Transmission for vehicle

Abstract

The planetary gear mechanism (P) has a first rotating member (E1) that rotates integrally with the input member (I), a second rotating member (E2) that rotates integrally with the output member (O), and a third rotating member (E3) that rotates integrally with the output member (O). A first rotating member (E1) or a second rotating member (E2) disposed on a first axis (X1) on which the planetary gear mechanism (P) is disposed and rotating integrally with the first rotating member (E1) or the second rotating member (E2); a fifth rotating member (E5) disposed on a second axis (X2) different from the first axis (X1) and rotating in conjunction with the third rotating member (E3); a sixth rotating member (E6) disposed on the second axis (X2) and rotating in conjunction with the fourth rotating member (E4); a first engagement mechanism (3) that interrupts or connects power transmission between the fifth rotating member (E5) and the sixth rotating member (E6); and a second engagement mechanism (4) that selectively fixes the fifth rotating member (E5) to the non-rotating member (NR).

Description

Technical Field

[0001] The present invention relates to a vehicle transmission including an input member drivingly connected to a drive source, an output member drivingly connected to wheels, a planetary gear mechanism, and a switching mechanism for switching the state of the planetary gear mechanism. Background Art

[0002] An example of such a vehicle transmission is disclosed in the following Patent Document 1. Hereinafter, in the description of the background art, the reference numerals in Patent Document 1 are cited within parentheses.

[0003] In the vehicle transmission disclosed in Patent Document 1, a planetary gear mechanism (22) includes a sun gear (51a), a planetary carrier (55), a first ring gear (53), and a second ring gear (54). The planetary carrier (55) supports a large-diameter pinion (52a) meshing with both the sun gear (51a) and the first ring gear (53) and a small-diameter pinion (52b) meshing with the second ring gear (54) so ​​that they rotate integrally.

[0004] In addition, the switching mechanism (23) includes a first engagement mechanism (23a) for disconnecting or connecting the first ring gear (53) and the non-rotating member (42); and a second engagement mechanism (23b) for disconnecting or connecting the second ring gear (54) and the non-rotating member (42). When the first engagement mechanism (23a) is in a disengaged state and the second engagement mechanism (23b) is in an engaged state, a first shift gear (low speed gear) with a larger shift ratio is formed. When the first engagement mechanism (23a) is in an engaged state and the second engagement mechanism (23b) is in a disengaged state, a second shift gear (high speed gear) with a smaller shift ratio is formed.

[0005] Prior art literature

[0006] Patent Literature

[0007] Patent Document 1: Japanese Patent Application Laid-Open No. 2012-240471 Summary of the Invention

[0008] Problems to be solved by the invention

[0009] In the vehicle transmission disclosed in Patent Document 1, a first engagement mechanism (23a) and a second engagement mechanism (23b) are arranged coaxially with a planetary gear mechanism (22) and radially outwardly relative to the planetary gear mechanism (22). Therefore, the radial dimensions of the first engagement mechanism (23a) and the second engagement mechanism (23b) are likely to become larger, and thus the overall vehicle transmission is likely to become larger in the radial direction.

[0010] Therefore, it is desired to realize a vehicle transmission that can easily achieve at least a portion of radial miniaturization in a structure including a planetary gear mechanism and a switching mechanism for switching the state of the planetary gear mechanism.

[0011] Technical means to solve the problem

[0012] In view of the above, the characteristic structure of the vehicle transmission is that

[0013] An input member, drivingly connected to a driving source;

[0014] An output member, connected to the wheel drive;

[0015] a planetary gear mechanism including a first rotating element, a second rotating element, and a third rotating element, wherein the order of the rotational speeds of the first rotating element, the second rotating element, and the third rotating element is as described; and

[0016] A switching mechanism switches the state of the planetary gear mechanism; wherein,

[0017] The first rotating member is connected to the input member for integral rotation.

[0018] The second rotating member is connected to the output member for integral rotation.

[0019] The switching mechanism has:

[0020] a fourth rotating member disposed on a first axis, which is an axis on which the planetary gear mechanism is disposed, and connected to rotate integrally with the first rotating member or the second rotating member;

[0021] a fifth rotating member disposed on a second axis different from the first axis and rotating in conjunction with the third rotating member;

[0022] a sixth rotating member disposed on the second axis and rotating in conjunction with the fourth rotating member;

[0023] a first engagement mechanism that disconnects or connects power transmission between the fifth rotation member and the sixth rotation member; and

[0024] The second engaging mechanism selectively fixes the fifth rotating member to the non-rotating member.

[0025] According to this characteristic configuration, by engaging the first engagement mechanism and disengaging the second engagement mechanism, the fifth and sixth rotational members rotate integrally, thereby establishing a first speed gear in which the rotation of the input member is decelerated and transmitted to the output member while maintaining a constant ratio between the rotational speeds of the first and third rotational members. Furthermore, by disengaging the first engagement mechanism and engaging the second engagement mechanism, the fifth rotational member is fixed to the non-rotating member, thereby establishing a second speed gear in which the rotation of the input member is decelerated and transmitted to the output member.

[0026] Furthermore, according to this characteristic structure, the first rotating member of the planetary gear mechanism is connected to the input member for integral rotation, and the second rotating member of the planetary gear mechanism is connected to the output member for integral rotation. Therefore, the input member and the output member are arranged on a first axis. Furthermore, the fifth and sixth rotating members of the switching mechanism are arranged on a second axis. Furthermore, the first engagement mechanism of the switching mechanism disconnects or connects power transmission between the fifth and sixth rotating members, while the second engagement mechanism of the switching mechanism selectively secures the fifth rotating member to a non-rotating member.

[0027] Thus, according to this characteristic structure, a configuration capable of selectively establishing a first speed and a second speed can be achieved by using an input member and an output member coaxially arranged with the planetary gear mechanism and a switching mechanism partially coaxially arranged with the planetary gear mechanism. Therefore, in a configuration including a planetary gear mechanism and a switching mechanism for switching the state of the planetary gear mechanism, radial miniaturization of at least a portion of the vehicle transmission can be easily achieved. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] Figure 1 is a cross-sectional view of a vehicle drive device having a vehicle transmission according to a first embodiment.

[0029] Figure 2 Schematic diagram of a vehicle drive device having a vehicle transmission according to a first embodiment

[0030] Figure 3 A partially enlarged cross-sectional view of the vehicle transmission according to the first embodiment

[0031] Figure 4 This is a velocity diagram of the planetary gear mechanism of the vehicle transmission according to the first embodiment.

[0032] Figure 5 is a cross-sectional view of a vehicle drive device having a vehicle transmission according to a second embodiment.

[0033] Figure 6Schematic diagram of a vehicle drive device having a vehicle transmission according to a second embodiment

[0034] Figure 7 is a cross-sectional view of a vehicle drive device having a vehicle transmission according to a third embodiment.

[0035] Figure 8 Schematic diagram of a vehicle drive device having a vehicle transmission according to a third embodiment

[0036] Figure 9 is a cross-sectional view of a vehicle drive device having a vehicle transmission according to a fourth embodiment.

[0037] Figure 10 Schematic diagram of a vehicle drive device having a vehicle transmission according to a fourth embodiment

[0038] Figure 11 A partially enlarged cross-sectional view of a vehicle transmission according to a fourth embodiment

[0039] Figure 12 is a cross-sectional view of a vehicle drive device having a vehicle transmission according to a fifth embodiment.

[0040] Figure 13 Schematic diagram of a vehicle drive device having a vehicle transmission according to a fifth embodiment

[0041] Figure 14 is a cross-sectional view of a vehicle drive device having a vehicle transmission according to the sixth and seventh embodiments

[0042] Figure 15 sectional view of a vehicle drive device having a vehicle transmission according to a sixth embodiment

[0043] Figure 16 Schematic diagram of a vehicle drive device having a vehicle transmission according to a sixth embodiment

[0044] Figure 17 sectional view of a vehicle drive device having a vehicle transmission according to a seventh embodiment

[0045] Figure 18 Schematic diagram of a vehicle drive device having a vehicle transmission according to a seventh embodiment DETAILED DESCRIPTION

[0046] 1. First Implementation

[0047] Below, refer to Figures 1 to 4 A vehicle transmission 10 according to the first embodiment will be described. The vehicle transmission 10 is provided in a vehicle drive device 100 .

[0048] like Figure 1 and Figure 2 As shown, in this embodiment, the vehicle drive device 100 includes, in addition to the vehicle transmission 10, a rotary electric machine MG as a drive source, and a case CS (see FIG. 1 ) that accommodates the vehicle transmission 10 and the rotary electric machine MG. Figure 1 ).

[0049] The vehicle transmission 10 includes an input member I drivingly connected to a drive source (here, a rotary electric machine MG); an output member O connected to wheels W (see FIG. Figure 2 ) driving connection; a planetary gear mechanism P; and a switching mechanism S for switching the state of the planetary gear mechanism P. In the present embodiment, the vehicle transmission 10 further includes a differential gear mechanism DF for distributing the rotation transmitted from the rotating electric machine MG to the pair of wheels W.

[0050] Here, in the present application, "drive connection" refers to a state in which two rotating members are connected so as to transmit driving force, including a state in which the two rotating members are connected so as to rotate as one body or a state in which the two rotating members are connected so as to transmit 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. In addition, as transmission members, coupling devices that selectively transmit rotation and driving force, such as friction coupling devices, meshing coupling devices, etc., may also be included. However, when the rotating members of the planetary gear mechanism P are "drive connected", it refers to a state in which they are connected to each other without being connected via other rotating members.

[0051] In the following description, the direction along the first axis X1, the axis on which the planetary gear mechanism P is arranged, is referred to as the "axial direction L." Furthermore, one side of the axial direction L is referred to as the "first axial side L1," and the other side of the axial direction L is referred to as the "second axial side L2." Furthermore, directions perpendicular to each of the multiple axes including the first axis X1 are referred to as the "radial direction R," with each axis as a reference. In cases where it is unnecessary to distinguish which axis is the reference, or when the reference axis is unclear, the term "radial direction R" may be used simply.

[0052] The rotating electrical machine MG includes a stator ST and a rotor RT. The stator ST is fixed to a non-rotating member NR. In the present embodiment, the stator ST is fixed to a case CS, which serves as the non-rotating member NR. The rotor RT is rotatably supported relative to the stator ST. In the present embodiment, the rotating electrical machine MG is arranged on a first axis X1. Furthermore, the rotating electrical machine MG is arranged on the first axial side L1 relative to the planetary gear mechanism P.

[0053] In the present application, the term “rotating electric machine” is used as a concept including any of a motor (electric motor), a generator (generator), and a motor / generator that realizes the functions of both a motor and a generator as needed.

[0054] The input member I is disposed on the first axis X1. In the present embodiment, the input member I is a rotor shaft 1 connected to rotate integrally with the rotor RT. The rotor shaft 1 is a shaft member extending in the axial direction L. In the present embodiment, the rotor shaft 1 is formed into a cylindrical shape centered on the first axis X1.

[0055] The planetary gear mechanism P includes a first rotating element E1, a second rotating element E2, and a third rotating element E3. The planetary gear mechanism P is configured in the order of the rotational speeds of the first, second, and third rotating elements E1, E2, and E3. The planetary gear mechanism P functions as a speed reducer that reduces the rotation of the input member I and transmits it to the output member O.

[0056] Here, the "order of rotational speeds" refers to the order of rotational speeds of the rotating components under their rotational states. The rotational speeds of the rotating components vary depending on the rotational state of the planetary gear mechanism P, but the order of the rotational speeds of the rotating components is constant because it is determined by the structure of the planetary gear mechanism P. In addition, the order of the rotational speeds of the rotating components is consistent with the speed diagram of the rotating components (see Figure 4 ). Here, "the arrangement order of each rotating element in the velocity diagram" refers to the order in which the axes corresponding to the rotating elements in the velocity diagram are arranged in a direction perpendicular to the axes. The arrangement direction of the axes corresponding to the rotating elements in the velocity diagram varies depending on the method of drawing the velocity diagram, but the arrangement order is constant because it is determined by the structure of the planetary gear mechanism P.

[0057] The first rotating element E1 is connected to the input member I for integral rotation. The second rotating element E2 is connected to the output member O for integral rotation. In this embodiment, the first rotating element E1 is the sun gear SG. The second rotating element E2 is the carrier CR. The third rotating element E3 is the ring gear RG having internal teeth.

[0058] In this embodiment, the planetary gear mechanism P is a single-pinion type. Therefore, the pinion gear PG, rotatably supported by the planetary carrier CR, meshes with both the sun gear SG and the ring gear RG. The pinion gear PG rotates about its axis (autorotation) and, along with the planetary carrier CR, revolves about the first axis X1. A plurality of pinion gears PG are provided at intervals along their orbital path.

[0059] In the present embodiment, the differential gear mechanism DF is disposed on the first axis X1 and is a bevel gear type differential gear mechanism including a differential case 21 , a pair of differential pinions 22 , a first side gear 23 , and a second side gear 24 .

[0060] The differential case 21 houses a pair of differential pinions 22, a first side gear 23, and a second side gear 24. The differential case 21 is rotatably supported relative to the case CS. In this embodiment, the differential case 21 is connected for integral rotation with the second rotating element E2 (here, the carrier CR) of the planetary gear mechanism P. In other words, in this embodiment, the differential case 21 functions as the output element O.

[0061] The pair of differential pinion gears 22 are arranged so as to face each other in the radial direction R. Furthermore, the pair of differential pinion gears 22 are mounted on a pinion shaft 22a, which is supported for integral rotation with the differential case 21. The pair of differential pinion gears 22 are each configured to rotate (rotate) about the pinion shaft 22a and to rotate (revolve) about the rotation axis of the differential case 21 (here, the first axis X1).

[0062] The first side gear 23 and the second side gear 24 mesh with the pair of differential pinions 22. The first side gear 23 is arranged on the first axial side L1 relative to the pinion shaft 22a, and the second side gear 24 is arranged on the second axial side L2 relative to the pinion shaft 22a.

[0063] In this embodiment, the first side gear 23 is connected to a first wheel connecting shaft 25 for integral rotation. The first wheel connecting shaft 25 is a shaft member that rotates integrally with the wheel W on the first axial side L1 via a drive shaft. The first wheel connecting shaft 25 extends from the first side gear 23 toward the first axial side L1. In this embodiment, the first wheel connecting shaft 25 is disposed on the first axis X1. Furthermore, the first wheel connecting shaft 25 is disposed radially inward of the rotor shaft 1 in the radial direction R, penetrating the rotor shaft 1 in the axial direction L.

[0064] Furthermore, in this embodiment, the second side gear 24 is connected to a second wheel connecting shaft 26 for integral rotation. The second wheel connecting shaft 26 is a shaft member that rotates integrally with the wheel W axially oriented to the second side L2 via a drive shaft. The second wheel connecting shaft 26 is arranged to extend from the second side gear 24 axially toward the second side L2. In this embodiment, the second wheel connecting shaft 26 is arranged on the first axis X1.

[0065] The switching mechanism S includes a fourth rotation element E4 , a fifth rotation element E5 , a sixth rotation element E6 , a first engagement mechanism 3 , and a second engagement mechanism 4 .

[0066] The fourth rotating member E4 is arranged on the first axis X1. The fourth rotating member E4 is connected to rotate integrally with the first rotating member E1 or the second rotating member E2 of the planetary gear mechanism P. In the present embodiment, the fourth rotating member E4 is connected to rotate integrally with the first rotating member E1. In addition, in the present embodiment, the fourth rotating member E4 is the first gear G1. In the present embodiment, the first gear G1 is an externally toothed gear arranged adjacent to the axial first side L1 of the sun gear SG serving as the first rotating member E1. Figure 1 In the example shown, the first gear G1 and the sun gear SG are formed on the outer peripheral surface of the rotor shaft 1. In addition, the first gear G1 and the sun gear SG are formed to have the same diameter.

[0067] The fifth rotating element E5 is arranged on a second axis X2, which is a different axis from the first axis X1. The fifth rotating element E5 is configured to rotate in conjunction with the third rotating element E3 of the planetary gear mechanism P. Here, "rotating in conjunction" with the two rotating elements encompasses both configurations in which the rotating elements rotate at the same speed as each other and configurations in which the rotating elements rotate synchronously at a constant speed ratio. Furthermore, in this example, the second axis X2 is arranged parallel to the first axis X1.

[0068] In this embodiment, the fifth rotating element E5 is the second gear G2. The second gear G2 is configured to mesh with the fourth gear G4. The fourth gear G4 is an externally toothed gear that rotates integrally with the ring gear RG, which serves as the third rotating element E3. In this embodiment, the fourth gear G4 is positioned outside the ring gear RG in the radial direction R and overlaps with the ring gear RG when viewed radially along the radial direction R. Alternatively, the fourth gear G4 may be positioned offset from the ring gear RG in the axial direction L. In this case, the fourth gear G4 may overlap with the ring gear RG when viewed axially along the axial direction L, or may be positioned radially inward relative to the ring gear RG. Here, regarding the arrangement of two elements, "overlapping when viewed in a particular direction" means that, if an imaginary line parallel to the viewing direction is moved in directions orthogonal to the imaginary line, at least a portion of the area lies within the region where the imaginary line intersects both elements.

[0069] The sixth rotating element E6 is arranged on the second axis X2. The sixth rotating element E6 is configured to rotate in conjunction with the fourth rotating element E4. In the present embodiment, the sixth rotating element E6 is the third gear G3. The third gear G3 is configured to mesh with the first gear G1 or with a gear meshing with the first gear G1. In the present embodiment, the third gear G3 meshes with the first idler gear IG1 meshing with the first gear G1. That is, in the present embodiment, the third gear G3 and the first gear G1 mesh with the first idler gear IG1 at different circumferential positions relative to the first idler gear IG1. Furthermore, in the present embodiment, the third gear G3 is arranged adjacent to the second gear G2 on the first axial side L1 of the second gear G2.

[0070] The first engagement mechanism 3 is configured to disconnect or connect the power transmission between the fifth rotating member E5 and the sixth rotating member E6. The second engagement mechanism 4 is configured to selectively fix the fifth rotating member E5 to the non-rotating member NR. In this embodiment, the first engagement mechanism 3 and the second engagement mechanism 4 are arranged on the second axis X2. Figure 1 In the illustrated example, the first engagement mechanism 3 is arranged adjacent to the second engagement mechanism 4 on the axial first side L1 of the second engagement mechanism 4. In the present embodiment, the first engagement mechanism 3 and the second engagement mechanism 4 are arranged on the axial second side L2 relative to the second gear G2.

[0071] like Figure 3 As shown, the first engaging mechanism 3 includes a first engaging member 31 and a second engaging member 32 that are configured to engage with each other. The second engaging mechanism 4 includes a third engaging member 41 and a fourth engaging member 42 that are configured to engage with each other.

[0072] In this embodiment, the first engagement mechanism 3 and the second engagement mechanism 4 are respectively friction-type engagement mechanisms. The friction-type engagement mechanism is configured to control the engagement state (engaged state / disengaged state) according to the engagement pressure of a pair of engagement members. In the friction-type engagement mechanism, the engagement state includes a "direct engagement state" and a "sliding engagement state". The direct engagement state is a state in which a pair of engagement members are engaged without a rotational difference. In addition, the sliding engagement state is a state in which a pair of engagement members are engaged with a rotational difference.

[0073] In this embodiment, the first engaging member 31 and the second engaging member 32 are arranged to face each other in the axial direction L. The first engaging member 31 and the second engaging member 32 are frictionally engaged with each other by being pressed in the axial direction L. A plurality of the first engaging members 31 and the second engaging members 32 are provided, and the first engaging members 31 and the second engaging members 32 are alternately arranged in the axial direction L.

[0074] In this embodiment, the third engaging member 41 and the fourth engaging member 42 are arranged to face each other in the axial direction L. The third engaging member 41 and the fourth engaging member 42 are frictionally engaged with each other by being pressed in the axial direction L. A plurality of the third engaging members 41 and the fourth engaging member 42 are provided, and the third engaging members 41 and the fourth engaging members 42 are alternately arranged in the axial direction L.

[0075] In the present embodiment, the first joining mechanism 3 further includes a first supporting member 33 that supports the first joining member 31 and a second supporting member 34 that supports the second joining member 32 .

[0076] The first support member 33 supports the first engaging member 31 so as to rotate integrally with the first engaging member 31 and to enable free sliding along the axial direction L. In this embodiment, the first support member 33 is formed into a cylindrical shape with the second axis X2 as its axis. Furthermore, the first support member 33 supports the first engaging member 31 from the outside in the radial direction R. In this example, a plurality of spline teeth extending along the axial direction L are formed in a circumferentially dispersed manner on the inner periphery of the first support member 33. On the other hand, similar spline teeth are also formed in a circumferentially dispersed manner on the outer periphery of the first engaging member 31. Furthermore, these spline teeth engage with each other.

[0077] The second support member 34 supports the second engaging member 32 so that it can slide along the axial direction L, rotating integrally with the second engaging member 32. In this embodiment, the second support member 34 is coaxial with the first support member 33 and is formed into a cylindrical shape with a smaller diameter than the first support member 33. Furthermore, the second support member 34 supports the second engaging member 32 from the inner side of the radial direction R. In this example, a plurality of spline teeth extending along the axial direction L are formed in a circumferentially dispersed manner on the outer periphery of the second support member 34. On the other hand, similar spline teeth are also formed in a circumferentially dispersed manner on the inner periphery of the second engaging member 32. Furthermore, these spline teeth engage with each other.

[0078] like Figure 1 and Figure 2 As shown, the first support member 33 is connected to the fifth rotating element E5 for integral rotation. In this embodiment, the first support member 33 is connected to the second gear G2, which serves as the fifth rotating element E5, via a first connecting shaft 35. The first connecting shaft 35 is a shaft member extending in the axial direction L. In this embodiment, the first connecting shaft 35 is formed into a cylindrical shape centered on the second axis X2.

[0079] The second support member 34 is connected to the sixth rotating element E6 for integral rotation. In this embodiment, the second support member 34 is connected to the third gear G3, serving as the sixth rotating element E6, via a second connecting shaft 36. The second connecting shaft 36 is a shaft member extending in the axial direction L. In this embodiment, the second connecting shaft 36 is disposed on the second axis X2. Furthermore, the second connecting shaft 36 is disposed radially inward of the first connecting shaft 35 in the radial direction R, penetrating the first connecting shaft 35 in the axial direction L.

[0080] When the first engaging member 31 and the second engaging member 32 are engaged without a rotational difference and the first engaging mechanism 3 is in a direct engagement state, the fifth rotating member E5 and the sixth rotating member E6 rotate integrally. On the other hand, when the first engaging member 31 and the second engaging member 32 are not engaged with each other and the first engaging mechanism 3 is in a disengaged state, or when the first engaging member 31 and the second engaging member 32 are engaged with a rotational difference and the first engaging mechanism 3 is in a sliding engagement state, the fifth rotating member E5 and the sixth rotating member E6 rotate relative to each other.

[0081] like Figure 3 As shown, in this embodiment, the second engaging mechanism 4 further includes a third supporting member 43 that supports the third engaging member 41 and a fourth supporting member 44 that supports the fourth engaging member 42 .

[0082] The third support member 43 supports the third engaging member 41 so that it can slide along the axial direction L, rotating integrally with the third engaging member 41. In this embodiment, the third support member 43 is formed into a cylindrical shape with the second axis X2 as its axis. Furthermore, the third support member 43 supports the third engaging member 41 from the outside in the radial direction R. In this example, a plurality of spline teeth extending along the axial direction L are formed in a circumferentially dispersed manner on the inner periphery of the third support member 43. On the other hand, similar spline teeth are also formed in a circumferentially dispersed manner on the outer periphery of the third engaging member 41. Furthermore, these spline teeth engage with each other.

[0083] The fourth support member 44 supports the fourth coupling member 42 so that it cannot rotate relative to the third support member 43 in the circumferential direction but can slide in the axial direction L. In this embodiment, the fourth support member 44 is coaxial with the third support member 43 and is formed into a cylindrical shape with a smaller diameter than the third support member 43. Furthermore, the fourth support member 44 supports the fourth coupling member 42 from the inner side of the radial direction R. In this example, a plurality of spline teeth extending in the axial direction L are formed in a circumferentially dispersed manner on the outer periphery of the fourth support member 44. On the other hand, similar spline teeth are also formed in a circumferentially dispersed manner on the inner periphery of the fourth coupling member 42. Furthermore, these spline teeth engage with each other.

[0084] The third support member 43 is connected to the fifth rotational member E5 for integral rotation. In this embodiment, the third support member 43 is connected to the first support member 33 for integral rotation. Therefore, in this embodiment, the third engagement member 41 supported by the third support member 43 and the first engagement member 31 supported by the first support member 33 rotate integrally with each other.

[0085] The fourth support member 44 is fixed to the non-rotating member NR. In this embodiment, the case CS as the non-rotating member NR has a first support wall portion 91 formed to extend in the radial direction R. Furthermore, the fourth support member 44 is fixed to the first support wall portion 91. Figure 3 In the illustrated example, the first support wall portion 91 is arranged to cover the second engagement mechanism 4 from the axial second side L2 . Furthermore, the fourth support member 44 is formed to project from the first support wall portion 91 toward the axial first side L1 .

[0086] When the third engagement member 41 and the fourth engagement member 42 are engaged without a rotational difference and the second engagement mechanism 4 is in a direct engagement state, the fifth rotational member E5 is fixed to the non-rotating member NR. On the other hand, when the third engagement member 41 and the fourth engagement member 42 are not engaged with each other and the second engagement mechanism 4 is in a disengaged state, or when the third engagement member 41 and the fourth engagement member 42 are engaged with a rotational difference and the second engagement mechanism 4 is in a sliding engagement state, the fifth rotational member E5 rotates relative to the non-rotating member NR.

[0087] In the vehicle transmission 10 constructed as described above, when the first engagement mechanism 3 is engaged (here, a directly engaged state) and the second engagement mechanism 4 is disengaged, the fifth rotational element E5 and the sixth rotational element E6 rotate integrally, establishing a first speed stage S1 in which the rotation of the input member I is decelerated and transmitted to the output member O while maintaining a constant ratio between the rotational speeds of the first rotational element E1 and the third rotational element E3. Furthermore, when the first engagement mechanism 3 is disengaged and the second engagement mechanism 4 is engaged (here, a directly engaged state), the fifth rotational element E5 is fixed to the non-rotating element NR, establishing a second speed stage S2 in which the rotation of the input member I is decelerated and transmitted to the output member O.

[0088] As described above, the vehicle transmission 10 includes:

[0089] An input member I drivingly connected to a drive source (here, the rotary electric machine MG);

[0090] Output member O, drivingly connected to wheels W;

[0091] The planetary gear mechanism P includes a first rotating element E1, a second rotating element E2, and a third rotating element E3, and is configured so that the order of the rotational speeds of the first rotating element E1, the second rotating element E2, and the third rotating element E3 is the order described; and

[0092] The switching mechanism S switches the state of the planetary gear mechanism P; wherein,

[0093] The first rotating element E1 is connected to the input element I for integral rotation.

[0094] The second rotating member E2 is connected to the output member O so as to rotate integrally with it.

[0095] The switching mechanism S has:

[0096] The fourth rotating element E4 is disposed on the first axis X1, which is the axis of the planetary gear mechanism P, and is connected to rotate integrally with the first rotating element E1 or the second rotating element E2.

[0097] The fifth rotating element E5 is arranged on a second axis X2 which is different from the first axis X1 and rotates in conjunction with the third rotating element E3;

[0098] The sixth rotating element E6 is disposed on the second axis X2 and rotates in conjunction with the fourth rotating element E4;

[0099] a first engagement mechanism 3 for disconnecting or connecting power transmission between the fifth rotational element E5 and the sixth rotational element E6; and

[0100] The second engagement mechanism 4 selectively fixes the fifth rotational element E5 to the non-rotational element NR.

[0101] According to this configuration, by engaging the first engagement mechanism 3 and disengaging the second engagement mechanism 4, the fifth rotational element E5 and the sixth rotational element E6 rotate integrally, thereby establishing a first speed stage S1 in which the rotation of the input member I is decelerated and transmitted to the output member O while maintaining a constant ratio between the rotational speeds of the first rotational element E1 and the third rotational element E3. Furthermore, by disengaging the first engagement mechanism 3 and engaging the second engagement mechanism 4, the fifth rotational element E5 is fixed to the non-rotating element NR, thereby establishing a second speed stage S2 in which the rotation of the input member I is decelerated and transmitted to the output member O.

[0102] Furthermore, according to this configuration, the first rotating element E1 of the planetary gear mechanism P is connected for integral rotation with the input member I, and the second rotating element E2 of the planetary gear mechanism P is connected for integral rotation with the output member O. Therefore, the input member I and the output member O are arranged on the first axis X1. Furthermore, the fifth rotating element E5 and the sixth rotating element E6 of the switching mechanism S are arranged on the second axis X2. Furthermore, the first engaging mechanism 3 of the switching mechanism S disconnects and connects power transmission between the fifth rotating element E5 and the sixth rotating element E6, while the second engaging mechanism 4 of the switching mechanism S selectively fixes the fifth rotating element E5 to the non-rotating element NR.

[0103] Thus, according to this configuration, the first speed S1 and the second speed S2 can be selectively established by the input member I and the output member O, which are coaxially arranged with the planetary gear mechanism P, and the switching mechanism S, which is partially coaxially arranged with the planetary gear mechanism P. Therefore, in a configuration including the planetary gear mechanism P and the switching mechanism S for switching the state of the planetary gear mechanism P, it is easy to achieve miniaturization in the radial direction R of at least a portion of the vehicle transmission 10.

[0104] In addition, as described above, in this embodiment,

[0105] The first rotating element E1 is the sun gear SG.

[0106] The second rotating element E2 is the planet carrier CR,

[0107] The third rotating element E3 is the ring gear RG with internal teeth.

[0108] The switching mechanism S has:

[0109] a first gear G1 serving as a fourth rotational element E4;

[0110] a second gear G2 serving as a fifth rotational member E5;

[0111] a third gear G3 as the sixth rotational member E6 ; and

[0112] A fourth gear G4 having external teeth that rotates integrally with the ring gear RG;

[0113] The second gear G2 is configured to mesh with the fourth gear G4.

[0114] The third gear G3 is configured to mesh with the first gear G1 or mesh with a gear (here, the first idler gear IG1 ) that meshes with the first gear G1 .

[0115] According to this configuration, the vehicle transmission 10 in which the dimension in the radial direction R is suppressed to be small can be realized with a simple structure.

[0116] like Figure 4As shown, in this embodiment, a power transmission path between the third rotational element E3 and the fifth rotational element E5 that rotates in conjunction with the third rotational element E3, and a power transmission path between the fourth rotational element E4 that is connected for integral rotation with the first rotational element E1 and the sixth rotational element E6 that rotates in conjunction with the fourth rotational element E4 are configured such that, when the first engagement mechanism 3 is engaged and the second engagement mechanism 4 is disengaged (i.e., the first shift speed S1 is established), and the input member I is rotating, the third rotational element E3 rotates in the opposite direction to the first rotational element E1. Furthermore, the gear ratio relationship between the power transmission path between the third rotational element E3 and the fifth rotational element E5 and the power transmission path between the fourth rotational element E4 and the sixth rotational element E6 is configured such that, when the input member I is rotating, the third rotational element E3 rotates in the opposite direction to the first rotational element E1.

[0117] With this configuration, the speed ratio of the first speed stage S1, achieved when the first engagement mechanism 3 is engaged and the second engagement mechanism 4 is disengaged, is greater than the speed ratio of the second speed stage S2, achieved when the first engagement mechanism 3 is disengaged and the second engagement mechanism 4 is engaged. Furthermore, with this configuration, the planetary gear mechanism P is configured so that the number of rotating elements required to form the power transmission path is smaller in the second speed stage S2 than in the first speed stage S1. Consequently, the transmission efficiency of the driving force in the second speed stage S2, which is used more frequently during high-speed travel than in the first speed stage S1, is higher than in the first speed stage S1. Consequently, this configuration facilitates improved energy efficiency during vehicle travel.

[0118] Figure 4 It is the velocity diagram of the planetary gear mechanism P of this embodiment. Figure 4 In the speed diagram, the vertical lines correspond to the rotation speeds of the respective rotating members of the planetary gear mechanism P. Furthermore, the plurality of vertical lines arranged in parallel correspond to the respective rotating members of the planetary gear mechanism P. Figure 4 In the velocity diagram, reference numerals shown above the plurality of vertical lines are reference numerals of the corresponding rotating elements of the planetary gear mechanism P. Furthermore, reference numerals shown below the plurality of vertical lines are reference numerals of elements that rotate integrally with the rotating elements corresponding to the reference numerals shown above.

[0119] like Figure 3 As shown, in this embodiment, the switching mechanism S further includes a first drive mechanism 5. The first drive mechanism 5 is configured to drive both the first engagement mechanism 3 and the second engagement mechanism 4. In other words, the first engagement mechanism 3 and the second engagement mechanism 4 are driven by a common first drive mechanism 5. The first drive mechanism 5 includes a first engagement member 51, a first drive motor 52, and a first direct motion conversion mechanism 53.

[0120] The first engaging member 51 is a "engaging member" that selectively engages either the first engaging mechanism 3 or the second engaging mechanism 4. The first drive motor 52 is a "drive motor" that outputs a predetermined rotational driving force. The first direct-motion conversion mechanism 53 is a screw-type "direct-motion conversion mechanism" that converts the rotational driving force of the first drive motor 52 into a driving force along the second axis X2 (here, the axial direction L) and transmits it to the first engaging member 51.

[0121] In this embodiment, the first joining member 51 has a first pressing portion 511 and a second pressing portion 512 .

[0122] The first pressing portion 511 is configured to press the first engaging member 31 and the second engaging member 32 of the first engaging mechanism 3 in the axial direction L. In the present embodiment, the first pressing portion 511 is formed to extend in the radial direction R. Furthermore, the first pressing portion 511 is configured to press the first engaging member 31 and the second engaging member 32 from the second axial side L2. In the present embodiment, the first pressing portion 511 is supported relative to the first supporting member 33 of the first engaging mechanism 3 so as to be movable in the axial direction L but not rotatable in the circumferential direction.

[0123] The second pressing portion 512 is configured to press the third joining member 41 and the fourth joining member 42 of the second joining mechanism 4 in the axial direction L. In the present embodiment, the second pressing portion 512 is formed to extend in the radial direction R. Moreover, the second pressing portion 512 is configured to press the third joining member 41 and the fourth joining member 42 from the first axial side L1. In addition, in the present embodiment, the second pressing portion 512 is composed of a component different from the first pressing portion 511, and is configured opposite to the first pressing portion 511 in the axial direction L. Moreover, the second pressing portion 512 is supported via the thrust bearing B1 so as to be able to rotate freely relative to the first pressing portion 511. Therefore, in the present embodiment, the first pressing portion 511 and the second pressing portion 512 are configured to be linked in the axial direction L in a state where they can rotate relative to each other.

[0124] In this embodiment, the first direct motion conversion mechanism 53 includes a first threaded shaft 54 ​​, a first nut member 55 , and a first transmission mechanism 56 .

[0125] The first threaded shaft 54 ​​is supported so as to be rotatable relative to the non-rotating member NR. Threads are formed on the outer periphery of the first threaded shaft 54. The first threaded shaft 54 ​​is formed to extend along the axial direction L. In this embodiment, the first threaded shaft 54 ​​is positioned on the second axis X2. Furthermore, in this embodiment, the first threaded shaft 54 ​​is positioned radially inward of the fourth support member 44 of the second joint mechanism 4 in the radial direction R and is positioned so as to overlap with the fourth support member 44 when viewed radially along the radial direction R.

[0126] The first nut member 55 is configured to threadably engage with the first threaded shaft 54. Specifically, a groove is formed on the inner circumference of the first nut member 55 to engage with the threads of the first threaded shaft 54. Furthermore, the first nut member 55 is supported relative to the non-rotating member NR so that it can move in the axial direction L but cannot rotate circumferentially. In this embodiment, the first nut member 55 is positioned radially inward of the fourth support member 44. Furthermore, the first nut member 55 is connected to the fourth support member 44 via a first connecting member 55a positioned radially R between the outer circumference of the first nut member 55 and the inner circumference of the fourth support member 44, allowing relative movement in the axial direction L but restricted relative rotation relative to the housing CS, which serves as the non-rotating member NR. Thus, the first nut member 55 rotates with the first threaded shaft 54, causing it to undergo linear motion in the axial direction L based on the direction of rotation and the orientation of the threads of the first threaded shaft 54.

[0127] In this embodiment, the first nut member 55 is connected to the second pressing portion 512 of the first engaging member 51 so as to be movable in the axial direction L. Figure 3 In the illustrated example, the first nut member 55 and the second pressing portion 512 are integrally formed such that the second pressing portion 512 extends outward in the radial direction R from the first nut member 55 .

[0128] The first transmission mechanism 56 is configured to transmit the rotational driving force of the first drive motor 52 to the first threaded shaft 54. In this embodiment, the first transmission mechanism 56 reduces the speed of the rotation of the first drive motor 52 and transmits the speed to the first threaded shaft 54. In this embodiment, the first transmission mechanism 56 includes a first transmission gear 561 and a first connecting body 562.

[0129] The first transmission gear 561 is drivably connected to the first drive motor 52 via at least one gear (not shown). In the present embodiment, the first transmission gear 561 is disposed on the second axis X2. Furthermore, the first transmission gear 561 is rotatably connected to the first connecting body 562 via the first shaft portion 563. The first shaft portion 563 is formed in the shape of an axis extending in the axial direction L. In the present embodiment, the first shaft portion 563 is formed to extend from the first transmission gear 561 toward the first axial side L1.

[0130] The first connecting body 562 connects the first transmission gear 561 and the first threaded shaft 54 ​​so that they rotate integrally. In this embodiment, the first connecting body 562 is integrally rotatably connected to the first threaded shaft 54, with the first threaded shaft 54 ​​protruding from the first connecting body 562 in the axial direction toward the first side L1. In addition, in this embodiment, the first connecting body 562 is formed into a cylindrical shape that is open in the axial direction toward the second side L2. Moreover, the first connecting body 562 is integrally rotatably connected to the first shaft portion 563, with the first shaft portion 563 disposed inwardly in the radial direction R relative to the first connecting body 562.

[0131] In this embodiment, when the first drive motor 52 is driven to rotate toward the first side, the rotational drive force of the first drive motor 52 is transmitted to the first threaded shaft 54 ​​via the first transmission mechanism 56, causing the first nut member 55 to move axially toward the first side L1. As described above, in this embodiment, a thrust bearing B1 is disposed between the first pressing portion 511 and the second pressing portion 512 in the axial direction L. Therefore, in this embodiment, when the first nut member 55 moves toward the first axial side L1, the second pressing portion 512 moves toward the first axial side L1 via the first nut member 55, and the first pressing portion 511 also moves toward the first axial side L1 via the thrust bearing B1. As a result, the first and second engaging members 31 and 32 are pressed by the first pressing portion 511, causing the first engaging mechanism 3 to enter an engaged state. The second pressing portion 512 releases its pressure on the third and fourth engaging members 41 and 42, causing the second engaging mechanism 4 to enter a disengaged state.

[0132] On the other hand, when the first drive motor 52 is driven to rotate toward a second side opposite to the first side, the rotational drive force of the first drive motor 52 is transmitted to the first threaded shaft 54 ​​via the first transmission mechanism 56, causing the first nut member 55 to move axially toward the second side L2. Consequently, the second pressing portion 512 moves axially toward the second side L2 via the first nut member 55. As a result, the third engagement member 41 and the fourth engagement member 42 are pressed by the second pressing portion 512, causing the second engagement mechanism 4 to enter an engaged state. The first pressing portion 511 releases the pressure on the first engagement member 31 and the second engagement member 32, causing the first engagement mechanism 3 to enter a disengaged state.

[0133] Thus, in this embodiment, the first joining mechanism 3 and the second joining mechanism 4 are arranged side by side on the second axis X2 and driven by the common first driving mechanism 5.

[0134] The first drive mechanism 5 includes: a first engaging member 51 that operates to selectively engage either the first engaging mechanism 3 or the second engaging mechanism 4; a first drive motor 52; and a first direct-acting conversion mechanism 53 of a lead screw type that converts the rotational drive force of the first drive motor 52 into a drive force in the direction of the second axis X2 (here, the axial direction L) and transmits the drive force to the first engaging member 51.

[0135] By rotating the first drive motor 52 toward the first side, the first engagement mechanism 3 is brought into engagement, and the second engagement mechanism 4 is brought into disengagement.

[0136] When the first drive motor 52 is rotationally driven toward the second side opposite to the first side, the second engagement mechanism 4 is brought into the engaged state, and the first engagement mechanism 3 is brought into the disengaged state.

[0137] According to this structure, the first drive mechanism 5 that drives the first engagement mechanism 3 and the second engagement mechanism 4 is composed of a first drive motor 52 and a screw-type first direct-acting conversion mechanism 53. Therefore, compared with the case of using a hydraulic drive mechanism, it is easy to achieve miniaturization of the vehicle transmission 10.

[0138] 2. Second Implementation

[0139] Below, refer to Figure 5 and Figure 6 A second embodiment of a vehicle transmission 10 will now be described. In this embodiment, the position of the differential gear mechanism DF differs from that of the first embodiment. The following description will focus on the differences from the first embodiment. Other points not specifically described remain the same as those of the first embodiment.

[0140] like Figure 5 and Figure 6 As shown, in this embodiment, the differential gear mechanism DF is arranged on a third axis X3 which is different from the first axis X1 and the second axis X2. Furthermore, the differential gear mechanism DF has a differential input gear 28, and the rotation of the differential input gear 28 is distributed to a pair of wheels W (see FIG. Figure 6 The differential input gear 28 is connected to the differential case 21 for integral rotation. The differential input gear 28 is formed to protrude outward from the differential case 21 in the radial direction R. In this embodiment, the differential input gear 28 meshes with the output gear 27 arranged on the first axis X1. In this example, the third axis X3 is arranged parallel to the first axis X1.

[0141] The output gear 27 is connected to rotate integrally with the second rotating element E2 (here, the carrier CR) of the planetary gear mechanism P. Therefore, in this embodiment, the output gear 27 functions as the output element O. Furthermore, in this embodiment, the output gear 27 is disposed adjacent to the planetary gear mechanism P on the second axial side L2 of the planetary gear mechanism P.

[0142] Furthermore, in this embodiment, the first wheel connecting shaft 25 is not arranged on the inner side of the rotor shaft 1 in the radial direction R, but is arranged in a region on the outer side of the rotating electrical machine MG in the radial direction R. This allows the radial dimension of the rotor shaft 1 to be kept small, and therefore the outer diameter of the sun gear SG provided on the rotor shaft 1 can also be kept small. Consequently, it is easier to ensure a large reduction ratio for the planetary gear mechanism P.

[0143] 3. Third Implementation

[0144] Below, refer to Figure 7 and Figure 8 A vehicle transmission 10 according to a third embodiment will now be described. In this embodiment, the structure of the planetary gear mechanism P differs from that of the first embodiment. The following description will focus on the differences from the first embodiment. Other points not specifically described are the same as those of the first embodiment.

[0145] like Figure 7 and Figure 8 As shown, in this embodiment, the pinion gear PG of the planetary gear mechanism P includes a first gear portion PG1 meshing with the sun gear SG and a second gear portion PG2 meshing with the ring gear RG.

[0146] The first gear portion PG1 and the second gear portion PG2 are connected to rotate integrally with each other. In this embodiment, the first gear portion PG1 is formed to have a larger diameter than the second gear portion PG2. In addition, the first gear portion PG1 is arranged on the first axial side L1 relative to the second gear portion PG2.

[0147] 4. Fourth embodiment

[0148] Below, refer to Figures 9 to 11 A fourth embodiment of a vehicle transmission 10 will now be described. In this embodiment, the structure of the switching mechanism S differs from that of the first embodiment. The following description will focus on the differences from the first embodiment. Other points not specifically described are the same as those of the first embodiment.

[0149] like Figure 9 and Figure 10 As shown, in this embodiment, the switching mechanism S further includes a friction-type third engagement mechanism 6 that selectively fixes the fourth rotational element E4 to the non-rotational element NR.

[0150] According to this structure, when shifting (upshifting) from a gear with a large speed ratio to a gear with a small speed ratio, that is, a gear with a lower rotation speed of the input member I at the same vehicle speed, even if the drive source (here is the rotating electric machine MG) cannot output negative torque, the rotation speed of the input member I can be reduced by changing the third engagement mechanism 6 to a sliding engagement state, thereby enabling rapid gear shifting.

[0151] Furthermore, according to this configuration, by engaging one of the first engagement mechanism 3 and the second engagement mechanism 4 with the third engagement mechanism 6 , the vehicle can also function as a parking brake.

[0152] like Figure 11 As shown, the third engagement mechanism 6 includes a fifth engagement member 61 and a sixth engagement member 62 that are configured to engage with each other. In this embodiment, the fifth engagement member 61 and the sixth engagement member 62 are arranged to face each other in the axial direction L. Furthermore, the fifth engagement member 61 and the sixth engagement member 62 are frictionally engaged with each other by being pressed in the axial direction L. Furthermore, a plurality of fifth engagement members 61 and a plurality of sixth engagement members 62 are provided, and these are alternately arranged along the axial direction L.

[0153] In this embodiment, the third joining mechanism 6 is arranged on a fourth axis X4, which is an axis different from the axis extending from the first axis X1 to the third axis X3. Furthermore, in this embodiment, the third joining mechanism 6 further includes a fifth support member 63 that supports the fifth joining member 61 and a sixth support member 64 that supports the sixth joining member 62. Furthermore, in this example, the fourth axis X4 is arranged parallel to the first axis X1.

[0154] The fifth support member 63 supports the fifth coupling member 61 so that it can slide freely in the axial direction L, rotating integrally with the fifth coupling member 61. In this embodiment, the fifth support member 63 is formed into a cylindrical shape with the fourth axis X4 as its axis. Furthermore, the fifth support member 63 supports the fifth coupling member 61 from the outside in the radial direction R. In this example, a plurality of spline teeth extending in the axial direction L are formed in a circumferentially dispersed manner on the inner periphery of the fifth support member 63. On the other hand, similar spline teeth are also formed in a circumferentially dispersed manner on the outer periphery of the fifth coupling member 61. Furthermore, these spline teeth engage with each other.

[0155] The sixth support member 64 supports the sixth engaging member 62 so that it can slide along the axial direction L, rotating integrally therewith. In this embodiment, the sixth support member 64 is formed into a cylindrical shape coaxial with the fifth support member 63 and having a smaller diameter than the fifth support member 63. Furthermore, the sixth support member 64 supports the sixth engaging member 62 from the inner side in the radial direction R. In this example, a plurality of spline teeth extending along the axial direction L are formed circumferentially dispersed on the outer periphery of the sixth support member 64. On the other hand, similar spline teeth are also formed circumferentially dispersed on the inner periphery of the sixth engaging member 62. Furthermore, these spline teeth engage with each other.

[0156] like Figure 9 and Figure 10 As shown, the fifth support member 63 is connected to the fifth gear G5 for integral rotation. The fifth gear G5 meshes with the second idler gear IG2, which in turn meshes with the first gear G1, the fourth rotating element E4, which is integrally connected to the first rotating element E1 of the planetary gear mechanism P for integral rotation. Specifically, the fifth gear G5 and the first gear G1 mesh with the second idler gear IG2 at different circumferential positions relative to the second idler gear IG2. Furthermore, the first and second idler gears IG1 and IG2 mesh with the first gear G1 at different circumferential positions relative to the first gear G1. Therefore, the fifth gear G5 rotates in conjunction with the first rotating element E1 of the planetary gear mechanism P (here, the sun gear SG).

[0157] In the present embodiment, the fifth gear G5 is disposed on the fourth axis X4 and on the first axial side L1 relative to the third engagement mechanism 6 .

[0158] like Figure 11 As shown, the sixth support member 64 is fixed to the non-rotating member NR. In this embodiment, the case CS as the non-rotating member NR has a second support wall portion 92 formed to extend in the radial direction R. Furthermore, the sixth support member 64 is fixed to the second support wall portion 92. Figure 11 In the illustrated example, the second support wall portion 92 is arranged to cover the third engagement mechanism 6 from the axial second side L2 . Furthermore, the sixth support member 64 is formed to project from the second support wall portion 92 toward the axial first side L1 .

[0159] When the fifth engagement member 61 and the sixth engagement member 62 are engaged without a rotational difference and the third engagement mechanism 6 is in direct engagement, the fifth gear G5 is fixed to the non-rotating member NR. As a result, the first rotating member E1, which rotates in conjunction with the fifth gear G5, is fixed to the non-rotating member NR. On the other hand, when the fifth engagement member 61 and the sixth engagement member 62 are not engaged with each other and the third engagement mechanism 6 is in a disengaged state, or when the fifth engagement member 61 and the sixth engagement member 62 are engaged with a rotational difference and the third engagement mechanism 6 is in a sliding engagement state, the first rotating member E1 rotates relative to the non-rotating member NR.

[0160] like Figure 11 As shown, in this embodiment, the switching mechanism S further includes a second drive mechanism 7 for driving the third engagement mechanism 6. The second drive mechanism 7 includes a second engagement member 71, a second drive motor 72, and a second direct motion conversion mechanism 73.

[0161] The second engagement member 71 is configured to switch the engagement state of the third engagement mechanism 6. The second drive motor 72 is configured to output a predetermined rotational driving force. The second direct-acting conversion mechanism 73 is a screw-type direct-acting conversion mechanism that converts the rotational driving force of the second drive motor 72 into a driving force along the fourth axis X4 (here, the axial direction L) and transmits the driving force to the second engagement member 71.

[0162] In the present embodiment, the second engaging member 71 is configured to press the fifth engaging member 61 and the sixth engaging member 62 in the axial direction L. In addition, in the present embodiment, the second engaging member 71 is formed to extend in the radial direction R. Furthermore, the second engaging member 71 is configured to press the fifth engaging member 61 and the sixth engaging member 62 from the axial first side L1.

[0163] In the present embodiment, the second direct motion conversion mechanism 73 includes a second threaded shaft 74 , a second nut member 75 , and a second transmission mechanism 76 .

[0164] The second threaded shaft 74 is supported so as to be rotatable relative to the non-rotating member NR. Threads are formed on the outer periphery of the second threaded shaft 74. The second threaded shaft 74 is formed to extend in the axial direction L. In this embodiment, the second threaded shaft 74 is positioned on the fourth axis X4. Furthermore, in this embodiment, the second threaded shaft 74 is positioned radially inward of the sixth support member 64 of the third joint mechanism 6 in the radial direction R and is positioned so as to overlap with the sixth support member 64 when viewed radially along the radial direction R.

[0165] The second nut member 75 is configured to threadably engage with the second threaded shaft 74. Specifically, a groove is formed on the inner circumference of the second nut member 75 to engage with the threads of the second threaded shaft 74. Furthermore, the second nut member 75 is supported so that it can move relative to the non-rotating member NR in the axial direction L and cannot rotate relative to the circumferential direction. In this embodiment, the second nut member 75 is positioned radially inward of the sixth support member 64. Furthermore, the second nut member 75 is connected to the sixth support member 64 via a second connecting member 75a positioned radially between the outer circumference of the second nut member 75 and the inner circumference of the sixth support member 64, while being able to move relative to the housing CS, serving as the non-rotating member NR, in the axial direction L and being restricted from relative rotation. Thus, the second nut member 75 rotates with the second threaded shaft 74, causing it to undergo linear motion in the axial direction L according to the direction of rotation and the orientation of the threads of the second threaded shaft 74.

[0166] In this embodiment, the second nut member 75 is connected to the second engagement member 71 so as to move integrally in the axial direction L. Figure 11 In the illustrated example, the second nut member 75 and the second engaging member 71 are integrally formed so that the second engaging member 71 extends outward in the radial direction R from the second nut member 75 .

[0167] The second transmission mechanism 76 is configured to transmit the rotational driving force of the second drive motor 72 to the second threaded shaft 74. In this embodiment, the second transmission mechanism 76 reduces the rotation speed of the second drive motor 72 and transmits the speed to the second threaded shaft 74. In this embodiment, the second transmission mechanism 76 includes a second transmission gear 761 and a second connecting body 762.

[0168] The second transmission gear 761 is drivably connected to the second drive motor 72 via at least one gear (not shown). In the present embodiment, the second transmission gear 761 is disposed on the fourth axis X4. Furthermore, the second transmission gear 761 is rotatably connected to the second connecting body 762 via the second shaft portion 763. The second shaft portion 763 is formed in the shape of an axis extending in the axial direction L. In the present embodiment, the second shaft portion 763 is formed to extend from the second transmission gear 761 toward the first axial side L1.

[0169] The second connecting body 762 connects the second transmission gear 761 and the second threaded shaft 74 so that they rotate integrally. In this embodiment, the second connecting body 762 is connected to the second threaded shaft 74 so that it rotates integrally with the second threaded shaft 74, while the second threaded shaft 74 protrudes from the second connecting body 762 axially toward the first side L1. In this embodiment, the second connecting body 762 is formed into a cylindrical shape that is open axially toward the second side L2. Furthermore, the second connecting body 762 is connected to the second shaft portion 763 so that it rotates integrally with the second shaft portion 763, while the second shaft portion 763 is disposed inwardly in the radial direction R relative to the second connecting body 762.

[0170] In this embodiment, when the second drive motor 72 is driven to rotate toward the first side, the rotational drive force of the second drive motor 72 is transmitted to the second threaded shaft 74 via the second transmission mechanism 76, causing the second nut member 75 to move axially toward the first side L1. Consequently, the second engaging member 71 moves axially toward the first side L1 via the second nut member 75. As a result, the pressure exerted by the second engaging member 71 on the fifth and sixth engaging members 61, 62 is released, and the third engaging mechanism 6 enters a disengaged state.

[0171] On the other hand, when the second drive motor 72 is driven to rotate toward a second side opposite to the first side, the rotational drive force of the second drive motor 72 is transmitted to the second threaded shaft 74 via the second transmission mechanism 76, causing the second nut member 75 to move axially toward the second side L2. Consequently, the second engagement member 71 moves axially toward the second side L2 via the second nut member 75. As a result, the fifth engagement member 61 and the sixth engagement member 62 are pressed by the second engagement member 71, and the third engagement mechanism 6 enters an engaged state.

[0172] 5. Fifth embodiment

[0173] Below, refer to Figure 12 and Figure 13 A fifth embodiment of a vehicle transmission 10 will now be described. This embodiment differs from the second embodiment in that it includes the third engagement mechanism 6 of the fourth embodiment. The following description will focus on the differences from the second embodiment. All other points not specifically described are the same as those of the second embodiment.

[0174] like Figure 12 and Figure 13 As shown, in this embodiment, the fifth gear G5 meshes with the third idler gear IG3 meshing with the first gear G1. That is, the fifth gear G5 and the first gear G1 mesh with the third idler gear IG3 at different positions in the circumferential direction of the third idler gear IG3.

[0175] 6. Sixth Implementation

[0176] Below, refer to Figures 14 to 16 A sixth embodiment of a vehicle transmission 10 will now be described. In this embodiment, the structures of the planetary gear mechanism P and the switching mechanism S differ from those of the second embodiment. The following description will focus on the differences from the second embodiment. Unless otherwise specified, the same principles apply as in the second embodiment.

[0177] like Figures 14 to 16 As shown, in this embodiment, the fourth rotating element E4 does not rotate integrally with the first rotating element E1, but is connected to rotate integrally with the second rotating element E2. That is, in this embodiment, the first gear G1 does not rotate integrally with the sun gear SG, but is connected to rotate integrally with the planetary carrier CR. Furthermore, in this embodiment, the first gear G1 is an externally toothed gear that meshes with the differential input gear 28. In other words, the output gear 27 that rotates integrally with the planetary carrier CR and meshes with the differential input gear 28 in the second embodiment described above is not provided in this embodiment. Therefore, in this embodiment, the first gear G1, which serves as the fourth rotating element E4, functions as the output element O.

[0178] like Figure 15 and Figure 16 As shown, in this embodiment, the third gear G3 meshes with the first idler gear IG1 meshing with the first gear G1. That is, in this embodiment, the third gear G3 and the first gear G1 mesh with the first idler gear IG1 at different positions in the circumferential direction of the first idler gear IG1.

[0179] 7. Seventh Implementation

[0180] Below, refer to Figure 17 and Figure 18 A vehicle transmission 10 according to a seventh embodiment will be described. Figure 14 The structure shown in FIG. 1 is common to the sixth embodiment described above. On the other hand, the structure of the switching mechanism S in this embodiment differs from that in the sixth embodiment described above. The following description will focus on the differences from the sixth embodiment described above. All other points not specifically described are the same as those in the sixth embodiment described above.

[0181] like Figure 17 and Figure 18As shown, in this embodiment, the first idler gear IG1 is not provided. Instead, the third gear G3 meshes with the differential input gear 28. Furthermore, in this embodiment, as in the sixth embodiment described above, the first gear G1 meshes with the differential input gear 28. Therefore, in this embodiment, the third gear G3 and the first gear G1 mesh with the differential input gear 28 at different positions in the circumferential direction of the differential input gear 28. Furthermore, in this embodiment, the differential input gear 28 corresponds to the "gear meshing with the first gear G1."

[0182] 8. Other Implementation Methods

[0183] (1) In the above embodiment, the third gear G3 is described as being meshed with the first idler gear IG1, which is meshed with the first gear G1. However, this configuration is not limiting; a configuration in which the third gear G3 directly meshes with the first gear G1 may also be employed. In this configuration, the first engagement mechanism 3 is engaged, the second engagement mechanism 4 is disengaged (i.e., the first speed stage S1 is established), and while the input member I is rotating, the third rotating element E3 rotates in the same direction as the first rotating element E1. Furthermore, the speed ratio of the first speed stage S1, which is achieved when the first engagement mechanism 3 is engaged and the second engagement mechanism 4 is disengaged, is smaller than the speed ratio of the second speed stage S2, which is achieved when the first engagement mechanism 3 is disengaged and the second engagement mechanism 4 is engaged.

[0184] (1) In the above embodiment, the driving source is described as an example of a configuration in which the rotary electric machine MG is used as the driving source. However, the present invention is not limited to this configuration, and for example, the driving source may be an internal combustion engine.

[0185] (2) In the above embodiment, the first direct-motion conversion mechanism 53 and the second direct-motion conversion mechanism 73 are each a lead screw type direct-motion conversion mechanism. However, this is not limiting. For example, at least one of the first direct-motion conversion mechanism 53 and the second direct-motion conversion mechanism 73 may include a guide rail and a sliding member that slides along the guide rail.

[0186] (3) In the first embodiment and other embodiments described above, the planetary gear mechanism P is described as a single-pinion type planetary gear mechanism. However, the planetary gear mechanism P is not limited to this configuration, and may be a double-pinion type planetary gear mechanism. In this case, for example, a configuration may be employed in which the first rotating element E1 is a sun gear SG, the second rotating element E2 is a ring gear RG, and the third rotating element E3 is a planetary carrier CR.

[0187] (4) In addition, the structures disclosed in the above-mentioned embodiments can also be combined with the structures disclosed in other embodiments as long as no contradiction arises. With respect to other structures, the embodiments disclosed in this specification are merely illustrative in all respects. Therefore, various modifications can be made as appropriate without departing from the scope of the present disclosure.

[0188] [Summary of this embodiment]

[0189] Hereinafter, the outline of the vehicle transmission (10) described above will be described.

[0190] A vehicle transmission (10) includes:

[0191] An input member (I) drivingly connected to a drive source (MG);

[0192] an output member (O) drivingly connected to wheels (W);

[0193] A planetary gear mechanism (P) having a first rotating element (E1), a second rotating element (E2), and a third rotating element (E3), wherein the order of the rotational speeds of the first rotating element (E1), the second rotating element (E2), and the third rotating element (E3) is as described; and

[0194] A switching mechanism (S) switches the state of the planetary gear mechanism (P); wherein,

[0195] The first rotating member (E1) is connected to the input member (I) for integral rotation.

[0196] The second rotating member (E2) is connected to the output member (O) for integral rotation.

[0197] The switching mechanism (S) has:

[0198] a fourth rotating member (E4) disposed on a first axis (X1) serving as an axis on which the planetary gear mechanism (P) is disposed, and connected to rotate integrally with the first rotating member (E1) or the second rotating member (E2);

[0199] a fifth rotating member (E5) disposed on a second axis (X2) different from the first axis (X1) and rotating in conjunction with the third rotating member (E3);

[0200] a sixth rotating member (E6) disposed on the second axis (X2) and rotating in conjunction with the fourth rotating member (E4);

[0201] a first engaging mechanism (3) for disconnecting or connecting power transmission between the fifth rotating member (E5) and the sixth rotating member (E6); and

[0202] The second engaging mechanism (4) selectively fixes the fifth rotating element (E5) to the non-rotating element (NR).

[0203] According to this structure, by engaging the first engagement mechanism (3) and disengaging the second engagement mechanism (4), the fifth rotating element (E5) and the sixth rotating element (E6) rotate integrally, thereby forming a first speed gear (S1) in which the rotation of the input element (I) is decelerated and transmitted to the output element (O) in a state where the ratio of the rotation speeds of the first rotating element (E1) and the third rotating element (E3) is constant. Furthermore, by disengaging the first engagement mechanism (3) and engaging the second engagement mechanism (4), the fifth rotating element (E5) is fixed to the non-rotating element (NR), thereby forming a second speed gear (S2) in which the rotation of the input element (I) is decelerated and transmitted to the output element (O).

[0204] In addition, according to this structure, the first rotating member (E1) of the planetary gear mechanism (P) is connected to the input member (I) for integral rotation, and the second rotating member (E2) of the planetary gear mechanism (P) is connected to the output member (O) for integral rotation. Therefore, the input member (I) and the output member (O) are arranged on the first axis (X1). In addition, the fifth rotating member (E5) and the sixth rotating member (E6) of the switching mechanism (S) are arranged on the second axis (X2). Moreover, the first engaging mechanism (3) of the switching mechanism (S) disconnects or connects the power transmission between the fifth rotating member (E5) and the sixth rotating member (E6), and the second engaging mechanism (4) of the switching mechanism (S) selectively fixes the fifth rotating member (E5) to the non-rotating member (NR).

[0205] Thus, according to this structure, a first speed gear (S1) and a second speed gear (S2) can be selectively formed by an input member (I) and an output member (O) arranged coaxially with the planetary gear mechanism (P) and a switching mechanism (S) partially arranged coaxially with the planetary gear mechanism (P). Therefore, in a structure including the planetary gear mechanism (P) and the switching mechanism (S) for switching the state of the planetary gear mechanism (P), it is easy to achieve miniaturization of at least a portion of the vehicle transmission (10) in the radial direction (R).

[0206] Here, preferably, a power transmission path between the third rotating member (E3) and the fifth rotating member (E5), and a power transmission path between the fourth rotating member (E4) and the sixth rotating member (E6) are formed so that when the first engagement mechanism (3) is in an engaged state, the second engagement mechanism (4) is in a disengaged state, and the input member (I) is rotating, the third rotating member (E3) rotates in a direction opposite to that of the first rotating member (E1),

[0207] According to this structure, the speed ratio of the first speed gear (S1) formed when the first engagement mechanism (3) is in an engaged state and the second engagement mechanism (4) is in a disengaged state is greater than the speed ratio of the second speed gear (S2) formed when the first engagement mechanism (3) is in a disengaged state and the second engagement mechanism (4) is in an engaged state. Moreover, according to this structure, the planetary gear mechanism (P) is configured so that the number of rotating components required to form the power transmission path of the second speed gear (S2) is smaller than that of the first speed gear (S1). Therefore, the transmission efficiency of the driving force of the second speed gear (S2), which is used at a higher ratio during high-speed driving, is higher than that of the first speed gear (S1). Therefore, according to this structure, it is easy to improve the energy efficiency when driving the vehicle.

[0208] In addition, preferably, the switching mechanism (S) further includes a friction-type third engagement mechanism (6) that selectively fixes the fourth rotating element (E4) to the non-rotating element (NR).

[0209] According to this structure, when shifting (upshifting) from a gear with a large speed ratio to a gear with a small speed ratio, that is, a gear with a low rotational speed of the input member (I) at the same vehicle speed, even if the drive source (MG) cannot output negative torque, the rotational speed of the input member (I) can be reduced by changing the third engagement mechanism (6) to a sliding engagement state, thereby quickly performing the shift.

[0210] Furthermore, according to this structure, by bringing any one of the first engagement mechanism (3) and the second engagement mechanism (4) into engagement with the third engagement mechanism (6), the vehicle can also function as a parking brake.

[0211] In addition, preferably, the first rotating member (E1) is a sun gear (SG),

[0212] The second rotating element (E2) is a planet carrier (CR),

[0213] The third rotating element (E3) is an internally toothed ring gear (RG),

[0214] The switching mechanism (S) has:

[0215] a first gear (G1) serving as the fourth rotating member (E4);

[0216] a second gear (G2) serving as the fifth rotating member (E5);

[0217] a third gear (G3) serving as the sixth rotating member (E6); and

[0218] a fourth gear (G4) having external teeth that rotates integrally with the ring gear (RG);

[0219] The second gear (G2) is configured to mesh with the fourth gear (G4),

[0220] The third gear (G3) is configured to mesh with the first gear (G1) or mesh with a gear (IG1) meshed with the first gear (G1).

[0221] According to this structure, a vehicle transmission (10) with a small radial (R) dimension can be realized with a simple structure.

[0222] In the above structure, preferably, a differential gear mechanism (DF) is further provided, wherein the differential gear mechanism (DF) is arranged on a third axis (X3) which is different from the first axis (X1) and the second axis (X2).

[0223] The differential gear mechanism (DF) includes a differential input gear (28) and is configured to distribute the rotation of the differential input gear (28) to a pair of wheels (W).

[0224] The first gear (G1) is an external gear that rotates integrally with the planetary carrier (CR) and meshes with the differential input gear (28).

[0225] The third gear (G3) is configured to mesh with a gear (IG1) meshed with the first gear (G1) or meshed with the differential input gear (28).

[0226] According to this structure, even when the differential gear mechanism (DF) is arranged on a third axis (X3) different from the first axis (X1) and the second axis (X2), it is easy to suppress the number of gears arranged on each axis, thereby easily simplifying the structure of the vehicle transmission (10).

[0227] In addition, preferably, the first joining mechanism (3) and the second joining mechanism (4) are arranged on the second axis (X2) and driven by a common driving mechanism (5).

[0228] The driving mechanism (5) comprises: a coupling member (51) that operates in a manner to selectively bring either the first coupling mechanism (3) or the second coupling mechanism (4) into a coupling state; a driving motor (52); and a screw-type direct-acting conversion mechanism (53) that converts the rotational driving force of the driving motor (52) into a driving force along the second axis (X2) and transmits the driving force to the coupling member (51);

[0229] The driving motor (52) is driven to rotate toward the first side, so that the first engaging mechanism (3) is in an engaged state and the second engaging mechanism (4) is in a disengaged state.

[0230] The driving motor (52) is driven to rotate toward a second side opposite to the first side, so that the second engaging mechanism (4) is brought into an engaged state and the first engaging mechanism (3) is brought into a disengaged state.

[0231] According to this structure, the drive mechanism (5) for driving the first engagement mechanism (3) and the second engagement mechanism (4) is composed of a drive motor (52) and a screw-type direct-acting conversion mechanism (53), so that the vehicle transmission (10) can be easily miniaturized compared to the case of using a hydraulic drive mechanism.

[0232] Industrial applicability

[0233] The technology disclosed herein can be utilized in a vehicle transmission including an input member drivingly connected to a drive source, an output member drivingly connected to wheels, a planetary gear mechanism, and a switching mechanism for switching the state of the planetary gear mechanism.

[0234] Description of reference numerals:

[0235] 10: Vehicle transmission, I: Input member, O: Output member, P: Planetary gear mechanism, E1: First rotating member, E2: Second rotating member, E3: Third rotating member, SG: Sun gear, CR: Carrier, RG: Ring gear, S: Switching mechanism, E4: Fourth rotating member, E5: Fifth rotating member, E6: Sixth rotating member, 3: First engaging mechanism, 4: Second engaging mechanism, 5: First drive mechanism (drive mechanism), 51: First engaging member (engaging member), 52: First drive motor (drive motor), 53: First direct-acting conversion mechanism (direct-acting conversion mechanism), 6: Third engaging mechanism, DF: Differential gear mechanism, G1: First gear, G2: Second gear, G3: Third gear, G4: Fourth gear, NR: Non-rotating member, MG: Rotating electric machine (drive source), W: Wheel, X1: First axis, X2: Second axis, X3: Third axis

Claims

1. A transmission for a vehicle, have: An input member, drivingly connected to a driving source; An output member connected to a wheel drive; A planetary gear mechanism including a first rotating element, a second rotating element, and a third rotating element, wherein the order of the rotational speeds of the first rotating element, the second rotating element, and the third rotating element is as described; as well as A switching mechanism switches the state of the planetary gear mechanism; wherein, The first rotating member is connected to the input member for integral rotation. The second rotating member is connected to the output member for integral rotation. The switching mechanism has: a fourth rotating member disposed on a first axis, which is an axis on which the planetary gear mechanism is disposed, and connected to rotate integrally with the first rotating member or the second rotating member; a fifth rotating member disposed on a second axis different from the first axis and rotating in conjunction with the third rotating member; a sixth rotating member disposed on the second axis and rotating in conjunction with the fourth rotating member; a first engagement mechanism that disconnects or connects power transmission between the fifth rotation member and the sixth rotation member; and The second engaging mechanism selectively fixes the fifth rotating member to the non-rotating member.

2. The vehicle transmission according to claim 1, wherein: A power transmission path is formed between the third rotating member and the fifth rotating member, and a power transmission path is formed between the fourth rotating member and the sixth rotating member, so that when the first engagement mechanism is in an engaged state, the second engagement mechanism is in a disengaged state, and the input member is rotating, the third rotating member rotates in a direction opposite to that of the first rotating member.

3. The vehicle transmission according to claim 1, wherein: The switching mechanism further includes a friction-type third engagement mechanism that selectively fixes the fourth rotation element to the non-rotation element.

4. The vehicle transmission according to any one of claims 1 to 3, wherein: The first rotating member is a sun gear, The second rotating member is a planet carrier, The third rotating member is a ring gear with internal teeth, The switching mechanism has: a first gear serving as the fourth rotating member; a second gear serving as the fifth rotating member; a third gear serving as the sixth rotating member; and a fourth gear with external teeth that rotates integrally with the ring gear, The second gear is configured to mesh with the fourth gear. The third gear is configured to mesh with the first gear or mesh with a gear meshing with the first gear.

5. The vehicle transmission according to claim 4, wherein: further comprising a differential gear mechanism, the differential gear mechanism being arranged on a third axis that is different from the first axis and the second axis, The differential gear mechanism includes a differential input gear and is configured to distribute the rotation of the differential input gear to the pair of wheels. The first gear is an external gear that rotates integrally with the planetary carrier and meshes with the differential input gear. The third gear is configured to mesh with a gear meshing with the first gear or mesh with the differential input gear.

6. The vehicle transmission according to any one of claims 1 to 3, wherein: The first joining mechanism and the second joining mechanism are arranged on the second axis and driven by a common driving mechanism. The drive mechanism comprises: a coupling member that operates to selectively bring one of the first coupling mechanism and the second coupling mechanism into an engaged state; a drive motor; and a screw-type linear motion conversion mechanism that converts the rotational drive force of the drive motor into a drive force along the second axial direction and transmits the drive force to the coupling member; The driving motor is driven to rotate toward the first side, so that the first engaging mechanism is in an engaged state and the second engaging mechanism is in a disengaged state. When the drive motor is rotationally driven toward a second side opposite to the first side, the second engagement mechanism is brought into an engaged state, and the first engagement mechanism is brought into a disengaged state.

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