of the ring gear R1 of the first planetary gear mechanism PG1 and the first planet of the carrier CA4 of the fourth planetary gear mechanism PG4. It is connected to the gear mechanism PG1 side. Further, the side of the carrier CA4 of the fourth planetary gear mechanism PG4 opposite to the first planetary gear mechanism PG1 is connected via the input shaft A1 and the first clutch C1. Further, the ring gear R4 of the fourth planetary gear mechanism PG4 is connected to the output shaft A2 of the fourth planetary gear mechanism PG4 via the opposite side to the first planetary gear mechanism PG1.

As a result, the number of radial extending portions provided at different positions from the four planetary gear mechanisms along the axial direction and extending in the radial direction is made different from that of the transmission 2 in the positional relationship of the four planetary gear mechanisms. The number can be reduced as compared with the case (for example, the transmission 1 according to the first embodiment described above). Therefore, the transmission 2 can be miniaturized in the axial direction.

Further, the number of layers in the multiple structure formed by the outer peripheral extending portion can be at most two. Therefore, as compared with the case where the positional relationship of the four planetary gear mechanisms is different from that of the transmission 2 (for example, the transmission 1 according to the first embodiment described above), the multiple structure formed by the outer peripheral extending portion. The number of layers in can be reduced. Therefore, the transmission 2 can be miniaturized in the radial direction.

Further, the number of inner peripheral extending portions interposed between the connecting mechanism to which the oil pressure is supplied from the oil passage formed in the input shaft A1 and the input shaft A1 can be at most two. Therefore, as compared with the case where the positional relationship of the four planetary gear mechanisms is different from that of the transmission 2, the interposition between the connecting mechanism and the input shaft A1 in which the oil supply is supplied from the oil passage formed in the input shaft A1. The number of extending inner circumferences can be relatively reduced. Therefore, it is possible to suppress an increase in energy loss with respect to the supply of hydraulic pressure.

<3. Conclusion>
As described above, according to the embodiment of the present invention, some of the rotating elements of the four planetary gear mechanisms are connected to other predetermined elements. Further, the six connecting mechanisms can switch the connected state between the rotating element of the predetermined planetary gear mechanism and the other rotating element. As a result, 10 forward stages and 1 reverse stage can be realized by providing four planetary gear mechanisms and six connecting mechanisms. Therefore, for example, the number of gears can be increased without increasing the number of planetary gears and coupling mechanisms as compared with a transmission having four planetary gears and six connecting mechanisms and capable of achieving eight forward gears and one reverse gear. Can be increased. Therefore, it is possible to further increase the number of gears while suppressing the increase in size of the transmission. As a result, it is possible to improve fuel efficiency and driveability.

In the above, the example in which the transmission according to the embodiment of the present invention is mounted on the vehicle has been mainly described, but the device on which the transmission according to the embodiment of the present invention is mounted is not limited to such an example. The transmission according to the embodiment of the present invention may be mounted on a device other than the vehicle as long as it is a device having a power transmission system.

Further, in the above description, an example in which a wet multi-plate brake and a wet multi-plate clutch are used as each brake and each clutch has been mainly described, but the types of each brake and each clutch are not limited to such examples. Each brake and each clutch may be capable of switching the connection state between the elements.

Further, in the above, the gear ratios of the first planetary gear mechanism PG1, the second planetary gear mechanism PG2, the third planetary gear mechanism PG3, and the fourth planetary gear mechanism PG4 are 0.57, 0.24, 0.67, and 0, respectively. Although the example of .30 has been mainly described, the gear ratio of each planetary gear mechanism is not limited to such an example. For example, the gear ratio of each planetary gear mechanism can be appropriately set according to the design specifications of a vehicle or the like on which the transmission according to the embodiment of the present invention is mounted. The gear ratio for each gear in the transmission according to the embodiment of the present invention is a value corresponding to the set value of the gear ratio of each planetary gear mechanism.

Further, in the above description, each component (for example, a connecting portion for connecting the rotating element of the planetary gear mechanism and other elements) in the transmission according to the embodiment of the present invention has been described with reference to each drawing. The shape of each component and the positional relationship between the components are not limited to the examples corresponding to the drawings, and the shape and the positional relationship shown in the drawings are only examples. Further, each component may be formed integrally or may be formed by a plurality of members.

Although the preferred embodiments of the present invention have been described in detail with reference to the accompanying drawings, the present invention is not limited to these examples. It is clear that a person having ordinary knowledge in the field of technology to which the present invention belongs can come up with various modifications or applications within the scope of the technical ideas described in the claims. , These are also naturally understood to belong to the technical scope of the present invention.

1, 2 Transmission 9 Case A1 Input shaft A2 Output shaft B1 1st brake B2 2nd brake C1 1st clutch C2 2nd clutch C3 3rd clutch C4 4th clutch CA1 Carrier CA2 Carrier CA3 Carrier CA4 Carrier P1 Pinion gear P2 Pinion gear P3 Pinion gear P4 Pinion gear PG1 1st planetary gear mechanism PG2 2nd planetary gear mechanism PG3 3rd planetary gear mechanism PG4 4th planetary gear mechanism R1 Ring gear R2 Ring gear R3 Ring gear R4 Ring gear S1 Sun gear S2 Sun gear S3 Sun gear S4 Sun gear

Claims (6)

The first planetary gear mechanism, the second planetary gear mechanism, the third planetary gear mechanism, and the fourth planetary gear mechanism, which are planetary gear mechanisms provided in the case and having a sun gear, a carrier, and a ring gear as rotating elements,
The first coupling mechanism, the second coupling mechanism, the third coupling mechanism, the fourth coupling mechanism, the fifth coupling mechanism, and the fifth coupling mechanism, which are coupling mechanisms capable of switching the coupling state between the rotating element and other elements of the planetary gear mechanism. 6 connection mechanism and
It is a transmission equipped with
The sun gear of the first planetary gear mechanism is connected to the case and
The carrier of the first planetary gear mechanism is connected to the carrier of the fourth planetary gear mechanism.
The ring gear of the second planetary gear mechanism is connected to the carrier of the third planetary gear mechanism.
The sun gear of the third planetary gear mechanism is connected to an input shaft to which power is input.
The ring gear of the third planetary gear mechanism is connected to the sun gear of the fourth planetary gear mechanism.
The ring gear of the fourth planetary gear mechanism is connected to an output shaft that outputs the transmitted power.
The first connecting mechanism can switch the connecting state between the carrier of the second planetary gear mechanism and the case.
The second connecting mechanism can switch the connecting state between the sun gear of the second planetary gear mechanism and the case.
The third connecting mechanism can switch the connection state between the sun gear of the third planetary gear mechanism and the input shaft and the carrier of the first planetary gear mechanism and the carrier of the fourth planetary gear mechanism.
The fourth connecting mechanism can switch the connection state between the carrier of the second planetary gear mechanism, the ring gear of the third planetary gear mechanism, and the sun gear of the fourth planetary gear mechanism.
The fifth connection mechanism can switch the connection state between the ring gear of the first planetary gear mechanism and the carrier of the second planetary gear mechanism.
The sixth connecting mechanism can switch the connection state between the ring gear of the first planetary gear mechanism and the sun gear of the second planetary gear mechanism.
transmission. In the case, the four planetary gear mechanisms are arranged concentrically in the order of the first planetary gear mechanism, the second planetary gear mechanism, the third planetary gear mechanism, and the fourth planetary gear mechanism.
The transmission according to claim 1. The input shaft is inserted into the inner peripheral side of the sun gear of the first planetary gear mechanism, the second planetary gear mechanism, the third planetary gear mechanism, and the fourth planetary gear mechanism.
The output shaft is arranged on the side opposite to the third planetary gear mechanism with respect to the fourth planetary gear mechanism.
The sun gear of the first planetary gear mechanism is connected to the case with respect to the first planetary gear mechanism via the opposite side to the second planetary gear mechanism.
The side of the carrier of the first planetary gear mechanism opposite to the second planetary gear mechanism passes through the outer peripheral side of the ring gears of the first planetary gear mechanism, the second planetary gear mechanism, and the third planetary gear mechanism. Connected to the third planetary gear mechanism side of the carrier of the fourth planetary gear mechanism,
The ring gear of the first planetary gear mechanism is connected to the sun gear of the second planetary gear mechanism via the first planetary gear mechanism and the second planetary gear mechanism via the sixth connecting mechanism.
The sun gear of the second planetary gear mechanism is connected to the case via the inner peripheral side of the sun gear of the first planetary gear mechanism and the side opposite to the second planetary gear mechanism with respect to the first planetary gear mechanism. Connected via the second connecting mechanism,
The first planetary gear mechanism side of the carrier of the second planetary gear mechanism includes the outer peripheral side of the ring gears of the second planetary gear mechanism and the third planetary gear mechanism, and the third planetary gear mechanism and the fourth planetary gear. It is connected to the sun gear of the fourth planetary gear mechanism via the mechanism and via the fourth connecting mechanism.
The side of the carrier of the second planetary gear mechanism opposite to the first planetary gear mechanism is relative to the inner peripheral side of the sun gear of the second planetary gear mechanism and the first planetary gear mechanism and the first planetary gear mechanism. The case is connected to the case via the first connecting mechanism via the opposite side to the second planetary gear mechanism.
The ring gear of the second planetary gear mechanism is connected to the second planetary gear mechanism side of the carrier of the third planetary gear mechanism.
The side of the carrier of the fourth planetary gear mechanism opposite to the third planetary gear mechanism is connected to the input shaft via the third connecting mechanism.
The ring gear of the fourth planetary gear mechanism is connected to the output shaft of the fourth planetary gear mechanism via the opposite side to the third planetary gear mechanism.
The transmission according to claim 2. In the case, the four planetary gear mechanisms are arranged concentrically in the order of the third planetary gear mechanism, the second planetary gear mechanism, the first planetary gear mechanism, and the fourth planetary gear mechanism.
The transmission according to claim 1. The input shaft is inserted into the inner peripheral side of the sun gear of the third planetary gear mechanism, the second planetary gear mechanism, the first planetary gear mechanism, and the fourth planetary gear mechanism.
The output shaft is arranged on the opposite side of the first planetary gear mechanism with respect to the fourth planetary gear mechanism.
The side of the carrier of the third planetary gear mechanism opposite to the second planetary gear mechanism is connected to the ring gear of the second planetary gear mechanism via the outer peripheral side of the ring gear of the third planetary gear mechanism.
The ring gear of the third planetary gear mechanism passes between the third planetary gear mechanism and the second planetary gear mechanism, and via the inner peripheral side of the sun gear of the second planetary gear mechanism and the first planetary gear mechanism. Connected to the sun gear of the 4th planetary gear mechanism,
The sun gear of the second planetary gear mechanism is connected to the case via the second connecting mechanism via the second planetary gear mechanism and the first planetary gear mechanism.
The first planetary gear mechanism side of the carrier of the second planetary gear mechanism is connected to the case via the first connecting mechanism.
The third planetary gear mechanism side of the carrier of the second planetary gear mechanism includes the inner peripheral side of the sun gear of the second planetary gear mechanism and the first planetary gear mechanism, the first planetary gear mechanism, and the fourth planet. It is connected to the ring gear of the first planetary gear mechanism via the gear mechanism and the fifth connecting mechanism.
The sun gear of the first planetary gear mechanism is connected to the case via between the second planetary gear mechanism and the first planetary gear mechanism.
The second planetary gear mechanism side of the carrier of the first planetary gear mechanism is with the first planetary gear mechanism side of the carrier of the fourth planetary gear mechanism via the outer peripheral side of the ring gear of the first planetary gear mechanism. Connected,
The side of the carrier of the fourth planetary gear mechanism opposite to the first planetary gear mechanism is connected to the input shaft via the third connecting mechanism.
The ring gear of the fourth planetary gear mechanism is connected to the output shaft of the fourth planetary gear mechanism via the opposite side to the first planetary gear mechanism.
The transmission according to claim 4. The fifth coupling mechanism is a dog clutch.
The transmission according to any one of claims 1 to 5.

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