English:
[0016] In this description, the first, second, or third planetary gear sets may be counted first to third in any order (i.e., left to right, right to left, etc.).
[0022] A third interconnecting member continuously connects the third member of the second planetary gear set with the first member of the third planetary gear set.
[0023] A fourth interconnecting member continuously connects a member of the first, second or third planetary gear set with a member of the third planetary gear set or with a stationary member (ground/transmission case).
[0031] The selectable torque transfer devices are engaged in combinations of zero, one or two to yield an EVT with a continuously variable range of speeds (including reverse) and up to four mechanically fixed forward speed ratios. A "fixed speed ratio" is an operating condition in which the mechanical power input to the transmission is transmitted mechanically to the output, and no power flow (i.e. almost zero) is present in the motor/generators. An electrically variable transmission that may selectively achieve several fixed speed ratios for operation near full engine power can be smaller and lighter for a given maximum capacity. Fixed ratio operation may also result in lower fuel consumption when operating under conditions where engine speed can approach its optimum without using the motor/generators. A variety of fixed speed ratios and variable ratio spreads can be realized by suitably selecting the tooth ratios of the planetary gear sets.
[0038] FIGURE 2b is an operating mode table and fixed ratio mode table depicting some of the operating characteristics of the powertrain shown in Figure 2a;
[0040] FIGURE 3b is an operating mode table and fixed ratio mode table depicting some of the operating characteristics of the powertrain shown in Figure 3 a;
[0042] FIGURE 4b is an operating mode table and fixed ratio mode table depicting some of the operating characteristics of the powertrain shown in Figure 4a;
[0044] FIGURE 5b is an operating mode table and fixed ratio mode table depicting some of the operating characteristics of the powertrain shown in Figure 5 a;
[0046] FIGURE 6b is an operating mode table and fixed ratio mode table depicting some of the operating characteristics of the powertrain shown in Figure 6a;
[0052] FIGURE 9b is an operating mode table and fixed ratio mode table depicting some of the operating characteristics of the powertrain shown in Figure 9a;
[0054] FIGURE 10b is an operating mode table and fixed ratio mode table depicting some of the operating characteristics of the powertrain shown in Figure 10a;
[0058] FIGURE 12b is an operating mode table and fixed ratio mode table depicting some of the operating characteristics of the powertrain shown in Figure 12a;
[0060] FIGURE 13b is an operating mode table and fixed ratio mode table depicting some of the operating characteristics of the powertrain shown in Figure 13a.
[0070] A first torque transfer device, such as input clutch 50, selectively connects the sun gear member 22 of the planetary gear set 20 with the input member 17. A second torque transfer device, such as input clutch 52, selectively connects the ring gear member 34 of the planetary gear set 30 with the input member 17. A third torque transfer device, such as brake 54, selectively connects the carrier member 26 of the planetary gear set 20 with the transmission housing 60. That is, the carrier member 26 is selectively secured against rotation by an operative connection to the non-rotatable housing 60. A fourth torque transfer device, such as the brake 55, is connected in parallel with the motor/generator 80 for selectively braking rotation thereof. A fifth torque transmitting device, such as brake 57, is connected in parallel with the motor/generator 82 for selectively braking rotation thereof. The first, second, third, fourth and fifth torque transfer devices 50, 52, 54, 55 and 57 are employed to assist in the selection of the operational modes of the hybrid transmission 14, as will be hereinafter more fully explained.
[0071] The output drive member 19 of the transmission 14 is secured to ring gear member 44 of the planetary gear set 40.
[0074] The invention may use simple or compound planetary gear sets. In a simple planetary gear set a single set of planet gears are normally supported for rotation on a carrier member that is itself rotatable.
[0080] The torque on the sun gear, the carrier member, and the ring gear can also be simply related to one another if this is done without consideration of the masses of the gears, the acceleration of the gears, or friction within the gear set, all of which have a relatively minor influence in a well designed transmission. The torque applied to the sun gear of a simple planetary gear set must balance the torque applied to the ring gear, in proportion to the number of teeth on each of these gears. For example, the torque applied to a ring gear with twice as many teeth as the sun gear in that set must be twice that applied to the sun gear, and must be applied in the same direction. The torque applied to the carrier member must be equal in magnitude and opposite in direction to the sum of the torque on the sun gear and the torque on the ring gear.
[0089] The first operating mode is the "battery reverse mode" which corresponds with the first row (Batt Rev) of each operating mode table, such as that of Figure Ib. In this mode, the engine is off and the transmission element connected to the engine is not controlled by engine torque, though there may be some residual torque due to the rotational inertia of the engine. The EVT is driven by one of the motor/generators using energy from the battery, causing the vehicle to move in reverse. Depending on the kinematic configuration, the other motor/generator may or may not rotate in this mode, and may or may not transmit torque. If it does rotate, it is used to generate energy which is stored in the battery. In the embodiment of Figure Ib, in the battery reverse mode, the clutch 50 is engaged, the motor 80 has a torque of -1.00, the generator 82 has a torque of -1.01, and a torque ratio of -2.01 is achieved, by way of example. In each operating mode table an (M) next to a torque value in the motor/generator columns 80 and 82 indicates that the motor/generator is acting as a motor, and the absence of an (M) indicates that the motor/generator is acting as generator.
[0090] The second operating mode is the "EVT reverse mode" (or mechanical reverse mode) which corresponds with the second row (EVT Rev) of each operating mode table, such as that of Figure Ib. In this mode, the EVT is driven by the engine and by one of the motor/generators. The other motor/generator operates in generator mode and transfers 100% of the generated energy back to the driving motor. The net effect is to drive the vehicle in reverse. Referring to Figure Ib, for example, in the EVT reverse mode, the clutch 50 is engaged, the motor 80 has a torque of -4.14 units, the generator 82 has a torque of -5.19 units, and an output torque of -8.33 is achieved, corresponding to an engine torque of 1 unit.
[0096] With reference to Figure 2a, a powertrain 110 is shown, including an engine 12 connected to one preferred embodiment of the improved electrically variable transmission, designated generally by the numeral 114. Transmission 114 is designed to receive at least a portion of its driving power from the engine 12.
[00102] The transmission output member 19 is connected with the ring gear member 144 of the planetary gear set 140. A first interconnecting member 170 continuously connects the carrier member 126 of the planetary gear set 120 with the carrier member 136 of the planetary gear set 130. A second interconnecting member 172 continuously connects the ring gear member 124 of the planetary gear set 120 with the sun gear member 132 of the planetary gear set 130. A third interconnecting member 174 continuously connects the ring gear member 134 of the planetary gear set 130 with the carrier member 146 of the planetary gear set 140. A fourth interconnecting member 176 continuously connects the sun gear member 132 of the planetary gear set 130 with the sun gear member 142 of the planetary gear set 140.
[00104] The stator of the second motor/generator 182 is also secured to the transmission housing 160. The rotor of the second motor/generator 182 is secured to the sun gear member 122 of the planetary gear set 120.
[00107] As described previously, each embodiment has thirteen or sixteen functional requirements (corresponding with the 13 or 16 rows of each operating mode table shown in the Figures) which may be grouped into five operating modes. The first operating mode is the "battery reverse mode" which corresponds with the first row (Batt Rev) of the operating mode table of Figure 2b. In this mode, the engine is off and the transmission element connected to the engine is effectively allowed to freewheel, subject to engine inertia torque. The EVT is driven by one of the motor/generators using energy from the battery, causing the vehicle to move in reverse. The other motor/generator may or may not rotate in this mode. As shown in Figure 2b, in this mode the motor 180 has a torque of -1.00 units, the generator 182 has a torque of -1.02 units and an output torque of -2.02 is achieved, by way of example.
[00113] With reference to Figure 3a, a powertrain 210 is shown, including an engine 12 connected to one preferred embodiment of the improved electrically variable transmission, designated generally by the numeral 214. The transmission 214 is designed to receive at least a portion of its driving power from the engine 12. As shown, the engine 12 has an output shaft that serves as the input member 17 of the transmission 214. A transient torque damper (not shown) may also be implemented between the engine 12 and the input member 17 of the transmission 214.
[00116] The planetary gear set 230 also has an outer ring gear member 234 that circumscribes an inner sun gear member 232. A plurality of planet gears 237 are also rotatably mounted in a carrier member 236 such that each planet gear 237 simultaneously, and meshingly, engages both the outer ring gear member 234 and the inner sun gear member 232 of the planetary gear set 230.
[00123] As set forth above the engagement schedule for the torque-transfer devices is shown in the operating mode table and fixed ratio mode table of Figure 3b. Figure 3b also provides an example of torque ratios that are available utilizing the ring gear/sun gear tooth ratios given by way of example in Figure 3b. The N R1 ZN S1 value is the tooth ratio of the planetary gear set 220; the N R2 /N S2 value is the tooth ratio of the planetary gear set 230; and the N R3 /N S3 value is the tooth ratio of the planetary gear set 240. Also, the chart of Figure 3b describes the ratio steps that are attained utilizing the sample of tooth ratios given. For example, the step ratio between the first and second fixed forward torque ratios is 1.32, and the ratio spread is 4.54.
[00129] The planetary gear set 340 also has an outer ring gear member 344 that circumscribes an inner sun gear member 342. A plurality of planet gears 347 are also rotatably mounted in a carrier member 346 such that each planet gear member 347 simultaneously, and meshingly, engages both the outer ring gear member 344 and the inner sun gear member 342 of the planetary gear set 340.
[00130] The transmission output member 19 is connected with the ring gear member 344. A first interconnecting member 370 continuously connects ring gear member 324 with the carrier member 336. A second interconnecting member 372 continuously connects the sun gear member 322 with the sun gear member 332. A third interconnecting. member 374 continuously connects the ring gear member 334 with the sun gear member 342. A fourth interconnecting member 376 continuously connects the carrier member 326 with the carrier member 346.
[00133] The hybrid transmission 314 receives power from the engine 12, and also exchanges power with an electric power source 386, which is operably connected to a controller 388.
[00136] With reference to Figure 5a, a powertrain 410 is shown, including an engine 12 connected to one preferred embodiment of the improved electrically variable transmission, designated generally by the numeral 414. The transmission 414 is designed to receive at least a portion of its driving power from the engine 12.
[00137] As shown, the engine 12 has an output shaft that serves as the input member 17 of the transmission 414. A transient torque damper (not shown) may also be implemented between the engine 12 and the input member 17 of the transmission.
[00138] Irrespective of the means by which the engine 12 is connected to the transmission input member 17, the transmission input member 17 is operatively connected to a planetary gear set in the transmission 414. An output member 19 of the transmission 414 is connected to a final drive 16.
[00141] The planetary gear set 440 also has an outer ring gear member 444 that circumscribes an inner sun gear member 442. A plurality of planet gears 447 are also rotatably mounted in a carrier member 446 such that each planet gear member 447 simultaneously, and meshingly, engages both the outer ring gear member 444 and the inner sun gear member 442 of the planetary gear set 440.
[00142] The transmission output member 19 is continuously connected with the ring gear member 444. A first interconnecting member 470 continuously connects the carrier member 426 with the carrier member 436. A second interconnecting member 472 continuously connects the ring gear member 424 with the sun gear member 432. A third interconnecting member 474 continuously connects the ring gear member 434 with the ring gear member 444. A fourth interconnecting 476 member continuously connects the sun gear member 422 with the sun gear member 442.
[00152] The planetary gear set 540 also has an outer ring gear member 544 that circumscribes an inner sun gear member 542. A plurality of planet gears 547 are also rotatably mounted in a carrier member 546 such that each planet gear member 547 simultaneously, and meshingly engages both the inner, sun gear member 542 and the outer, ring gear member 544 of the planetary gear set 540.
[00153] The transmission output member 19 is continuously connected with the ring gear member 544. The first interconnecting member 570 continuously connects the sun gear member 522 with the sun gear member 532. A second interconnecting member 572 continuously connects the ring gear member 524 with the carrier member 536. A third interconnecting member 574 continuously connects the ring gear member 534 with the sun gear member 542. A fourth interconnecting member 576 continuously connects the carrier member 526 with the carrier member 546.
[00155] A first torque-transfer device, such as input clutch 550, selectively connects the carrier member 546 with the input member 17. A second torque-transfer device, such as input clutch 552, selectively connects the ring gear member 534 with the input member 17. A third torque-transfer device, such as a brake 554, selectively connects the carrier member 526 with the transmission housing 560. A fourth torque transfer device, such as the brake 555, is connected in parallel with the motor/generator 580 for selectively braking rotation thereof. A fifth torque transmitting device, such as the brake 557; is connected in parallel with the motor/generator 582 for selectively braking rotation thereof. The first, second, third, fourth and fifth torque-transfer devices 550, 552, 554, 555 and 557 are employed to assist in the selection of the operational modes of the hybrid transmission 514.
[00156] The hybrid transmission 514 receives power from the engine 12, and also exchanges power with an electric power source 586, which is operably connected to a controller 588.
[00157] The operating mode table of Figure 6b illustrates the clutching engagements, motor/generator conditions and output/input ratios for the five operating modes of the transmission 514. These modes include the "battery reverse mode" (Batt Rev), the "EVT reverse mode" (EVT Rev), "reverse and forward launch modes" (TC Rev and TC For), "continuously variable transmission range modes" (Range 1.1, 1.2, 1.3. . . ) and "fixed ratio modes" (Fl, F2, F3, F4) as described previously.
[00158] As set forth above, the engagement schedule for the torque-transfer devices is shown in the operating mode table and fixed ratio mode table of Figure 6b. Figure 6b also provides an example of torque ratios that are available utilizing the ring gear/sun gear tooth ratios given by way of example in Figure 6b. The N R1 ZN SI value is the tooth ratio of the planetary gear set 520; the N R2 ZN S2 value is the tooth ratio of the planetary gear set 530; and the N R3 ZN S3 value is the tooth ratio of the planetary gear set 540. Also, the chart of Figure 4b describes the ratio steps that are attained utilizing the sample of tooth ratios given. For example, the step ratio between first and second fixed forward torque ratios is 1.93, and the ratio spread is 5.57.
[00164] The planetary gear set 640 also has an outer ring gear member 644 that circumscribes an inner sun gear member 642. A plurality of planet gears 647 are also rotatably mounted in a carrier member 646 such that each planet gear member 647 simultaneously, and meshingly, engages both the outer ring gear member 644 and the inner sun gear member 642 of the planetary gear set 640.
[00167] A first torque-transfer device, such as input clutch 650, selectively connects the sun gear member 642 with the input member 17. A second torque transfer device, such as the brake 655, is connected in parallel with the motor/generator 682 for selectively braking rotation thereof. The first and second torque-transfer devices 650 and 655 are employed to assist in the selection of the operational modes of the transmission 614.
[00168] The hybrid transmission 614 receives power from the engine 12, and also exchanges power with an electric power source 686, which is operably connected to a controller 688.
[00169] The operating mode table of Figure 7b illustrates the clutching engagements, motor/generator conditions and output/input ratios for the five operating modes of the transmission 614. These modes include the "battery reverse mode" (Batt Rev), the "EVT reverse mode" (EVT Rev), "reverse and forward launch modes" (TC Rev and TC For), "continuously variable transmission range modes" (Range 1.1, 1.2, 1.3. . . ) and "fixed ratio mode" (Fl) as described previously.
[00170] As set forth above, the engagement schedule for the torque-transfer devices is shown in the operating mode table and fixed ratio mode table of Figure 7b. Figure 7b also provides an example of torque ratios that are available utilizing the ring gear/sun gear tooth ratios given by way of example in Figure 7b. The Niu/Nsi value is the tooth ratio of the planetary gear set 620; the N R2 ZN S2 value is the tooth ratio of the planetary gear set 630; and the N R3 /N S3 value is the tooth ratio of the planetary gear set 640.
[00171] With reference to Figure 8a, a powertrain 710 is shown, including an engine 12 connected to one preferred embodiment of the improved electrically variable transmission, designated generally by the numeral 714. The transmission 714 is designed to receive at least a portion of its driving power from the engine 12.
[00172] As shown, the engine 12 has an output shaft that serves as the input member 17 of the transmission 714. A transient torque damper (not shown) may also be implemented between the engine 12 and the input member 17 of the transmission.
[00173] Irrespective of the means by which the engine 12 is connected to the transmission input member 17, the transmission input member 17 is operatively connected to a planetary gear set in the transmission 714. An output member 19 of the transmission 714 is connected to a final drive 16.
[00176] The planetary gear set 740 also has an outer ring gear member 744 that circumscribes an inner sun gear member 742. A plurality of planet gears 747 are also rotatably mounted in a carrier member 746 such that each planet gear member 747 simultaneously, and meshingly, engages both the outer ring gear member 744 and the inner sun gear member 742 of the planetary gear set 740.
[00177] The transmission output member 19 is continuously connected with the carrier member 746. A first interconnecting member 770 continuously connects the ring gear member 724 with the sun gear member 732. A second interconnecting member 772 continuously connects the sun gear member 722 with the carrier member 736. A third interconnecting member 774 continuously connects the ring gear member 734 with the sun gear member 742. A fourth interconnecting member 776 continuously connects the carrier member 726 with the transmission housing 760.
[00179] A first torque-transfer device, such as input clutch 750, selectively connects the ring gear member 744 with the input member 17. A second torque-transfer device, such as brake 752, selectively connects the ring gear member 724 with the transmission housing 760. The first and second torque-transfer devices 750 and 752 are employed to assist in the selection of the operational modes of the transmission 714.
[00182] As set forth above, the engagement schedule for the torque-transfer devices is shown in the operating mode table and fixed ratio mode table of Figure 8b. Figure 8b also provides an example of torque ratios that are available utilizing the ring gear/sun gear tooth ratios given by way of example in Figure 8b. The N R1 ZN S i value is the tooth ratio of the planetary gear set 720; the N R2 ZN S2 value is the tooth ratio of the planetary gear set 730; and the N R3 ZN S3 value is the tooth ratio of the planetary gear set 740.
[00183] With reference to Figure 9a, a powertrain 810 is shown, including an engine 12 connected to one preferred embodiment of the improved electrically variable transmission, designated generally by the numeral 814. The transmission 814 is designed to receive at least a portion of its driving power from the engine 12.
[00184] As shown, the engine 12 has an output shaft that serves as the input member 17 of the transmission 814. A transient torque damper (not shown) may also be implemented between the engine 12 and the input member 17 of the transmission.
[00185] Irrespective of the means by which the engine 12 is connected to the transmission input member 17, the transmission input member 17 is operatively connected to a planetary gear set in the transmission 814. An output member 19 of the transmission 814 is connected to a final drive 16.
[00186] The transmission 814 utilizes three planetary gear sets 820, 830 and 840. an inner sun gear member 822. A plurality of planet gears 827 are also rotatably mounted in a carrier member 826 such that each planet gear member 827 simultaneously, and meshingly engages both the outer, ring gear member 824 and the inner, sun gear member 822 of the planetary gear set 820.
[00187] ■ The planetary gear set 830 also has an outer ring gear member 834 that circumscribes an inner sun gear member 832. A plurality of planet gears 837 are also rotatably mounted in a carrier member 836 such that each planet gear member 837 simultaneously, and meshingly engages both the outer, ring gear member 834 and the inner, sun gear member 832 of the planetary gear set 830.
[00188] The planetary gear set 840 also has an outer ring gear member 844 that circumscribes an inner sun gear member 842. A plurality of planet gears 847 are also rotatably mounted in a carrier member 846 such that each planet gear member 847 simultaneously, and meshingly engages both the outer, ring gear member 844 and the inner, sun gear member 842 of the planetary gear set 840.
[00189] The transmission output member 19 is continuously connected with the carrier member 826. The first interconnecting member 870 continuously connects the ring gear member 824 with the sun gear member 832. A second interconnecting member 872 continuously connects the sun gear member 822 with the ring gear member 834. A third interconnecting member 874 continuously connects the carrier member 836 with the carrier member 846. A fourth interconnecting member 876 continuously connects the sun gear member 842 with the transmission housing 860.
[00191] A first torque-transfer device, such as input clutch 850, selectively connects the ring gear member 834 with the input member 17. A second torque-transfer device, such as input clutch 852, selectively connects the carrier member 846 with the input member 17. A third torque-transfer device, such as a brake 854, selectively connects the ring gear member 834 with the transmission housing 860. A fourth torque transfer device, such as the brake 855, is connected in parallel with the motor/generator 880 for selectively braking rotation thereof. The first, second, third and fourth torque-transfer devices 850, 852, 854 and 855 are employed to assist in the selection of the operational modes of the hybrid transmission 814.
[00192] The hybrid transmission 814 receives power from the engine 12, and also exchanges power with an electric power source 886, which is operably connected to a controller 888.
[00200] The planetary gear set 940 also has an outer ring gear member 944 that circumscribes an inner sun gear member 942. A plurality of planet gears 947 are also rotatably mounted in a carrier member 946 such that each planet gear member 947 simultaneously, and meshingly engages both the outer, ring gear member 944 and the inner, sun gear member 942 of the planetary gear set 940.
[00201] The transmission output member 19 is continuously connected with the carrier member 946. The first interconnecting member 970 continuously connects the sun gear member 922 with the ring gear member 934. A second interconnecting member 972 continuously connects the ring gear member 924 with the sun gear member 932. A third interconnecting member 974 continuously connects the carrier member 936 with the ring gear member 944. A fourth interconnecting member 976 continuously connects the sun gear member 942 with the transmission housing 960.
[00203] A first torque-transfer device, such as input clutch 950, selectively connects the sun gear member 922 with the input member 17. A second torque-transfer device, such as input clutch 952, selectively connects the carrier member 926 with the input member 17. A third torque transfer device, such as the brake 955, is connected in parallel with the motor/generator 980 for selectively braking rotation thereof. A fourth torque transmitting device, such as brake 957, is connected in parallel with the motor/generator 982 for selectively braking rotation thereof. The first, second, third and fourth torque-transfer devices 950, 952, 955 and 957 are employed to assist in the selection of the operational modes of the hybrid transmission 914. [00204] The hybrid transmission 914 receives power from the engine 12, and also exchanges power with an electric power source 986, which is operably connected to a controller 988.
[00211] The planetary gear set 1030 also has an outer ring gear member 1034 that circumscribes an inner sun gear member 1032. A plurality of planet gears 1037, 1038 are also rotatably mounted in a carrier member 1036 such that each planet gear member 1038 meshingly engages the sun gear member 1032, and each planet gear 1037 meshingly engages the ring gear member 1034, while the planet gears 1037 and 1038 meshingly engage each other.
[00212] The planetary gear set 1040 also has an outer ring gear member 1044 that circumscribes an inner sun gear member 1042. A plurality of planet gears 1047 are also rotatably mounted in a carrier member 1046 such that each planet gear member 1047 simultaneously, and meshingly engages both the outer, ring gear member 1044 and the inner, sun gear member 1042 of the planetary gear set 1040.
[00213] The transmission output member 19 is continuously connected with the ring gear member 1044. The first interconnecting member 1070 continuously connects the ring gear member 1024 with the sun gear member 1032. A second interconnecting member 1072 continuously connects the carrier member 1026 with the ring gear member 1034. A third interconnecting member 1074 continuously connects the carrier member 1036 with the carrier member 1046. A fourth interconnecting member 1076 continuously connects the sun gear member 1032 with the sun gear member 1042. [00214] The transmission 1014 also incorporates first and second motor/generators
[00215] A first torque-transfer device, such as input clutch 1050, selectively connects the sun gear member 1022 with the input member 17. A second torque-transfer device, such as input clutch 1052, selectively connects the carrier member 1036 with the input member 17. A third torque-transfer device, such as a brake 1054, selectively connects the carrier member 1026 with the transmission housing 1060. A fourth torque transfer device, such as the brake 1055, is connected in parallel with the motor/generator 1080 for selectively braking rotation thereof. A fifth torque transmitting device, such as brake 1057, is connected in parallel with the motor/generator 1082 for selectively braking rotation thereof. The first, second, third, fourth and fifth torque-transfer devices 1050, 1052, 1054, 1055 and 1057 are employed to assist in the selection of the operational modes of the hybrid transmission 1014.
[00216] The hybrid transmission 1014 receives power from the engine 12, and also exchanges power with an electric power source 1086, which is operably connected to a controller 1088.
[00224] The planetary gear set 1140 also has an outer ring gear member 1144 that circumscribes an inner sun gear member 1142. A plurality of planet gears 1147 are also rotatably mounted in a carrier member 1146 such that each planet gear member 1147 simultaneously, and meshingly engages both the outer, ring gear member 1144 and the inner, sun gear member 1142 of the planetary gear set 1140.
[00225] The transmission output member 19 is continuously connected with the ring gear member 1144. The planet carrier assembly member 1126 is continuously connected with (i.e. integral with) the planet carrier assembly member 1136. This integral connection is referred to herein as the first interconnecting member 1170. The integral connection of the long pinion gears 1128 and 1137 is referred to herein as the second interconnecting member 1172. A third interconnecting member 1174 continuously connects the sun gear member 1132 with the sun gear member 1142. A fourth interconnecting member 1176 continuously connects the ring gear member 1134 with the carrier member 1146.
[00227] A first torque-transfer device, such as input clutch 1150, selectively connects the sun gear member 1132 with the input member 17. A second torque-transfer device, such as input clutch 1152, selectively connects the carrier member 1146 with the input member 17. A third torque-transfer device, such as a brake 1154, selectively connects the sun gear member 1132 with the transmission housing 1160. A fourth torque transfer device, such as the brake 1155, is connected in parallel with the motor/generator 1182 for selectively braking rotation thereof. The first, second, third, fourth and fifth torque-transfer devices 1150, 1152, 1154 and 1155 are employed to assist in the selection of the operational modes of the hybrid transmission 1114.
[00228] The hybrid transmission 1114 receives power from the engine 12, and also exchanges power with an electric power source 1186, which is operably connected to a controller 1188.
[00235] The planetary gear set 1230 also has an outer ring gear member 1234 that circumscribes an inner sun gear member 1232. A plurality of planet gears 1237 are also rotatably mounted in a carrier member 1236 such that each planet gear member 1237 simultaneously, and meshingly engages both the outer, ring gear member 1234 and the inner, sun gear member 1232 of the planetary gear set 1230.
[00236] The planetary gear set 1240 also has an outer ring gear member 1244 that circumscribes an inner sun gear member 1242. A plurality of planet gears 1247 are also rotatably mounted in a carrier member 1246 such that each planet gear member 1247 simultaneously, and meshingly engages both the outer, ring gear member 1244 and the inner, sun gear member 1242 of the planetary gear set 1240.
[00237] The transmission output member 19 is continuously connected with the ring gear member 1244. The first interconnecting member 1270 continuously connects the ring gear member 1224 with the carrier member 1232. A second interconnecting member 1272 continuously connects the carrier member 1226 with the carrier member 1236. A third interconnecting member 1274 continuously connects the ring gear member 1234 with the ring gear member 1244. A fourth interconnecting member 1276 continuously connects the sun gear member 1222 with the sun gear member 1242. [00238] The transmission 1214 also incorporates first and second motor/generators
[00239] The stator of the second motor/generator 1282 is also secured to the transmission housing 1260. The rotor of the second motor/generator 1282 is secured to the sun gear member 1222.

中文:
[0016]在本说明书中,所述第一、第二或第三行星齿轮组可以任意的顺序从第一计数到第三(例如,从左到右、从右到左等)。
[0022]第三互连元件将所述第二行星齿轮组的所述第三元件与所述第三行星齿轮组的所述第一元件持续地连接。
[0023]第四互连元件将所述第一、第二或第三行星齿轮组的元件与所述第三行星齿轮组的另一元件或与固定元件(接地/变速器壳体)持续地连接。
[0031]所述可选扭矩传递装置以零个、一个或两个的组合进行接合,以给EVT提供连续可变速度范围(包括倒车)以及多达四个的机械固定前进传动比。“固定传动比”为输入到变速器的机械动力机械地传递到输出,在电动机/发电机内不存在能量流动(即,几乎为零)的操作情形。对于给定的最大容量,可对靠近满发动机功率的操作选择性获得几个固定传动比的电动无级变速器更小、更轻。当运行在发动机速度接近其最大速度而未使用电动机/发电机的状况下时,固定传动比运行还导致更低的燃料消耗。通过适当地选择所述行星齿轮组的齿数比,可实现多种固定传动比和可变传动比范围。
[0038]图2b为示出图2a中所示动力系一些操作特性的操作模式表和固定传动比模式表;
[0040]图3b为示出图3a中所示动力系一些操作特性的操作模式表和固定传动比模式表;
[0042]图4b为示出图4a中所示动力系一些操作特性的操作模式表和固定传动比模式表;
[0044]图5b为示出图5a中所示动力系一些操作特性的操作模式表和固定传动比模式表;
[0046]图6b为示出图6a中所示动力系一些操作特性的操作模式表和固定传动比模式表;
[0052]图9b为示出图9a中所示动力系一些操作特性的操作模式表和固定传动比模式表;
[0054]图10b为示出图10a中所示动力系一些操作特性的操作模式表和固定传动比模式表;
[0058]图12b为示出图12a中所示动力系一些操作特性的操作模式表和固定传动比模式表;
[0060]图13b为示出图13a中所示动力系一些操作特性的操作模式表和固定传动比模式表。
[0070]第一扭矩传递装置(例如,输入离合器50)有选择地将行星齿轮组20的中心齿轮元件22与输入元件17连接。第二扭矩传递装置(例如,输入离合器52)有选择地将行星齿轮组30的齿圈元件34与输入元件17连接。第三扭矩传递装置(例如,制动器54)有选择地将行星齿轮组20的行星架元件26与变速器壳体60连接。即,通过不可旋转的壳体60的操作性连接来有选择地固定行星架元件26的旋转。第四扭矩传递装置(例如,制动器55)与电动机/发电机80并联,以有选择地制动其旋转。第五扭矩传递装置(例如,制动器57)与电动机/发电机82并联,以有选择地制动其旋转。第一、第二、第三、第四和第五扭矩传递装置50、52、54、55和57用于辅助混合动力变速器14的操作模式的选择,将在下文中更加全面地解释。
[0071]变速器14的输出驱动元件19固定到行星齿轮组40的齿圈元件44上。
[0074]本发明可使用简单式或复合式行星齿轮组。在简单式行星齿轮组中,在本身可旋转的行星架元件上通常支撑一组行星齿轮用以旋转。
[0080]如果不考虑齿轮的质量、齿轮的加速度或齿轮组内的摩擦(所有这些都对良好设计的变速器具有比较轻微的影响),那么中心齿轮、行星架元件和齿圈上的扭矩也彼此简单地相关。施加到简单式行星齿轮组的中心齿轮的扭矩必须与施加到齿圈的扭矩相平衡,与这些齿轮各齿轮上的齿数成比例。例如,在齿圈具有中心齿轮两倍齿数的齿轮组中,施加到齿圈的扭矩是施加到中心齿轮的扭矩的两倍,并且必须沿相同方向施加。施加到行星架元件的扭矩必须跟中心齿轮上的扭矩与齿圈上的扭矩之和的大小相等、方向相反。
[0089]第一操作模式为对应于各操作模式表(例如,图1b的操作模式表)的第一行(Batt Rev)的“电池倒车模式”。在该模式中,发动机关闭,并且连接到发动机的变速器元件不由发动机扭矩控制,但由于发动机的旋转惯性可能存在一些残留扭矩。EVT由一个电动机/发电机使用电池的电能来驱动,使得车辆反向运动。依赖于其动力学结构,在该模式中,另一电动机/发电机可能旋转或不旋转,并且可能传递扭矩或不传递扭矩。如果其旋转,其用于产生存储在电池中的能量。在图1b的实施例中,在电池倒车模式中,作为实例,离合器50接合,电动机80具有-1.00的扭矩,发电机82具有-1.01的扭矩,获得-2.01的扭矩比。在各操作模式表中,紧接于电动机/发电机80和82栏中扭矩值的(M)表示电动机/发电机用作电动机,没有(M)表示电动机/发电机用作发电机。
[0090]第二操作模式为对应于各操作模式表(例如,图1b的操作模式表)的第二行(EVT Rev)的“EVT倒车模式”(或机械倒车模式)。在该模式中,EVT由发动机和一个电动机/发电机驱动。另一电动机/发电机操作于发电机模式,并将产生的100%的能量传递回驱动电动机。其实际效果是反向驱动车辆。参考图1b,例如,在EVT倒车模式中,离合器50接合,对应于1单位的发动机扭矩,电动机80具有-4.14单位的扭矩,发电机82具有-5.19单位的扭矩,获得-8.33的输出扭矩。
[0096]参考图2a,所示动力系110包括连接到总地由标记114表示的改进型电动无级变速器的发动机12。变速器114设计成从发动机12接收其至少一部分驱动动力。
[00102]变速器输出元件19与行星齿轮组140的齿圈元件144连接。第一互连元件170将行星齿轮组120的行星架元件126与行星齿轮组130的行星架元件136持续地连接。第二互连元件172将行星齿轮组120的齿圈元件124与行星齿轮组130的中心齿轮元件132持续地连接。第三互连元件174将行星齿轮组130的齿圈元件134与行星齿轮组140的行星架元件146持续地连接。第四互连元件176将行星齿轮组130的中心齿轮元件132与行星齿轮组140的中心齿轮元件142持续地连接。
[00104]第二电动机/发电机182的定子也固定到变速器壳体160上。第一电动机/发电机180的转子固定到行星齿轮组120的中心齿轮元件122上。
[00107]如上所述,各实施例具有可分为五个操作模式的13或16个功能需求(对应于图中所示各操作模式表的13或16行)。第一操作模式为对应于图2b的操作模式表的第一行(Batt Rev)的“电池倒车模式”。在该模式中,发动机关闭,并且连接到发动机的变速器元件有效地允许飞轮经受发动机的旋转惯性。EVT由一个电动机/发电机使用电池的电能来驱动,使得车辆反向运动。另一电动机/发电机可能旋转或不旋转。如图2b中所示,在该模式中,作为实例,电动机180具有-1.00单位的扭矩,发电机182具有-1.02单位的扭矩,获得-2.02的扭矩比。
[00113]参考图3a,所示动力系210包括连接到总地由标记214表示的改进型电动无级变速器的发动机12。变速器214设计成从发动机12接收其至少一部分驱动动力。如图所示,发动机12具有用作变速器214的输入元件17的输出轴。在发动机12与变速器214的输入元件17之间还可使用瞬时扭矩减振器(未示出)。
[00116]行星齿轮组230也具有环绕内中心齿轮元件232的外齿圈元件234。行星架元件236中也可旋转地支撑多个行星齿轮237,使得各行星齿轮元件237同时与行星齿轮组230的外齿圈元件234和内中心齿轮元件232都啮合。
[00123]如上所述,在图3b的操作模式表和固定传动比模式表中示出了扭矩传递装置的接合策略。图3b还提供了利用借助于图3b的实例给出的齿圈/中心齿轮齿数比可获得的扭矩比实例。NR1/NS1值为行星齿轮组220的齿数比;NR2/NS2值为行星齿轮组230的齿数比;NR3/NS3值为行星齿轮组240的齿数比。图3b的图表还描述了利用给出的齿数比样例得到的传动比步长。例如,第一与第二固定前进扭矩比之间的传动比步长为1.32,传动比跨度为4.54。
[00129]行星齿轮组340也具有环绕内中心齿轮元件342的外齿圈元件344。行星架元件346中也可旋转地支撑多个行星齿轮347,使得各行星齿轮元件347同时与行星齿轮组340的外齿圈元件344和内中心齿轮元件342都啮合。
[00130]变速器输出元件19与齿圈元件344相连。第一互连元件370将齿圈元件324与行星架元件336持续地连接。第二互连元件372将中心齿轮元件322与中心齿轮元件332持续地连接。第三互连元件374将齿圈元件334与中心齿轮元件342持续地连接。第四互连元件376将行星架元件336与行星架元件346持续地连接。
[00133]混合变速器314从发动机12接收动力,还与可操作地连接到控制器388的电源386交换动力。
[00136]参考图5a,所示动力系410包括连接到总地由标记414表示的改进型电动无级变速器的发动机12。变速器414设计成从发动机12接收其至少一部分驱动动力。
[00137]如图所示,发动机12具有用作变速器414的输入元件17的输出轴。在发动机12与变速器的输入元件17之间还可使用瞬时扭矩减振器(未示出)。
[00138]与将发动机12连接到变速器输入元件17的方法无关,变速器输入元件17可操作地连接到变速器414中的行星齿轮组。变速器414的输出元件19连接到主减速器16。
[00141]行星齿轮组440也具有环绕内中心齿轮元件442的外齿圈元件444。行星架元件446中也可旋转地支撑多个行星齿轮447,使得各行星齿轮元件447同时与行星齿轮组440的外齿圈元件444和内中心齿轮元件442都啮合。
[00142]变速器输出元件19与齿圈元件444相连。第一互连元件470将行星架元件426与行星架元件436持续地连接。第二互连元件472将齿圈元件424与中心齿轮元件432持续地连接。第三互连元件474将齿圈元件434与齿圈元件444持续地连接。第四互连元件476将中心齿轮元件422与中心齿轮元件442持续地连接。
[00152]行星齿轮组540也具有环绕内中心齿轮元件542的外齿圈元件544。行星架元件546中也可旋转地支撑多个行星齿轮547,使得各行星齿轮元件547同时与行星齿轮组540的内中心齿轮元件542和外齿圈元件544都啮合。
[00153]变速器输出元件19与齿圈元件544持续地连接。第一互连元件570将中心齿轮元件522与中心齿轮元件532持续地连接。第二互连元件572将齿圈元件524与行星架元件536持续地连接。第三互连元件574将齿圈元件534与中心齿轮元件542持续地连接。第四互连元件576将行星架元件526与行星架元件546持续地连接。
[00155]第一扭矩传递装置(例如,输入离合器550)有选择地将行星架元件546与输入元件17连接。第二扭矩传递装置(例如,输入离合器552)有选择地将齿圈元件534与输入元件17连接。第三扭矩传递装置(例如,制动器554)有选择地将行星架元件526与变速器壳体560连接。第四扭矩传递装置(例如,制动器555)与电动机/发电机580并联,以有选择地制动其旋转。第五扭矩传递装置(例如,制动器557)与电动机/发电机582并联,以有选择地制动其旋转。第一、第二、第三、第四和第五扭矩传递装置550、552、554、555和557用于辅助混合变速器514的操作模式的选择。
[00156]混合变速器514从发动机12接收动力,还与可操作地连接到控制器588的电源586交换收动力。
[00157]图6b的操作模式表示出了变速器514五个操作模式的离合接合、电动机/发电机状况及输出/输入比。这些模式包括如前所述的“电池倒车模式”(Batt Rev)、“EVT倒车模式”(EVT Rev)、“倒车和前进起动模式”、“无级变速器范围模式”(范围1.1、1.2、1.3...)和“固定传动比模式”(F1、F2、F3、F4)。
[00158]如上所述,在图6b的操作模式表和固定传动比模式表中示出了扭矩传递装置的接合策略。图6b还提供了利用借助于图6b的实例给出的齿圈/中心齿轮齿数比可获得的扭矩比实例。NR1/NS1值为行星齿轮组520的齿数比;NR2/NS2值为行星齿轮组530的齿数比;NR3/NS3值为行星齿轮组540的齿数比。图6b的图表还描述了利用给出的齿数比样例得到的传动比步长。例如,第一与第二固定前进扭矩比之间的传动比步长为1.93,传动比跨度为5.57。
[00164]行星齿轮组640也具有环绕内中心齿轮元件642的外齿圈元件644。行星架元件646中也可旋转地支撑多个行星齿轮647,使得各行星齿轮元件647同时与行星齿轮组640的内中心齿轮元件642和外齿圈元件644都啮合。
[00167]第一扭矩传递装置(例如,输入离合器650)有选择地将中心齿轮元件642与输入元件17连接。第二扭矩传递装置(例如,制动器655)与电动机/发电机682并联,以有选择地制动其旋转。第一和第二扭矩传递装置650和655用于辅助混合动力变速器614的操作模式的选择。
[00168]混合变速器614从发动机12接收动力,还与可操作地连接到控制器688的电源686交换动力。
[00169]图7b的操作模式表示出了变速器614五个操作模式的离合接合、电动机/发电机状况及输出/输入比。这些模式包括如前所述的“电池倒车模式”(Batt Rev)、“EVT倒车模式”(EVT Rev)、“倒车和前进起动模式”、“无级变速器范围模式”(范围1.1、1.2、1.3...)和“固定传动比模式”(F1)。
[00170]如上所述,在图7b的操作模式表和固定传动比模式表中示出了扭矩传递装置的接合策略。图7b还提供了利用借助于图7b的实例给出的齿圈/中心齿轮齿数比可获得的扭矩比实例。NR1/NS1值为行星齿轮组620的齿数比;NR2/NS2值为行星齿轮组630的齿数比;NR3/NS3值为行星齿轮组640的齿数比。
[00171]参考图8a,所示动力系710包括连接到总地由标记714表示的改进型电动无级变速器的发动机12。变速器714设计成从发动机12接收其至少一部分驱动动力。
[00172]如图所示,发动机12具有用作变速器714的输入元件17的输出轴。在发动机12与变速器的输入元件17之间还可使用瞬时扭矩减振器(未示出)。
[00173]与将发动机12连接到变速器输入元件17的方法无关,变速器输入元件17可操作地连接到变速器714中的行星齿轮组。变速器714的输出元件19连接到主减速器16。
[00176]行星齿轮组740也具有环绕内中心齿轮元件742的外齿圈元件744。行星架元件746中也可旋转地支撑多个行星齿轮747,使得各行星齿轮元件747同时与行星齿轮组740的内中心齿轮元件742和外齿圈元件744都啮合。
[00177]变速器输出元件19与行星架元件746持续地连接。第一互连元件770将齿圈元件724与中心齿轮元件732持续地连接。第二互连元件772将中心齿轮元件722与行星架元件736持续地连接。第三互连元件774将齿圈元件734与中心齿轮元件742持续地连接。第四互连元件776将行星架元件726与变速器壳体760持续地连接。
[00179]第一扭矩传递装置(例如,输入离合器750)有选择地将齿圈元件744与输入元件17连接。第二扭矩传递装置(例如,制动器752)有选择地将齿圈元件724与变速器壳体760连接。第一和第二扭矩传递装置750和752用于辅助混合动力变速器714的操作模式的选择。
[00182]如上所述,在图8b的操作模式表和固定传动比模式表中示出了扭矩传递装置的接合策略。图8b还提供了利用借助于图8b的实例给出的齿圈/中心齿轮齿数比可获得的扭矩比实例。NR1/NS1值为行星齿轮组720的齿数比;NR2/NS2值为行星齿轮组730的齿数比;NR3/NS3值为行星齿轮组740的齿数比。
[00183]参考图9a,所示动力系810包括连接到总地由标记814表示的改进型电动无级变速器的发动机12。变速器814设计成从发动机12接收其至少一部分驱动动力。
[00184]如图所示,发动机12具有用作变速器814的输入元件17的输出轴。在发动机12与变速器的输入元件17之间还可使用瞬时扭矩减振器(未示出)。
[00185]与将发动机12连接到变速器输入元件17的方法无关,变速器输入元件17可操作地连接到变速器814中的行星齿轮组。变速器814的输出元件19连接到主减速器16。
[00186]变速器814使用三个行星齿轮组820、830和840。行星齿轮组820使用环绕内中心齿轮822的外齿圈元件824。行星架元件826可旋转地支撑多个行星齿轮827,使得各行星齿圈元件827同时与行星齿轮组820的外齿圈元件824和内中心齿轮元件822都啮合。
[00187]行星齿轮组830也具有环绕内中心齿轮元件832的外齿圈元件834。行星架元件836中也可旋转地支撑多个行星齿轮837,使得各行星齿轮元件837同时与行星齿轮组830的内中心齿轮元件832和外齿圈元件834都啮合。
[00188]行星齿轮组840也具有环绕内中心齿轮元件842的外齿圈元件844。行星架元件846中也可旋转地支撑多个行星齿轮847,使得各行星齿轮元件847同时与行星齿轮组840的内中心齿轮元件842和外齿圈元件844都啮合。
[00189]变速器输出元件19与行星架元件826持续地连接。第一互连元件870将齿圈元件824与中心齿轮元件832持续地连接。第二互连元件872将中心齿轮元件822与齿圈元件834持续地连接。第三互连元件874将行星架元件836与行星架元件846持续地连接。第四互连元件876将中心齿轮元件842与变速器壳体860持续地连接。
[00191]第一扭矩传递装置(例如,输入离合器850)有选择地将齿圈元件834与输入元件17连接。第二扭矩传递装置(例如,输入离合器852)有选择地将行星架元件846与输入元件17连接。第三扭矩传递装置(例如,制动器854)有选择地将齿圈元件834与变速器壳体860连接。第四扭矩传递装置(例如,制动器855)与电动机/发电机880并联,以有选择地制动其旋转。第一、第二、第三和第四扭矩传递装置850、852、854和855用于辅助混合变速器814的操作模式的选择。
[00192]混合变速器814从发动机12接收动力,还与可操作地连接到控制器888的电源886交换动力。
[00200]行星齿轮组940也具有环绕内中心齿轮元件942的外齿圈元件944。行星架元件946中也可旋转地支撑多个行星齿轮947,使得各行星齿轮元件947同时与行星齿轮组940的内中心齿轮元件942和外齿圈元件944都啮合。
[00201]变速器输出元件19与行星架元件946持续地连接。第一互连元件970将中心齿轮元件922与齿圈元件934持续地连接。第二互连元件972将齿圈元件924与中心齿轮元件932持续地连接。第三互连元件974将行星架元件936与齿圈元件944持续地连接。第四互连元件976将中心齿轮元件942与变速器壳体960持续地连接。
[00203]第一扭矩传递装置(例如,输入离合器950)有选择地将中心齿轮元件922与输入元件17连接。第二扭矩传递装置(例如,输入离合器952)有选择地将行星架元件926与输入元件17连接。第三扭矩传递装置(例如,制动器955)与电动机/发电机980并联,以有选择地制动其旋转。第四扭矩传递装置(例如,制动器957)与电动机/发电机982并联,以有选择地制动其旋转。第一、第二、第三和第四扭矩传递装置950、952、955和957用于辅助混合变速器914的操作模式的选择。
[00211]行星齿轮组1030也具有环绕内中心齿轮元件932的外齿圈元件1034。行星架元件1036中也可旋转地支撑多个行星齿轮1037、1038,使得各行星齿轮元件1038与中心齿轮元件1032啮合,各行星齿轮1037同时与齿圈元件1034啮合,同时行星齿轮1037、1038彼此啮合。
[00212]行星齿轮组1040也具有环绕内中心齿轮元件1042的外齿圈元件1044。行星架元件1046中也可旋转地支撑多个行星齿轮1047,使得各行星齿轮元件1047同时与行星齿轮组1040的内中心齿轮元件1042和外齿圈元件1044都啮合。
[00213]变速器输出元件19与齿圈元件1044持续地连接。第一互连元件1070将齿圈元件1024与中心齿轮元件1032持续地连接。第二互连元件1072将行星架元件1026与齿圈元件1034持续地连接。第三互连元件1074将行星架元件1036与行星架元件1046持续地连接。第四互连元件1076将中心齿轮元件1032与中心齿轮元件1042持续地连接。
[00215]第一扭矩传递装置(例如,输入离合器1050)有选择地将中心齿轮元件1022与输入元件17连接。第二扭矩传递装置(例如,输入离合器1052)有选择地将行星架元件1036与输入元件17连接。第三扭矩传递装置(例如,制动器1054)有选择地将行星架元件1026与变速器壳体1060连接。第四扭矩传递装置(例如,制动器1055)与电动机/发电机1080并联,以有选择地制动其旋转。第五扭矩传递装置(例如,制动器1057)与电动机/发电机1082并联,以有选择地制动其旋转。第一、第二、第三、第四和第五扭矩传递装置1050、1052、1054、1055和1057用于辅助混合变速器1014的操作模式的选择。
[00216]混合变速器1014从发动机12接收动力,还与可操作地连接到控制器1088的电源1086交换动力。
[00224]行星齿轮组1140也具有环绕内中心齿轮元件1142的外齿圈元件1144。行星架元件1146中也可旋转地支撑多个行星齿轮1147,使得各行星齿轮元件1147同时与行星齿轮组1140的内中心齿轮元件1142和外齿圈元件1144都啮合。
[00225]变速器输出元件19与齿圈元件1144持续地连接。行星架元件1126与行星架元件1136持续地连接(即,成一整体)。该一体连接这里称为第一互连元件1170。长行星齿轮1128与1137的一体连接这里称为第二互连元件1172。第三互连元件1174将中心齿轮元件1132与中心齿轮元件1142持续地连接。第四互连元件1176将齿圈元件1134与行星架元件1146持续地连接。
[00227]第一扭矩传递装置(例如,输入离合器1150)有选择地将中心齿轮元件1132与输入元件17连接。第二扭矩传递装置(例如,输入离合器1152)有选择地将行星架元件1146与输入元件17连接。第三扭矩传递装置(例如,制动器1154)有选择地将中心齿轮元件1132与变速器壳体1160连接。第四扭矩传递装置(例如,制动器1155)与电动机/发电机1182并联,以有选择地制动其旋转。第一、第二、第三和第四扭矩传递装置1150、1152、1154和1155用于辅助混合变速器1114的操作模式的选择。
[00228]混合变速器1114从发动机12接收动力,还与可操作地连接到控制器1188的电源1186交换动力。
[00235]行星齿轮组1230也具有环绕内中心齿轮元件1232的外齿圈元件1234。行星架元件1236内也可旋转地支撑多个行星齿轮1237,使得各行星齿轮1237同时与行星齿轮组1230的外齿圈元件1234和内中心齿轮元件1232都啮合。
[00236]行星齿轮组1240也具有环绕内中心齿轮元件1242的外齿圈元件1244。行星架元件1246中也可旋转地支撑多个行星齿轮1247,使得各行星齿轮元件1247同时与行星齿轮组1240的内中心齿轮元件1242和外齿圈元件1244都啮合。
[00237]变速器输出元件19与齿圈元件1244持续地连接。第一互连元件1270将齿圈元件1224与行星架元件1232持续地连接。第二互连元件1272将行星架元件1226与行星架元件1236持续地连接。第三互连元件1274将齿圈元件1234与齿圈元件1244持续地连接。第四互连元件1276将中心齿轮元件1222与中心齿轮元件1242持续地连接。
[00239]第二电动机/发电机1282的定子也固定到变速器壳体1260上。第二电动机/发电机1282的转子固定到中心齿轮元件1222上。