JP2020008027A - Speed change gear - Google Patents

Abstract

To further increase a shift stage while restraining enlargement of a speed change gear.SOLUTION: In the speed change gear, a ring gear of a first planetary gear mechanism is coupled to a ring gear of a third planetary gear mechanism, a sun gear of a second planetary gear mechanism is coupled to a case, a carrier of the second planetary gear mechanism is coupled to a sun gear of the third planetary gear mechanism, a carrier of the third planetary gear mechanism is coupled to a carrier of a fourth planetary gear mechanism, a sun gear of the fourth planetary gear mechanism is coupled to an input shaft, and a carrier of the fourth planetary gear mechanism is coupled to an output shaft. Coupling states between the carrier of the first planetary gear mechanism and the case, the sun gear of the first planetary gear mechanism and the case, the carrier of the second planetary gear mechanism, the sun gear of the third planetary gear mechanism, the sun gear of the fourth planetary gear mechanism and the input shaft, the sun gear of the first planetary gear mechanism, the carrier of the second planetary gear mechanism and the sun gear of the third planetary gear mechanism, the carrier of the first planetary gear mechanism and the ring gear of the fourth planetary gear mechanism, and the carrier of the first planetary gear mechanism and the ring gear of the second planetary gear mechanism can be switched.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a transmission.

  2. Description of the Related Art Conventionally, in vehicles and the like, transmissions capable of shifting input power and outputting the power have been used. A conventional transmission includes a plurality of planetary gear mechanisms each including a sun gear, a carrier, and a ring gear as rotating elements, and a plurality of coupling mechanisms that can switch a coupling state between the rotating elements of the planetary gear mechanism and other elements, and includes a multi-stage transmission. There are those that can realize the above-mentioned speed stages.

  For example, Patent Document 1 discloses a transmission including four planetary gear mechanisms and six coupling mechanisms, and capable of realizing eight forward speeds and one reverse speed.

US Patent Application Publication No. 2014/0128199

  By the way, in a vehicle equipped with a transmission, in order to improve fuel efficiency and drivability, it is considered that it is desirable to further increase the number of shift stages and to increase a gear ratio width (ratio coverage). By increasing the number of gears, the engine can always be operated in a region where fuel efficiency is high, so that fuel efficiency can be improved. In addition, since the ratio coverage is expanded, the acceleration performance at low gears can be improved without impairing the fuel efficiency at high gears, so that the drivability can be improved. However, when the number of gears is increased, the number of components constituting the transmission increases, which may increase the size of the transmission.

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

  In order to solve the above problems, according to an aspect of the present invention, a first planetary gear mechanism, a second planetary gear mechanism, which is a planetary gear mechanism provided in a case and including a sun gear, a carrier, and a ring gear as rotating elements, A first connection mechanism, a second connection mechanism, and a third connection, which are connection mechanisms capable of switching a connection state between a third planetary gear mechanism and a fourth planetary gear mechanism, and a connection state between the rotary element and another element of the planetary gear mechanism. A transmission including a mechanism, a fourth connection mechanism, a fifth connection mechanism, and a sixth connection mechanism, wherein a ring gear of the first planetary gear mechanism is connected to a ring gear of the third planetary gear mechanism; The sun gear of the second planetary gear mechanism is connected to the case, the carrier of the second planetary gear mechanism is connected to the sun gear of the third planetary gear mechanism, and the carrier of the third planetary gear mechanism is connected to the A sun gear of the fourth planetary gear mechanism is connected to an input shaft to which power is input, and a carrier of the fourth planetary gear mechanism is connected to an output shaft that outputs power to be transmitted. Connected, the first connection mechanism is capable of switching a connection state between the carrier of the first planetary gear mechanism and the case, and the second connection mechanism is provided with a sun gear of the first planetary gear mechanism and the case. The third connection mechanism is capable of switching the connection state between the carrier of the second planetary gear mechanism, the sun gear of the third planetary gear mechanism, the sun gear of the fourth planetary gear mechanism, and the input shaft. The fourth connection mechanism changes the connection state between the sun gear of the first planetary gear mechanism, the carrier of the second planetary gear mechanism, and the sun gear of the third planetary gear mechanism. The fifth connection mechanism is capable of switching a connection state between a carrier of the first planetary gear mechanism and a ring gear of the fourth planetary gear mechanism, and the sixth connection mechanism is capable of switching the first planetary gear mechanism. A transmission is provided which is capable of switching a connection state between a carrier of a planetary gear mechanism and a ring gear of the second planetary gear mechanism.

  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 through an inner peripheral side of a sun gear of the first planetary gear mechanism, the second planetary gear mechanism, and the third planetary gear mechanism, and the output shaft is provided with respect to the fourth planetary gear mechanism. The sun gear of the first planetary gear mechanism is arranged on the opposite side to the third planetary gear mechanism, and the case and the second gear are connected to the first planetary gear mechanism via a side opposite to the second planetary gear mechanism. The second planetary gear of the carrier of the first planetary gear mechanism, which is connected via a connection mechanism and connected to the first planetary gear mechanism side of the carrier of the second planetary gear mechanism via the fourth connection mechanism. The mechanism and the opposite side are connected to the case via the first connection mechanism, and the outer side of the ring gear of the first planetary gear mechanism, the second planetary gear mechanism, and the third planetary gear mechanism, A ring gear of the fourth planetary gear mechanism and the ring gear; 5, the carrier of the first planetary gear mechanism is connected to the second planetary gear mechanism side via a ring gear of the second planetary gear mechanism via the sixth connection mechanism. The ring gear of the planetary gear mechanism is connected to the ring gear of the third planetary gear mechanism via an outer peripheral side of the ring gear of the second planetary gear mechanism, and the sun gear of the second planetary gear mechanism is connected to the first planetary gear mechanism. And the third planetary gear of the carrier of the second planetary gear mechanism is connected to the case via the inner peripheral side of the sun gear and the opposite side of the first planetary gear mechanism from the second planetary gear mechanism. The gear mechanism side is connected to the sun gear of the third planetary gear mechanism, and the fourth planetary gear mechanism side of the carrier of the third planetary gear mechanism is connected to the third planetary gear mechanism of the carrier of the fourth planetary gear mechanism. Contact with the side Is, the third planetary gear mechanism and the reverse side of the carrier of the fourth planetary gear mechanism may be connected to the output shaft.

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

  The input shaft is inserted through an inner peripheral side of a sun gear of the third planetary gear mechanism, and the output shaft is inserted through an inner peripheral side of a sun gear of the first planetary gear mechanism and the second planetary gear mechanism, The sun gear of the third planetary gear mechanism has a side opposite to the fourth planetary gear mechanism with respect to the third planetary gear mechanism, and the third planetary gear mechanism, the fourth planetary gear mechanism, the first planetary gear mechanism, and The carrier of the second planetary gear mechanism is connected to the opposite side to the first planetary gear mechanism via the outer peripheral side of the ring gear of the second planetary gear mechanism, and the fourth carrier of the carrier of the third planetary gear mechanism is connected to the fourth planetary gear mechanism. The planetary gear mechanism side is connected to the third planetary gear mechanism side of the carrier of the fourth planetary gear mechanism, and the ring gear of the third planetary gear mechanism passes through the outer peripheral side of the ring gear of the fourth planetary gear mechanism. Of the first planetary gear mechanism The first planetary gear mechanism side of the carrier of the fourth planetary gear mechanism is connected to the output shaft, and the sun gear of the first planetary gear mechanism is connected to the carrier of the second planetary gear mechanism. The fourth planetary gear mechanism is connected to the first planetary gear mechanism via the fourth connection mechanism, and the carrier of the first planetary gear mechanism is connected to the ring gear of the fourth planetary gear mechanism and the fifth connection mechanism. , And connected to the sun gear of the second planetary gear mechanism via the inner peripheral side of the sun gear of the first planetary gear mechanism via the first coupling mechanism, and to the carrier of the first planetary gear mechanism. The second planetary gear mechanism side is connected to the ring gear of the second planetary gear mechanism via the sixth coupling mechanism, and the sun gear of the second planetary gear mechanism has the sun gear with respect to the second planetary gear mechanism. 1st planet Via the car mechanism and opposite side it may be connected to the case.

  The first connection mechanism may be a dog brake.

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

1 is a skeleton diagram illustrating an example of a schematic configuration of a transmission according to a first embodiment of the present invention. FIG. 4 is an alignment chart showing a relationship between rotation speeds of a sun gear, a carrier, and a ring gear in a planetary gear mechanism. FIG. 3 is an explanatory diagram illustrating a fastening state of each coupling mechanism at each shift speed in the transmission according to the embodiment. FIG. 3 is an explanatory diagram illustrating an example of a gear ratio at each shift speed in the transmission according to the embodiment. FIG. 3 is an explanatory diagram illustrating an example of a step ratio between each shift speed in the transmission according to the embodiment. FIG. 7 is a skeleton diagram illustrating an example of a schematic configuration of a transmission according to a second embodiment of the present invention.

  Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. In the specification and the drawings, components having substantially the same functional configuration are denoted by the same reference numerals, and redundant description is omitted.

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

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

  The transmission 1 includes, for example, as shown in FIG. 1, 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, It includes a four planetary gear mechanism PG4, a first brake B1, a second brake B2, a first clutch C1, a second clutch C2, a third clutch C3, and a fourth clutch C4. The transmission 1 is mounted on a vehicle, for example, and shifts power output from a drive source such as an engine at a gear ratio according to each gear 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 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 driving wheels via a differential device, and the power output from the output shaft A2 is transmitted to the driving 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 provided in the case 9 and include a sun gear, a carrier, and a ring gear as rotating elements. is there. As described above, the transmission 1 includes the 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.

  Each planetary gear mechanism is, specifically, 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 alignment chart. The ratio between the interval D1 on each vertical axis indicating the rotational speed of the sun gear and the carrier and the interval D2 on each vertical axis indicating the rotational speed of the carrier and the ring gear matches the ratio between the number of teeth of the ring gear and the number of teeth of the sun gear. . Therefore, if the ratio of the rotation speed of the ring gear to the rotation speed of the sun gear when the carrier is fixed is defined as the gear ratio of the planetary gear mechanism, the gear ratio of the planetary gear mechanism is obtained by dividing the number of teeth of the sun gear by the number of teeth of the ring gear. It is the value obtained by By appropriately setting the number of teeth of the ring gear and the number of teeth of the sun gear in each planetary gear mechanism, the gear ratio of each planetary gear mechanism can be set to a desired gear ratio.

  The first planetary gear mechanism PG1 rotates the sun gear S1, a ring gear R1 arranged concentrically on the outer peripheral side with respect to the sun gear S1, a plurality of pinion gears P1 meshing with the sun gear S1 and the ring gear R1, and a plurality of pinion gears P1. And a carrier CA1 that freely supports. The gear ratio of the first planetary gear mechanism PG1 is set to, for example, 0.56.

  The second planetary gear mechanism PG2 rotates the sun gear S2, a ring gear R2 concentrically arranged on the outer peripheral side with respect to the sun gear S2, a plurality of pinion gears P2 meshing with the sun gear S2 and the ring gear R2, and a plurality of pinion gears P2. And a carrier CA2 that supports freely. The gear ratio of the second planetary gear mechanism PG2 is set to, for example, 0.32.

  The third planetary gear mechanism PG3 rotates the sun gear S3, a ring gear R3 arranged concentrically on the outer peripheral side with respect to the sun gear S3, a plurality of pinion gears P3 meshing with the sun gear S3 and the ring gear R3, and a plurality of pinion gears P3. And a carrier CA3 that supports freely. The gear ratio of the third planetary gear mechanism PG3 is set to, for example, 0.26.

  The fourth planetary gear mechanism PG4 rotates the sun gear S4, a ring gear R4 concentrically arranged on the outer peripheral side with respect to the sun gear S4, a plurality of pinion gears P4 meshing with the sun gear S4 and the ring gear R4, and a plurality of pinion gears P4. And a carrier CA4 that is freely supported. The gear ratio of the fourth planetary gear mechanism PG4 is set to, for example, 0.53.

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

  The ring gear R1 of the first planetary gear mechanism PG1 is connected to the ring gear R3 of the third planetary gear mechanism PG3. Therefore, the rotation speeds of the ring gear R1 of the first planetary gear mechanism PG1 and the ring gear R3 of the third planetary gear mechanism PG3 match.

  The sun gear S2 of the second planetary gear mechanism PG2 is connected to the case 9. Therefore, the sun gear S2 of the second planetary gear mechanism PG2 is fixed to the case 9.

  The carrier CA2 of the second planetary gear mechanism PG2 is connected to the sun gear S3 of the third planetary gear mechanism PG3. Therefore, the rotation speeds of the carrier CA2 of the second planetary gear mechanism PG2 and the sun gear S3 of the third planetary gear mechanism PG3 match.

  The carrier CA3 of the third planetary gear mechanism PG3 is connected to the carrier CA4 of the fourth planetary gear mechanism PG4. Therefore, the rotation speeds of the carrier CA3 of the third planetary gear mechanism PG3 and the carrier CA4 of the fourth planetary gear mechanism PG4 match.

  The sun gear S4 of the fourth planetary gear mechanism PG4 is connected to the input shaft A1. Therefore, the rotation speeds of the sun gear S4 and the input shaft A1 of the fourth planetary gear mechanism PG4 match.

  The carrier CA4 of the fourth planetary gear mechanism PG4 is connected to the output shaft A2. Therefore, the rotation speeds of the carrier CA4 and the output shaft A2 of the fourth planetary gear mechanism PG4 match.

  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 capable of switching a connection state between a rotating element of the planetary gear mechanism and another element. Mechanism. As described above, the transmission 1 includes the six connection 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 a first connection mechanism, a second connection mechanism, a third connection mechanism according to the present invention, They correspond to a fourth connection mechanism, a fifth connection mechanism, and a sixth connection mechanism, respectively.

  Each of the brakes 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. Each brake is engaged or released by controlling the hydraulic pressure supplied to each brake. When the brake is engaged, the rotating element of the planetary gear mechanism and the case 9 are connected, 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 CA1 of the first planetary gear mechanism PG1 and the case 9. When the first brake B1 is engaged, the carrier CA1 of the first planetary gear mechanism PG1 is fixed to the case 9. On the other hand, when the first brake B1 is released, the fixing of the first planetary gear mechanism PG1 to the case 9 of the carrier CA1 is released.

  Further, the first brake B1 may be a dog brake. Here, the engagement state of the first brake B1 is switched before and after switching between the second forward speed (2nd) and the third forward speed (3rd), as described later. Before and after switching between the second forward speed (2nd) and the third forward speed (3rd), the direction of the torque generated in the first brake B1 is reversed, so that a dog brake is used as the first brake B1. Also, it is possible to smoothly switch the engagement state of the first brake B1.

  The second brake B2 can switch the connection state between the sun gear S1 of the first planetary gear mechanism PG1 and the case 9. When the second brake B2 is engaged, the sun gear S1 of the first planetary gear mechanism PG1 is fixed to the case 9. On the other hand, when the second brake B2 is released, the fixing of the sun gear S1 of the first planetary gear mechanism PG1 to the case 9 is released.

  Each clutch can switch the connection state between the rotating element of the planetary gear mechanism and another rotating element. The other rotating elements may include an input shaft A1 and an 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 hydraulic pressure supplied to each clutch, each clutch is engaged or released. When the clutch is engaged, the rotating element of the planetary gear mechanism is connected to another rotating element, and the rotational speed of the rotating element of the planetary gear mechanism is equal to that of the other rotating element. On the other hand, when the clutch is released, the connection between the rotating element of the planetary gear mechanism and the other rotating element is released, and the transmission of power between the rotating element of the planetary gear mechanism and the other rotating element is performed. Is shut off.

  The first clutch C1 can switch the connection state between the carrier CA2 of the second planetary gear mechanism PG2, the sun gear S3 of the third planetary gear mechanism PG3, the sun gear S4 of the fourth planetary gear mechanism PG4, and the input shaft A1. When the first clutch C1 is engaged, the rotation speed between the carrier CA2 of the second planetary gear mechanism PG2, the sun gear S3 of the third planetary gear mechanism PG3, and the sun gear S4 of the fourth planetary gear mechanism PG4 and the input shaft A1. Matches. On the other hand, when the first clutch C1 is released, the carrier CA2 of the second planetary gear mechanism PG2, the sun gear S3 of the third planetary gear mechanism PG3, and the sun gear S4 of the fourth planetary gear mechanism PG4 and the input shaft A1. Power transmission is interrupted.

  The second clutch C2 can switch the connection state between the sun gear S1 of the first planetary gear mechanism PG1 and the carrier CA2 of the second planetary gear mechanism PG2 and the sun gear S3 of the third planetary gear mechanism PG3. When the second clutch C2 is engaged, the rotational speeds of the sun gear S1 of the first planetary gear mechanism PG1, the carrier CA2 of the second planetary gear mechanism PG2, and the sun gear S3 of the third planetary gear mechanism PG3 match. On the other hand, when the second clutch C2 is released, power is transmitted between the sun gear S1 of the first planetary gear mechanism PG1 and the carrier CA2 of the second planetary gear mechanism PG2 and the sun gear S3 of the third planetary gear mechanism PG3. Is shut off.

  The third clutch C3 can switch the connection state between the carrier CA1 of the first planetary gear mechanism PG1 and the ring gear R4 of the fourth planetary gear mechanism PG4. By engaging the third clutch C3, the rotational speeds of the carrier CA1 of the first planetary gear mechanism PG1 and the ring gear R4 of the fourth planetary gear mechanism PG4 match. On the other hand, when the third clutch C3 is released, transmission of power between the carrier CA1 of the first planetary gear mechanism PG1 and the ring gear R4 of the fourth planetary gear mechanism PG4 is interrupted.

  The fourth clutch C4 can switch the connection state between the carrier CA1 of the first planetary gear mechanism PG1 and the ring gear R2 of the second planetary gear mechanism PG2. By engaging the fourth clutch C4, the rotation speeds of the carrier CA1 of the first planetary gear mechanism PG1 and the ring gear R2 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 carrier CA1 of the first planetary gear mechanism PG1 and the ring gear R2 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. Hereinafter, 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 inserted through sun gears S1, S2, and S3, which are sun gears of the first planetary gear mechanism PG1, the second planetary gear mechanism PG2, and the third planetary gear mechanism PG3. The input shaft A1 can be arranged concentrically with each planetary gear mechanism. The input shaft A1 is connected to a drive source on the opposite side of the first planetary gear mechanism PG1 from the second planetary gear mechanism PG2. 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 can be arranged concentrically with each planetary gear mechanism. The opposite side of the output shaft A2 from the fourth planetary gear mechanism PG4 is connected to the drive wheels. Therefore, power is output from the output shaft A2 to the fourth planetary gear mechanism PG4 toward the side opposite to the third planetary gear mechanism PG3.

  The sun gear S1 of the first planetary gear mechanism PG1 is connected to the first planetary gear mechanism PG1 via the case 9 and the second brake B2 via a side opposite to the second planetary gear mechanism PG2, and is connected to the second planetary gear mechanism PG1. The mechanism CA is connected to the first planetary gear mechanism PG1 side of the carrier CA2 of the mechanism PG2 via the second clutch C2. Therefore, the connecting portion connecting the sun gear S1 of the first planetary gear mechanism PG1 to the case 9 and the carrier CA2 of the second planetary gear mechanism PG2 is on the opposite side of the first planetary gear mechanism PG1 from the second planetary gear mechanism PG2. , A radially extending portion 102 extending in the radial direction, and an inner peripherally extending axially extending from the side opposite to the second planetary gear mechanism PG2 to the second planetary gear mechanism PG2 with respect to the inner peripheral side of the sun gear S1. There may be a portion 124 and a radially extending portion 105 extending radially between the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2.

  The opposite side of the carrier CA1 of the first planetary gear mechanism PG1 from the second planetary gear mechanism PG2 is connected to the case 9 via the first brake B1, and the first planetary gear mechanism PG1, the second planetary gear mechanism PG2, and the third The ring gear of the planetary gear mechanism PG3 is connected to the ring gear R4 of the fourth planetary gear mechanism PG4 via the outer peripheral side of the ring gear and the third clutch C3. Therefore, the connecting portion connecting the carrier CA1 of the first planetary gear mechanism PG1 to the case 9 and the ring gear R4 of the fourth planetary gear mechanism PG4 is on the opposite side of the first planetary gear mechanism PG1 from the second planetary gear mechanism PG2. , A radially extending portion 103 extending in the radial direction, and an outer peripherally extending portion 121 axially extending from the side opposite to the second planetary gear mechanism PG2 to the outer peripheral side of the ring gear R4 with respect to the outer peripheral side of the ring gear R1. And

  The second planetary gear mechanism PG2 side of the carrier CA1 of the first planetary gear mechanism PG1 is connected to the ring gear R2 of the second planetary gear mechanism PG2 via the fourth clutch C4. Therefore, the connecting portion connecting the carrier CA1 of the first planetary gear mechanism PG1 and the ring gear R2 of the second planetary gear mechanism PG2 extends in the radial direction between the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2. Radially extending portion 104 and an outer peripheral extending portion 123 extending axially from the first planetary gear mechanism PG1 side to the outer peripheral side of the ring gear R2 with respect to the outer peripheral side of the ring gear R2.

  The ring gear R1 of the first planetary gear mechanism PG1 is connected to the ring gear R3 of the third planetary gear mechanism PG3 via the outer peripheral side of the ring gear R2 of the second planetary gear mechanism PG2. Therefore, the connecting portion connecting the ring gear R1 of the first planetary gear mechanism PG1 to the ring gear R3 of the third planetary gear mechanism PG3 extends in the axial direction from the outer peripheral side of the ring gear R1 to the outer peripheral side of the ring gear R3. It may have a part 122.

  The sun gear S2 of the second planetary gear mechanism PG2 is connected to the 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. 9 is connected. Therefore, the connecting portion connecting the sun gear S2 of the second planetary gear mechanism PG2 and the case 9 is arranged in the axial direction from the inner peripheral side of the sun gear S2 to the inner peripheral side of the sun gear S1 in a direction opposite to the second planetary gear mechanism PG2. And a radially extending portion 101 that extends in the radial direction on the opposite side of the first planetary gear mechanism PG1 from the second planetary gear mechanism PG2.

  The third planetary gear mechanism PG3 side of the carrier CA2 of the second planetary gear mechanism PG2 is connected to the sun gear S3 of the third planetary gear mechanism PG3. Therefore, the connecting portion connecting the carrier CA2 of the second planetary gear mechanism PG2 and the sun gear S3 of the third planetary gear mechanism PG3 extends in the radial direction between the second planetary gear mechanism PG2 and the third planetary gear mechanism PG3. Radially extending portion 106 and an inner peripheral extending portion 125 axially extending from the second planetary gear mechanism PG2 side to the inner peripheral side of the sun gear S3 with respect to the inner peripheral side of the sun gear S3.

  The fourth planetary gear mechanism PG4 side of the carrier CA3 of the third planetary gear mechanism PG3 is connected to the third planetary gear mechanism PG3 side of the carrier CA4 of the fourth planetary gear mechanism PG4.

  The other side of the carrier CA4 of the fourth planetary gear mechanism PG4 from the third planetary gear mechanism PG3 is connected to the output shaft A2. Therefore, the connecting portion connecting the carrier CA4 of the fourth planetary gear mechanism PG4 and the output shaft A2 is provided in the radial direction extending radially on the side opposite to the third planetary gear mechanism PG3 with respect to the fourth planetary gear mechanism PG4. It may have an extension 107.

  In this way, in the transmission 1, seven radially extending portions extending in the radial direction can be provided at positions different from the four planetary gear mechanisms along the axial direction.

  In the transmission 1, the outer peripheral extension portion 122 may be provided so as to cover the outer peripheral portion of the outer peripheral extension portion 123. Further, the outer peripheral extension portion 121 may be provided so as to cover the outer peripheral portion of the outer peripheral extension portion 122. Therefore, a triple structure can be formed by the outer peripheral extension portion 123, the outer peripheral extension portion 122, and the outer peripheral extension portion 121.

  Further, in the transmission 1, the inner peripheral extending portion 126 may be provided so as to cover the outer peripheral portion of the input shaft A1. Further, the inner peripheral extending portion 124 can be provided so as to cover the outer peripheral portion of the inner peripheral extending portion 126. Therefore, a triple structure can be formed by the input shaft A1, the inner peripheral extension 126, and the inner peripheral extension 124.

  Further, in the transmission 1, the inner peripheral extending portion 125 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 extension 125.

  Here, an oil passage may be formed in the input shaft A1. The hydraulic pressure for driving the first clutch C1 can be supplied from an oil passage formed in the input shaft A1.

  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 can be supplied through an oil passage formed in the case 9. The hydraulic pressure for driving the second clutch C2 is transmitted from the oil passage formed in the case 9 through the radially extending portion 101, the inner peripherally extending portion 126, the inner peripherally extending portion 124, and the radially extending portion 105. Can be supplied. Further, the hydraulic pressure for driving the third clutch C3 can be supplied from an oil passage formed in the case 9 via the outer peripheral extending portion 121. The hydraulic pressure for driving the fourth clutch C4 is supplied from the oil passage formed in the case 9 via the radially extending portion 101, the inner peripherally extending portion 126, the inner peripherally extending portion 124, and the outer peripherally extending portion 123. Can be supplied.

  Further, the transmission 1 is provided with, for example, a sensor capable of detecting the number of revolutions of the input shaft A1, and the detection result of the sensor can be used for controlling the shift speed of the transmission 1. The sensor can be installed, for example, closer to the drive source than the radially extending portion 101.

[1-2. Transmission operation]
Subsequently, an operation of the transmission 1 according to the present embodiment will be described with reference to FIGS. FIG. 3 is an explanatory diagram showing a fastening state of each coupling mechanism at each shift speed in the transmission 1 according to the present embodiment. FIG. 4 is an explanatory diagram illustrating an example of a gear ratio at each shift speed in the transmission 1 according to the present embodiment. The gear ratio in the transmission 1 shown in FIG. 4 is a ratio of the rotation speed of the input shaft A1 to the rotation speed of the output shaft A2 at each shift speed. FIG. 5 is an explanatory diagram illustrating an example of the step ratio between the respective shift speeds in the transmission 1 according to the present embodiment. The step ratio in the transmission 1 shown in FIG. 5 is the ratio of the gear ratio for the low gear side gear ratio to the gear ratio for the high gear side gear stage in adjacent gear positions. The gear ratio and the step ratio in the transmission 1 shown in FIGS. 4 and 5 are, as described above, the first planetary gear mechanism PG1, the second planetary gear mechanism PG2, the third planetary gear mechanism PG3, and the fourth planetary gear. These values are obtained when the gear ratios of the gear mechanism PG4 are 0.56, 0.32, 0.26, and 0.53, respectively.

  In the transmission 1, the gears are switched by switching the engagement state of each coupling mechanism. Thereby, the gear ratio of the transmission 1 is switched to a gear ratio corresponding to the gear position. The fastening state of each coupling mechanism is controlled by, for example, a control device mounted on the vehicle according to the running state of the vehicle.

  The first forward speed (1st) is realized by engaging the first brake B1, the second brake B2, and the first clutch C1. The gear ratio for the first forward speed (1st) is 4.78.

  The second forward speed (2nd) is realized by engaging the first brake B1, the second brake B2, and the third clutch C3. The gear ratio for the second forward speed (2nd) is 2.90. The step ratio between the first forward speed (1st) and the second forward speed (2nd) is 1.65.

  The third forward speed (3rd) is realized by engaging the second brake B2, the first clutch C1, and the third clutch C3. The gear ratio for the third forward speed (3rd) is 2.00. The step ratio between the second forward speed (2nd) and the third forward speed (3rd) is 1.45.

  The fourth forward speed (4th) is realized by engaging the second brake B2, the third clutch C3, and the fourth clutch C4. The gear ratio for the fourth forward speed (4th) is 1.53. The step ratio between the third forward speed (3rd) and the fourth forward speed (4th) is 1.31.

  The fifth forward speed (5th) is realized by engaging the second brake B2, the second clutch C2, and the third clutch C3. The gear ratio for the fifth forward speed (5th) is 1.36. The step ratio between the fourth forward speed (4th) and the fifth forward speed (5th) is 1.13.

  The sixth forward speed (6th) is realized by engaging the second clutch C2, the third clutch C3, and the fourth clutch C4. The gear ratio for the sixth forward speed (6th) is 1.10. The step ratio between the fifth forward speed (5th) and the sixth forward speed (6th) is 1.23.

  The seventh forward speed (7th) is realized by engaging the first clutch C1, the second clutch C2, and the third clutch C3. The gear ratio for the seventh forward speed (7th) is 1.00. The step ratio between the sixth forward speed (6th) and the seventh forward speed (7th) is 1.10.

  The eighth forward speed (8th) is realized by engaging the first clutch C1, the third clutch C3, and the fourth clutch C4. The gear ratio for the eighth forward speed (8th) is 0.83. The step ratio between the seventh forward speed (7th) and the eighth forward speed (8th) is 1.21.

  The ninth forward speed (9th) is realized by engaging the first clutch C1, the second clutch C2, and the fourth clutch C4. The gear ratio for the ninth forward speed (9th) is 0.72. The step ratio between the eighth forward speed (8th) and the ninth forward speed (9th) is 1.15.

  The tenth forward speed (10th) is realized by engaging the second brake B2, the first clutch C1, and the fourth clutch C4. The gear ratio for the tenth forward speed (10th) is 0.55. The step ratio between the ninth forward speed (9th) and the tenth forward speed (10th) is 1.32.

  The reverse gear (Rev) is realized by engaging the first brake B1, the first clutch C1, and the second clutch C2. The gear ratio for the reverse gear (Rev) is -4.35.

  As described above, the transmission 1 can realize 10 forward speeds and 1 reverse speed. Further, in the transmission 1, two of the three coupling mechanisms that are fastened between the adjacent shift speeds are common. Thus, by switching one of the three coupling mechanisms to be engaged, the gear can be switched to an adjacent gear. Therefore, the gears can be smoothly switched.

  Further, the transmission 1 is engaged between the first forward speed (1st) and the tenth forward speed (10th) between two speeds (for example, between 1st and 3rd). Two of the three connecting mechanisms are common. Thus, by switching one of the three coupling mechanisms to be engaged, the gear can be switched to a gear having a two-step difference. Therefore, the shift speed can be smoothly switched between the shift speeds having two steps.

  Further, at each shift speed of the transmission 1, three of the six coupling mechanisms are engaged, and the other three coupling mechanisms are released. Therefore, it is possible to suppress an increase in friction loss that occurs in the coupling mechanism at each shift speed, for example, as compared with a transmission in which four or more coupling mechanisms of the six coupling mechanisms are opened.

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

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

  Thus, by providing four planetary gear mechanisms and six connecting mechanisms, it is possible to realize ten forward steps and one reverse step. Therefore, as compared with a transmission having four planetary gear mechanisms and six coupling mechanisms and capable of realizing eight forward gears and one reverse gear, for example, the number of gears can be reduced without increasing the number of planetary gear mechanisms and coupling mechanisms. Can be increased. Therefore, it is possible to further increase the number of shift speeds while suppressing an increase in the size of the transmission. Thereby, improvement in fuel efficiency and improvement in drivability can be realized.

  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 is inserted into the sun gear S1, which is the sun gear of the first planetary gear mechanism PG1, the second planetary gear mechanism PG2, and the third planetary gear mechanism PG3, and the inner side of the sun gear S2 and the sun gear S3. . 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. The sun gear S1 of the first planetary gear mechanism PG1 is connected to the first planetary gear mechanism PG1 via the case 9 and the second brake B2 via a side opposite to the second planetary gear mechanism PG2. The carrier CA2 of the planetary gear mechanism PG2 is connected to the first planetary gear mechanism PG1 side via a second clutch C2. Further, the side of the first planetary gear mechanism PG1 opposite to the second planetary gear mechanism PG2 of the carrier CA1 is connected to the case 9 via the first brake B1, and the first planetary gear mechanism PG1, the second planetary gear mechanism PG2, The third planetary gear mechanism PG3 is connected to the ring gear R4 of the fourth planetary gear mechanism PG4 via an outer peripheral side of the ring gear via the third clutch C3. The carrier CA1 of the first planetary gear mechanism PG1 has the second planetary gear mechanism PG2 side connected to the ring gear R2 of the second planetary gear mechanism PG2 via a fourth clutch C4. The ring gear R1 of the first planetary gear mechanism PG1 is connected to the ring gear R3 of the third planetary gear mechanism PG3 via the outer peripheral side of the ring gear R2 of the second planetary gear mechanism PG2. 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. Connected to the case 9. Further, the third planetary gear mechanism PG3 side of the carrier CA2 of the second planetary gear mechanism PG2 is connected to the sun gear S3 of the third planetary gear mechanism PG3. Further, the side of the fourth planetary gear mechanism PG4 of the carrier CA3 of the third planetary gear mechanism PG3 is connected to the side of the third planetary gear mechanism PG3 of the carrier CA4 of the fourth planetary gear mechanism PG4. Further, the side of the carrier CA4 of the fourth planetary gear mechanism PG4 opposite to the third planetary gear mechanism PG3 is connected to the output shaft A2.

  Thereby, the number of radially extending portions provided at positions different from the four planetary gear mechanisms along the axial direction and extending in the radial direction is different from that of the transmission 1 in the positional relationship between the four planetary gear mechanisms. As compared with the case, the number can be relatively small (specifically, seven). Therefore, the transmission 1 can be downsized in the axial direction.

  Furthermore, the number of layers in the multiple structure formed by the inner peripheral extension can be at most three. Therefore, the number of layers in the multiplex structure formed by the inner circumferential extension can be relatively reduced as compared with the case where the positional relationship between the four planetary gear mechanisms is different from that of the transmission 1. The multiple structure formed by the inner peripheral extension is realized by providing a bearing that rotatably supports each member forming the multiple structure. Therefore, by reducing the number of layers in such a multi-layer structure, the number of bearings provided can be reduced, so that an increase in friction loss occurring in the bearings can be suppressed.

  Further, the number of inner peripheral extending portions interposed between the connecting mechanism to which the hydraulic pressure is supplied from the shaft on which the oil passage is formed and the shaft can be made at most two. Therefore, as compared with the case where the positional relationship between the four planetary gear mechanisms is different from that of the transmission 1, the inner circumferential extension interposed between the connection mechanism to which the hydraulic pressure is supplied from the shaft on which the oil passage is formed and the shaft is provided. The number of existing parts can be relatively reduced. Therefore, it is possible to suppress an increase in energy loss in supplying hydraulic pressure.

  Further, the number of layers in the multiplex structure formed by the outer peripheral extension portion can be at most three. Therefore, the number of layers in the multiplex structure formed by the outer peripheral extension can be relatively reduced as compared with the case where the positional relationship between the four planetary gear mechanisms is different from that of the transmission 1. Therefore, the transmission 1 can be downsized in the radial direction.

  In the transmission 1, the first brake B1 may be a dog brake. Thus, it is possible to suppress an increase in friction loss that occurs in the first brake B1 when the first brake B1 is released.

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

[2-1. Configuration of transmission]
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 illustrating 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 of the transmission 1 described above. Accordingly, the transmission 2 has a different connection path between the rotation 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 and other elements of the planetary gear mechanism connected to each other is the same as that of the transmission 1 described above. In the transmission 2, the combination of the rotation element of the planetary gear mechanism and the other elements to be switched for the connection state of each connection mechanism is the same as that of the transmission 1 described above. In the transmission 2, the engagement state of each coupling mechanism at each shift speed is the same as that of the above-described transmission 1. In the transmission 2, when the gear ratio of each planetary gear mechanism is the same as that of the above-described transmission 1, the gear ratio for each shift speed and the step ratio between each shift speed are the same as those of the above-described transmission 1. The same is true. Further, in the transmission 2, the first brake B1 may be a dog brake, similarly to the transmission 1 described above.

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

  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 inserted through an inner peripheral side of the sun gear S3 of the third planetary gear mechanism PG3. Note that the input shaft A1 can be disposed concentrically with each planetary gear mechanism, similarly to the transmission 1 described above. Further, power is input to the input shaft A1 from the opposite side of the third planetary gear mechanism PG3 from the fourth planetary gear mechanism PG4.

  The output shaft A2 is inserted through sun gears S1 and S2, which are sun gears of the first and second planetary gear mechanisms PG1 and PG2. Note that the output shaft A2 can 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 second planetary gear mechanism PG2 in a direction opposite to the first planetary gear mechanism PG1.

  The sun gear S3 of the third planetary gear mechanism PG3 has a side opposite to the fourth planetary gear mechanism PG4 with respect to the third planetary gear mechanism PG3, the third planetary gear mechanism PG3, the fourth planetary gear mechanism PG4, and the first planetary gear mechanism. The carrier CA2 of the second planetary gear mechanism PG2 is connected to the opposite side of the first planetary gear mechanism PG1 via the PG1 and the outer peripheral side of the ring gear of the second planetary gear mechanism PG2. Therefore, the connecting portion connecting the sun gear S3 of the third planetary gear mechanism PG3 and the carrier CA2 of the second planetary gear mechanism PG2 extends axially from the inner peripheral side of the sun gear S3 to the side opposite to the fourth planetary gear mechanism PG4. The inner peripheral extending portion 225, the radial extending portion 201 extending radially on the side opposite to the fourth planetary gear mechanism PG4 with respect to the third planetary gear mechanism PG3, and the outer peripheral side of the ring gear R3. With respect to an outer peripheral extension 221 axially extending from the side opposite to the fourth planetary gear mechanism PG4 to the outer side of the ring gear R2 in a direction opposite to the first planetary gear mechanism PG1, and to the second planetary gear mechanism PG2. It may have a radially extending portion 206 that extends in the radial direction on the side opposite to the first planetary gear mechanism PG1.

  The fourth planetary gear mechanism PG4 side of the carrier CA3 of the third planetary gear mechanism PG3 is connected to the third planetary gear mechanism PG3 side of the carrier CA4 of the fourth planetary gear mechanism PG4.

  The ring gear R3 of the third planetary gear mechanism PG3 is connected to the ring gear R1 of the first planetary gear mechanism PG1 via the outer peripheral side of the ring gear R4 of the fourth planetary gear mechanism PG4. Therefore, the connecting portion that connects the ring gear R3 of the third planetary gear mechanism PG3 and the ring gear R1 of the first planetary gear mechanism PG1 extends in the axial direction from the outer peripheral side of the ring gear R3 to the outer peripheral side of the ring gear R1. It may have a part 222.

  The first planetary gear mechanism PG1 side of the carrier CA4 of the fourth planetary gear mechanism PG4 is connected to the output shaft A2. Therefore, the connecting part connecting the carrier CA4 of the fourth planetary gear mechanism PG4 and the output shaft A2 is a radially extending part extending in the radial direction between the fourth planetary gear mechanism PG4 and the first planetary gear mechanism PG1. 202.

  The sun gear S1 of the first planetary gear mechanism PG1 is connected to the first planetary gear mechanism PG1 side of the carrier CA2 of the second planetary gear mechanism PG2 via the second clutch C2. Therefore, the connecting portion connecting the sun gear S1 of the first planetary gear mechanism PG1 and the carrier CA2 of the second planetary gear mechanism PG2 extends in the axial direction from the inner peripheral side of the sun gear S1 to the second planetary gear mechanism PG2. It may have an inner peripheral extension 226 and a radial extension 205 extending radially between the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2. Note that the inner peripheral extension 226 can be connected to the sun gear S2 of the second planetary gear mechanism PG2 via the second brake B2.

  The fourth planetary gear mechanism PG4 side of the carrier CA1 of the first planetary gear mechanism PG1 is connected to the ring gear R4 of the fourth planetary gear mechanism PG4 via the third clutch C3, and the sun gear S1 of the first planetary gear mechanism PG1. It is connected to the sun gear S2 of the second planetary gear mechanism PG2 via the peripheral side via the first brake B1. Therefore, the connecting portion connecting the carrier CA1 of the first planetary gear mechanism PG1 to the ring gear R4 of the fourth planetary gear mechanism PG4 and the sun gear S2 of the second planetary gear mechanism PG2 is formed from the outer peripheral side of the ring gear R4 to the first planetary gear mechanism. An outer peripheral extension 223 extending in the axial direction toward PG1, a radial extension 203 extending in the radial direction between the first planetary gear mechanism PG1 and the fourth planetary gear mechanism PG4, and a sun gear S1. An inner peripheral extending portion 227 extending in the axial direction from the fourth planetary gear mechanism PG4 side to the inner peripheral side of the sun gear S2 with respect to the peripheral side may be provided.

  The second planetary gear mechanism PG2 side of the carrier CA1 of the first planetary gear mechanism PG1 is connected to the ring gear R2 of the second planetary gear mechanism PG2 via the fourth clutch C4. Therefore, the connecting portion connecting the carrier CA1 of the first planetary gear mechanism PG1 and the ring gear R2 of the second planetary gear mechanism PG2 extends in the radial direction between the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2. Radially extending portion 204 and an outer peripheral extending portion 224 that extends axially from the first planetary gear mechanism PG1 side to the outer peripheral side of the ring gear R2 with respect to the outer peripheral side of the ring gear R2.

  The sun gear S2 of the second planetary gear mechanism PG2 is connected to the case 9 via a side opposite to the first planetary gear mechanism PG1 with respect to the second planetary gear mechanism PG2. Therefore, the connecting portion connecting the sun gear S2 of the second planetary gear mechanism PG2 and the case 9 is formed in a radial direction extending in the radial direction on the side opposite to the first planetary gear mechanism PG1 with respect to the second planetary gear mechanism PG2. There may be a portion 207. Note that the radially extending portion 207 can be connected to the inner peripheral extending portion 227.

  As described above, in the transmission 2, seven radially 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 2, the outer peripheral extension portion 222 may be provided so as to cover the outer peripheral portion of the outer peripheral extension portion 223. Further, the outer peripheral extension portion 221 may be provided so as to cover the outer peripheral portion of the outer peripheral extension portion 222. Therefore, a triple structure can be formed by the outer peripheral extension portion 223, the outer peripheral extension portion 222, and the outer peripheral extension portion 221.

  Further, in the transmission 2, the outer peripheral extension portion 221 may be provided so as to cover the outer peripheral portion of the outer peripheral extension portion 224. Therefore, a double structure can be formed by the outer peripheral extension portion 224 and the outer peripheral extension portion 221.

  Further, in the transmission 2, the inner peripheral extending portion 225 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 extension 225.

  Further, in the transmission 2, the inner peripheral extending portion 227 may be provided so as to cover the outer peripheral portion of the output shaft A2. Further, the inner peripheral extending portion 226 may be provided so as to cover the outer peripheral portion of the inner peripheral extending portion 227. Therefore, a triple structure can be formed by the output shaft A2, the inner peripheral extension 227, and the inner peripheral extension 226.

  Here, an oil passage may be formed in the input shaft A1. The hydraulic pressure for driving the first clutch C1 can be supplied from an oil passage formed in the input shaft A1.

  Further, an oil passage may be formed in the case 9. Oil pressure for driving the first brake B1 and the second brake B2 can be supplied from an oil passage formed in the case 9 via the radially extending portion 207 and the inner peripherally extending portion 227. The hydraulic pressure for driving the second clutch C2 is transmitted from the oil passage formed in the case 9 via the radially extending portion 207, the inner peripherally extending portion 227, the inner peripherally extending portion 226, and the radially extending portion 205. Can be supplied. Further, hydraulic pressure for driving the third clutch C3 can be supplied from an oil passage formed in the case 9 via the output shaft A2 and the radially extending portion 203. The hydraulic pressure for driving the fourth clutch C4 is supplied from an oil passage formed in the case 9 via the radially extending portion 207, the inner peripherally extending portion 227, the inner peripherally extending portion 226, and the outer peripherally extending portion 224. Can be supplied.

  Further, the transmission 2 is provided with, for example, a sensor capable of detecting the number of revolutions of the input shaft A1, and the detection result of the sensor can be used for controlling the shift speed of the transmission 2. The sensor can be installed, for example, closer to the drive source than the radially extending portion 201.

[2-2. Effect of transmission]
Subsequently, effects 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 and other elements connected to each other, and the combination of the rotating element of the planetary gear mechanism and the other element to be switched in the connection state of each connecting mechanism are as follows. And the transmission 1. Therefore, similarly to the transmission 1, the transmission 2 includes four planetary gear mechanisms and six coupling mechanisms, thereby realizing ten forward speeds and one reverse speed.

  In the transmission 2, in the case 9, the four planetary gear mechanisms are concentrically arranged in the order of the third planetary gear mechanism PG3, the fourth planetary gear mechanism PG4, the first planetary gear mechanism PG1, and the second planetary gear mechanism PG2. Be placed. Specifically, the input shaft A1 is inserted through the inner peripheral side of the sun gear S3 of the third planetary gear mechanism PG3. The output shaft A2 is inserted through the sun gears S1 and S2 as sun gears of the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2. Further, the sun gear S3 of the third planetary gear mechanism PG3 is opposite to the fourth planetary gear mechanism PG4 with respect to the third planetary gear mechanism PG3, the third planetary gear mechanism PG3, the fourth planetary gear mechanism PG4, and the first planetary gear. The carrier CA2 of the second planetary gear mechanism PG2 is connected to the side opposite to the first planetary gear mechanism PG1 via the gear mechanism PG1 and the outer peripheral side of the ring gear of the second planetary gear mechanism PG2. Further, the side of the fourth planetary gear mechanism PG4 of the carrier CA3 of the third planetary gear mechanism PG3 is connected to the side of the third planetary gear mechanism PG3 of the carrier CA4 of the fourth planetary gear mechanism PG4. The ring gear R3 of the third planetary gear mechanism PG3 is connected to the ring gear R1 of the first planetary gear mechanism PG1 via the outer peripheral side of the ring gear R4 of the fourth planetary gear mechanism PG4. The carrier CA4 of the fourth planetary gear mechanism PG4 has the first planetary gear mechanism PG1 side connected to the output shaft A2. The sun gear S1 of the first planetary gear mechanism PG1 is connected to the first planetary gear mechanism PG1 side of the carrier CA2 of the second planetary gear mechanism PG2 via the second clutch C2. The fourth planetary gear mechanism PG4 side of the carrier CA1 of the first planetary gear mechanism PG1 is connected to the ring gear R4 of the fourth planetary gear mechanism PG4 via the third clutch C3, and the sun gear S1 of the first planetary gear mechanism PG1 is connected. Is connected to the sun gear S2 of the second planetary gear mechanism PG2 via the first brake B1. The carrier CA1 of the first planetary gear mechanism PG1 has the second planetary gear mechanism PG2 side connected to the ring gear R2 of the second planetary gear mechanism PG2 via a fourth clutch C4. The sun gear S2 of the second planetary gear mechanism PG2 is connected to the case 9 via the side opposite to the first planetary gear mechanism PG1 with respect to the second planetary gear mechanism PG2.

  Thereby, the number of radially extending portions provided at positions different from the four planetary gear mechanisms in the axial direction and extending in the radial direction is different from that of the transmission 2 in the positional relationship between the four planetary gear mechanisms. As compared with the case, the number can be relatively small (specifically, seven). Therefore, the transmission 2 can be downsized in the axial direction.

  Furthermore, the number of layers in the multiple structure formed by the inner peripheral extension can be at most three. Therefore, the number of layers in the multiplex structure formed by the inner circumferential extension can be relatively reduced as compared with the case where the positional relationship of the four planetary gear mechanisms is different from that of the transmission 2. The multiple structure formed by the inner peripheral extension is realized by providing a bearing that rotatably supports each member forming the multiple structure. Therefore, by reducing the number of layers in such a multi-layer structure, the number of bearings provided can be reduced, so that an increase in friction loss occurring in the bearings can be suppressed.

  Further, the number of inner peripheral extending portions interposed between the connecting mechanism to which the hydraulic pressure is supplied from the shaft on which the oil passage is formed and the shaft can be made at most two. Therefore, compared to the case where the positional relationship of the four planetary gear mechanisms is different from that of the transmission 2, the inner circumferential extension interposed between the coupling mechanism to which the hydraulic pressure is supplied from the shaft on which the oil passage is formed and the shaft is provided. The number of existing parts can be relatively reduced. Therefore, it is possible to suppress an increase in energy loss in supplying hydraulic pressure.

  Further, the number of layers in the multiplex structure formed by the outer peripheral extension portion can be at most three. Therefore, the number of layers in the multiplex structure formed by the outer peripheral extension portion can be relatively reduced as compared with the case where the positional relationship between the four planetary gear mechanisms is different from that of the transmission 2. Therefore, the transmission 2 can be downsized in the radial direction.

<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 predetermined other elements. In addition, the six connection mechanisms can switch a connection state between a rotation element of a predetermined planetary gear mechanism and another predetermined element. Thus, by providing four planetary gear mechanisms and six connecting mechanisms, it is possible to realize ten forward steps and one reverse step. Therefore, as compared with a transmission having four planetary gear mechanisms and six coupling mechanisms and capable of realizing eight forward gears and one reverse gear, for example, the number of gears can be reduced without increasing the number of planetary gear mechanisms and coupling mechanisms. Can be increased. Therefore, it is possible to further increase the number of shift speeds while suppressing an increase in the size of the transmission. Thereby, improvement in fuel efficiency and improvement in drivability can be realized.

  Although the example in which the transmission according to the embodiment of the present invention is mounted on a vehicle has been mainly described above, the device in 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 the device has a power transmission system.

  Further, in the above description, the example in which the wet multi-plate brake and the wet multi-plate clutch are used as the brakes and the clutches has been mainly described, but the types of the brakes and the clutches are not limited to the examples. Each brake and each clutch need only be able to switch the connection state between the elements.

  In the above description, 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 0.56, 0.32, 0.26, and 0, respectively. .53, but the gear ratio of each planetary gear mechanism is not limited to this 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. It should be noted that the gear ratio at each speed stage 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, with reference to each drawing, each component (for example, a connecting portion that connects a rotating element of a planetary gear mechanism and another element) in the transmission according to the embodiment of the present invention has been described. The shapes of the components and the positional relationship between the components are not limited to the examples corresponding to the drawings, and the shapes and the positional relationships shown in the drawings are merely examples. Further, each component may be formed integrally, or may be formed by a plurality of members.

  As described above, the preferred embodiments of the present invention have been described in detail with reference to the accompanying drawings, but the present invention is not limited to such examples. It is obvious that those skilled in the art to which the present invention pertains can conceive various modifications or applications within the scope of the technical idea described in the claims. It is understood that these also belong to the technical scope of the present invention.

1, transmission 9 case A1 input shaft A2 output shaft B1 first brake B2 second brake C1 first clutch C2 second clutch C3 third clutch C4 fourth clutch CA1 carrier CA2 carrier CA3 carrier CA4 carrier P1 pinion gear P2 pinion gear P3 Pinion gear P4 Pinion gear PG1 First planetary gear mechanism PG2 Second planetary gear mechanism PG3 Third planetary gear mechanism PG4 Fourth 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)

A first planetary gear mechanism, a second planetary gear mechanism, a third planetary gear mechanism, and a fourth planetary gear mechanism, which are planetary gear mechanisms provided in a case and having a sun gear, a carrier, and a ring gear as rotating elements;
A first connection mechanism, a second connection mechanism, a third connection mechanism, a fourth connection mechanism, a fifth connection mechanism, and a first connection mechanism that are switchable connection states of the rotation element and other elements of the planetary gear mechanism. 6 coupling mechanisms;
A transmission comprising:
A ring gear of the first planetary gear mechanism is connected to a ring gear of the third planetary gear mechanism;
A sun gear of the second planetary gear mechanism is connected to the case,
The carrier of the second planetary gear mechanism is connected to a sun gear of the third planetary gear mechanism,
The carrier of the third planetary gear mechanism is connected to the carrier of the fourth planetary gear mechanism,
A sun gear of the fourth planetary gear mechanism is connected to an input shaft to which power is input;
The carrier of the fourth planetary gear mechanism is connected to an output shaft that outputs transmitted power,
The first connection mechanism is capable of switching a connection state between the carrier of the first planetary gear mechanism and the case,
The second connection mechanism can switch a connection state between a sun gear of the first planetary gear mechanism and the case,
The third connection mechanism can switch a connection state between a carrier of the second planetary gear mechanism, a sun gear of the third planetary gear mechanism, a sun gear of the fourth planetary gear mechanism, and the input shaft,
The fourth connection mechanism can switch a connection state between a sun gear of the first planetary gear mechanism, a carrier of the second planetary gear mechanism, and a sun gear of the third planetary gear mechanism,
The fifth connection mechanism is capable of switching a connection state between a carrier of the first planetary gear mechanism and a ring gear of the fourth planetary gear mechanism,
The sixth connection mechanism is capable of switching a connection state between a carrier of the first planetary gear mechanism and a ring 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 through an inner peripheral side of a sun gear of the first planetary gear mechanism, the second planetary gear mechanism, and the third planetary gear mechanism,
The output shaft is disposed on a side opposite to the third planetary gear mechanism with respect to the fourth planetary gear mechanism,
A sun gear of the first planetary gear mechanism is connected to the case via the second coupling mechanism via a side opposite to the second planetary gear mechanism with respect to the first planetary gear mechanism, and the second planetary gear mechanism. The carrier of the gear mechanism is connected to the first planetary gear mechanism side via the fourth connection mechanism,
The opposite side of the carrier of the first planetary gear mechanism from the second planetary gear mechanism is connected to the case via the first connection mechanism, and the first planetary gear mechanism, the second planetary gear mechanism, and the second The ring gear of the third planetary gear mechanism is connected to the ring gear of the fourth planetary gear mechanism via the outer peripheral side of the ring gear of the third planetary gear mechanism, and
The second planetary gear mechanism side of the carrier of the first planetary gear mechanism is connected to the ring gear of the second planetary gear mechanism via the sixth connection mechanism,
The ring gear of the first planetary gear mechanism is connected to the ring gear of the third planetary gear mechanism via an outer peripheral side of the ring gear of the second planetary gear mechanism,
The sun gear of the second planetary gear mechanism is connected to the case via an inner peripheral side of the sun gear of the first planetary gear mechanism and a side opposite to the second planetary gear mechanism with respect to the first planetary gear mechanism. Connected
The third planetary gear mechanism side of the carrier of the second planetary gear mechanism is connected to a sun gear of the third planetary gear mechanism,
The fourth planetary gear mechanism side of the carrier of the third planetary gear mechanism is connected to the third planetary gear mechanism side of the carrier of the fourth planetary gear mechanism,
A side of the carrier of the fourth planetary gear mechanism opposite to the third planetary gear mechanism is connected to the output shaft.
The transmission according to claim 2. In the case, the four planetary gear mechanisms are concentrically arranged in the order of the third planetary gear mechanism, the fourth planetary gear mechanism, the first planetary gear mechanism, and the second planetary gear mechanism,
The transmission according to claim 1. The input shaft is inserted through an inner peripheral side of a sun gear of the third planetary gear mechanism,
The output shaft is inserted through an inner peripheral side of a sun gear of the first planetary gear mechanism and the second planetary gear mechanism,
The sun gear of the third planetary gear mechanism includes a side opposite to the fourth planetary gear mechanism with respect to the third planetary gear mechanism, and the third planetary gear mechanism, the fourth planetary gear mechanism, and the first planetary gear mechanism. And the other side of the carrier of the second planetary gear mechanism and the first planetary gear mechanism via the outer peripheral side of the ring gear of the second planetary gear mechanism,
The fourth planetary gear mechanism side of the carrier of the third planetary gear mechanism is connected to the third planetary gear mechanism side of the carrier of the fourth planetary gear mechanism,
The ring gear of the third planetary gear mechanism is connected to the ring gear of the first planetary gear mechanism via an outer peripheral side of the ring gear of the fourth planetary gear mechanism,
The first planetary gear mechanism side of the carrier of the fourth planetary gear mechanism is connected to the output shaft,
A sun gear of the first planetary gear mechanism is connected to the carrier of the second planetary gear mechanism on the first planetary gear mechanism side via the fourth connection mechanism;
The fourth planetary gear mechanism side of the carrier of the first planetary gear mechanism is connected to the ring gear of the fourth planetary gear mechanism via the fifth connection mechanism, and is an inner peripheral side of a sun gear of the first planetary gear mechanism. Is connected to the sun gear of the second planetary gear mechanism via the first coupling mechanism,
The second planetary gear mechanism side of the carrier of the first planetary gear mechanism is connected to the ring gear of the second planetary gear mechanism via the sixth connection mechanism,
A sun gear of the second planetary gear mechanism is connected to the case via a side opposite to the first planetary gear mechanism with respect to the second planetary gear mechanism.
The transmission according to claim 4. The first connection mechanism is a dog brake;
The transmission according to claim 1.

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