Multi-stage gearbox

Abstract

Transmission, which includes the following: an input wave (64); an output wave (60); an intermediate shaft (62); a first simple planetary gear set (20) with a first sun gear (26), a first planet carrier (22), a first ring gear (28) and several first planet gears (24); a second simple planetary gear set (30) with a second sun gear (36), a second planet carrier (32), a second ring gear (38) and several second planet gears (34); a third simple planetary gear set (40) with a third sun gear (46), a third planet carrier (42), a third ring gear (48) and several third planet gears (44); a fourth simple planetary gear set (50) comprising a fourth sun gear (56), a fourth planet carrier (52), a fourth ring gear (58) and several fourth planet gears (54); wherein the first planet carrier (22) is rigidly coupled to the second planet carrier (32), the first ring gear (28) to the second sun gear (36), the third planet carrier (42) to the fourth ring gear (58), the third ring gear (48) to the fourth sun gear (56) and the fourth ring gear (58) to the output shaft (60); the second planet carrier (32) is rigidly coupled to the third ring gear (48) via the intermediate shaft (62); the input shaft (64) is selectively coupled to the first sun gear (26) by a first clutch (66), to the second sun gear (36) by a second clutch (68), and to the fourth planet carrier (52) by a third clutch (70); and the first sun gear (26) is held against rotation by a first brake (72), the second ring gear (38) by a second brake (74) and the third sun gear (46) by a third brake (76).

Description

[0001] The present disclosure relates to the field of automatic transmissions for motor vehicles. In particular, the disclosure relates to an arrangement of gears, clutches and the connections between them in a power transmission.

[0002] Many vehicles are used across a wide range of vehicle speeds, both forwards and backwards. However, some engine types can only operate efficiently within a narrow speed range. Therefore, transmissions are often used that can efficiently transfer power at different gear ratios. At low vehicle speeds, the transmission typically operates at a high gear ratio, thus increasing engine torque for improved acceleration. At high vehicle speeds, operating the transmission at a low gear ratio allows for an engine speed that is conducive to smooth and fuel-efficient driving.A gearbox typically has a housing attached to the vehicle structure, an input shaft driven by an engine crankshaft, and an output shaft that drives the vehicle wheels, often by means of a differential arrangement that allows the left and right wheels to rotate at slightly different speeds when the vehicle is turned.

[0003] From DE 101 15 995 A1, DE 10 2011 111 776 A1, DE 10 2009 028 670 A1, DE 10 2008 000 429 A1, DE 10 2012 206 809 A1, DE 10 2012 207 091 A1, DE 10 2008 041 211 A1 and JP 2006 - 349 153 A, a transmission is known in each case, comprising: an input shaft, an output shaft and a first intermediate shaft; a first switchable gear arrangement configured to produce at least five gear ratios between the first intermediate shaft and the input shaft; a second switchable gear arrangement configured to selectively limit the output shaft to a rotation with a speed between zero and a speed of the first intermediate shaft;and a first fixed gear arrangement configured to restrict the input shaft to a rotation at a speed between the speeds of an eighth element and a sixth element, the eighth element being coupled to the first intermediate shaft and the sixth element being coupled to the output shaft.

[0004] Furthermore, DE 10 2012 206 809 A1 describes a gearbox with the subject matter of the Fig. 2 known.

[0005] DE 10 2012 207 091 A1 describes a gearbox with the object of the Fig. 6.

[0006] The object of the invention is to provide a multi-stage planetary gearbox that offers improvements over known gearboxes with regard to shifting energy, planet gear speeds, thermal load, shifting comfort, and / or packaging. This object is achieved by the features of the independent claims. Advantageous embodiments of the invention are described in the dependent claims.

[0007] Accordingly, a group of gear assemblies is disclosed. Each gear assembly includes a front switchable gear assembly configured to produce the various gear ratios between an intermediate shaft and an input shaft, including a reverse gear ratio, a neutral gear ratio, two creeper gear ratios, and a direct drive ratio. The front switchable gear assembly may, for example, comprise two simple planetary gear sets and four clutches. Each gear assembly may further include a rear switchable gear assembly configured to selectively produce specific speed ratios between the input shaft, the intermediate shaft, and an output shaft. The rear switchable gear assembly may, for example, comprise two simple planetary gear sets and two clutches.By engaging the clutches in various combinations of three, nine forward gear ratios and one reverse gear ratio are produced. Fig. Figure 1 is a schematic diagram of a first gear arrangement. Fig. Figure 2 is a schematic diagram of a second gear arrangement known from DE 10 2012 206 809 A1. Fig. Figure 3 is a schematic diagram of a third gear arrangement. Fig. 4 is a lever diagram corresponding to the first, second and third gear arrangement; Fig. 5 is a schematic diagram of a fourth gear arrangement; Fig. Figure 6 is a schematic diagram of a fifth gear arrangement known from DE 10 2012 207 091 A1; Fig. Figure 7 is a schematic diagram of a sixth gear arrangement and Fig. Figure 8 is a schematic diagram of a seventh gear arrangement.

[0008] This document describes embodiments of the present disclosure. It is understood, however, that the disclosed embodiments are merely examples of the invention and that other embodiments may take different and alternative forms. The figures are not necessarily to scale; some features may be exaggerated or minimized to show details of certain components. Therefore, the specific structural and functional details disclosed herein are not to be interpreted as limiting, but merely as a representative basis for teaching a person skilled in the art how to use the present invention in different ways.As is obvious to the average person skilled in the art, various features illustrated and described with reference to any of the figures can be combined with features illustrated in one or more other figures to create embodiments not explicitly illustrated or described. The combinations of the illustrated features provide representative embodiments for typical applications. However, for specific applications or implementations, various combinations and modifications of the features that comply with the teachings of this disclosure may be desirable.

[0009] A gear assembly is a group of rotating elements and clutches designed to establish specific speed ratios between elements. Some speed ratios, called fixed speed ratios, are fixed regardless of the state of any clutches. A gear assembly that only establishes fixed ratios is called a fixed gear assembly. Other speed ratios are only established when certain clutches are fully engaged. A gear assembly that selectively establishes speed ratios is called a selectable gear assembly. A transmission with separate gear ratios has a selectable gear assembly that selectively establishes different gear ratios between an input shaft and an output shaft.

[0010] Elements of a group are rigidly coupled if they are restricted to rotate as a single unit under all operating conditions. Elements can be rigidly coupled by splined connections, welding, press fits, machining from a common solid, or other methods. Minor variations in rotational displacement may occur between rigidly coupled elements, such as displacement due to clearance or shaft compliance. In contrast, two elements are purposefully coupled by a clutch if the clutch restricts them to rotation as a single unit whenever the clutch is fully engaged, and they are free to rotate at different speeds under at least some other operating conditions. Clutches include actively controlled devices, such as hydraulically or electrically actuated clutches, and passive devices, such as freewheel clutches.A coupling that prevents an element from rotating by selectively connecting it to the housing can be described as a brake. Elements of a group are coupled when they are rigidly or selectively coupled.

[0011] An example of a gearbox is in Fig.Figure 1 shows a schematic representation. The transmission uses four simple planetary gear sets 20, 30, 40, and 50. A simple planetary gear set is a type of fixed gear arrangement. A planet carrier 22 rotates about a central axis and supports a set of planet gears 24 such that the planet gears rotate with respect to the planet carrier. The external teeth on the planet gears mesh with the external teeth on a sun gear 26 and with the internal teeth on a ring gear 28. The sun gear and the ring gear are supported to rotate about the same axis as the carrier. A simple planetary gear set specifies the fixed speed ratio such that the speed of the carrier is between the speed of the sun gear and the speed of the ring gear. (This ratio, by definition, includes the state in which all three rotate at the same speed.)More precisely, the rotational speed of the carrier is a weighted average of the rotational speeds of the sun gear and the ring gear, with the weighting factors determined by the number of teeth on each gear. Similar speed ratios are given by other known types of fixed gear assemblies. A double-pinion planetary gear set, for example, limits the rotational speed of the ring gear to a weighted average between the rotational speed of the sun gear and the rotational speed of the carrier.

[0012] Carrier 22 is rigidly coupled to carrier 32, and ring gear 28 is rigidly coupled to sun gear 36. This creates a fixed gear arrangement with four elements. The first element, sun gear 26, and the fourth element, the combination of ring gear 28 and sun gear 36, always exhibit the highest rotational speeds. The rotational speeds of the second element, ring gear 38, and the third element, the combination of carrier 22 and carrier 32, are a weighted average of the rotational speeds of the first and fourth elements. Similarly, carrier 42 is rigidly coupled to ring gear 58, and ring gear 48 is rigidly coupled to sun gear 56, creating a second fixed gear arrangement with four elements. The fifth element, sun gear 46, and the eighth element, the combination of ring gear 48 and sun gear 56, always exhibit the highest rotational speeds.The rotational speeds of the sixth element, the combination of the carrier 42 and the ring gear 58, and of the seventh element, the carrier 52, are a weighted average of the rotational speeds of the fifth and eighth elements.

[0013] A proposed gear tooth ratio for each planetary gear set in Fig. 1 is listed in Table 1. TABLE 1 Ring gear 28 / Sun gear 26 1,85 Ring gear 38 / Sun gear 36 1,75 Ring gear 48 / Sun gear 46 1,60 Ring gear 58 / Sun gear 56 2,30

[0014] The sixth element, 42 and 58, is rigidly coupled to the output shaft 60. The third element, 22 and 32, is rigidly coupled to the eighth element, 48 and 56, via the intermediate shaft 62. The input shaft 64 is selectively coupled to the first element 26 by the coupling 66, selectively coupled to the fourth element, 28 and 36, by the coupling 68, and selectively coupled to the seventh element 52 by the coupling 70. The first element 26 is selectively held against rotation by the brake 72, the second element 38 is selectively held against rotation by the brake 74, and the fifth element 46 is selectively held against rotation by the brake 76.

[0015] As shown in Table 2, engaging the clutches and brakes in combinations of three produces nine forward gear ratios and one reverse gear ratio between input shaft 64 and output shaft 60. An X indicates that the clutch should engage the gear ratio. An (X) indicates that the clutch can be engaged, but this is not required. When the gear sets of Fig.Since the gear sets 20 and 30 have the tooth counts shown in Table 1, the gear ratios are listed in Table 2. The gear sets 20 and 30, the clutches 66 and 68, and the brakes 72 and 74 form a front switchable gear assembly that produces the various gear ratios between the intermediate shaft 62 and the input shaft 64. In particular, engaging the clutch 66 and the brake 74 produces a reverse gear ratio in which the intermediate shaft 62 rotates in the opposite direction to the input shaft 64. Engaging both brakes 72 and 74 holds the intermediate shaft 62 stationary. Engaging the clutch 68 in combination with the brake 72 or the brake 74 produces two creeper gear ratios in which the intermediate shaft 62 rotates more slowly than the input shaft 64.Finally, engaging both clutches 66 and 68 establishes a direct drive ratio in which the intermediate shaft 62 rotates at the same speed as the input shaft 64. Gear sets 40 and 50, clutch 70, and brake 76 form a rear selectable gear arrangement that provides selectable speed ratios between the input shaft 64, intermediate shaft 62, and output shaft 60. In particular, engaging brake 76 establishes a creeper gear ratio between the intermediate shaft 62 and output shaft 60. This creeper gear ratio, in combination with various gear ratios provided by the front gear arrangement, provides the reverse gear and the three forward gear ratios of the transmission. When clutch 70 is engaged, the speed of the input shaft 64 is limited to a weighted average of the speeds of the intermediate shaft 62 and output shaft 60.This speed ratio, in combination with various gear ratios produced by the front gear assembly, establishes the first five forward gear ratios of the transmission. The remaining gear ratio, the 4th, is produced by the simultaneous engagement of clutch 70 and brake 76. The front gear assembly is not involved in producing the 4th gear ratio; however, if desired, one of the clutches or brakes of the front gear assembly can be engaged. TABLE 2 66 68 70 72 74 / 78 76 Relationship Level Backward X X X -3,64 81% 1. X X X 4,47 2. X X X 2,50 1,79 3. X X X 1,63 1,54 4. (X) X X 1,19 1,37 5. X X X 1,00 1,19 6. X X X 0,87 1,15 7. X X X 0,78 1,11 8. X X X 0,70 1,12 9. X X X 0,61 1,14

[0016] The optional freewheel brake 78 passively prevents the second element 38 from rotating in one direction while allowing rotation in the other. Including this element facilitates shifting from 1st to 2nd gear. If a freewheel brake 78 is provided, the brake 74 is not engaged in 1st gear. Shifting into 2nd gear requires only a gradual engagement of the brake 72. If the torque capacity of the brake 72 is sufficient, the freewheel brake 78 is passively overridden. If the freewheel brake 78 is omitted, the brake 74 is engaged in 1st gear. Shifting from 1st to 2nd gear is then accomplished by the coordinated release of the brake 74 and the engagement of the brake 72. All remaining shifts are accomplished by the coordinated release of one clutch or brake and the engagement of another clutch or brake.

[0017] Another exemplary transmission, known from DE 10 2012 206 809 A1, is described in Fig.Figure 2 illustrates the design. The transmission uses four simple planetary gear sets 80, 90, 100, and 110. Carrier 82 is rigidly coupled to ring gear 98, and ring gear 88 is rigidly coupled to carrier 92, forming a fixed four-element gear assembly. The first element, sun gear 86, and the fourth element, sun gear 96, always have the highest rotational speeds. The rotational speeds of the second element, the combination of carrier 82 and ring gear 98, and the third element, the combination of ring gear 88 and carrier 92, are a weighted average of the rotational speeds of the first and fourth elements. Similarly, sun gear 106 is rigidly coupled to sun gear 116, and ring gear 108 is rigidly coupled to carrier 112, forming a second fixed four-element gear assembly. The fifth element, the combination of the sun gear 106 and the sun gear 116, and the eighth element, the ring gear 118, always exhibit the most extreme rotational speeds.The rotational speeds of the sixth element, the carrier 102, and of the seventh element, the combination of the ring gear 108 and the carrier 112, are a weighted average of the rotational speeds of the fifth and eighth elements.

[0018] A proposed gear tooth ratio for each planetary gear set in Fig. 2 is listed in Table 3. TABLE 3 Ring gear 88 / Sun gear 86 1,85 Ring gear 98 / Sun gear 96 1,70 Ring gear 108 / Sun gear 106 3,70 Ring gear 118 / Sun gear 116 2,30

[0019] The sixth element 102 is rigidly coupled to the output shaft 60. The third element, 88 and 92, is rigidly coupled to the eighth element 118 via the intermediate shaft 62. The input shaft 64 is selectively coupled to the first element 86 by the clutch 66, selectively coupled to the fourth element 96 by the clutch 68, and selectively coupled to the seventh element, 108 and 112, by the clutch 70. The first element 86 is selectively prevented from rotating by the brake 72, the second element, 82 and 98, is selectively prevented from rotating by the brake 74, and the fifth element, 106 and 116, is selectively prevented from rotating by the brake 76. Optionally, the freewheel brake 78 passively prevents the second element, 82 and 98, from rotating in one direction, while allowing rotation in the other direction.

[0020] As shown in Table 4, engaging the clutches and brakes in combinations of three produces nine forward gear ratios and one reverse gear ratio between input shaft 64 and output shaft 60. When the gear sets of Fig. 2. For teeth with the numbers shown in Table 3, the gear ratios have the values ​​shown in Table 4. TABLE 4 66 68 70 72 74 / 78 76 Relationship Level Backward X X X -3,37 69% 1. X X X 4,92 2. X X X 2,91 1,69 3. X X X 1,82 1,60 4. (X) X X 1,27 1,44 5. X X X 1,00 1,27 6. X X X 0,85 1,18 7. X X X 0,76 1,11 8. X X X 0,67 1,14 9. X X X 0,57 1,18

[0021] A third exemplary gearbox is shown in Fig.Figure 3 shows the gearbox using four simple planetary gear sets 120, 130, 140, and 150. The sun gear 126 is rigidly coupled to the sun gear 136 via the intermediate shaft 135, and the ring gear 128 is rigidly coupled to the carrier 132, forming a fixed gear arrangement with four elements. The first element, the combination of the sun gear 126 and the sun gear 136, and the fourth element, the ring gear 138, always have the highest rotational speeds. The rotational speeds of the second element, the carrier 122, and the third element, the combination of the ring gear 128 and the carrier 132, are a weighted average of the rotational speeds of the first and fourth elements. Likewise, the carrier 142 is rigidly coupled to the ring gear 158, and the ring gear 148 is rigidly coupled to the carrier 152, creating a second fixed gear arrangement with four elements.The fifth element, the sun gear 146, and the eighth element, the sun gear 156, always exhibit the most extreme rotational speeds. The rotational speeds of the sixth element, the combination of the carrier 142 and the ring gear 158, and of the seventh element, the combination of the ring gear 148 and the carrier 152, are a weighted average of the rotational speeds of the fifth and eighth elements.

[0022] A proposed gear tooth ratio for each planetary gear set in Fig. 3 is listed in Table 5. TABLE 5 Ring gear 128 / Sun gear 126 2,00 Ring gear 138 / Sun gear 136 1,90 Ring gear 148 / Sun gear 146 3,70 Ring gear 158 / Sun gear 156 1,70

[0023] The sixth element, 142 and 158, is rigidly coupled to the output shaft 60. The third element, 128 and 132, is rigidly coupled to the eighth element, 156, via the intermediate shaft 62. The input shaft 64 is selectively coupled to the first element, 126 and 136, by the coupling 66; to the fourth element, 138, by the coupling 68; and to the seventh element, 148 and 152, by the coupling 70. The first element, 126 and 136, is selectively held against rotation by the brake 72; the second element, 122, is selectively held against rotation by the brake 74; and the fifth element, 146, is selectively held against rotation by the brake 76. Optionally, the freewheel brake 78 passively holds the second element 122 against rotation in one direction, while allowing rotation in the other direction.

[0024] As shown in Table 6, engaging the clutches and brakes in combinations of three produces nine forward gear ratios and one reverse gear ratio between input shaft 64 and output shaft 60. When the gear sets of Fig. For teeth 3 shown in Table 5, the gear ratios have the values ​​shown in Table 6. TABLE 6 66 68 70 72 74 / 78 76 Relationship Level Backward X X X -3,46 78% 1. X X X 4,46 2. X X X 2,64 1,69 3. X X X 1,73 1,53 4. (X) X X 1,27 1,36 5. X X X 1,00 1,27 6. X X X 0,83 1,20 7. X X X 0,74 1,13 8. X X X 0,63 1,17 9. X X X 0,53 1,19

[0025] Fig. 4 describes the gearboxes of the Fig. 1, Fig. 2 and Fig. Figure 3 is presented as a lever diagram. Gear elements are shown along a lever according to their relative rotational speeds. These elements rotate about a common axis and have rotational speeds with a fixed linear ratio. The two elements with the most extreme rotational speeds are shown at the endpoints of the lever. The remaining elements are shown at intermediate points according to the weighting factors. Lever 160 corresponds to gear sets 20 and 30 of Fig. 1, the wheelsets 80 and 90 of Fig. 2 and the wheelsets 120 and 130 from Fig. 3. Any fixed gear arrangement consisting of four elements, which imposes the intended speed ratios with the appropriate weighting factors, can replace the corresponding gear sets without affecting the gear stages. In addition to the ones described in the Fig. Of the fixed gear arrangements shown in Figures 1-3, many others are known. Any combination of two two-element planetary gear sets, each rigidly connected to two elements of the other, forms a four-element fixed gear arrangement. Some fixed gear arrangements are preferred over others with respect to packaging, performance, and planetary gear speeds. Similarly, lever 162 corresponds to gear sets 40 and 50 of Figure 1. Fig. 1, the wheelsets 100 and 110 of Fig. 2 and the wheelsets 140 and 150 from Fig.3. Any fixed gear arrangement consisting of four elements, which imposes the intended speed ratios, may replace the corresponding gear sets.

[0026] A fourth exemplary gearbox will be shown in Fig. Figure 5 shows the transmission using four simple planetary gear sets 210, 220, 230, and 240. The ring gear 218 and carrier 222 are rigidly coupled to the sun gear 246 via the intermediate shaft 62. Carrier 232 is rigidly coupled to the output shaft 60. The sun gear 226 and carrier 242 are rigidly coupled to the input shaft 64. The sun gear 236 is fixed against rotation. A suggested gear tooth ratio for each planetary gear set is shown in Figure 5. Fig. 5 is listed in Table 7. TABLE 7 Ring gear 218 / Sun gear 216 1,85 Ring gear 228 / Sun gear 226 1,70 Ring gear 238 / Sun gear 236 1,60 Ring gear 248 / Sun gear 246 2,30

[0027] The sun gear 216 is selectively coupled to the input shaft 64 by the clutch 250 and selectively held against rotation by the brake 256. The carrier 212 is selectively coupled to the ring gear 228 by the clutch 252 and selectively held against rotation by the brake 258. The ring gear 238 is selectively coupled to the sun gear 246 and the intermediate shaft 62 by the clutch 260. The ring gear 248 is selectively coupled to the carrier 232 and the output shaft 60 by the clutch 254. Optionally, a freewheel brake 262 passively holds the carrier 212 against rotation in one direction, while allowing rotation in the other direction.

[0028] As shown in Table 8, engaging the clutches and brakes in combinations of three produces nine forward gear ratios and one reverse gear ratio between input shaft 64 and output shaft 60. When the gear sets of Fig.For teeth 5, the gear ratios shown in Table 7 are as follows: the gear ratios are as shown in Table 8. TABLE 8 250 252 254 256 258 / 262 260 Relationship Level Backward X X X -3,01 69% 1. X X X 4,39 2. X X X 2,59 1,69 3. X X X 1,63 1,60 4. (X) X X 1,19 1,37 5. X X X 1,00 1,19 6. X X X 0,86 1,16 7. X X X 0,79 1,10 8. X X X 0,70 1,13 9. X X X 0,60 1,16

[0029] A fifth exemplary transmission, known from DE 10 2012 207 091 A1, is described in Fig. Figure 6 shows the gearbox using four simple planetary gear sets 310, 320, 330, and 340. The ring gear 318 is rigidly coupled to the ring gear 338 and the sun gear 346 via the intermediate shaft 62. The carrier 312 is rigidly coupled to the ring gear 328. The sun gear 326 and the carrier 342 are rigidly coupled to the input shaft 64. The sun gear 336 is held against rotation. A suggested gear tooth ratio for each planetary gear set is shown in Figure 6. Fig. 6 is listed in Table 9. TABLE 9 Ring gear 318 / Sun gear 316 1,85 Ring gear 328 / Sun gear 326 1,70 Ring gear 338 / Sun gear 336 1,60 Ring gear 348 / Sun gear 346 2,30

[0030] The sun gear 316 is selectively coupled to the input shaft 64 by the clutch 350 and selectively held against rotation by the brake 356. The carrier 312 and the ring gear 328 are selectively held against rotation by the brake 358. The carrier 322 is selectively coupled to the ring gear 318 and the intermediate shaft 62 by the clutch 352. The output shaft 60 is selectively coupled to the carrier 332 by the clutch 360 and selectively coupled to the ring gear 348 by the clutch 354. Optionally, a freewheel brake 362 passively holds the carrier 312 and the ring gear 328 against rotation in one direction, while allowing rotation in the other direction.

[0031] As shown in Table 10, engaging the clutches and brakes in combinations of three produces nine forward gear ratios and one reverse gear ratio between input shaft 64 and output shaft 60. When the gear sets of Fig.For teeth 6, the gear ratios shown in Table 9 are as follows: the gear ratios are as shown in Table 10. TABLE 10 350 352 354 356 358 / 362 360 Relationship Level Backward X X X -3,01 69% 1. X X X 4,39 2. X X X 2,59 1,69 3. X X X 1,63 1,60 4. (X) X X 1,19 1,37 5. X X X 1,00 1,19 6. X X X 0,86 1,16 7. X X X 0,79 1,10 8. X X X 0,70 1,13 9. X X X 0,60 1,16

[0032] A sixth exemplary gearbox will be shown in Fig. Figure 7 shows the gearbox using four simple planetary gear sets 410, 420, 430, and 440. The ring gear 418 is rigidly coupled to the ring gear 438 and the sun gear 446 via the intermediate shaft 62. The sun gear 426 is rigidly coupled to the intermediate shaft 415. The ring gear 428 and the carrier 442 are rigidly coupled to the input shaft 64. The carrier 412 and the sun gear 436 are held against rotation. A suggested gear tooth ratio for each planetary gear set is shown in Figure 7. Fig. 7 is listed in Table 11. TABLE 11 Ring gear 418 / Sun gear 416 2,00 Ring gear 428 / Sun gear 426 1,90 Ring gear 438 / Sun gear 436 1,60 Ring gear 448 / Sun gear 446 2,30

[0033] The intermediate shaft 415 is selectively coupled to the input shaft 64 by the coupling 450, selectively coupled to the sun gear 416 by the coupling 458, and selectively held against rotation by the brake 456. The carrier 422 is selectively coupled to the ring gear 418 and the intermediate shaft 62 by the coupling 452. The output shaft 60 is selectively coupled to the carrier 432 by the coupling 460 and selectively coupled to the ring gear 448 by the coupling 454.

[0034] As shown in Table 12, engaging the clutches and brakes in combinations of three produces nine forward gear ratios and one reverse gear ratio between input shaft 64 and output shaft 60. When the gear sets of Fig. For teeth 7, the gear ratios shown in Table 11 are as follows: the gear ratios are as shown in Table 12. TABLE 12 450 452 454 456 458 460 Relationship Level Backward X X X -3,25 78% 1. X X X 4,19 2. X X X 2,48 1,69 3. X X X 1,63 1,53 4. (X) X X 1,19 1,37 5. X X X 1,00 1,19 6. X X X 0,87 1,15 7. X X X 0,79 1,10 8. X X X 0,70 1,13 9. X X X 0,61 1,15

[0035] A seventh exemplary gearbox is shown in Fig.Figure 8 shows the gearbox using four simple planetary gear sets 510, 520, 530, and 540. Carrier 522 is rigidly coupled to ring gear 538 via intermediate shaft 62. Sun gear 516 is rigidly coupled to intermediate shaft 515. Ring gear 548 is rigidly coupled to output shaft 60. Ring gear 528 and carrier 542 are rigidly coupled to input shaft 64. Carrier 512 and sun gear 536 are fixed against rotation. A suggested gear tooth ratio for each planetary gear set is shown in Figure 8. Fig. 8 is listed in Table 13. TABLE 13 Ring gear 518 / Sun gear 516 2,00 Ring gear 528 / Sun gear 526 1,90 Ring gear 538 / Sun gear 536 1,60 Ring gear 548 / Sun gear 546 2,30

[0036] The intermediate shaft 515 is selectively coupled to the input shaft 64 by the coupling 550, selectively coupled to the sun gear 526 by the coupling 552, and selectively held against rotation by the brake 556. The ring gear 518 is selectively coupled to the carrier 522 and the intermediate shaft 62 by the coupling 558. The output shaft 60 is selectively coupled to the carrier 532 by the coupling 560. The sun gear 546 is selectively coupled to the intermediate shaft 62 by the coupling 554.

[0037] As shown in Table 14, engaging the clutches and brakes in combinations of three produces nine forward gear ratios and one reverse gear ratio between the input shaft 64 and the output shaft 60. When the gear sets of Fig. For teeth 8, the gear ratios shown in Table 13 are as follows: the gear ratios are as shown in Table 14. TABLE 14 550 552 554 556 558 / 562 560 Relationship Level Backward X X X -3,25 78% 1. X X X 4,19 2. X X X 2,48 1,69 3. X X X 1,63 1,53 4. (X) X X 1,19 1,37 5. X X X 1,00 1,19 6. X X X 0,87 1,15 7. X X X 0,79 1,10 8. X X X 0,70 1,13 9. X X X 0,61 1,15

[0038] Although exemplary embodiments are described above, it is not intended that these embodiments describe all possible forms encompassed by the claims. Instead, the terms used in the description serve to describe rather than limit the scope, and it is understood that various modifications can be made without departing from the intent and scope of protection of the disclosure. As previously described, the features of different embodiments can be combined to form further embodiments of the invention that may not be explicitly described or illustrated.While various embodiments may have been described as offering advantages or being preferable to other embodiments or implementations of the prior art with respect to one or more desired properties, it is, as is obvious to the person skilled in the art, that compromises may be made between one or more features or properties in order to achieve the desired overall system characteristics, depending on the specific application and implementation. These features may include, but are not limited to, cost, strength, durability, life-cycle costs, marketability, appearance, packaging, size, ease of maintenance, weight, manufacturability, ease of assembly, etc.Embodiments that are described as less desirable than other embodiments or implementations of the prior art with respect to one or more properties are therefore not outside the scope of protection of the disclosure and may be desirable for certain applications.

Claims

[1] Transmission comprising the following: an input wave (64); an output wave (60); an intermediate shaft (62); a first simple planetary gear set (20) with a first sun gear (26), a first planet carrier (22), a first ring gear (28) and several first planet gears (24); a second simple planetary gear set (30) with a second sun gear (36), a second planet carrier (32), a second ring gear (38) and several second planet gears (34); a third simple planetary gear set (40) with a third sun gear (46), a third planet carrier (42), a third ring gear (48) and several third planet gears (44); a fourth simple planetary gear set (50) comprising a fourth sun gear (56), a fourth planet carrier (52), a fourth ring gear (58) and several fourth planet gears (54); wherein the first planet carrier (22) is rigidly coupled to the second planet carrier (32), the first ring gear (28) to the second sun gear (36), the third planet carrier (42) to the fourth ring gear (58), the third ring gear (48) to the fourth sun gear (56) and the fourth ring gear (58) to the output shaft (60); the second planet carrier (32) is rigidly coupled to the third ring gear (48) via the intermediate shaft (62); the input shaft (64) is selectively coupled to the first sun gear (26) by a first clutch (66), to the second sun gear (36) by a second clutch (68), and to the fourth planet carrier (52) by a third clutch (70); and the first sun gear (26) is held against rotation by a first brake (72), the second ring gear (38) by a second brake (74) and the third sun gear (46) by a third brake (76). [2] Gearbox according to the previous claim, wherein a freewheel brake (78) passively holds the second ring gear (38) against rotation in one direction and allows rotation in the other direction. [3] Transmission comprising the following: an input wave (64); an output wave (60); a first intermediate wave (62); a second intermediate wave (135); a first simple planetary gear set (120) with a first sun gear (126), a first planet carrier (122), a first ring gear (128) and several first planet gears (124); a second simple planetary gear set (130) with a second sun gear (136), a second planet carrier (132), a second ring gear (138) and several second planet gears (134); a third simple planetary gear set (140) with a third sun gear (146), a third planet carrier (142), a third ring gear (148) and several third planet gears (144); a fourth simple planetary gear set (150) comprising a fourth sun gear (156), a fourth planet carrier (152), a fourth ring gear (158) and several fourth planet gears (154); wherein the third planet carrier (142) is rigidly coupled to the fourth ring gear (158) and the output shaft (60), and the third ring gear (148) is rigidly coupled to the fourth planet carrier (152); the first ring gear (128) and the second planet carrier (132) are rigidly coupled to the fourth sun gear (156) via the first intermediate shaft (62) and the first sun gear (126) to the second sun gear (136) via the second intermediate shaft (135); the input shaft (64) is specifically coupled to the first and second sun gears (126, 136) by a first clutch (66), to the second ring gear (138) by a second clutch (68), and to the fourth planet carrier (152) by a third clutch (70); and the first and second sun gears (126, 136) are held against rotation by a first brake (72), the first planet carrier (122) by a second brake (74) and the third sun gear (146) by a third brake (76). [4] Gearbox according to the previous claim, wherein a freewheel brake (78) passively holds the first planet carrier (122) against rotation in one direction and allows rotation in the other direction. [5] Transmission comprising the following: an input wave (64); an output wave (60); a first intermediate wave (62); a first simple planetary gear set (210) with a first sun gear (216), a first planet carrier (212), a first ring gear (218) and several first planet gears (214); a second simple planetary gear set (220) with a second sun gear (226), a second planet carrier (222), a second ring gear (228) and several second planet gears (224); a third simple planetary gear set (230) with a third sun gear (236), a third planet carrier (232), a third ring gear (238) and several third planet gears (234); a fourth simple planetary gear set (240) comprising a fourth sun gear (246), a fourth planet carrier (242), a fourth ring gear (248) and several fourth planet gears (244); wherein the third planet carrier (232) is rigidly coupled to the output shaft (60) and the second sun wheel (226) and the fourth planet carrier (242) to the input shaft (64); the first ring gear (218) and the second planet carrier (222) are rigidly coupled to the fourth sun gear (246) via the first intermediate shaft (62); the third sun wheel (236) is held against rotation; the input wave (64) through a first coupling (250) with the first sun gear (216), the first planet carrier (212) is connected to the second ring gear (228) by a second coupling (252), the third ring gear (238) is connected to the fourth sun gear (246) and the first intermediate shaft (62) by a third coupling (260) and the fourth ring gear (248) is connected by a fourth clutch (254) to the third planet carrier (232) and the output shaft (60) are specifically coupled; and the first sun gear (216) is held against rotation by a first brake (256) and the first planet carrier (212) by a second brake (258). [6] Gearbox according to claim 5, wherein a freewheel brake (262) passively holds the first planet carrier (212) against rotation in one direction and allows rotation in the other direction. [7] Transmission comprising the following: an input wave (64); an output wave (60); a first intermediate wave (62); a second intermediate shaft (415); a first simple planetary gear set (410) with a first sun gear (416), a first planet carrier (412), a first ring gear (418) and several first planet gears (414); a second simple planetary gear set (420) with a second sun gear (426), a second planet carrier (422), a second ring gear (428) and several second planet gears (424); a third simple planetary gear set (430) with a third sun gear (436), a third planet carrier (432), a third ring gear (438) and several third planet gears (434); a fourth simple planetary gear set (440) comprising a fourth sun gear (446), a fourth planet carrier (442), a fourth ring gear (448) and several fourth planet gears (444); wherein the first ring gear (418), the third ring gear (438) and the fourth sun gear (446) are rigidly coupled by the first intermediate shaft (62); the second sun gear (426) is rigidly coupled to the second intermediate shaft (415) and the second ring gear (428) and the fourth planet carrier (442) are rigidly coupled to the input shaft (64); the first planet carrier (412) and the third sun wheel (436) are held against rotation; the second intermediate wave (415) through a first coupling (450) with the input shaft (64) and by a second coupling (458) with the first sun gear (416), the second planet carrier (422) by a third coupling (452) with the first ring gear (418) and the first intermediate shaft (62), the output wave (60) by a fourth coupling (460) with the third planet carrier (432) and are selectively coupled to the fourth ring gear (448) by a fifth clutch (454); and the second intermediate shaft (415) is held against rotation by a first brake (456). [8] Transmission comprising the following: an input wave (64); an output wave (60); a first intermediate wave (62); a second intermediate shaft (515); a first simple planetary gear set (510) with a first sun gear (516), a first planet carrier (512), a first ring gear (518) and several first planet gears (514); a second simple planetary gear set (520) with a second sun gear (526), ​​a second planet carrier (522), a second ring gear (528) and several second planet gears (524); a third simple planetary gear set (530) with a third sun gear (536), a third planet carrier (532), a third ring gear (538) and several third planet gears (534); a fourth simple planetary gear set (540) comprising a fourth sun gear (546), a fourth planet carrier (542), a fourth ring gear (548) and several fourth planet gears (544); wherein the second planet carrier (522) is rigidly coupled to the third ring gear (538) via the first intermediate shaft (62) and the first sun gear (516) is rigidly coupled to the second intermediate shaft (515); the second ring gear (528) and the fourth planet carrier (542) are rigidly coupled to the input shaft (64) and the fourth ring gear (548) to the output shaft (60); the first planet carrier (512) and the third sun wheel (536) are held firmly against rotation; the second intermediate shaft (515) through a first coupling (550) with the input shaft (64) and by a second coupling (552) with the second sun gear (526), ​​the first ring gear (518) by a third coupling (558) with the second planet carrier (522) and the first intermediate shaft (62), the output shaft (60) is connected to the third planet carrier (532) by a fourth coupling (560) and the fourth sun gear (546) is connected to the first intermediate shaft (62) by a fifth coupling (554) are specifically coupled; and the second intermediate shaft (515) is held against rotation by a first brake (556).

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