JP6164004B2 - Automatic transmission - Google Patents

Description

  The present invention relates to an automatic transmission that shifts rotation of an input shaft, which is driven to rotate by an engine of a vehicle, to a plurality of shift speeds and transmits it to an output shaft.

  2. Description of the Related Art Conventionally, there is an automatic transmission for a vehicle that can form a forward gear and a reverse gear. For example, in the technology disclosed in Patent Document 1 shown below, four single-pinion planetary gears and six engagement elements in which first to fourth planetary gears are sequentially arranged in parallel from the input shaft side to the output shaft side. By engaging these three elements, a forward speed of 10 stages and a reverse speed of 1 speed are formed.

US Pat. No. 8,052,567

  In the automatic transmission shown in Patent Document 1, the input shaft is connected to the carrier of the first planetary gear, and the output shaft is connected to the carrier of the third planetary gear through the outer peripheral side of the ring gear of the third planetary gear. It is connected to the planetary gear carrier. The sun gear of the first planetary gear is connected to the sun gear of the second planetary gear, the ring gear of the first planetary gear is connected to the sun gear of the third planetary gear, and the carrier of the second planetary gear passes through the outer peripheral side of the ring gear of the third planetary gear. It is connected with the ring gear. In order to form the fourth speed and the tenth speed, it is necessary to rotate the third planetary gear and the fourth planetary gear together with the first friction engagement element and the second friction engagement element engaged. .

  Since the first friction engagement element is disposed between the ring gear of the fourth planetary gear and the sun gear of the third planetary gear, the second friction engagement element must be disposed between the sun gear of the third planetary gear and the sun gear of the fourth planetary gear. It becomes the composition which cannot be obtained. Therefore, the second friction engagement element includes a shaft connecting the third planetary gear carrier and the fourth planetary gear carrier passing through the outer peripheral side of the ring gear of the third planetary gear, and the second planetary gear carrier and the fourth planetary gear ring gear. Since it becomes the structure which must be arrange | positioned inside the connected axis | shaft, radial direction space is restrict | limited. As a result, in this arrangement on the inner diameter side, it is necessary to increase the number of friction materials in order to ensure the transmission torque capacity, leading to an increase in the axial length.

  Further, in order to form the sixth speed, the seventh speed, and the eighth speed reverse, the third friction engagement element that needs to be engaged is also connected to the ring gear of the first planetary gear with the sun gear of the third planetary gear. Since the configuration is unavoidably arranged between the ring gear of the third planetary gear and the sun gear of the fourth planetary gear, the radial space is limited as described above.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide an automatic transmission in which a friction engagement element can be arranged on the outer diameter side.

  In order to solve the above-described problem, an automatic transmission according to a first aspect includes a housing, an input shaft that is rotatably supported by the housing around a rotation axis, and the input shaft side that is coaxial with the rotation axis of the housing. Single-pinion type first to fourth planetary gears, which are sequentially supported, an output shaft which is rotatably supported by the housing around a rotation axis, and which is connected to a fourth carrier of the fourth planetary gear; and An input shaft connecting member connected to the first carrier from the output shaft side and connected to the input shaft through the outer peripheral side of the first ring gear of the first planetary gear; and a first sun gear and a second planetary gear of the first planetary gear. A first connecting member for connecting the second sun gear, a second carrier of the second planetary gear, and a fourth ring of the fourth planetary gear; A second connecting member for connecting a gear through an outer peripheral side of a third ring gear of the third planetary gear; and a third sun gear of the third planetary gear connected to a third carrier of the third planetary gear from the input shaft side. A third connecting member connected from the input shaft side to the fourth carrier of the fourth planetary gear through the inner peripheral side of the third connecting member, and extending through the inner peripheral side of the third connecting member on the rotation axis, A first connection part connected to the fourth sun gear from the input shaft side; a second connection part connected to the first connection part and extending toward the outer diameter side of the housing; and the second connection part And a third connection portion connected to the third ring gear from the input shaft side, and a fourth connection portion connected to the first connection portion and extending on the rotation axis. A fourth connecting member, a first brake for releasably fixing the first connecting member to the inner peripheral surface of the housing, and a second ring gear engageable with the inner peripheral surface of the housing. A second brake that is fixed to the first shaft, a first clutch that releasably connects the input shaft connecting member and the fourth connecting member, a sixth connecting portion that is connected to the first ring gear from the input shaft side, and A seventh connection part that is connected to the sixth connection part and extends toward the rotation axis; and a connection to the seventh connection part and the first connection member and the fourth connection member in the rotation axis direction; An eighth connecting part extending between the ninth connecting part, a ninth connecting part connected to the eighth connecting part and extending toward the outer diameter side of the housing, and a connection to the ninth connecting part and the rotation axis In the direction A clutch connecting member having a tenth connecting portion extending between the third ring gear and the second connecting member, and provided on an outer peripheral side of the third ring gear, the third ring gear and the clutch connecting A second clutch for releasably connecting members; a third clutch provided on the outer peripheral side of the third ring gear for releasably connecting a third sun gear of the third planetary gear and the clutch connecting member; The gist of the invention is to include a second coupling member and a fourth clutch for detachably coupling the clutch coupling member.

  According to this, by eliminating the connection between the first ring gear of the first planetary gear and the third sun gear of the third planetary gear, the third planetary gear is connected from the input shaft side to the third carrier of the third planetary gear, and the third planetary gear third gear is connected. A third connecting member that connects from the input shaft side to the fourth carrier of the fourth planetary gear through the inner peripheral side of the sun gear can be provided. For this reason, it extends through the inner peripheral side of the third connecting member on the rotation axis, and is connected to the fourth sun gear from the input shaft side, and is connected to the first connecting portion and the outer diameter of the housing. A second connecting part extending toward the side, a third connecting part connected to the second connecting part and connected to the third ring gear from the input shaft side, and connected to the first connecting part and extended on the rotation axis And a fourth connecting member having a fourth connecting portion. As a result, a sixth connection portion connected to the first ring gear from the input shaft side, a seventh connection portion connected to the sixth connection portion and extending toward the rotation axis, and connected to the seventh connection portion and rotated. An eighth connecting portion extending between the first connecting member and the fourth connecting member in the axial direction; a ninth connecting portion connected to the eighth connecting portion and extending toward the outer diameter side of the housing; A clutch connecting member that is connected to the ninth connecting portion and has a tenth connecting portion that extends between the third ring gear and the second connecting member in the direction of the rotation axis is disposed on the outer peripheral side of the third ring gear. It can be configured. Moreover, the 2nd clutch provided in the outer peripheral side of a 3rd ring gear and connecting a 3rd ring gear and a clutch connection member so that engagement / disengagement is possible can be set as the structure arrange | positioned in an outer peripheral side rather than a 3rd ring gear. Therefore, by disposing the third connecting member on the inner diameter side, the second clutch, which is a friction engagement element, is provided on the outer peripheral side with respect to the third ring gear, and the third ring gear and the clutch connecting member are detachably connected. Can do. For this reason, the outer diameter side arrangement | positioning of a friction engagement element is attained.

  According to a second aspect of the present invention, in the automatic transmission for a vehicle according to the first aspect, a power external take-out member for taking out the power from the engine to the outside is provided on the outer peripheral surface on the outer peripheral side of the input shaft connecting member. The gist.

  According to this, the power external takeout member can always take out the power of the same rotation as the input rotation of the input shaft as the PTO from the input shaft connecting member connected to the input shaft regardless of the gear position.

1 is a skeleton diagram schematically showing a first embodiment of an automatic transmission for a vehicle of the present invention. It is a figure which shows the operating state of the brake and clutch in each gear stage of 1st Embodiment. It is a speed diagram which shows the rotation ratio of each element of the planetary gear in each gear position of 1st Embodiment.

  An automatic transmission according to the present invention will be described with reference to the drawings. In the drawings referred to below, the same or corresponding members are denoted by the same reference numerals.

  Referring to FIG. 1, reference numeral 10 denotes an automatic transmission according to the present invention for shifting the output rotation of an engine of a commercial vehicle such as an agricultural tractor, a dump truck, or a pump car such as a fire truck and transmitting it to a drive wheel. Used for. The automatic transmission 10 includes an input shaft 12, a first planetary gear 13, a second planetary gear 14, a third planetary gear 15, and a fourth gear 4 that are sequentially supported so as to be rotatable coaxially with the rotation axis 18 in a housing 11 attached to the vehicle body. It is composed of a planetary gear 16 and an output shaft 17.

  The first planetary gear 13 is a single pinion planetary gear mechanism. The first planetary gear 13 includes a first sun gear S1, a first ring gear R1, a first pinion P1 that meshes with the first sun gear S1 and the first ring gear R1, and a first pinion P1 that is rotatably supported coaxially with the rotation axis 18. It is comprised by the 1st carrier C1 which supports 1 pinion P1. The second planetary gear 14 is a single pinion planetary gear mechanism.

  The second planetary gear 14 includes a second sun gear S2, a second ring gear R2, a second pinion P2 that meshes with the second sun gear S2 and the second ring gear R2, and a second pinion P2 that is rotatably supported coaxially with the rotation axis 18. It is comprised by the 2nd carrier C2 which supports 2 pinion P2. The third planetary gear 15 is a single pinion planetary gear mechanism.

  The third planetary gear 15 includes a third sun gear S3, a third ring gear R3, a third pinion P3 that meshes with the third sun gear S3 and the third ring gear R3, and a third pinion P3 that is rotatably supported coaxially with the rotation axis 18. It is comprised by the 3rd carrier C3 which supports 3 pinion P3. The fourth planetary gear 16 is a single pinion planetary gear mechanism.

  The fourth planetary gear 16 includes a fourth sun gear S4, a fourth ring gear R4, a fourth pinion P4 that meshes with the fourth sun gear S4 and the fourth ring gear R4, and a fourth pinion P4 that is rotatably supported coaxially with the rotation axis 18. It is comprised by the 4th carrier C4 which supports 4 pinion P4.

  The input shaft 12 and the output shaft 17 are supported by the housing 11 so as to be rotatable around a rotation axis 18. The input shaft 12 is a shaft member that inputs engine output rotational power to the automatic transmission 10 via a clutch device (not shown) or the like. The output shaft 17 is a shaft member that outputs the shifted output rotational power to the drive wheels via a differential (not shown) or the like.

  The first carrier C 1 of the first planetary gear 13 is connected to the input shaft 12 via the input shaft connecting member 19. The input shaft connecting member 19 has one end connected to the input shaft 12 and the other end connected to the first carrier C1. The input shaft connecting member 19 includes a portion extending from the input shaft 12 toward the outer diameter side of the housing 11, a portion extending through the outer peripheral side of the first ring gear R <b> 1 in the direction of the rotation axis 18, and the rotation axis 18. And a portion connected to the first carrier C1 from the output shaft 17 side. The output shaft 17 is connected to the fourth carrier C4 of the fourth planetary gear 16.

  The first sun gear S1 of the first planetary gear 13 is connected to the second sun gear S2 of the second planetary gear 14 via the first connecting member 20. The first connecting member 20 has one end connected to the first sun gear S1 and the other end connected to the second sun gear S2. The first connecting member 20 extends from the first sun gear S1 to the second sun gear S2 along the direction of the rotation axis 18.

  The second carrier C 2 of the second planetary gear 14 is connected to the fourth ring gear R 4 of the fourth planetary gear 16 via the second connecting member 21. One end of the second connecting member 21 is connected to the second carrier C2 and the fourth clutch CL4, and the other end is connected to the fourth ring gear R4. One end of the second connecting member 21 is connected to the second carrier C2 and the fourth clutch CL4, and the other end is connected to the fourth ring gear R4. The second connecting member 21 includes a portion connected to the second carrier C2 from the output shaft 12 side, a portion extending toward the outer diameter side of the housing 11, and the outer peripheral side of the third ring gear R3 in the direction of the rotation axis 18. And a portion that extends through and is connected to the fourth ring gear R4 from the input shaft 12 side.

  The third carrier C3 of the third planetary gear 15 is connected to the fourth carrier C4 of the fourth planetary gear 16 via the third connecting member 22. The third connecting member 22 has one end connected to the third carrier C3 and the other end connected to the fourth carrier C4. The third connecting member 22 includes a portion extending from the third carrier C3 toward the input shaft 12, a portion extending toward the rotation axis 18, and the third sun gear S3 of the third planetary gear 15 in the direction of the rotation axis 18. A portion extending through the inner peripheral side, a portion extending toward the outer diameter side of the housing 11, and a portion connected to the fourth carrier C4 from the input shaft 12 side are provided.

  The third ring gear R3 of the third planetary gear 15 is connected to the fourth sun gear S4 of the fourth planetary gear 16 via the fourth connecting member 23. One end of the fourth connecting member 23 is connected to the first clutch CL1 and the third ring gear R3, and the other end is connected to the fourth sun gear S4. The fourth connecting member 23 extends on the rotation axis 18 through the inner peripheral side of the third connecting member 22, and has one end connected to the fourth sun gear S4 from the input shaft 12 side and one end. Is connected to the first connection part 23a, the other end is connected to the outer diameter side of the housing 11, the one end is connected to the second connection part 23b, and the other end is on the input shaft 12 side. To a third ring gear R3. The fourth connecting member 23 has one end connected to the first connecting part 23a and the other end connected to the fourth connecting part 23d extending on the rotation axis 18 through the inner peripheral side of the clutch connecting member 24, and one end Is connected to the fourth connection part 23d, and the other end is provided with a fifth connection part 23e connected to the first clutch CL1 from the inner diameter side of the housing 11.

  The first brake B <b> 1 is provided on the outer diameter side of the first ring gear R <b> 1 of the first planetary gear 13. The first brake B1 fixes the first connecting member 20 to the inner peripheral surface of the housing 11 so as to be disengageable. The second brake B2 is provided on the outer diameter side of the second ring gear R2 of the second planetary gear 14. The second brake B <b> 2 fixes the second ring gear R <b> 2 to the inner peripheral surface of the housing 11 so that it can be engaged and disengaged.

  The first clutch CL1 couples the fourth coupling member 23 and the input shaft coupling member 19 in a detachable manner. The clutch connecting member 24 includes a sixth connecting portion 24a that is connected to the first ring gear R1 from the input shaft 12 side, a seventh connecting portion that is connected to the sixth connecting portion 24a, and a second end that extends toward the rotation axis 18. The connection portion 24b, one end connected to the seventh connection portion 24b, and the other end connected to the eighth connection portion 24c extending between the first connection member 20 and the fourth connection member 23 in the direction of the rotation axis 18 and one end Is connected to the eighth connecting part 24c, the other end is connected to the ninth connecting part 24d, and the other end is in the direction of the rotational axis 18 direction. And a tenth connecting portion 24e extending between the third ring gear R3 and the second connecting member 21.

  The second clutch CL2 is provided on the outer peripheral side of the third ring gear R3. The second clutch CL2 releasably connects the third ring gear R3 and the clutch connecting member 24. The third clutch CL3 is provided on the outer peripheral side of the third ring gear R3. The third clutch CL3 couples the third sun gear S3 of the third planetary gear 15 and the clutch coupling member 24 in a detachable manner. The fourth clutch CL4 couples the second coupling member 21 and the clutch coupling member 24 so that they can be engaged and disengaged.

  As shown in FIG. 1, a power external take-out member M for taking out power from the engine to the outside is provided on the outer peripheral surface of the input shaft connecting member 19 on the outer peripheral side. The operations of the first clutch CL1, the second clutch CL2, the third clutch CL3, the fourth clutch CL4, the first brake B1 and the second brake B2 are controlled by a transmission ECU (hereinafter simply referred to as TM-ECU) 25. .

  In the automatic transmission 10 configured as described above, the third carrier C3 of the third planetary gear 15 and the fourth carrier C4 of the fourth planetary gear 16 are connected, and the third ring gear R3 and the fourth ring gear R3 of the third planetary gear 15 are connected. By adopting a configuration in which the fourth sun gear S4 of the planetary gear 16 is connected, the third and fourth planetary gears 15 and 16 form one double planetary gear device. As shown in FIG. 2, the vehicle automatic transmission 10 selectively engages / disengages the first to fourth control clutches CL1 to CL4, selectively operates the first and second brakes B1 and B2, and performs first operation. By restricting the rotation of the elements of the fourth planetary gears 13 to 16, it is possible to establish 10 forward speeds and 1 reverse speed. In FIG. 2, when each clutch and brake column corresponding to each gear position is marked with a white circle, it indicates that the clutch is in the connected state, and if it is the brake, it is in the rotation restricted state.

In the first to fourth planetary gears 13 to 16 which are single pinion type planetary gear mechanisms, the relationship among the rotation speed Ns of the sun gear, the rotation speed Nc of the carrier, the rotation speed Nr of the ring gear and the gear ratio λ of the planetary gear mechanism is The gear ratio at each gear stage is calculated based on the equation (1). When the number of teeth of the sun gears S1, S2, S3, S4 is Zs1, Zs2, Zs3, Zs4 and the number of teeth of the ring gears R1, R2, R3, R4 is Zr1, Zr2, Zr3, Zr4, the first to fourth pinion gears The gear ratios 13 to 14 are λ1 = Zs1 / Zr1, λ2 = Zs2 / Zr2, λ3 = Zs3 / Zr3, and λ4 = Zs4 / Zr4.
Nr = (1 + λ) Nc−λNs (1)

  When the first and second brakes B1 and B2 are selectively operated and the first to fourth clutches CL1 to CL4 are selectively connected, the speed ratio of each element of the first to fourth planetary gears 13 to 16 is It becomes like the velocity diagram shown in FIG. In the speed diagram, the elements consisting of the sun gear, carrier, and ring gear of the planetary gear unit are arranged at intervals corresponding to the gear ratio in the horizontal axis direction, and the speed ratio is taken corresponding to each element in the vertical axis direction. Is.

  FIG. 3 is a velocity diagram of the first to fourth planetary gears 13 to 16. In the first to fourth planetary gears 13 to 16, the fourth sun gear S4 and the third ring gear R3 are connected, and the fourth carrier C4 and the third carrier C3 are connected. Therefore, in FIG. 3, the fourth sun gear S4 and the third ring gear R3, the fourth carrier C4 and the third carrier C3, and the fourth sun gear S4 and the fourth Respective speed ratios of the 3-ring gear R3 and the fourth carrier C4 and the third carrier C3 are represented, and the respective speed ratios of the third sun gear S3 and the second carrier C2 are indicated on the respective vertical lines with S3 and R2. Represent.

  The fourth planetary gear 16 that is a single pinion planetary gear mechanism regards the vertical line of the fourth carrier C4 as the fourth sun gear S4, with the interval between the vertical line of the fourth ring gear R4 and the vertical line of the fourth sun gear S4 being 1 + λ4. Is spaced apart from the vertical line by the interval 1 on the same side as the vertical line of the fourth ring gear R4.

  Also for the third planetary gear 15 that is a single pinion planetary gear mechanism, the distance between the vertical line of the third ring gear R3 and the vertical line of the third sun gear S3 is regarded as 1 + λ3, and the vertical line of the third sun gear S3 is defined as the third carrier. It is arranged at a distance of 1 from the vertical line of C3 on the same side as the vertical line of the third sun gear S3.

  Also for the second planetary gear 14 which is a single pinion planetary gear mechanism, the interval between the second ring gear R2 and the vertical line of the second carrier C2 is regarded as λ2, and the vertical line of the second sun gear S2 is defined as the vertical line of the second carrier C2. The first ring gear R2 is disposed away from the vertical line of the second ring gear R2 by a distance 1 from the line.

  Further, in the speed diagram of FIG. 3, B1 to B2 and CL1 to CL4 are respectively written at points where the first to third brakes B2 to B3 and the first to fourth clutches CL1 to CL4 are selectively operated. ing.

  In the speed diagram of the vehicle automatic transmission 10 configured as described above, the elements corresponding to the five vertical lines are arranged in the order of the vertical lines in the first, second, third, fourth, and fifth constituent elements. And In the case of the first embodiment, the first component is the fourth sun gear S4 and the third ring gear R3. The fourth sun gear S4 and the third ring gear R3 are connected to each other and are connected to the input shaft 12 by the first clutch CL1. The second component is a fourth carrier C4 and a third carrier C3. The fourth carrier C4 and the third carrier C3 are connected to each other and to the output shaft 17. The third component is the fourth ring gear R4 and the second carrier C2. The fourth ring gear R4 and the second carrier C2 are connected to each other and are connected to the first ring gear R1 by the fourth clutch CL4. The fourth component is the second ring gear R2. The rotation of the fourth component is restricted by the second brake B2. The fifth component is the third sun gear S3. The fifth component is connected to the first ring gear R1 by the third clutch CL3.

  Hereinafter, the operation of each gear stage will be described. In the case of the first forward speed, the rotation of the second sun gear S2 is restricted by the operation of the first brake B1, and the rotation of the second ring gear R2 is restricted by the operation of the second brake B2. Thereby, the rotation of the second carrier C2 and the fourth ring gear R4 of the third component is restricted. By connecting the first clutch CL1, the fourth sun gear S4 as the first component is driven to rotate by the input shaft 12. Thereby, the 4th carrier C4 which is the 2nd component, and the output shaft 17 connected with the 4th carrier C4 are driven forward by the gear ratio of the 1st gear stage.

  In the case of the second forward speed, the rotation of the second sun gear S2 is restricted by the operation of the first brake B1, and the rotation of the second ring gear R2 is restricted by the operation of the second brake B2. Thereby, the rotation of the second carrier C2 and the fourth ring gear R4 of the third component is restricted. Further, the first brake B1 is operated to restrict the rotation of the first sun gear S1, so that a speed-up rotation having a larger rotational speed than the rotation of the input shaft 12 occurs in the first ring gear R1. As the second clutch CL2 is connected, the rotation of the first ring gear R1 is transmitted to the third ring gear R3 and the fourth sun gear S4 of the first component. Thereby, the 4th carrier C4 which is the 2nd component, and the output shaft 17 connected with the 4th carrier C4 are driven forward by the gear ratio of the 2nd gear stage.

  In the case of the third forward speed, the first clutch CL1 is connected, so that the fourth sun gear S4 and the third ring gear R3, which are the first components, are rotationally driven by the input shaft 12. By connecting the second clutch CL2, the rotation of the input shaft 12 is transmitted from the third ring gear R3 to the first ring gear R1. Thereby, the rotation of the first sun gear S1 and the second sun gear S2 is determined. The operation of the second brake B2 determines the rotation of the second carrier C2 and the fourth ring gear R4 of the third component. Thereby, the 4th carrier C4 which is the 2nd component, and the output shaft 17 connected with the 4th carrier C4 are driven forward by the gear ratio of the 3rd gear stage.

  In the fourth forward speed, the fourth clutch CL4 is connected to connect the second carrier C2 of the second planetary gear 14 and the first ring gear R1 of the first planetary gear 13 so that the second sun gear of the second planetary gear 14 is connected. By the configuration in which S2 and the first sun gear S1 of the first planetary gear 13 are connected, the first and second planetary gears 13 and 14 form one compound planetary gear device. The first carrier C1 is rotationally driven by the input shaft 12, and the rotation of the second ring gear R2 is restricted by the operation of the second brake B2. Thereby, the rotation of the second carrier C2 and the fourth ring gear R4 of the third component is determined. By connecting the second clutch CL2, the rotation of the second carrier C2 via the fourth clutch CL4 is transmitted to the third ring gear R3 and the fourth sun gear S4, which are the first components. Thereby, the 4th carrier C4 which is the 2nd component, and the output shaft 17 connected with the 4th carrier C4 are driven forward by the gear ratio of the 4th gear stage.

  In the case of the fifth forward speed, the fourth clutch CL4 is connected to connect the second carrier C2 of the second planetary gear 14 and the first ring gear R1 of the first planetary gear 13 so that the second sun gear of the second planetary gear 14 is connected. By the configuration in which S2 and the first sun gear S1 of the first planetary gear 13 are connected, the first and second planetary gears 13 and 14 form one compound planetary gear device. The first carrier C1 is rotationally driven by the input shaft 12, and the rotation of the second ring gear R2 is restricted by the operation of the second brake B2. Thereby, the rotation of the second carrier C2 and the fourth ring gear R4 of the third component is determined. When the first clutch CL <b> 1 is connected, the fourth sun gear S <b> 4 and the third ring gear R <b> 3 of the first component are rotationally driven by the input shaft 12. Thereby, the 4th carrier C4 which is the 2nd component, and the output shaft 17 connected with the 4th carrier C4 are driven forward by the gear ratio of the 5th gear stage.

  In the case of the sixth forward shift speed, the third clutch CL3 is connected, whereby the third sun gear S3 of the third planetary gear 15 and the first ring gear R1 of the first planetary gear 13 are connected, and the first clutch CL1 is connected. As a result, the third ring gear R3 of the third planetary gear 15 and the first carrier C1 of the first planetary gear 13 are connected. Then, the fourth ring gear R4 of the fourth planetary gear 16 and the second carrier C4 of the second planetary gear 14 are connected, and the first sun gear S1 of the first planetary gear 13 and the second sun gear S2 of the second planetary gear 14 are connected. It becomes composition. Accordingly, the first carrier C1 of the first planetary gear 13 is rotationally driven by the input shaft 12, and the second brake B2 is operated, whereby the rotation of the second carrier C2 and the fourth ring gear R4, which are the third components, is determined. When the first clutch CL <b> 1 is connected, the fourth sun gear S <b> 4 and the third ring gear R <b> 3 that are the first components are rotationally driven by the input shaft 12. Thereby, the 4th carrier C4 which is the 2nd component, and the output shaft 17 connected with the 4th carrier C4 are driven forward by the gear ratio of the 5th gear stage.

  In the case of the seventh forward speed, the first clutch CL1 is connected, so that the fourth sun gear S4 and the third ring gear R3, which are the first constituent elements, are rotationally driven by the input shaft 12, and the second clutch CL2 and the third clutch By connecting CL3, the third sun gear S3 is rotationally driven by the input shaft 12. As a result, the fourth carrier C4, which is the second component, and the output shaft 17 connected to the fourth carrier C4 are driven to rotate forward at a gear ratio of 1.000 of the seventh gear.

  In the case of the eighth forward shift speed, the first brake B1 is activated and the first sun gear S1 of the first planetary gear 13 is restricted from rotating, so that the speed-up rotation having a larger rotational speed than the rotation of the input shaft 12 is It occurs in the ring gear R1. By connecting the third clutch CL3, the rotation of the first ring gear R1 is transmitted to the third sun gear S3. When the first clutch CL <b> 1 is connected, the fourth sun gear S <b> 4 and the third ring gear R <b> 3 that are the first components are rotationally driven by the input shaft 12. As a result, the third carrier C3 and the fourth carrier C4, which are the second components, and the output shaft 17 connected to the fourth carrier C4 are driven to rotate forward at the gear ratio of the eighth gear.

  In the case of the ninth forward shift speed, the fourth clutch CL4 is connected, the second carrier C2 of the second planetary gear 14 and the first ring gear R1 of the first planetary gear 13 are connected, and the second sun gear S2 of the second planetary gear 14 is connected. With the configuration in which the first sun gear S1 of the first planetary gear 13 is connected, the first and second planetary gears 13 and 14 form one double planetary gear device. The first carrier C1 is rotationally driven by the input shaft 12, the first brake B1 is operated, and the rotation of the first sun gear S1 and the second sun gear S2 of the first planetary gear 13 is restricted. Thereby, rotation of the 2nd carrier C2 and 2nd ring gear R4 which are the 3rd component is decided. When the first clutch CL <b> 1 is connected, the fourth sun gear S <b> 4 and the third ring gear R <b> 3 that are the first components are rotationally driven by the input shaft 12. Thereby, the 4th carrier C4 which is the 2nd component, and the output shaft 17 connected with the 4th carrier C4 are driven forward by the gear ratio of the 9th gear stage.

  In the case of the forward tenth shift speed, the fourth clutch CL4 is connected, the second carrier C2 of the second planetary gear 14 and the first ring gear R1 of the first planetary gear 13 are coupled, and the second sun gear S2 of the second planetary gear 14 is connected. With the configuration in which the first sun gear S1 of the first planetary gear 13 is connected, the first and second planetary gears 13 and 14 form one double planetary gear device. The first carrier C1 is rotationally driven by the input shaft 12, the first brake B1 is operated, and the rotation of the first sun gear S1 and the second sun gear S2 of the first planetary gear 13 is restricted. Thereby, rotation of the 2nd carrier C2 and 2nd ring gear R4 which are the 3rd component is decided. By connecting the second clutch CL2, the rotation of the second carrier C2 via the fourth clutch CL4 is transmitted to the third ring gear R3 and the fourth sun gear S4, which are the first components. Thereby, the 4th carrier C4 which is the 2nd component, and the output shaft 17 connected with the 4th carrier C4 are driven forward by the gear ratio of the 10th gear stage.

  In the case of the reverse first shift speed, the rotation of the second sun gear S2 is restricted by the operation of the first brake B1, and the rotation of the second ring gear R2 is restricted by the operation of the second brake B2. As a result, the rotation of the second carrier C2 and the fourth ring gear R4, which are third components, is restricted. Further, when the first brake B1 is operated and the rotation of the first sun gear S1 of the first planetary gear 13 is restricted, a speed-up rotation having a higher rotation speed than the rotation of the input shaft 12 is generated in the first ring gear R1. By connecting the third clutch CL3, the rotation of the first ring gear R1 is transmitted to the third sun gear S3. As a result, the fourth carrier C4, which is the second component, and the output shaft 17 connected to the fourth carrier C4 are driven in reverse at the gear ratio of the reverse first gear.

  According to the above-described shift stage, the first clutch CL1 and the third clutch are maintained while maintaining the engagement of the first brake B1 and the second brake B2 with respect to switching between the forward first speed shift stage and the reverse first shift stage. By switching the engagement of CL3, the rotation of the fourth carrier C4 of the fourth planetary gear 16 can be reversed. As a result, when shifting is performed in the garage, the first clutch CL1 or the third clutch CL3 is used when shift switching between the first forward shift speed and the reverse first shift speed (hereinafter referred to as a garage shift) is performed. It is possible to switch by simply switching one of the fastening elements. For this reason, the response time required to perform the garage shift can be shortened.

  As described above, according to the automatic transmission 10 according to the embodiment of the present invention, the third planetary gear 15 is removed by eliminating the connection between the first ring gear R1 of the first planetary gear 13 and the third sun gear S3 of the third planetary gear 15. The third carrier C3 is connected from the input shaft 12 side, passes through the inner peripheral side of the third sun gear S3 of the third planetary gear 15, and is connected to the fourth carrier C4 of the fourth planetary gear 16 from the input shaft 12 side. A member 22 can be provided. For this reason, the first connection part 23a that extends through the inner peripheral side of the third connection member 22 on the rotation axis 18 and is connected to the fourth sun gear S4 from the input shaft 12 side is connected to the first connection part 23a. A second connecting portion 23b extending toward the outer diameter side of the housing 11, a third connecting portion 23c connected to the second connecting portion 23b and connected to the third ring gear R3 from the input shaft 12 side, The 4th connection member 23 which has the 4th connection part 23d extended on the axis of rotation 18 while connecting with 1 connection part 23a can be provided. As a result, a sixth connection part 24a connected to the first ring gear R1 from the input shaft 12 side, a seventh connection part 24b connected to the sixth connection part and extending toward the rotation axis 18, and a seventh connection part 24b and the eighth connecting part 24c extending between the first connecting member 20 and the fourth connecting member 23 in the direction of the rotation axis 18 and the eighth connecting part 24c and the outer diameter side of the housing 11 A ninth connection part 24d extending toward the first direction, a tenth connection part 24e connected to the ninth connection part 24d and extending between the third ring gear R3 and the second connection member 21 in the direction of the rotation axis 18; , And the clutch connecting member 24 can be arranged on the outer peripheral side of the third ring gear R3. Further, the second clutch CL2 provided on the outer peripheral side of the third ring gear R3 and detachably connecting the third ring gear R3 and the clutch connecting member 24 is disposed on the outer peripheral side of the third ring gear R3. it can. Therefore, by disposing the third connecting member 22 on the inner diameter side, the second clutch CL2 that is a friction engagement element is provided on the outer peripheral side with respect to the third ring gear R3, and the third ring gear R3 and the clutch connecting member 24 are engaged and disengaged. Can be linked together. For this reason, the outer diameter side arrangement | positioning of a friction engagement element is attained.

  As described above, according to the automatic transmission 10 according to the embodiment of the present invention, the configuration in which the power external extraction member M for extracting the power from the engine to the outside is provided on the outer peripheral surface of the input shaft coupling member 19 on the outer peripheral side. Is adopted. Thereby, the power external take-out member M can always take out the power of the same rotation as the input rotation of the input shaft as the PTO from the input shaft connecting member 19 connected to the input shaft 12 regardless of the gear position.

10: Vehicle automatic transmission 11: Housing 12: Input shaft 13: First planetary gear 14: Second planetary gear 15: Third planetary gear 16: Fourth planetary gear 17: Output shaft 18: Rotating axis 19: Input shaft connecting member 20: 1st connection member 21: 2nd connection member 22: 3rd connection member 23: 4th connection member 23a: 1st connection part 23b: 2nd connection part 23c: 3rd connection part 23d: 4th connection part 24: Clutch connection Member 24a: Sixth connecting part 24b: Seventh connecting part 24c: Eighth connecting part 24d: Ninth connecting part 24e: Tenth connecting part B1: First brake B2: Second brake C1: First carrier C2: Second Carrier C3: Third carrier C4: Fourth carrier CL1: First clutch CL2: Second clutch CL3: Third clutch CL4: Fourth clutch M: Out of power Picker R1: first ring gear R2: second ring gear R3: the third ring gear R4: the fourth ring gear R4
S1: First sun gear S2: Second sun gear S3: Third sun gear S4: Fourth sun gear

Claims (2)

A housing;
An input shaft supported by the housing so as to be rotatable around a rotation axis;
Single pinion type first to fourth planetary gears that are sequentially supported from the input shaft side coaxially with the rotation axis on the housing;
An output shaft that is supported by the housing so as to be rotatable about a rotation axis, and that is coupled to a fourth carrier of the fourth planetary gear;
An input shaft coupling member coupled to the first carrier of the first planetary gear from the output shaft side and coupled to the input shaft through the outer peripheral side of the first ring gear of the first planetary gear;
A first connecting member that connects the first sun gear of the first planetary gear and the second sun gear of the second planetary gear;
A second connecting member for connecting the second carrier of the second planetary gear and the fourth ring gear of the fourth planetary gear through the outer peripheral side of the third ring gear of the third planetary gear;
The third planetary gear is connected from the input shaft side to the third carrier of the third planetary gear, and is connected to the fourth carrier of the fourth planetary gear from the input shaft side through the inner peripheral side of the third sun gear of the third planetary gear. A connecting member;
The housing extends on an inner peripheral side of the third connecting member on the rotation axis, and is connected to the fourth sun gear from the input shaft side, and is connected to the first connecting portion and the housing. A second connection part extending toward the outer diameter side of the first connection part, a third connection part connected to the second ring part and connected to the third ring gear from the input shaft side, and connected to the first connection part. And a fourth connection member having a fourth connection part extending on the rotation axis, and a first brake for releasably fixing the first connection member to the inner peripheral surface of the housing,
A second brake for releasably fixing the second ring gear to the inner peripheral surface of the housing;
A first clutch for releasably connecting the input shaft connecting member and the fourth connecting member;
A sixth connection part connected to the first ring gear from the input shaft side, a seventh connection part connected to the sixth connection part and extending toward the rotation axis, and connected to the seventh connection part And an eighth connecting portion extending between the first connecting member and the fourth connecting member in the rotational axis direction, and connecting to the eighth connecting portion and extending toward the outer diameter side of the housing. A clutch connecting member having a ninth connecting part, and a tenth connecting part that is connected to the ninth connecting part and extends between the third ring gear and the second connecting member in the rotational axis direction; ,
A second clutch provided on an outer peripheral side of the third ring gear and releasably connecting the third ring gear and the clutch connecting member;
A third clutch provided on an outer peripheral side of the third ring gear and detachably connecting a third sun gear of the third planetary gear and the clutch connecting member;
A fourth clutch for releasably connecting the second connecting member and the clutch connecting member;
An automatic transmission comprising:   The automatic transmission according to claim 1, wherein a power external take-out member for taking out power from the engine to the outside is provided on an outer peripheral surface on an outer peripheral side of the input shaft connecting member.

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