Transmission

Abstract

To provide a transmission having a plurality of shift stages and enabling easy reduction in the size.SOLUTION: A planetary gear device 1 has at least three rotating elements including: a first input element 11 driven by and coupled to a driving power source D, a first output element 12 driven by and coupled to an output member O; and a first reaction force element 13 that is a ring gear. A first engagement device 4 includes: a first brake B1 that selectively fixes a first transmission gear 31 engaging with a first interlocking gear 21 rotating integrally with the first reaction force element 13 to a non-rotating member 9; and a first clutch C1 that connects / disconnects power transmission between the first transmission gear 31 and a first target rotating element T1. A second engagement device 5 includes at least one of a second brake that selectively fixes a second transmission gear 32 engaging with the first interlocking gear 21 or a second interlocking gear to the non-rotating member 9 and a second clutch C2 that connects / disconnects power transmission between the second transmission gear 32 and a second target rotating element T2.SELECTED DRAWING: Figure 2

Description

[Technical field]

[0001] The present invention relates to a transmission having a plurality of gear stages. [Background technology]

[0002] An example of such a transmission is disclosed in the following Patent Document 1. In the following description of the background art, reference symbols in Patent Document 1 will be cited in parentheses.

[0003] The transmission of Patent Document 1 includes a planetary gear device (5) and an engagement device (6).

[0004] The planetary gear device (5) includes a carrier (53) that rotatably supports a large diameter pinion gear (52a) and a small diameter pinion gear (52b) that rotate integrally with each other, a sun gear (51) that rotates integrally with the rotor (32) of the rotating electric machine (3) and meshes with the large diameter pinion gear (52a), a first ring gear (54a) that meshes with the large diameter pinion gear (52a), and a second ring gear (55a) that meshes with the small diameter pinion gear (52b).

[0005] The engagement device (6) includes a first brake (61) and a second brake (62). The first brake (61) is configured to selectively fix the first ring gear (54a) to the case (2) serving as a non-rotating member. The second brake (62) is configured to selectively fix the second ring gear (55a) to the case (2) serving as a non-rotating member.

[0006] In the above-mentioned transmission, a low gear is established when the first brake (61) is in a released state and the second brake (62) is in an engaged state, and a high gear is established when the first brake (61) is in an engaged state and the second brake (62) is in a released state. [Prior art documents] [Patent documents]

[0007] [Patent Document 1] JP 2013-200012 A Summary of the Invention [Problem to be solved by the invention]

[0008] In the transmission of Patent Document 1, the first brake (61) and the second brake (62) are disposed radially outward from the planetary gear device (5) (upper side in FIG. 1 of Patent Document 1). This makes it easy for the engagement device (6) to have a large diameter, which leads to an increase in the size of the transmission.

[0009] Therefore, it is desirable to realize a transmission that has a plurality of gears and that can be easily made compact. [Means for solving the problem]

[0010] In view of the above, the characteristic configuration of the transmission is as follows: a planetary gear device including at least three rotating elements including a first input element drivingly connected to a driving force source, a first output element drivingly connected to an output member, and a first reaction element that is a ring gear; a first interlocking gear having external teeth that rotates integrally with the first reaction element; a first transmission gear that meshes with the first interlocking gear; A second transmission gear; A first engagement device; a second engagement device, the second transmission gear is configured to mesh with the first interlocking gear, or, when the planetary gear set includes a second reaction element that is a ring gear different from the first reaction element, to mesh with a second interlocking gear having external teeth that rotates integrally with the second reaction element; The first engagement device is a first brake arranged coaxially with the first transmission gear and configured to selectively fix the first transmission gear to a non-rotating member; a first clutch that is arranged coaxially with the first transmission gear and that connects and disconnects power transmission between the first transmission gear and a first target rotating element that is one of the rotating elements other than the first reaction element in the planetary gear device, The second engagement device is a second brake arranged coaxially with the second transmission gear and configured to selectively fix the second transmission gear to the non-rotating member; The planetary gear device has at least one of a second clutch that is arranged coaxially with the second transmission gear, which is the first interlocking gear or the second interlocking gear with which the second transmission gear is meshed, and that connects and disconnects the power transmission between the second transmission gear and a second interlocking gear, which is one of the rotating elements other than the rotating element that rotates integrally with the interlocking gear in the planetary gear device.

[0011] According to this characteristic configuration, two gears can be formed by switching the engagement state of the first engagement device, and one or two gears can be formed by switching the engagement state of the second engagement device. In addition, by controlling the engagement states of both the first engagement device and the second engagement device, a neutral state in which no power transmission occurs between the first input element and the first output element, and a rotation restricted state in which the rotation of the first output element is restricted can also be realized. Therefore, according to this characteristic configuration, a transmission having three or four gears, a neutral state function, and a parking lock function can be realized. According to this characteristic configuration, the first transmission gear meshes with the first interlocking gear having external teeth that rotates integrally with the first reaction element, which is a ring gear, and the first brake and first clutch of the first engagement device are arranged coaxially with the first transmission gear. This makes it easier to reduce the diameter of the first engagement device compared to a configuration in which the first brake and first clutch are arranged coaxially with the first reaction element. The same is true for the second engagement device. This makes it easier to reduce the size of the transmission. [Brief description of the drawings]

[0012] [Figure 1] 1 is a cross-sectional view of a transmission according to a first embodiment; [Diagram 2] FIG. 1 is a skeleton diagram of a transmission according to a first embodiment. [Diagram 3]FIG. 1 is a diagram showing the operating states of a first engagement device and a second engagement device according to the state of a transmission according to a first embodiment; [Figure 4] 1 is a speed diagram of a planetary gear device in a transmission according to a first embodiment of the present invention; [Diagram 5] 1 is a skeleton diagram of a transmission according to a second embodiment; [Figure 6] FIG. 11 is a diagram showing the operating states of a first engagement device and a second engagement device according to the state of a transmission according to a second embodiment. [Figure 7] 11 is a speed diagram of a planetary gear device in a transmission according to a second embodiment of the present invention; [Figure 8] A skeleton diagram of a transmission according to a third embodiment. [Figure 9] FIG. 13 is a diagram showing the operating states of a first engagement device and a second engagement device according to the state of a transmission according to a third embodiment. [Figure 10] 13 is a speed diagram of a planetary gear device in a transmission according to a third embodiment. [Figure 11] A skeleton diagram of a transmission according to a fourth embodiment. [Figure 12] FIG. 13 is a diagram showing the operating states of a first engagement device and a second engagement device according to the state of a transmission according to a fourth embodiment. [Figure 13] 13 is a speed diagram of a planetary gear device in a transmission according to a fourth embodiment. [Figure 14] A skeleton diagram of a transmission according to a fifth embodiment. [Figure 15] FIG. 13 is a diagram showing the operating states of a first engagement device and a second engagement device according to the state of a transmission according to a fifth embodiment. [Figure 16] 13 is a speed diagram of a planetary gear device in a transmission according to a fifth embodiment. [Figure 17] A skeleton diagram of a transmission according to a sixth embodiment. [Figure 18] FIG. 13 is a diagram showing the operating states of a first engagement device and a second engagement device according to the state of a transmission according to a sixth embodiment. [Figure 19] 13 is a speed diagram of a planetary gear device in a transmission according to a sixth embodiment. [Figure 20] A skeleton diagram of a transmission according to a seventh embodiment. [Figure 21] FIG. 13 is a diagram showing the operating states of a first engagement device and a second engagement device according to the state of a transmission according to a seventh embodiment; [Figure 22] 13 is a speed diagram of a planetary gear device in a transmission according to a seventh embodiment. [Diagram 23] A skeleton diagram of a transmission according to an eighth embodiment. [Figure 24] FIG. 13 is a skeleton diagram of a transmission according to a ninth embodiment. [Diagram 25] FIG. 13 is a diagram showing the operating states of a first engagement device and a second engagement device according to the state of a transmission according to a ninth embodiment. [Figure 26] 13 is a speed diagram of a planetary gear device in a transmission according to a ninth embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0013] 1. First embodiment A transmission 100 according to a first embodiment will be described below with reference to FIGS. 1 to 4. FIG.

[0014] As shown in Fig. 1 and Fig. 2, the transmission 100 includes a planetary gear device 1, a first interlocking gear 21, a first transmission gear 31, a second transmission gear 32, a first engagement device 4, and a second engagement device 5. In this embodiment, the transmission 100 further includes a third interlocking gear 23, a fourth interlocking gear 24, a third transmission gear 33, a fourth transmission gear 34, an input shaft 61, an input gear 62, an output shaft 63, and a case 9. Note that the transmission 100 may include a second interlocking gear 22. In this embodiment, the transmission 100 does not include the second interlocking gear 22.

[0015] In this embodiment, there are mainly a first axis X1, a second axis X2, and a third axis X3 as rotation axes of a plurality of rotating members included in the transmission 100. The first axis X1, the second axis X2, and the third axis X3 are arranged parallel to one another.

[0016] In the following description, the direction along each of the first axis X1, the second axis X2, and the third axis X3 is referred to as the "axial direction L". One side of the axial direction L is referred to as the "axial first side L1", and the other side of the axial direction L is referred to as the "axial second side L2". In this embodiment, the side in the axial direction L where the input shaft 61 is arranged relative to the planetary gear set 1 is the axial first side L1, and the side in the axial direction L where the output shaft 63 is arranged relative to the planetary gear set 1 is the axial second side L2. In addition, the direction perpendicular to each of the first axis X1, the second axis X2, and the third axis X3 is referred to as the "radial direction R" based on the corresponding axis. Note that when it is not necessary to distinguish which axis is used as the reference or when it is clear which axis is used as the reference, it may be simply referred to as the "radial direction R".

[0017] The planetary gear device 1 includes at least three rotating elements including a first input element 11, a first output element 12, and a first reaction element 13. In this embodiment, the planetary gear device 1 includes a first planetary gear mechanism P1 including the first input element 11, the first output element 12, and the first reaction element 13. The first planetary gear mechanism P1 is disposed on a first axis X1.

[0018] The first input element 11 is drivingly connected to a driving force source D (see FIG. 2). The driving force source D is, for example, an internal combustion engine or a rotating electric machine.

[0019] Here, in the present application, the term "driving connection" refers to a state in which two rotating elements are connected so as to be able to transmit a driving force, and includes a state in which the two rotating elements are connected so as to rotate integrally, or a state in which the two rotating elements are connected so as to be able to transmit a driving force via one or more transmission members. Such transmission members include various members that transmit rotation at the same speed or at a variable speed, such as shafts, gear mechanisms, belts, chains, etc. Note that the transmission members may also include engagement devices that selectively transmit rotation and driving force, such as friction engagement devices and meshing engagement devices. However, when the term "driving connection" is used for each rotating element of a planetary gear mechanism, it refers to a state in which multiple rotating elements in the planetary gear mechanism are connected to each other without passing through other rotating elements.

[0020] In this embodiment, the first input element 11 is drivingly connected to a driving force source D via an input shaft 61. The input shaft 61 is formed to extend along the axial direction L. The input shaft 61 is connected to the first input element 11 and an input gear 62 so as to rotate integrally with them. In this embodiment, the input shaft 61 and the input gear 62 are disposed on a first axis X1. Also, in this embodiment, the input gear 62 is disposed on a first axial side L1 with respect to the first input element 11.

[0021] The first output element 12 is drivingly connected to the output member O (see FIG. 2). In this embodiment, the first output element 12 is drivingly connected to the output member O via an output shaft 63. The output shaft 63 is formed to extend along the axial direction L. The output shaft 63 is connected to the first output element 12 so as to rotate integrally therewith. In this embodiment, the output shaft 63 is disposed on the first axis X1. Note that the output member O is, for example, an axle when the transmission 100 is mounted on a vehicle, and a propeller shaft when the transmission 100 is mounted on a ship.

[0022] The first reaction element 13 is a ring gear. In this embodiment, the first input element 11 is a sun gear. And the first output element 12 is a carrier. In this embodiment, the first output element 12 as a carrier supports a pinion gear that meshes with both the first input element 11 as a sun gear and the first reaction element 13 as a ring gear. That is, in this embodiment, the first planetary gear mechanism P1 is a single-pinion type planetary gear mechanism.

[0023] The first interlocking gear 21 is an externally toothed gear that rotates integrally with the first reaction element 13. In this embodiment, the first interlocking gear 21 is disposed on the first axis X1. In the example shown in FIG. 1, the first interlocking gear 21 is disposed on the outside of the first reaction element 13 in the radial direction R based on the first axis X1, and is disposed at a position overlapping with the first reaction element 13 when viewed in the radial direction R. Here, with regard to the arrangement of the two elements, "overlapping when viewed in a specific direction" refers to the existence of at least a part of an area where a virtual line parallel to the line of sight intersects with both of the two elements when the virtual line is moved in each direction perpendicular to the virtual line.

[0024] The first transmission gear 31 meshes with the first interlocking gear 21. In this embodiment, the first transmission gear 31 is disposed on the second axis X2.

[0025] In this embodiment, the second transmission gear 32 meshes with the first interlocking gear 21. That is, in this embodiment, the second transmission gear 32 and the first transmission gear 31 mesh with the first interlocking gear 21 at different positions in the circumferential direction of the first interlocking gear 21. Also, in this embodiment, the second transmission gear 32 is disposed on the third axis X3.

[0026] The third interlocking gear 23 is a gear that rotates in conjunction with the first input element 11. In this embodiment, the third interlocking gear 23 is an idler gear that meshes with an input gear 62 that rotates integrally with the first input element 11.

[0027] The third transmission gear 33 meshes with the third interlocking gear 23. The third transmission gear 33 is disposed coaxially with the first transmission gear 31. In this embodiment, the third transmission gear 33 is disposed on the second axis X2. The third transmission gear 33 is disposed on the first axial side L1 with respect to the first transmission gear 31. In this embodiment, the third transmission gear 33 is formed to have a smaller diameter than the input gear 62.

[0028] The fourth interlocking gear 24 is a gear that rotates in conjunction with the first input element 11. In this embodiment, the fourth interlocking gear 24 is an idler gear that meshes with the input gear 62 that rotates integrally with the first input element 11. That is, in this embodiment, the fourth interlocking gear 24 and the third interlocking gear 23 mesh with the input gear 62 at different positions in the circumferential direction of the input gear 62.

[0029] The fourth transmission gear 34 meshes with the fourth interlocking gear 24. The fourth transmission gear 34 is disposed coaxially with the second transmission gear 32. In this embodiment, the fourth transmission gear 34 is disposed on the third axis X3. The fourth transmission gear 34 is disposed on the first axial side L1 with respect to the second transmission gear 32. In this embodiment, the fourth transmission gear 34 is formed to have a larger diameter than the input gear 62.

[0030] The case 9 functions as a non-rotating member. In this embodiment, the case 9 accommodates the planetary gear set 1, the first interlocking gear 21, the third interlocking gear 23, the fourth interlocking gear 24, the first transmission gear 31, the second transmission gear 32, the third transmission gear 33, the fourth transmission gear 34, the first engagement device 4, the second engagement device 5, the input shaft 61, the input gear 62, and the output shaft 63. The input shaft 61 and the output shaft 63 are accommodated in the case 9 with parts of them exposed to the outside of the case 9.

[0031] The first engagement device 4 includes a first brake B1 and a first clutch C1. The first brake B1 and the first clutch C1 are disposed coaxially with the first transmission gear 31. In this embodiment, the first brake B1 and the first clutch C1 are disposed on the second axis X2. The first brake B1 and the first clutch C1 are disposed on the second axial side L2 with respect to the first transmission gear 31. The first clutch C1 is disposed on the first axial side L1 with respect to the first brake B1.

[0032] The first brake B1 is configured to selectively fix the first transmission gear 31 to a non-rotating member (here, the case 9). The first brake B1 includes a first friction member 41, a first inner support member 42, and a first outer support member 43.

[0033] The first friction member 41 includes a first inner friction material 411 and a first outer friction material 412. The first inner friction material 411 and the first outer friction material 412 are arranged to face each other in the axial direction L. In this embodiment, the first inner friction material 411 and the first outer friction material 412 are provided in multiple sheets, which are arranged alternately along the axial direction L.

[0034] The first inner support member 42 supports the first inner friction material 411 so that it cannot rotate relative to the first inner friction material 411 in the circumferential direction and can slide freely in the axial direction L. In this embodiment, the first inner support member 42 is formed in a cylindrical shape with the second axis X2 as its axis. The first inner support member 42 supports the first inner friction material 411 from the inside in the radial direction R. In this example, a plurality of splines extending in the axial direction L are formed on the outer periphery of the first inner support member 42 and distributed in the circumferential direction. Meanwhile, similar splines are also formed on the inner periphery of the first inner friction material 411 and distributed in the circumferential direction. These splines are engaged with each other.

[0035] In this embodiment, the first inner support member 42 is fixed to the case 9. In this embodiment, the case 9 has a first side wall portion 91 formed to extend along the radial direction R. The first inner support member 42 is fixed to the first side wall portion 91. In the example shown in FIG. 1, the first side wall portion 91 is disposed so as to cover the first brake B1 from the second axial side L2. The first inner support member 42 is formed so as to protrude from the first side wall portion 91 to the first axial side L1.

[0036] The first outer support member 43 supports the first outer friction material 412 so that it cannot rotate relative to the first outer friction material 412 in the circumferential direction and can slide freely in the axial direction L. In this embodiment, the first outer support member 43 is formed in a cylindrical shape with the second axis X2 as its axis. The first outer support member 43 supports the first outer friction material 412 from the outside in the radial direction R. In this example, a plurality of splines extending in the axial direction L are formed in a distributed manner in the circumferential direction on the inner peripheral portion of the first outer support member 43. On the other hand, similar splines are also formed in a distributed manner in the circumferential direction on the outer peripheral portion of the first outer friction material 412. These splines are engaged with each other.

[0037] The first clutch C1 is configured to connect and disconnect power transmission between the first transmission gear 31 and the first target rotating element T1. In this embodiment, the first clutch C1 is configured to connect and disconnect power transmission between the first transmission gear 31 and the third transmission gear 33. The first target rotating element T1 is one rotating element in the planetary gear device 1 other than the first reaction element 13. In this embodiment, the first target rotating element T1 is the first input element 11.

[0038] The first clutch C1 includes a second friction member 44, a second inner support member 45, and a second outer support member .

[0039] The second friction member 44 includes a second inner friction material 441 and a second outer friction material 442. The second inner friction material 441 and the second outer friction material 442 are arranged to face each other in the axial direction L. In this embodiment, the second inner friction material 441 and the second outer friction material 442 are provided in multiple sheets, which are arranged alternately along the axial direction L.

[0040] The second inner support member 45 supports the second inner friction material 441 so that it cannot rotate relative to the second inner friction material 441 in the circumferential direction and can slide freely in the axial direction L. In this embodiment, the second inner support member 45 is formed in a cylindrical shape with the second axis X2 as its axis. The second inner support member 45 supports the second inner friction material 441 from the inside in the radial direction R. In this example, a plurality of splines extending in the axial direction L are formed in a distributed manner in the circumferential direction on the outer periphery of the second inner support member 45. On the other hand, similar splines are also formed in a distributed manner in the circumferential direction on the inner periphery of the second inner friction material 441. These splines are engaged with each other.

[0041] In this embodiment, the second inner support member 45 is connected to the third transmission gear 33 via a first connecting shaft 71 so as to rotate integrally with the third transmission gear 33. The first connecting shaft 71 is formed so as to extend along the axial direction L.

[0042] The second outer support member 46 supports the second outer friction material 442 so that it cannot rotate relative to the second outer friction material 442 in the circumferential direction and can slide freely in the axial direction L. In this embodiment, the second outer support member 46 is formed in a cylindrical shape with the second axis X2 as its axis. The second outer support member 46 supports the second outer friction material 442 from the outside in the radial direction R. In this example, a plurality of splines extending in the axial direction L are formed in a distributed manner in the circumferential direction on the inner peripheral portion of the second outer support member 46. On the other hand, similar splines are also formed in a distributed manner in the circumferential direction on the outer peripheral portion of the second outer friction material 442. These splines are engaged with each other.

[0043] In this embodiment, the second outer support member 46 is connected to the first outer support member 43 of the first brake B1 so as to rotate integrally with the first outer support member 43. In the example shown in FIG.

[0044] In this embodiment, the second outer support member 46 is connected to the first transmission gear 31 via a second connecting shaft 72 so as to rotate integrally with the first transmission gear 31. The second connecting shaft 72 is formed to extend along the axial direction L. In this embodiment, the second connecting shaft 72 is formed in a cylindrical shape with the second axis X2 as its axis. The first connecting shaft 71 is disposed inside the second connecting shaft 72 in the radial direction R so as to penetrate the cylindrical second connecting shaft 72 in the axial direction L.

[0045] 1, in this embodiment, the first engagement device 4 further includes a first drive device D1. The first drive device D1 is a "drive device" that drives the first brake B1 and the first clutch C1. The first drive device D1 includes a first pressing member 47, a first drive motor 48, and a first linear motion conversion mechanism 49.

[0046] The first pressing member 47 is a “pressing member” that presses the first friction member 41 and the second friction member 44 in the axial direction L. In the present embodiment, the first pressing member 47 includes a first pressing portion 471 and a second pressing portion 472.

[0047] The first pressing portion 471 is disposed adjacent to the first axial side L1 of the first friction member 41. In the present embodiment, the first pressing portion 471 is supported so as to be movable relative to the first inner support member 42 in the axial direction L and non-rotatable relative to the first inner support member 42 in the circumferential direction.

[0048] The second pressing portion 472 is disposed adjacent to the second axial side L2 with respect to the second friction member 44. In the present embodiment, the second pressing portion 472 is supported so as to be movable relative to the second outer support member 46 in the axial direction L and so as not to be rotatable relative to the second outer support member 46 in the circumferential direction.

[0049] In this embodiment, the first pressing portion 471 and the second pressing portion 472 are configured as separate members arranged to face each other in the axial direction L. The first pressing portion 471 and the second pressing portion 472 are supported so as to be rotatable relative to each other via a first thrust bearing 473 arranged between them in the axial direction L. Therefore, in this embodiment, the first pressing portion 471 and the second pressing portion 472 are configured to move in conjunction with each other in the axial direction L while being rotatable relative to each other.

[0050] The first drive motor 48 is a “drive motor” that outputs a predetermined rotational drive force. In this embodiment, the first drive motor 48 is an electric motor.

[0051] The first linear motion conversion mechanism 49 is a screw-type “linear motion conversion mechanism” that converts the rotational driving force of the first drive motor 48 into a driving force in the axial direction L and transmits the driving force to the first pressing member 47. In this embodiment, the first linear motion conversion mechanism 49 includes a first screw shaft 491, a first nut member 492, and a first transmission mechanism 493.

[0052] A screw thread is formed on the outer periphery of the first screw shaft 491. The first screw shaft 491 is formed to extend along the axial direction L. In this embodiment, the first screw shaft 491 is disposed on the second axis X2.

[0053] The first nut member 492 is configured to screw onto the first screw shaft 491. That is, a groove that engages with the thread of the first screw shaft 491 is formed on the inner periphery of the first nut member 492. In this embodiment, the first nut member 492 is connected to the first pressing portion 471 of the first pressing member 47 so as to move integrally in the axial direction L. Thus, in this embodiment, when the first screw shaft 491 rotates, the first pressing portion 471 connected to the first nut member 492 moves in the axial direction L according to the rotation direction and the orientation of the thread of the first screw shaft 491.

[0054] The first transmission mechanism 493 is configured to transmit the rotational driving force of the first drive motor 48 to the first screw shaft 491. In this embodiment, the first transmission mechanism 493 is configured with a plurality of gears. The first transmission mechanism 493 reduces the rotation of the first drive motor 48 and transmits it to the first screw shaft 491.

[0055] In this embodiment, when the first drive motor 48 is driven to rotate in one direction in the rotational direction, the rotational driving force of the first drive motor 48 is transmitted to the first screw shaft 491 via the first transmission mechanism 493, and the first pressing portion 471 connected to the first nut member 492 moves to the first axial side L1. Here, as described above, in this embodiment, the first thrust bearing 473 is disposed between the first pressing portion 471 and the second pressing portion 472 in the axial direction L. Therefore, in this embodiment, when the first pressing portion 471 moves to the first axial side L1, the second pressing portion 472 moves to the first axial side L1 via the first thrust bearing 473. As a result, the second friction member 44 is pressed by the second pressing portion 472, the first clutch C1 is engaged, and the pressing of the first friction member 41 by the first pressing portion 471 is released, and the first brake B1 is released.

[0056] On the other hand, when the first drive motor 48 is driven to rotate in the other direction, the rotational drive force of the first drive motor 48 is transmitted to the first screw shaft 491 via the first transmission mechanism 493, and the first pressing portion 471 connected to the first nut member 492 moves to the second axial side L2. As a result, the first friction member 41 is pressed by the first pressing portion 471, the first brake B1 is engaged, and the pressing of the second friction member 44 by the second pressing portion 472 is released, and the first clutch C1 is released.

[0057] In this manner, in this embodiment, the first engagement device 4 is configured to selectively put either one of the first brake B1 or the first clutch C1 into an engaged state. Note that, in this embodiment, the first engagement device 4 can also put both the first brake B1 and the first clutch C1 into a released state.

[0058] In this embodiment, the first screw shaft 491 and the first nut member 492 of the first linear motion conversion mechanism 49 are disposed on the inside of the first friction member 41 in the radial direction R, and are arranged at a position overlapping the first friction member 41 as viewed in the radial direction along the radial direction R. On the other hand, in this embodiment, the first screw shaft 491 and the first nut member 492 are disposed on the inside of the second friction member 44 in the radial direction R, but are not overlapping the second friction member 44 as viewed in the radial direction along the radial direction R. Note that the first screw shaft 491 and the first nut member 492 may or may not overlap the second friction member 44 as viewed in the radial direction along the radial direction R. In this way, it is preferable that the first linear motion conversion mechanism 49 is disposed on the inside of the first friction member 41 and the second friction member 44 in the radial direction R, and is arranged at a position overlapping at least one of the first friction member 41 and the second friction member 44 as viewed in the radial direction along the radial direction R.

[0059] The second engagement device 5 includes at least one of a second brake B2 and a second clutch C2. In this embodiment, the second engagement device 5 does not include the second brake B2, but includes the second clutch C2. The second clutch C2 is disposed coaxially with the second transmission gear 32. In this embodiment, the second clutch C2 is disposed on the third axis X3. The second clutch C2 is disposed on the second axial side L2 with respect to the second transmission gear 32.

[0060] The second clutch C2 is configured to connect and disconnect the power transmission between the second transmission gear 32 and the second target rotating element T2. In this embodiment, the second clutch C2 is configured to connect and disconnect the power transmission between the second transmission gear 32 and the fourth transmission gear 34. The second target rotating element T2 is one rotating element other than the rotating element that rotates integrally with the target interlocking gear G in the planetary gear device 1. The target interlocking gear G is the gear that meshes with the second transmission gear 32 out of the first interlocking gear 21 and the second interlocking gear 22. As described above, in this embodiment, since the second interlocking gear 22 is not provided, the first interlocking gear 21 corresponds to the target interlocking gear G. Also, in this embodiment, the second target rotating element T2 is the first input element 11.

[0061] The second clutch C2 includes a fourth friction member 54, a fourth inner support member 55, and a fourth outer support member 56.

[0062] The fourth friction member 54 includes a fourth inner friction material 541 and a fourth outer friction material 542. The fourth inner friction material 541 and the fourth outer friction material 542 are arranged to face each other in the axial direction L. In the present embodiment, the fourth inner friction material 541 and the fourth outer friction material 542 are provided in multiple sheets, which are arranged alternately along the axial direction L.

[0063] The fourth inner support member 55 supports the fourth inner friction material 541 so as to be non-rotatable in the circumferential direction and slidable in the axial direction L. In this embodiment, the fourth inner support member 55 is formed in a cylindrical shape with the third axis X3 as its axis. The fourth inner support member 55 supports the fourth inner friction material 541 from the inside in the radial direction R. In this example, a plurality of splines extending in the axial direction L are formed in a distributed manner in the circumferential direction on the outer periphery of the fourth inner support member 55. On the other hand, similar splines are also formed in a distributed manner in the circumferential direction on the inner periphery of the fourth inner friction material 541. These splines are engaged with each other.

[0064] In this embodiment, the fourth inner support member 55 is connected to the fourth transmission gear 34 via a third connecting shaft 73 so as to rotate integrally with the fourth transmission gear 34. The third connecting shaft 73 is formed so as to extend along the axial direction L.

[0065] The fourth outer support member 56 supports the fourth outer friction material 542 so as to be non-rotatable in the circumferential direction and slidable in the axial direction L. In this embodiment, the fourth outer support member 56 is formed in a cylindrical shape with the third axis X3 as its axis. The fourth outer support member 56 supports the fourth outer friction material 542 from the outside in the radial direction R. In this example, a plurality of splines extending in the axial direction L are formed in a distributed manner in the circumferential direction on the inner periphery of the fourth outer support member 56. On the other hand, similar splines are also formed in a distributed manner in the circumferential direction on the outer periphery of the fourth outer friction material 542. These splines are engaged with each other.

[0066] In this embodiment, the fourth outer support member 56 is connected to the second transmission gear 32 via a fourth connecting shaft 74 so as to rotate integrally with the second transmission gear 32. The fourth connecting shaft 74 is formed to extend along the axial direction L. In this embodiment, the fourth connecting shaft 74 is formed in a cylindrical shape with the third axis X3 as its axis. The third connecting shaft 73 is disposed on the inside in the radial direction R with respect to the fourth connecting shaft 74 so as to penetrate the cylindrical fourth connecting shaft 74 in the axial direction L.

[0067] 1, in this embodiment, the second engagement device 5 further includes a second drive device D2. In this embodiment, the second drive device D2 is configured to drive the second clutch C2.

[0068] The second driving device D2 includes a second pressing member 57, a second driving motor 58, and a second linear motion conversion mechanism 59.

[0069] In the present embodiment, the second pressing member 57 is configured to press the fourth friction member 54 in the axial direction L. The second pressing member 57 includes a third pressing portion 571 and a fourth pressing portion 572.

[0070] In this embodiment, the third pressing portion 571 and the fourth pressing portion 572 are configured as separate members arranged to face each other in the axial direction L. The third pressing portion 571 and the fourth pressing portion 572 are supported so as to be rotatable relative to each other via a second thrust bearing 573 arranged between them in the axial direction L. Therefore, in this embodiment, the third pressing portion 571 and the fourth pressing portion 572 are configured to move in conjunction with each other in the axial direction L while being rotatable relative to each other.

[0071] In this embodiment, the case 9 includes a second side wall portion 92 formed to extend along the radial direction R. In the example shown in Fig. 1, the second side wall portion 92 is disposed to cover the second clutch C2 from the second axial side L2.

[0072] In this embodiment, the third pressing portion 571 is supported relative to the second side wall portion 92 so as to be movable in the axial direction L and non-rotatable in the circumferential direction. In this embodiment, the fourth pressing portion 572 is disposed adjacent to the fourth friction member 54 on the second axial side L2. The fourth pressing portion 572 is supported relative to the fourth outer support member 56 so as to be movable relative to the fourth outer support member 56 in the axial direction L and non-rotatable in the circumferential direction.

[0073] The second drive motor 58 is a motor that outputs a predetermined rotational drive force. In this embodiment, the second drive motor 58 is an electric motor.

[0074] The second linear motion conversion mechanism 59 is a screw-type linear motion conversion mechanism that converts the rotational driving force of the second drive motor 58 into a driving force in the axial direction L and transmits the driving force to the second pressing member 57. In this embodiment, the second linear motion conversion mechanism 59 includes a second screw shaft 591, a second nut member 592, and a second transmission mechanism 593.

[0075] A screw thread is formed on the outer periphery of the second screw shaft 591. The second screw shaft 591 is formed to extend along the axial direction L. In this embodiment, the second screw shaft 591 is disposed on the third axis X3.

[0076] The second nut member 592 is configured to screw onto the second screw shaft 591. That is, a groove that engages with the thread of the second screw shaft 591 is formed on the inner periphery of the second nut member 592. In this embodiment, the second nut member 592 is connected to the third pressing portion 571 of the second pressing member 57 so as to move integrally in the axial direction L. Thus, in this embodiment, when the second screw shaft 591 rotates, the third pressing portion 571 connected to the second nut member 592 moves in the axial direction L according to the rotation direction and the orientation of the thread of the second screw shaft 591.

[0077] The second transmission mechanism 593 is configured to transmit the rotational driving force of the second drive motor 58 to the second screw shaft 591. In this embodiment, the second transmission mechanism 593 is configured with a plurality of gears. The second transmission mechanism 593 reduces the rotation of the second drive motor 58 and transmits it to the second screw shaft 591.

[0078] In this embodiment, when the second drive motor 58 is driven to rotate in one direction in the rotational direction, the rotational driving force of the second drive motor 58 is transmitted to the second screw shaft 591 via the second transmission mechanism 593, and the third pressing portion 571 connected to the second nut member 592 moves to the first axial side L1. Here, as described above, in this embodiment, the second thrust bearing 573 is disposed between the third pressing portion 571 and the fourth pressing portion 572 in the axial direction L. Therefore, in this embodiment, when the third pressing portion 571 moves to the first axial side L1, the fourth pressing portion 572 moves to the first axial side L1 via the second thrust bearing 573. As a result, the fourth friction member 54 is pressed by the fourth pressing portion 572, and the second clutch C2 is engaged.

[0079] On the other hand, when the second drive motor 58 is driven to rotate in the other direction, the rotational drive force of the second drive motor 58 is transmitted to the second screw shaft 591 via the second transmission mechanism 593, and the third pressing portion 571 connected to the second nut member 592 moves to the second axial side L2. As a result, the pressing of the fourth friction member 54 by the fourth pressing portion 572 is released, and the second clutch C2 is released.

[0080] As shown in FIG. 3, in this embodiment, the transmission 100 has a first forward gear, a second forward gear, and a reverse gear as gear stages. The transmission 100 also has a neutral state function and a parking lock function. FIG. 3 is an operation table showing the operation states of the first engagement device 4 (here, the first brake B1 and the first clutch C1) and the second engagement device 5 (here, the second clutch C2) according to the state of the transmission 100. In FIG. 3, "◯" indicates that the corresponding engagement device is in an engaged state, and "×" indicates that the corresponding engagement device is in a released state. In FIG. 3, "1st" indicates the first forward gear, "2nd" indicates the second forward gear, and "Rev" indicates the reverse gear. "N" indicates the neutral state, and "P" indicates the parking lock state.

[0081] As shown in Fig. 3, in this embodiment, when the first brake B1 is in a released state, the first clutch C1 is in a released state, and the second clutch C2 is in an engaged state, a first forward gear is formed in the transmission 100. When the first brake B1 is in an engaged state, the first clutch C1 is in a released state, and the second clutch C2 is in a released state, a second forward gear is formed in the transmission 100. When the first brake B1 is in a released state, the first clutch C1 is in an engaged state, and the second clutch C2 is in a released state, a reverse gear is formed in the transmission 100.

[0082] In this embodiment, when the first brake B1, the first clutch C1, and the second clutch C2 are all in a released state, the transmission 100 is in a neutral state in which the driving force of the driving force source D is not transmitted to the output member O. When the first brake B1 is in an engaged state, the first clutch C1 is in a released state, and the second clutch C2 is in an engaged state, the transmission 100 is in a parking lock state in which the rotation of the output member O is restricted. Note that the parking lock state is not limited to the above case, and can be realized by simultaneously establishing two or more gears. The same applies to each of the following embodiments.

[0083] Fig. 4 is a speed diagram of the planetary gear set 1 according to this embodiment. In the speed diagram of Fig. 4, the vertical lines correspond to the rotational speeds of the respective rotating elements of the planetary gear set 1. Moreover, the symbols shown above the vertical lines are the symbols of the corresponding rotating elements of the planetary gear set 1. And the symbols shown below the vertical lines are the symbols of the elements that are drivingly connected to the rotating elements corresponding to the symbols shown above. Also, a cross shown on a vertical line indicates that the corresponding brake is in an engaged state (a state in which the corresponding gear is fixed relative to a non-rotating member).

[0084] 4, in the first forward gear of this embodiment, the first reaction element 13 rotates in the reverse direction, and the rotation of the first input element 11 rotating in the forward direction is decelerated at a relatively large gear ratio and output from the first output element 12. In the second forward gear of this embodiment, the first reaction element 13 is fixed, and the rotation of the first input element 11 rotating in the forward direction is decelerated at a relatively small gear ratio and output from the first output element 12. In the reverse gear of this embodiment, the first reaction element 13 rotates in the reverse direction, and the rotation of the first input element 11 rotating in the forward direction is reversed and output from the first output element 12.

[0085] 2. Second embodiment A transmission 100 according to the second embodiment will be described below with reference to Figs. 5 to 7. In this embodiment, the configuration of the planetary gear device 1, the configuration of the second engagement device 5, and the target interlocking gear G are different from those of the first embodiment. In addition, in this embodiment, the transmission 100 does not include the input gear 62, the third interlocking gear 23, the fourth interlocking gear 24, the third transmission gear 33, and the fourth transmission gear 34, but includes a fifth transmission gear 35, which is different from that of the first embodiment. The following description will focus on the differences from the first embodiment. Note that points that are not particularly described are the same as those of the first embodiment.

[0086] 5, in this embodiment, the planetary gear device 1 further includes a second planetary gear mechanism P2 in addition to the first planetary gear mechanism P1. The second planetary gear mechanism P2 includes a second input element 14, a second output element 15, and a second reaction element 16. In this embodiment, the second planetary gear mechanism P2 is disposed on the first axis X1. The second planetary gear mechanism P2 is disposed adjacent to the first planetary gear mechanism P1 on a first axial side L1.

[0087] The second input element 14 is connected to the first input element 11 of the first planetary gear mechanism P1 so as to rotate integrally therewith.

[0088] The second output element 15 is connected to the first output element 12 of the first planetary gear mechanism P1 so as to rotate integrally therewith.

[0089] The second reaction element 16 is a ring gear different from the first reaction element 13 of the first planetary gear mechanism P1. In this embodiment, the second input element 14 is a sun gear. And the second output element 15 is a carrier. In this embodiment, the second output element 15 as a carrier supports a first pinion gear meshing with the second input element 14 as a sun gear, and a second pinion gear meshing with both the first pinion gear and the second reaction element 16 as a ring gear. That is, in this embodiment, the second planetary gear mechanism P2 is a double-pinion type planetary gear mechanism.

[0090] In this embodiment, the first planetary gear mechanism P1 is also a double pinion type planetary gear mechanism. Thus, in this embodiment, both the first planetary gear mechanism P1 and the second planetary gear mechanism P2 are double pinion type planetary gear mechanisms. Note that either the first planetary gear mechanism P1 or the second planetary gear mechanism P2 may be a planetary gear mechanism other than the double pinion type. In other words, it is preferable that at least one of the first planetary gear mechanism P1 and the second planetary gear mechanism P2 is a double pinion type planetary gear mechanism.

[0091] In this embodiment, the transmission 100 includes a second interlocking gear 22. The second interlocking gear 22 is an externally toothed gear that rotates integrally with the second reaction element 16 of the second planetary gear mechanism P2. In this embodiment, the second transmission gear 32 does not mesh with the first interlocking gear 21, but meshes with the second interlocking gear 22. In this manner, when the planetary gear device 1 includes the second reaction element 16, the second transmission gear 32 is configured to mesh with the externally toothed second interlocking gear 22 that rotates integrally with the second reaction element 16. As described above, the target interlocking gear G is the gear with which the second transmission gear 32 meshes, out of the first interlocking gear 21 and the second interlocking gear 22. Therefore, in this embodiment, the second interlocking gear 22 corresponds to the target interlocking gear G.

[0092] In this embodiment, the second interlocking gear 22 is meshed with the fifth transmission gear 35 in addition to the second transmission gear 32. The fifth transmission gear 35 is arranged coaxially with the first transmission gear 31. In this embodiment, the fifth transmission gear 35 is arranged on the second axis X2. The fifth transmission gear 35 is arranged on the first axial side L1 with respect to the first transmission gear 31.

[0093] In this embodiment, the fifth transmission gear 35 is connected to the second inner support member 45 of the first clutch C1 via the first connecting shaft 71 so as to rotate integrally with the second inner support member 45 of the first clutch C1. As described above, the first clutch C1 is configured to connect and disconnect the power transmission between the first transmission gear 31 and the first target rotating element T1. In this embodiment, the first clutch C1 is configured to connect and disconnect the power transmission between the first transmission gear 31 and the fifth transmission gear 35. In this embodiment, the first target rotating element T1 is the second reaction element 16.

[0094] In this embodiment, the first interlocking gear 21 and the second interlocking gear 22 are formed to have the same diameter. In addition, the first transmission gear 31 that meshes with the first interlocking gear 21 and the fifth transmission gear 35 that meshes with the second interlocking gear 22 are formed to have the same diameter.

[0095] In this embodiment, the second engagement device 5 does not include a second clutch C2, but includes a second brake B2. The second brake B2 is disposed coaxially with the second transmission gear 32. In this embodiment, the second brake B2 is disposed on the third axis X3. The second brake B2 is disposed on the second axial side L2 with respect to the second transmission gear 32.

[0096] The second brake B2 is configured to selectively fix the second transmission gear 32 to a non-rotating member (here, the case 9). The second brake B2 includes a third friction member 51, a third inner support member 52, and a third outer support member 53.

[0097] The third friction member 51 includes a third inner friction material 511 and a third outer friction material 512. The third inner friction material 511 and the third outer friction material 512 are arranged to face each other in the axial direction L. In this embodiment, the third inner friction material 511 and the third outer friction material 512 are provided in multiple sheets, which are arranged alternately along the axial direction L.

[0098] The third inner support member 52 supports the third inner friction material 511 so as to be non-rotatable in the circumferential direction and slidable in the axial direction L. In this embodiment, the third inner support member 52 is formed in a cylindrical shape with the third axis X3 as its axis. The third inner support member 52 supports the third inner friction material 511 from the inside in the radial direction R. In this example, a plurality of splines extending in the axial direction L are formed in a distributed manner in the circumferential direction on the outer periphery of the third inner support member 52. On the other hand, similar splines are also formed in a distributed manner in the circumferential direction on the inner periphery of the third inner friction material 511. These splines are engaged with each other.

[0099] In this embodiment, the third inner support member 52 is fixed to the case 9. In this embodiment, the third inner support member 52 is fixed to the second side wall portion 92 of the case 9.

[0100] The third outer support member 53 supports the third outer friction material 512 so that it cannot rotate relative to the third outer friction material 512 in the circumferential direction and can slide freely in the axial direction L. In this embodiment, the third outer support member 53 is formed in a cylindrical shape with the third axis X3 as its axis. The third outer support member 53 supports the third outer friction material 512 from the outside in the radial direction R. In this example, a plurality of splines extending in the axial direction L are formed in a distributed manner in the circumferential direction on the inner peripheral portion of the third outer support member 53. On the other hand, similar splines are also formed in a distributed manner in the circumferential direction on the outer peripheral portion of the third outer friction material 512. These splines are engaged with each other.

[0101] In this embodiment, the third outer support member 53 is connected to the second transmission gear 32 via a fifth connecting shaft 75 so as to rotate integrally with the second transmission gear 32. The fifth connecting shaft 75 is formed so as to extend along the axial direction L.

[0102] Although not shown in the drawings, in this embodiment, the second drive device D2 of the second engagement device 5 is configured to drive the second brake B2. In this embodiment, similar to the second clutch C2 in the first embodiment, the rotational drive force of the second drive motor 58 is converted into a drive force in the axial direction L by a screw-type second linear motion conversion mechanism 59 and transmitted to the second pressing member 57. In this manner, the second drive device D2 switches the second brake B2 between an engaged state and a released state.

[0103] As shown in Fig. 6, in this embodiment, the transmission 100 has a first forward gear, a second forward gear, and a reverse gear as gear stages. The transmission 100 also has a neutral state function and a parking lock function. Fig. 6 is an operation table showing the operation states of the first engagement device 4 (here, the first brake B1 and the first clutch C1) and the second engagement device 5 (here, the second brake B2) according to the state of the transmission 100. The description method of Fig. 6 is the same as that of Fig. 3, so a detailed description thereof will be omitted.

[0104] As shown in Fig. 6, in this embodiment, when the first brake B1 is engaged, the first clutch C1 is released, and the second brake B2 is released, the first forward gear is formed in the transmission 100. When the first brake B1 is released, the first clutch C1 is released, and the second brake B2 is engaged, the second forward gear is formed in the transmission 100. When the first brake B1 is released, the first clutch C1 is engaged, and the second brake B2 is released, the reverse gear is formed in the transmission 100.

[0105] In this embodiment, when the first brake B1, the first clutch C1, and the second brake B2 are all in a released state, the transmission 100 is in a neutral state. When the first brake B1 is in an engaged state, the first clutch C1 is in a released state, and the second brake B2 is in an engaged state, the transmission 100 is in a parking lock state.

[0106] Fig. 7 is a speed diagram of the planetary gear device 1 according to this embodiment. The description method of Fig. 7 is the same as that of Fig. 4, so a detailed description thereof will be omitted.

[0107] As shown in FIG. 7, in the first forward gear of this embodiment, the first reaction element 13 is fixed, and the rotation of the first input element 11, which rotates in the reverse direction, is changed in speed by the first planetary gear mechanism P1 and reversed, and is output from the first output element 12. In the second forward gear of this embodiment, the second reaction element 16 is fixed, and the rotation of the second input element 14, which rotates in the reverse direction, is changed in speed by the second planetary gear mechanism P2 and reversed, and is output from the second output element 15. As described above, in this embodiment, since both the first planetary gear mechanism P1 and the second planetary gear mechanism P2 are double pinion type planetary gear mechanisms, it is easy to reduce the gear ratio of the planetary gear device 1. In addition, in the reverse gear of this embodiment, the rotation of the first input element 11 and the second input element 14, which rotates in the reverse direction, is output from the first output element 12 and the second output element 15 as it is.

[0108] 3. Third embodiment A transmission 100 according to the third embodiment will be described below with reference to Figs. 8 to 10. In this embodiment, the configuration of the planetary gear device 1, the configuration of the second engagement device 5, and the target interlocking gear G are different from those of the first embodiment. In addition, this embodiment differs from the first embodiment in that the transmission 100 does not include the input gear 62, the fourth interlocking gear 24, and the fourth transmission gear 34, but includes a sixth transmission gear 36. The following description will focus on the differences from the first embodiment. Note that points that are not particularly described are the same as those of the first embodiment.

[0109] 8, in this embodiment, the third interlocking gear 23 is disposed on the first axis X1. The third interlocking gear 23 is connected to the input shaft 61 so as to rotate integrally with the input shaft 61.

[0110] In this embodiment, the planetary gear device 1 further includes a second planetary gear mechanism P2 in addition to the first planetary gear mechanism P1, as in the second embodiment. In this embodiment, the second planetary gear mechanism P2 is disposed on the first axis X1. The second planetary gear mechanism P2 is disposed adjacent to the first planetary gear mechanism P1 on a second axial side L2. In this embodiment, both the first planetary gear mechanism P1 and the second planetary gear mechanism P2 are double-pinion type planetary gear mechanisms.

[0111] In this embodiment, the second engagement device 5 further includes a second brake B2 in addition to the second clutch C2. In this embodiment, the second brake B2 and the second clutch C2 are disposed on the third axis X3. The second brake B2 is disposed on the second axial side L2 with respect to the second clutch C2.

[0112] Although not shown in the drawings, in this embodiment, the second drive device D2 of the second engagement device 5 is configured to drive the second brake B2 and the second clutch C2. In this embodiment, the second engagement device 5 is configured to selectively put either the second brake B2 or the second clutch C2 into an engaged state, similar to the first engagement device 4. Note that in this embodiment, the second engagement device 5 is also capable of putting both the second brake B2 and the second clutch C2 into a released state.

[0113] In this embodiment, the transmission 100 includes a second interlocking gear 22. In this embodiment, the second interlocking gear 22 corresponds to the target interlocking gear G. That is, in this embodiment, the second transmission gear 32 does not mesh with the first interlocking gear 21, but meshes with the second interlocking gear 22.

[0114] In this embodiment, the first interlocking gear 21 meshes with the sixth transmission gear 36 in addition to the first transmission gear 31. The sixth transmission gear 36 is disposed coaxially with the second transmission gear 32. In this embodiment, the sixth transmission gear 36 is disposed on the third axis X3. The sixth transmission gear 36 is disposed on the first axial side L1 with respect to the second transmission gear 32.

[0115] In this embodiment, the sixth transmission gear 36 is connected to the fourth inner support member 55 of the second clutch C2 via a sixth connecting shaft 76 so as to rotate integrally with the fourth inner support member 55 of the second clutch C2. The sixth connecting shaft 76 is formed to extend along the axial direction L. In this embodiment, instead of the third connecting shaft 73, the sixth connecting shaft 76 is disposed on the inside in the radial direction R with respect to the fourth connecting shaft 74 so as to penetrate the cylindrical fourth connecting shaft 74 in the axial direction L.

[0116] As described above, the second clutch C2 is configured to connect and disconnect the power transmission between the second transmission gear 32 and the second target rotating element T2. In this embodiment, the second clutch C2 is configured to connect and disconnect the power transmission between the second transmission gear 32 and the sixth transmission gear 36. In this embodiment, the second target rotating element T2 is the first reaction element 13.

[0117] In this embodiment, the first interlocking gear 21 and the second interlocking gear 22 are formed to have the same diameter. In addition, the sixth transmission gear 36 that meshes with the first interlocking gear 21 and the second transmission gear 32 that meshes with the second interlocking gear 22 are formed to have the same diameter.

[0118] As shown in Fig. 9, in this embodiment, the transmission 100 has a first forward gear, a second forward gear, a third forward gear, and a reverse gear as gear stages. The transmission 100 also has a neutral state function and a parking lock function. Fig. 9 is an operation table showing the operation states of the first engagement device 4 (here, the first brake B1 and the first clutch C1) and the second engagement device 5 (here, the second brake B2 and the second clutch C2) according to the state of the transmission 100. The notation in Fig. 9 is the same as that in Fig. 3 except that "3rd" indicates the third forward gear, and therefore a detailed description thereof will be omitted.

[0119] As shown in FIG. 9, in this embodiment, the first forward gear is formed in the transmission 100 when the first brake B1 is in the released state, the first clutch C1 is in the engaged state, the second brake B2 is in the released state, and the second clutch C2 is in the released state. Also, the second forward gear is formed in the transmission 100 when the first brake B1 is in the released state, the first clutch C1 is in the released state, the second brake B2 is in the engaged state, and the second clutch C2 is in the released state. Also, the third forward gear is formed in the transmission 100 when the first brake B1 is in the engaged state, the first clutch C1 is in the released state, the second brake B2 is in the released state, and the second clutch C2 is in the released state. Also, the reverse gear is formed in the transmission 100 when the first brake B1 is in the released state, the first clutch C1 is in the released state, the second brake B2 is in the released state, and the second clutch C2 is in the engaged state.

[0120] In this embodiment, when the first brake B1, the first clutch C1, the second brake B2, and the second clutch C2 are all in a released state, the transmission 100 is in a neutral state. When the first brake B1 is in an engaged state, the first clutch C1 is in a released state, the second brake B2 is in an engaged state, and the second clutch C2 is in a released state, the transmission 100 is in a parking lock state.

[0121] Fig. 10 is a speed diagram of the planetary gear device 1 according to this embodiment. The description method of Fig. 10 is the same as that of Fig. 4, so a detailed description thereof will be omitted.

[0122] As shown in FIG. 10, in the first forward gear of this embodiment, the first reaction element 13 and the second reaction element 16 rotate in the reverse direction, and the rotations of the first input element 11 and the second input element 14 that rotate in the reverse direction are reversed and output from the first output element 12 and the second output element 15. In the second forward gear of this embodiment, the second reaction element 16 is fixed, and the rotation of the second input element 14 that rotates in the reverse direction is shifted and reversed by the second planetary gear mechanism P2, and output from the second output element 15. In the third forward gear of this embodiment, the first reaction element 13 is fixed, and the rotation of the first input element 11 that rotates in the reverse direction is shifted and reversed by the first planetary gear mechanism P1, and output from the first output element 12. As described above, in this embodiment, since both the first planetary gear mechanism P1 and the second planetary gear mechanism P2 are double pinion type planetary gear mechanisms, it is easy to reduce the gear ratio of the planetary gear device 1. In the reverse gear of this embodiment, the rotations of the first input element 11 and the second input element 14 which rotate in the reverse direction are outputted from the first output element 12 and the second output element 15 as they are.

[0123] 4. Fourth embodiment A transmission 100 according to a fourth embodiment will be described below with reference to Figs. 11 to 13. In this embodiment, the configuration of the planetary gear device 1, the configuration of the second engagement device 5, and the target interlocking gear G are different from those of the first embodiment. In addition, this embodiment is different from that of the first embodiment in that the transmission 100 does not include the fourth interlocking gear 24 and the fourth transmission gear 34. The following description will focus on the differences from the first embodiment. Note that points that are not particularly described are the same as those of the first embodiment.

[0124] 11, in this embodiment, the planetary gear device 1 further includes a second planetary gear mechanism P2 in addition to the first planetary gear mechanism P1, as in the third embodiment. In this embodiment, the second planetary gear mechanism P2 is disposed on the first axis X1. The second planetary gear mechanism P2 is disposed adjacent to the first planetary gear mechanism P1 on a second axial side L2. In this embodiment, the first planetary gear mechanism P1 is a single-pinion type planetary gear mechanism, and the second planetary gear mechanism P2 is a double-pinion type planetary gear mechanism.

[0125] In this embodiment, the second engagement device 5 does not include a second clutch C2, but includes a second brake B2. The second brake B2 is disposed coaxially with the second transmission gear 32. In this embodiment, the second brake B2 is disposed on the third axis X3. The second brake B2 is disposed on the second axial side L2 with respect to the second transmission gear 32.

[0126] In this embodiment, the transmission 100 includes a second interlocking gear 22. In this embodiment, the second interlocking gear 22 corresponds to the target interlocking gear G. That is, in this embodiment, the second transmission gear 32 does not mesh with the first interlocking gear 21, but meshes with the second interlocking gear 22.

[0127] As shown in Fig. 12, in this embodiment, the transmission 100 has a first forward gear, a second forward gear, and a reverse gear as gear stages. The transmission 100 also has a neutral state function and a parking lock function. Fig. 12 is an operation table showing the operation states of the first engagement device 4 (here, the first brake B1 and the first clutch C1) and the second engagement device 5 (here, the second brake B2) according to the state of the transmission 100. The description method of Fig. 12 is the same as that of Fig. 3, so a detailed description thereof will be omitted.

[0128] 12, in this embodiment, when the first brake B1 is in a released state, the first clutch C1 is in an engaged state, and the second brake B2 is in a released state, a first forward gear is formed in the transmission 100. When the first brake B1 is in an engaged state, the first clutch C1 is in a released state, and the second brake B2 is in a released state, a second forward gear is formed in the transmission 100. When the first brake B1 is in a released state, the first clutch C1 is in a released state, and the second brake B2 is in an engaged state, a reverse gear is formed in the transmission 100.

[0129] In this embodiment, when the first brake B1, the first clutch C1, and the second brake B2 are all in a released state, the transmission 100 is in a neutral state. When the first brake B1 is in an engaged state, the first clutch C1 is in a released state, and the second brake B2 is in an engaged state, the transmission 100 is in a parking lock state.

[0130] Fig. 13 is a speed diagram of the planetary gear device 1 according to this embodiment. The description method of Fig. 13 is the same as that of Fig. 4, so a detailed description thereof will be omitted.

[0131] 13, in the first forward gear of this embodiment, the first reaction element 13 rotates in the reverse direction and the second reaction element 16 rotates in the forward direction, and the rotations of the first input element 11 and the second input element 14 which rotate in the forward direction are decelerated and output from the first output element 12 and the second output element 15. In the second forward gear of this embodiment, the first reaction element 13 is fixed and the rotation of the first input element 11 which rotates in the forward direction is decelerated by the first planetary gear mechanism P1 and output from the first output element 12. In the reverse gear of this embodiment, the second reaction element 16 is fixed and the rotation of the second input element 14 which rotates in the forward direction is reversed by the second planetary gear mechanism P2 and output from the second output element 15.

[0132] In this embodiment, the second reaction element 16 is located between the second input element 14 and the second output element 15 on the speed diagram. Since the second reaction element 16 is fixed, it is easy to reverse the rotation of the second input element 14 and transmit it to the second output element 15. Therefore, in this embodiment, it is easy to set the reverse gear.

[0133] 5. Fifth embodiment A transmission 100 according to the fifth embodiment will be described below with reference to Figs. 14 to 16. In this embodiment, the configuration of the second engagement device 5 is different from that of the fourth embodiment. Also, in this embodiment, the transmission 100 is different from that of the fourth embodiment in that it includes a sixth transmission gear 36. The following description will focus on the differences from the fourth embodiment. Note that points that are not particularly described are the same as those of the fourth embodiment.

[0134] 14, in this embodiment, the first interlocking gear 21 meshes with the sixth transmission gear 36 in addition to the first transmission gear 31. The sixth transmission gear 36 is disposed coaxially with the second transmission gear 32. In this embodiment, the sixth transmission gear 36 is disposed on the third axis X3. The sixth transmission gear 36 is disposed on the first axial side L1 with respect to the second transmission gear 32.

[0135] In this embodiment, the second engagement device 5 further includes a second clutch C2 in addition to the second brake B2. In this embodiment, the second brake B2 and the second clutch C2 are disposed on the third axis X3. The second brake B2 is disposed on the second axial side L2 with respect to the second clutch C2.

[0136] Although not shown in the drawings, in this embodiment, the second drive device D2 of the second engagement device 5 is configured to drive the second brake B2 and the second clutch C2. In this embodiment, the second engagement device 5 is configured to selectively put either the second brake B2 or the second clutch C2 into an engaged state, similar to the first engagement device 4. Note that in this embodiment, the second engagement device 5 is also capable of putting both the second brake B2 and the second clutch C2 into a released state.

[0137] In this embodiment, the third outer support member 53 of the second brake B2 and the fourth outer support member 56 of the second clutch C2 are connected to each other so as to rotate integrally. The third outer support member 53 and the fourth outer support member 56 are connected to the second transmission gear 32 via a fourth connecting shaft 74 so as to rotate integrally with each other.

[0138] In this embodiment, the fourth inner support member 55 of the second clutch C2 is connected to the sixth transmission gear 36 via a sixth connecting shaft 76 so as to rotate integrally with the sixth transmission gear 36. The sixth connecting shaft 76 is disposed on the inside in the radial direction R with respect to the fourth connecting shaft 74 so as to penetrate the cylindrical fourth connecting shaft 74 in the axial direction L.

[0139] As described above, the second clutch C2 is configured to connect and disconnect the power transmission between the second transmission gear 32 and the second target rotating element T2. In this embodiment, the second clutch C2 is configured to connect and disconnect the power transmission between the second transmission gear 32 and the sixth transmission gear 36. In this embodiment, the second target rotating element T2 is the first reaction element 13.

[0140] In this embodiment, the first interlocking gear 21 and the second interlocking gear 22 are formed to have the same diameter. In addition, the sixth transmission gear 36 that meshes with the first interlocking gear 21 and the second transmission gear 32 that meshes with the second interlocking gear 22 are formed to have the same diameter.

[0141] As shown in Fig. 15, in this embodiment, the transmission 100 has a first forward gear, a second forward gear, a third forward gear, and a reverse gear as gear stages. The transmission 100 also has a neutral state function and a parking lock function. Fig. 15 is an operation table showing the operation states of the first engagement device 4 (here, the first brake B1 and the first clutch C1) and the second engagement device 5 (here, the second brake B2 and the second clutch C2) according to the state of the transmission 100. The notation in Fig. 15 is the same as that in Fig. 12 except that "3rd" indicates the third forward gear, and therefore a detailed description thereof will be omitted.

[0142] As shown in FIG. 15, in this embodiment, the first forward gear is formed in the transmission 100 when the first brake B1 is in the released state, the first clutch C1 is in the engaged state, the second brake B2 is in the released state, and the second clutch C2 is in the released state. Also, the second forward gear is formed in the transmission 100 when the first brake B1 is in the engaged state, the first clutch C1 is in the released state, the second brake B2 is in the released state, and the second clutch C2 is in the released state. Also, the third forward gear is formed in the transmission 100 when the first brake B1 is in the released state, the first clutch C1 is in the released state, the second brake B2 is in the released state, and the second clutch C2 is in the engaged state. Also, the reverse gear is formed in the transmission 100 when the first brake B1 is in the released state, the first clutch C1 is in the released state, the second brake B2 is in the engaged state, and the second clutch C2 is in the released state.

[0143] In this embodiment, when the first brake B1, the first clutch C1, the second brake B2, and the second clutch C2 are all in a released state, the transmission 100 is in a neutral state. When the first brake B1 is in an engaged state, the first clutch C1 is in a released state, the second brake B2 is in an engaged state, and the second clutch C2 is in a released state, the transmission 100 is in a parking lock state.

[0144] Fig. 16 is a speed diagram of the planetary gear device 1 according to this embodiment. The description method of Fig. 16 is the same as that of Fig. 13, so a detailed description thereof will be omitted.

[0145] 16, the first forward gear, the second forward gear, and the reverse gear of this embodiment are similar to those of the above-mentioned fourth embodiment, and therefore their description will be omitted. In the third forward gear of this embodiment, the rotation of the first input element 11 and the second input element 14, which rotate forward, is output as it is from the first output element 12 and the second output element 15.

[0146] 6. Sixth embodiment A transmission 100 according to the sixth embodiment will be described below with reference to Figs. 17 to 19. In this embodiment, the configuration of the planetary gear device 1 is different from that of the fifth embodiment. The following description will focus on the differences from the fifth embodiment. Note that points that are not particularly described are the same as those in the fifth embodiment.

[0147] 17, in this embodiment, the planetary gear device 1 includes a third planetary gear mechanism P3 instead of the first planetary gear mechanism P1 and the second planetary gear mechanism P2. The third planetary gear mechanism P3 is disposed on the first axis X1. The third planetary gear mechanism P3 includes a first input element 11, a first output element 12, a first reaction element 13, and a second reaction element 16.

[0148] In this embodiment, the first output element 12 is a carrier that supports a first pinion gear 12a and a second pinion gear 12b that are connected to rotate integrally with each other.

[0149] The first pinion gear 12a meshes with the first reaction element 13 serving as a ring gear. In this embodiment, the first pinion gear 12a also meshes with the first input element 11 serving as a sun gear. The second pinion gear 12b meshes with the second reaction element 16 serving as a ring gear. In this embodiment, the second pinion gear 12b is formed to have a smaller diameter than the first pinion gear 12a. The second pinion gear 12b is disposed on the second axial side L2 with respect to the first pinion gear 12a.

[0150] As shown in Fig. 18, in this embodiment, the transmission 100 has a first forward gear, a second forward gear, a third forward gear, and a fourth forward gear as gear stages. The transmission 100 also has a neutral state function and a parking lock function. Note that Fig. 18 is an operation table showing the operation states of the first engagement device 4 (here, the first brake B1 and the first clutch C1) and the second engagement device 5 (here, the second brake B2 and the second clutch C2) according to the state of the transmission 100. The notation in Fig. 18 is the same as that in Fig. 15 except that "4th" indicates the fourth forward gear, and therefore a detailed description thereof will be omitted.

[0151] As shown in FIG. 18, in this embodiment, the first forward gear is formed in the transmission 100 when the first brake B1 is in the released state, the first clutch C1 is in the engaged state, the second brake B2 is in the released state, and the second clutch C2 is in the released state. Also, the second forward gear is formed in the transmission 100 when the first brake B1 is in the released state, the first clutch C1 is in the released state, the second brake B2 is in the engaged state, and the second clutch C2 is in the released state. Also, the third forward gear is formed in the transmission 100 when the first brake B1 is in the engaged state, the first clutch C1 is in the released state, the second brake B2 is in the released state, and the second clutch C2 is in the released state. Also, the fourth forward gear is formed in the transmission 100 when the first brake B1 is in the released state, the first clutch C1 is in the released state, the second brake B2 is in the released state, and the second clutch C2 is in the engaged state.

[0152] In this embodiment, when the first brake B1, the first clutch C1, the second brake B2, and the second clutch C2 are all in a released state, the transmission 100 is in a neutral state. When the first brake B1 is in an engaged state, the first clutch C1 is in a released state, the second brake B2 is in an engaged state, and the second clutch C2 is in a released state, the transmission 100 is in a parking lock state.

[0153] Fig. 19 is a speed diagram of the planetary gear device 1 according to this embodiment. The description method of Fig. 19 is the same as that of Fig. 16, so a detailed description thereof will be omitted.

[0154] As shown in FIG. 19, in the first forward stage of this embodiment, the first reaction element 13 and the second reaction element 16 rotate in the reverse direction, and the rotation of the first input element 11 rotating in the forward direction is decelerated and output from the first output element 12. In the second forward stage of this embodiment, the second reaction element 16 is fixed, and the rotation of the first input element 11 rotating in the forward direction is decelerated and output from the first output element 12. In the third forward stage of this embodiment, the first reaction element 13 is fixed, and the rotation of the first input element 11 rotating in the forward direction is decelerated and output from the first output element 12. In the fourth forward stage of this embodiment, the rotation of the first input element 11 rotating in the forward direction is output from the first output element 12 as it is.

[0155] 7. Seventh embodiment A transmission 100 according to the seventh embodiment will be described below with reference to Figs. 20 to 22. In this embodiment, the configuration of the planetary gear device 1 is different from that of the sixth embodiment. Also, this embodiment differs from the sixth embodiment in that the transmission 100 does not include a sixth transmission gear 36, but includes a fourth interlocking gear 24 and a fourth transmission gear 34. The following description will focus on the differences from the sixth embodiment. Note that points that are not particularly described are the same as those of the sixth embodiment.

[0156] 20, in this embodiment, instead of the first pinion gear 12a, a second pinion gear 12b also meshes with the first input element 11 serving as a sun gear. In this embodiment, the second pinion gear 12b is formed to have a larger diameter than the first pinion gear 12a. The second pinion gear 12b is disposed on the first axial side L1 with respect to the first pinion gear 12a.

[0157] As described above, the second clutch C2 is configured to connect and disconnect the power transmission between the second transmission gear 32 and the second target rotating element T2. In this embodiment, the second clutch C2 is configured to connect and disconnect the power transmission between the second transmission gear 32 and the fourth transmission gear 34. In this embodiment, the second target rotating element T2 is the first input element 11.

[0158] As shown in Fig. 21, in this embodiment, the transmission 100 has a first forward gear, a second forward gear, a third forward gear, and a reverse gear as gear stages. The transmission 100 also has a neutral state function and a parking lock function. Note that Fig. 21 is an operation table showing the operation states of the first engagement device 4 (here, the first brake B1 and the first clutch C1) and the second engagement device 5 (here, the second brake B2 and the second clutch C2) according to the state of the transmission 100. The description method of Fig. 21 is the same as that of Fig. 18, so a detailed description thereof will be omitted.

[0159] As shown in FIG. 21, in this embodiment, the first forward gear is formed in the transmission 100 when the first brake B1 is in the released state, the first clutch C1 is in the released state, the second brake B2 is in the released state, and the second clutch C2 is in the engaged state. Also, the second forward gear is formed in the transmission 100 when the first brake B1 is in the engaged state, the first clutch C1 is in the released state, the second brake B2 is in the released state, and the second clutch C2 is in the released state. Also, the third forward gear is formed in the transmission 100 when the first brake B1 is in the released state, the first clutch C1 is in the released state, the second brake B2 is in the engaged state, and the second clutch C2 is in the released state. Also, the reverse gear is formed in the transmission 100 when the first brake B1 is in the released state, the first clutch C1 is in the engaged state, the second brake B2 is in the released state, and the second clutch C2 is in the released state.

[0160] In this embodiment, when the first brake B1, the first clutch C1, the second brake B2, and the second clutch C2 are all in a released state, the transmission 100 is in a neutral state. When the first brake B1 is in an engaged state, the first clutch C1 is in a released state, the second brake B2 is in an engaged state, and the second clutch C2 is in a released state, the transmission 100 is in a parking lock state.

[0161] Fig. 22 is a speed diagram of the planetary gear device 1 according to this embodiment. The description method of Fig. 22 is the same as that of Fig. 19, so a detailed description thereof will be omitted.

[0162] As shown in FIG. 22, in the first forward gear of this embodiment, the first reaction element 13 and the second reaction element 16 rotate in the reverse direction, and the rotation of the first input element 11 rotating in the forward direction is decelerated and output from the first output element 12. In the second forward gear of this embodiment, the first reaction element 13 is fixed, and the rotation of the first input element 11 rotating in the forward direction is decelerated and output from the first output element 12. In the third forward gear of this embodiment, the second reaction element 16 is fixed, and the rotation of the first input element 11 rotating in the forward direction is decelerated and output from the first output element 12. In the reverse gear of this embodiment, the first reaction element 13 and the second reaction element 16 rotate in the reverse direction, and the rotation of the first input element 11 rotating in the forward direction is reversed and output from the first output element 12.

[0163] 8. Eighth embodiment A transmission 100 according to the eighth embodiment will be described below with reference to FIG. 23. In this embodiment, the connection target of the input shaft 61 is different from that of the seventh embodiment. The following description will focus on the differences from the seventh embodiment. Note that points that are not particularly described are the same as those of the seventh embodiment.

[0164] As shown in FIG. 23, in this embodiment, an input shaft 61 is connected to a fourth interlocking gear 24 instead of an input gear 62 so as to rotate integrally therewith.

[0165] In addition, since the operation table of the first engagement device 4 and the second engagement device 5 and the speed diagram of the planetary gear device 1 in this embodiment are the same as those in the seventh embodiment, the description thereof will be omitted.

[0166] 9. Ninth embodiment A transmission 100 according to a ninth embodiment will be described below with reference to Figs. 24 to 26. In this embodiment, the configuration of the planetary gear device 1 is different from that of the second embodiment. The following description will focus on the differences from the second embodiment. Note that points that are not particularly described are the same as those in the second embodiment.

[0167] As shown in FIG. 24, in this embodiment, the first planetary gear mechanism P1 is a double-pinion type planetary gear mechanism, and the second planetary gear mechanism P2 is a single-pinion type planetary gear mechanism.

[0168] As shown in Fig. 25, in this embodiment, the transmission 100 has a first forward gear, a second forward gear, and a reverse gear as gear stages. The transmission 100 also has a neutral state function and a parking lock function. Note that Fig. 25 is an operation table showing the operation states of the first engagement device 4 (here, the first brake B1 and the first clutch C1) and the second engagement device 5 (here, the second brake B2) according to the state of the transmission 100. The description method of Fig. 25 is the same as that of Fig. 6, so a detailed description thereof will be omitted.

[0169] As shown in Fig. 25, in this embodiment, when the first brake B1 is released, the first clutch C1 is released, and the second brake B2 is engaged, a first forward gear is formed in the transmission 100. When the first brake B1 is released, the first clutch C1 is engaged, and the second brake B2 is released, a second forward gear is formed in the transmission 100. When the first brake B1 is engaged, the first clutch C1 is released, and the second brake B2 is released, a reverse gear is formed in the transmission 100.

[0170] In this embodiment, when the first brake B1, the first clutch C1, and the second brake B2 are all in a released state, the transmission 100 is in a neutral state. When the first brake B1 is in an engaged state, the first clutch C1 is in a released state, and the second brake B2 is in an engaged state, the transmission 100 is in a parking lock state.

[0171] Fig. 26 is a speed diagram of the planetary gear device 1 according to this embodiment. The description method of Fig. 26 is the same as that of Fig. 7, so a detailed description thereof will be omitted.

[0172] 26, in the first forward gear of this embodiment, the second reaction element 16 is fixed, and the rotation of the second input element 14 rotating in the forward direction is decelerated by the second planetary gear mechanism P2 and output from the second output element 15. In the second forward gear of this embodiment, the rotation of the first input element 11 and the second input element 14 rotating in the forward direction is output as is from the first output element 12 and the second output element 15. In the reverse gear of this embodiment, the first reaction element 13 is fixed, and the rotation of the first input element 11 rotating in the forward direction is reversed by the first planetary gear mechanism P1 and output from the first output element 12.

[0173] In addition, the configurations disclosed in each of the above-mentioned embodiments can be applied in combination with configurations disclosed in other embodiments as long as no contradiction occurs. Regarding other configurations, the embodiments disclosed in this specification are merely examples in all respects. Therefore, various modifications can be made as appropriate within the scope of the present disclosure.

[0174] 10. Summary of this embodiment The above-described transmission (100) will now be outlined.

[0175] The transmission (100) is A planetary gear set (1) including at least three rotating elements including a first input element (11) drivingly connected to a driving force source (D), a first output element (12) drivingly connected to an output member (O), and a first reaction element (13) that is a ring gear; a first interlocking gear (21) having external teeth that rotates integrally with the first reaction element (13); a first transmission gear (31) meshing with the first interlocking gear (21); A second transmission gear (32); A first engagement device (4), A second engagement device (5), the second transmission gear (32) is configured to mesh with the first interlocking gear (21), or, in a case where the planetary gear set (1) includes a second reaction element (16) which is a ring gear different from the first reaction element (13), to mesh with a second interlocking gear (22) having external teeth and which rotates integrally with the second reaction element (16); The first engagement device (4) is a first brake (B1) arranged coaxially with the first transmission gear (31) and selectively fixing the first transmission gear (31) to a non-rotating member (9); a first clutch (C1) that is disposed coaxially with the first transmission gear (31) and that connects and disconnects power transmission between the first transmission gear (31) and a first target rotating element (T1) that is one of the rotating elements other than the first reaction element (13) in the planetary gear set (1), The second engagement device (5) is a second brake (B2) arranged coaxially with the second transmission gear (32) and selectively fixing the second transmission gear (32) to the non-rotating member (9); The planetary gear set (1) is provided with at least one of a second clutch (C2) which is arranged coaxially with the second transmission gear (32), and which defines the first interlocking gear (21) and the second interlocking gear (22) as the target interlocking gear (G) and which disconnects the power transmission between the second transmission gear (32) and a second target rotating element (T2), which is one of the rotating elements other than the rotating element that rotates integrally with the target interlocking gear (G) in the planetary gear set (1).

[0176] According to this configuration, two gears can be formed by switching the engagement state of the first engagement device (4), and one or two gears can be formed by switching the engagement state of the second engagement device (5). In addition, by controlling the engagement states of both the first engagement device (4) and the second engagement device (5), a neutral state in which no power is transmitted between the first input element (11) and the first output element (12) and a rotation restricted state in which the rotation of the first output element (12) is restricted can also be realized. Therefore, according to this configuration, it is possible to realize a transmission (100) having three or four gears, a neutral state function, and a parking lock function. Furthermore, according to this configuration, the first transmission gear (31) meshes with the first interlocking gear (21) having external teeth that rotates integrally with the first reaction element (13) that is a ring gear, and the first brake (B1) and the first clutch (C1) of the first engagement device (4) are arranged coaxially with the first transmission gear (31). This makes it easier to reduce the diameter of the first engagement device (4) compared to a configuration in which the first brake (B1) and the first clutch (C1) are arranged coaxially with the first reaction element (13). The same applies to the second engagement device (5). This makes it easier to reduce the size of the transmission (100).

[0177] Here, a third interlocking gear (23) that rotates in conjunction with the first input element (11); a third transmission gear (33) that is arranged coaxially with the first transmission gear (31) and meshes with the third interlocking gear (23), the first symmetric rotating element (T1) is the first input element (11); It is preferable that the first clutch (C1) is configured to connect and disconnect power transmission between the first transmission gear (31) and the third transmission gear (33).

[0178] According to this configuration, the first brake (B1) and the first clutch (C1) can be easily disposed coaxially. In addition, according to this configuration, by appropriately setting the gear ratio between the first transmission gear (31) and the first interlocking gear (21), and the gear ratio between the third transmission gear (33) and the third interlocking gear (23), it is easy to optimize the step ratios of the multiple gear stages.

[0179] In addition, the planetary gear device (1) a first planetary gear mechanism (P1) including the first input element (11) which is a sun gear, the first output element (12) which is a carrier, and the first reaction element (13); a second planetary gear mechanism (P2) including a second input element (14) which is a sun gear, a second output element (15) which is a carrier, and the second reaction element (16), The first input element (11) and the second input element (14) are connected to each other so as to rotate together. the first output element (12) and the second output element (15) are connected so as to rotate integrally, At least one of the first planetary gear mechanism (P1) and the second planetary gear mechanism (P2) is preferably a double-pinion type planetary gear mechanism.

[0180] According to this configuration, since the planetary gear device (1) includes the first planetary gear mechanism (P1) and the second planetary gear mechanism (P2), it is easy to optimize the step ratios of the multiple gear stages. Furthermore, according to this configuration, at least one of the first planetary gear mechanism (P1) and the second planetary gear mechanism (P2) is a double-pinion type planetary gear mechanism, so that one of the multiple gear stages can be easily set as a reverse stage.

[0181] In addition, the direction along the rotation axis of the first transmission gear (31) is defined as an axial direction (L), and the direction perpendicular to the rotation axis is defined as a radial direction (R), The first brake (B1) includes a first friction member (41), The first clutch (C1) includes a second friction member (44), the first engagement device (4) further includes a drive device (D1) that drives the first brake (B1) and the first clutch (C1); the drive device (D1) includes a pressing member (47) that presses the first friction member (41) and the second friction member (44) in the axial direction (L), a drive motor (48), and a screw-type linear motion conversion mechanism (49) that converts a rotational driving force of the drive motor (48) into a driving force in the axial direction (L) and transmits the driving force to the pressing member (47); It is preferable that the linear motion conversion mechanism (49) is arranged on the inside of the first friction member (41) and the second friction member (44) in the radial direction (R) and at a position overlapping with at least one of the first friction member (41) and the second friction member (44) when viewed in the radial direction along the radial direction (R).

[0182] According to this configuration, the linear motion conversion mechanism (49) of the drive device (D1) is disposed in the space radially inside (R) of the first friction member (41) of the first brake (B1) and the second friction member (44) of the first clutch (C1). This makes it easier to reduce the size of the first engagement device (4) including the drive device (D1), and therefore makes it easier to reduce the size of the transmission (100). According to this configuration, the pressing member (47) is moved in the axial direction (L) by the screw-type linear motion conversion mechanism (49). This makes it possible to hold the position of the pressing member (47) even when no driving force is being generated by the drive motor (48). Therefore, the first brake (B1) and the first clutch (C1) can be maintained in an engaged state even when no power is being supplied to the drive motor (48). [Industrial Applicability]

[0183] The technology disclosed herein can be used in a transmission having a plurality of gear stages. [Explanation of symbols]

[0184] 100: transmission, 1: planetary gear device, P1: first planetary gear mechanism, 11: first input element, 12: first output element, 13: first reaction element, P2: second planetary gear mechanism, 14: second input element, 15: second output element, 16: second reaction element, 21: first interlocking gear, 22: second interlocking gear, 23: third interlocking gear, 31: first transmission gear, 32: second transmission gear, 33: third transmission gear, 4: first engagement device, B1: First brake, 41: first friction member, C1: first clutch, 44: second friction member, D1: first drive device (drive device), 47: first pressing member (pressing member), 48: first drive motor (drive motor), 49: first linear motion conversion mechanism (linear motion conversion mechanism), 5: second engagement device, B2: second brake, C2: second clutch, 9: case (non-rotating member), D: drive force source, O: output member, L: axial direction, R: radial direction

Claims

1. a planetary gear device including at least three rotating elements including a first input element drivingly connected to a driving force source, a first output element drivingly connected to an output member, and a first reaction element that is a ring gear; a first interlocking gear having external teeth that rotates integrally with the first reaction element; a first transmission gear that meshes with the first interlocking gear; A second transmission gear; A first engagement device; a second engagement device, the second transmission gear is configured to mesh with the first interlocking gear, or, when the planetary gear set includes a second reaction element that is a ring gear different from the first reaction element, to mesh with a second interlocking gear having external teeth that rotates integrally with the second reaction element; The first engagement device is a first brake arranged coaxially with the first transmission gear and configured to selectively fix the first transmission gear to a non-rotating member; a first clutch that is arranged coaxially with the first transmission gear and that connects and disconnects power transmission between the first transmission gear and a first target rotating element that is one of the rotating elements other than the first reaction element in the planetary gear device, The second engagement device is a second brake arranged coaxially with the second transmission gear and configured to selectively fix the second transmission gear to the non-rotating member; a second clutch that is arranged coaxially with the second transmission gear, with the first interlocking gear and the second interlocking gear being the target interlocking gear that meshes with the second transmission gear, and that connects and disconnects the power transmission between the second transmission gear and a second target rotating element, which is one of the rotating elements other than the rotating element that rotates integrally with the target interlocking gear in the planetary gear device.

2. a third interlocking gear that rotates in conjunction with the first input element; a third transmission gear arranged coaxially with the first transmission gear and meshing with the third interlocking gear, the first symmetric rotation element is the first input element, The transmission according to claim 1 , wherein the first clutch is configured to connect and disconnect power transmission between the first transmission gear and the third transmission gear.

3. The planetary gear device is a first planetary gear mechanism including the first input element which is a sun gear, the first output element which is a carrier, and the first reaction element; a second planetary gear mechanism including a second input element which is a sun gear, a second output element which is a carrier, and the second reaction element; the first input element and the second input element are connected to each other so as to rotate together; the first output element and the second output element are connected to each other so as to rotate together; 3. The transmission according to claim 1, wherein at least one of the first planetary gear mechanism and the second planetary gear mechanism is a double-pinion type planetary gear mechanism.

4. A direction along a rotation axis of the first transmission gear is defined as an axial direction, and a direction perpendicular to the rotation axis is defined as a radial direction, The first brake includes a first friction member. The first clutch includes a second friction member. The first engagement device further includes a drive device that drives the first brake and the first clutch, the drive device includes a pressing member that presses the first friction member and the second friction member in the axial direction, a drive motor, and a screw-type linear motion conversion mechanism that converts a rotational driving force of the drive motor into a driving force in the axial direction and transmits the driving force to the pressing member, 3. The transmission according to claim 1, wherein the linear motion conversion mechanism is disposed radially inward with respect to the first friction member and the second friction member, and at a position overlapping with at least one of the first friction member and the second friction member as viewed in the radial direction along the radial direction.

Images