Planetary gear system

Abstract: A planetary gear system includes a main planetary gear train including first (20) and second (22) planetary gear sets coaxial with an input shaft (12), and a secondary planetary gear train (10) including a third planetary gear set (26) coaxial with an output shaft (14). Each gear set has three rotary active elements, a sun gear, a ring gear and a planet carrier. Among six rotary active elements of the first (20) and second (22) gear sets, one active element of the first gear set (20) is connected with one active element of the second gear set (22), and another active element of the first gear set (20) is connected with another active element of the second gear set (22) so that each connected element pair rotate as a unit. Furthermore, the third gear set (26) is combined with the main gear train in such a compound manner that rotations of two different active elements of the third gear set are restricted, respectively by two different active elements of the main gear train.

Description: BACKGROUND OF THE INVENTION The present invention relates to planetary gear systems for automatic transmissions, especially of a type having three planetary gear sets. JP-A-6283541 discloses a conventional planetary gear system for providing five or more forward speeds. This planetary gear system has a main planetary gear train composed of two planetary gear sets for providing four forward speeds, and a secondary planetary gear train which is composed of one planetary gear set, and which is connected in series with the main planetary gear train. JP-A-6347542 discloses a planetary gear system for a transaxle of an F.F. vehicle. This planetary gear system has a main planetary gear train coaxial with an input shaft, and a secondary planetary gear train coaxial with an output shaft which is parallel to the input shaft. The input and output shafts are connected by gearing. However, the latter system requires two friction devices for the secondary planetary gear train in addition to five friction devices for the main planetary gear train, so that the number of the required friction devices is relatively great. Furthermore, the gear ratio finally obtained by the gear arrangement in which the main planetary gear train is connected in series with the secondary planetary gear train, is determined by a product between the gear ratio of the main planetary gear train and the gear ratio of the secondary gear train. Therefore, the gear ratios of the conventional gear system tend to be too high or too low, and it is difficult to set the gear ratios of all the forward speeds equal to the optimum values. The conventional gear systems are so arranged that the main and secondary gear trains are shifted independently. Therefore, these systems require a complicated control unit for controlling the friction devices in order to reduce a shift shock, especially to reduce a shift shock when both planetary gear trains are shifted simultaneously. JP-A-62155356 discloses another conventional planetary gear system for F.F. vehicles. This conventional gear system is composed of one planetary gear set and a plurality of pairs of mating gears of a parallel shaft type. However, the parallel shaft type gears of this conventional system increases the size of the transmission. Some of the friction devices must have a sufficiently great torque capacity to endure torque of a considerable magnitude. Furthermore, some clutches are arranged in series with the parallel shaft type gears, so that the size of the system is increased. The controllability of this conventional gear system is relatively poor because some clutches are switched while they are rotating. A planetary gear system as indicated in the precharacterizing part of claim 1 is disclosed in EP-A-0 371 651 falling under Article 54(3) EPC which planetary transmission using two simple planetatry gear sets forming a first gear train connected to a third double-pinion planetary gear set having two connections between each two sets providing five forwards ratios and one reverse ratio while a clutch remains closed. This prior art transmission comprises a first planetary gear train having first and second planetary gear sets which are interconnected twice, said first panetary gear train being connected with said input means; a second planetary gear train having a third planetary gear set, said second planetary gear train being connected with said output means; a first connecting means for connecting said first planetary carrier of the first planetary gear set of the first gear train with said second planetary gear train and with the output element, and a second connecting means for connecting said first planetary gear train with said second planetary gear train. It is the object of the invention to improve a planetary gear system as indicated in the precharacteriziing part of claim 1 such that shift control is facilitated and the size of the gear system is reduced. In accordance with the invention this object is solved by the features as claimed in claim 1. A planetary gear drive according to the preamble of claim 1 is known from DE-A-2 141 354. The planetary gear drive disclosed in this document is basically designed to have three different forward speeds. A fourth forward speed is obtained by the second planetary gear train. GB-A-2 171 766 discloses a planetary gear system, having a first planetary gear train which is connected with an input shaft of the gear system. The first planetary gear train comprises a first and a second planetary gear set. Further, a second planetary gear train is provided which is connected to an output shaft of the gear system and which includes a third planetary gear set. A first and a second spur gear connect said first planetary gear train with said second planetary gear train. SUMMARY OF THE INVENTION It is an object of the present invention to provide a planetary gear system having at least three planetary gear sets which is designed to provide a desired number of gear ratios and which facilitate the shift control and reduces the size of the gear system. This object is solved according to the invention by the subject-matter of claim 1. Preferred embodiments of the invention are subject-matter of the subclaims. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a schematic view (skeleton diagram) of a planetary gear system according to a first embodiment of the invention. Fig. 2A is a table showing the operating states of friction devices of the planetary gear system of the first embodiment. Fig. 2B is a table showing gear sizes employed in the gear system of the first embodiment. Fig. 2C is a table showing the gear ratio value of each speed obtained by the gear system of the first embodiment. Fig. 3 is a schematic view of a planetary gear system according to a second embodiment of the invention. DETAILED DESCRIPTION OF THE INVENTION A first embodiment of the present invention is shown in Figs. 1 and 2A-2C. A planetary gear system 10 of the first embodiment is a component part of an automatic transmission of an F.F. vehicle. The planetary gear system 10 of the first embodiment includes an input means for receiving an input rotation from a torque converter 11 which is connected with an engine of the vehicle, and an output means for outputting an output rotation. The input means comprises an input shaft 12, and the output means comprises an output shaft 14. In this embodiment, the input and output shafts 12 and 14 are arranged in parallel to each other. An engine torque of the engine is transmitted through the torque converter 11 disposed on the left side of the planetary gear system as viewed in Fig. 1, to the input shaft 12. The output rotation of the planetary gear system 10 is delivered from the output shaft 14 through a final gear 16 to a differential gear 18. The left end of the output shaft 14 is connected with the final gear 16, as shown in Fig. 1. The planetary gear system 10 further includes a first (or main) planetary gear train and a second (or secondary) planetary gear train. In this embodiment, the first planetary gear train consists of a first planetary gear set 20 and a second planetary gear set 22, and the second planetary gear train consists of a third planetary gear set 26. The first planetary gear set 20 includes a first sun gear 20s, a first ring gear 20r, and a first planet carrier 20pc. These three elements are rotary active elements of the first planetary gear set 20. The first planetary gear set 20 is a single pinion type planetary gear set(or a simple planetary arrangement). In this embodiment, the first planet carrier 20pc rotatably supports at least one first pinion 20p which is in dirct engagement with both the first sun gear 20s and the first ring gear 20r. The first planetary gear set 20 is coaxial with the input shaft 12. The second planetary gear set 22 includes a second sun gear 22s, a second ring gear 22r, and a second planet carrier 22pc. These three elements are rotary active elements of the second planetary gear set 22. The second planetary gear set 22 is also of the single pinion type. In this embodiment, at least one second pinion 22p is rotatably supported on the second planet carrier 22pc. The second pinion 22p is in direct mesh with both the second sun gear 22s and the second ring gear 22r. The second planetary gear set 22 is also coaxial with the input shaft 12. The second planetary gear set 22 is disposed on the left side of the first planetary gear set 20, as viewed in Fig. 1. The third planetary gear set 26 includes a third sun gear 26s, a third ring gear 26r and a third planet carrier 26pc, which are three active elements of the third planetary gear set 26. The third planetary gear set 26 is a double pinion type planetary gear set (a dual planetary arrangement). In this embodiment, the third planet carrier 26pc rotatably supports one or more pinion groups each of which includes a third inner pinion 26p1 and a third outer pinion 26p2. In the pinion group or each of the pinion groups, the third inner pinion 26p1 is in direct mesh with both the third sun gear 26s and the third outer pinion 26p2, and the third outer pinion 26p2 is in direct mesh with both the third inner pinion 26p1 and the third ring gear 26r. Therefore, rotation can be transmitted from the third sun gear 26s to the third ring gear 26r in such a manner that the rotational direction of the third ring gear 26r is the same as the rotational direction of the third sun gear 26s. The third planetary gear set 26 is mounted on the output shaft 14 so that the third planetary gear set 26 is coaxial with the output shaft 14. The third planetary gear set 26 is disposed at an axial position corresponding to the axial position of the first planetary gear set 20. The planetary gear system further includes a friction device group which, in this embodiment, includes six friction devices. The friction devices of this embodiment are first, second and third clutches C1, C2 and C3, and first, second and third band brakes B1, B2 and B3. The first clutch C1 is disposed between the input shaft 12 and the first sun gear 20s. The first clutch C1 can connect the first sun gear 20s with the input shaft 12, and disconnect the first sun gear 20s from the input shaft 12. The first band brake B1 is disposed between a stationary housing (transmission case) and the first ring gear 20r. The first band brake B1 can hold or ground the first ring gear 20r. The second sun gear 22s is connected to the input shaft 12 through the third clutch C3, and further connected to the stationary housing through the third band brake B3. The third clutch C3 can connect the second sun gear 22s with the input shaft 12, and the third brake B3 can hold the second sun gear 22s. The second planet carrier 22pc is connected to the input shaft 12 through the second clutch C2. The second clutch C2 can make a driving connection between the input shaft 12 and the second planet carrier 22pc. The second band brake B2 is disposed between the stationary housing and the third planet carrier 26pc, so that the second brake B2 can hold the third planet carrier 26pc. A shift control unit is connected with the friction devices C1-C3 and B1-B3. The shift control unit controls each friction device as shown in Fig. 2A. The planetary gear system of this embodiment further includes first and second connecting means each of which connects one active element of the first and second planetary gear sets 20 and 22 with one active element of the third planetary gear set 26, and third and fourth connecting means each of which connects one active element of the first planetary gear set 20 with one active element of the second planetary gear set 22. In this embodiment, the first ring gear 20r and the second planet carrier 22pc are connected together by the third connecting means, and the second ring gear 22r and the first planet carrier 20pc are connected together by the fourth connecting means. The first ring gear 20r and the second planet carrier 22pc constitute a single rotary member, and they rotate as a unit. The second ring gear 22r and the first planet carrier 20pc constitute another single rotary member, and they rotate as a unit. Thus, the first planetary gear train consisting of the first and second planetary gear sets 20 and 22 has four rotary members which are rotatable relative to one another. Two of the four rotary members are two-element members each consisting of two active elements. The remaining two of the four rotary members are single element members each of which consists of only one active element. The first two-element member is composed of the first ring gear 20r and the second planet carrier 22pc, and the second two-element member is composed of the second ring gear 22r and the first planet carrier 20pc. The first sun gear 20s forms the first single element member, and the second sun gear 22s forms the second single element member. In this embodiment, each of the first and second connecting means includes a gearing means for connecting, by gearing, one active element coaxial with the input shaft 12 with one active element coaxial with the output shaft 14 which is parallel to the input shaft 12. The first connecting means comprises a pair 24 of a first primary gear (first input shaft's side gear) 24a and a first counter gear (first output shaft's side gear) 24b. The second connecting means comprises a pair 28 of a second primary gear (second input shaft's side gear) 28a and a second counter gear (second output shaft's side gear) 28b. The first and second primary gears 24a and 28a are coaxial with the input shaft 12, and the first and second counter gears 24b and 28b are coaxial with the output shaft 14. The primary and counter gears of each of the first and second connecting means are gears of a parallel shaft type which can transmit rotation between two parallel shafts. In each pair 24 or 28, the primary gear is in mesh with the counter gear. The first primary gear 24a is connected with the first planet carrier 20pc. Therefore, the first planet carrier 20pc, the second ring gear 22r and the first primary gear 24a rotate as a unit. The first counter gear 24b is mounted on the right end of the output shaft 14. The third sun gear 26s and the first counter gear 24b are connected with the output shaft 14 in such a manner that the first counter gear 24b, the third sun gear 26s and the output shaft 14 rotate as a unit. Therefore, the first connecting means connects the first planet carrier 20pc with the third sun gear 26 in such a manner that rotation can be transmitted therebetween. In this embodiment, the second primary gear 28a is formed on the outer periphery of the first ring gear 20r, and the second counter gear 28b is formed on the outer periphery of the third ring gear 26r. Therefore, the second primary gear 28a is an integral part of the first ring gear 20r, and the second counter gear 28b is an integral part of the third ring gear 26r. Each of the first and third ring gears is formed with internal gear teeth and external gear teeth. Thus, the second pair 28 of the primary and counter gears connects the first ring gear 20r and the third ring gear 26r in such a manner that rotation can be transmitted therebetween. The planetary gear system has first and second ends which are spaced axially along an axial direction parallel to the input and output shafts 12 and 14. In Fig. 1, the first end is the left end, and the second end is the right end. The first primary and counter gears 24a and 24b are located at the second end of the planetary gear system. The second planetary gear set 22 is disposed axially between the first (left) end of the gear system and the first planetary gear set 20. The first planetary gear set 20 is disposed axially between the second planetary gear set 22 and the first primary gear 24a. The first and second planetary gear sets 20 and 22 are disposed between the first end of the planetary gear system and the first primary gear 24a. The first planetary gear set 20 is disposed axially between the input shaft 12 and the first primary gear 24a. The planetary gear system 10 of this embodiment can provide five forward speeds and one reverse speed. In each speed, two of the friction devices are engaged as shown by small circles in the table shown in Fig. 2A. In the first speed, the friction devices in the engaged state are the first clutch C1 and the first brake B1. The first clutch C1 transmits the input rotation of the input shaft 12 to the first sun gear 20s, and the first brake B1 holds the first ring gear 20r stationary. In the first planetary gear set, therefore, the first ring gear 20r functions as a held element, the first sun gear 20s functions as an input driving element, and the first planet carrier 20pc functions as an output driven element for forward reduction. Then, the first pair 24 of the parallel shaft type gears transmits the rotation of the first planet carrier 20pc to the output shaft 14. The planetary gear system achieves the shift from the first speed to the second speed by disengaging the first brake B1 and instead engaging the second brake B2. The first brake B1 releases the first ring gear 20r, and instead the second brake B2 holds the third planet carrier 26pc stationary. Therefore, rotation of the output shaft 14 is transmitted through the third sun gear 16s and the third pinions 26p1 and 26p2 to the third ring gear 26r, and rotation of the third ring gear 26r is transmitted to the first ring gear 20r through the second pair 28 of the primary and counter gears. In this case, the third ring gear 26r rotates in the same direction as the third sun gear 26s because the third planetary gear set 26 is of the double pinion type. Therefore, the third ring gear 26r causes the first ring gear 20r to rotate in the rotational direction of the first planet carrier 20pc. As a result, the first planet carrier 20pc rotates faster than in the first speed. The planetary gear system 10 provides the third speed by engaging the first clutch C1 and the third brake B3. The third brake B3 holds the second sun gear 22s stationary. Therefore, rotation of the first planet carrier 20pc is transmitted through the second ring gear 22r to the second planet carrier 22pc, and the first ring gear 20r rotates together with the second planet carrier 22pc in the same direction as the first planet carrier 20pc. The planetary gear system 10 is so designed that the rotational speed of the first ring gear 20r is higher in the third speed than in the second speed. Therefore, the upshift from the second speed to the third speed results in an increase of the speed of the first planet carrier 20pc. The planetary gear system 10 provides the fourth forward speed by engaging the first clutch C1 and the second clutch C2. The second clutch C2 connects the second planet carrier 22pc with the input shaft 12, so that the input rotation is transmitted to the first ring gear 20r. Therefore, the first ring gear 20r and the first sun gear 20s rotate at the same speed in the same direction. As a result, the first planet carrier 20pc rotates at the input speed of the input shaft 12. The fifth forward speed is obtained by engaging the second clutch C2 and the third brake B3. The third brake B3 holds the second sun gear 22s, and the second clutch C2 transmits the input rotation of the input shaft 12 to the second planet carrier 22pc. Therefore, the second ring gear 22r rotates at a speed higher than the input speed together with the first planet carrier 20pc. The planetary gear system 10 provide the reverse speed by engaging the third clutch C3 and the first brake B1. The first brake B1 holds the second planet carrier 22pc, and the third clutch C3 transmits the input rotation from the input shaft 12 to the second sun gear 22s. Therefore, the second ring gear 22r is driven in the opposite direction at a reduced speed together with the first planet carrier 20pc. Fig. 2B shows the gear sizes of the first, second and third planetary gear sets 20, 22 and 26 of this embodiment. The numbers of teeth of the ring gears of the first, second and third planetary gear sets 20, 22 and 26 are equal to each other. The number of teeth of the sun gear of the third planetary gear set 26 is greater than that of the first planetary gear set 20, and smaller than that of the second planetary gear set 22. The ratio of the number of sun gear teeth to the number of ring gear teeth of the third planetary gear set 26 is greater than that of the first planetary gear set 20, and smaller than that of the second planetary gear set 22. Fig. 2C shows the gear ratio of each speed obtained by the planetary gear system 10 of this embodiment. In the thus-constructed planetary gear system 10, the third planetary gear set 26 is combined with the first and second planetary gear sets 20 and 22 in a compound manner. This compound combination makes it possible to choose the gear ratio of each speed more freely from values in a wider range, as compared with the conventional series combination of the main planetary gear train on the input shaft's side, and the third planetary gear set which is arranged to receive the output rotation of the main gear train and to change the speed ratio again on the output shaft's side. The compound combination of the first, second and third planetary gear sets 20, 22 and 26 according to the present invention makes it possible to reduce the number of required friction devices. The third planetary gear set 26 of the invention requires only one friction device (B2) for allowing and preventing transmission of rotation from the output shaft 14 to the third ring gear 26r. The planetary gear system 10 of this embodiment provides each forward speed by engaging two of the friction devices, and performs each shift between two successive forward speeds by holding one device invariably in the engaged state. As shown in Fig. 2A, the first clutch C1 remains constantly engaged from the first speed to the fourth speed, and the second clutch C2 remains engaged between the fourth and fifth speeds. The upshift or downshift from each forward speed to the next speed is effected by disengaging one device and instead engaging another device. Therefore, the planetary gear system of this embodiment can improve the quality of shifting, facilitate the shift control, and simplify the construction of the shift control unit. In this embodiment, the first, second and third clutches C1, C2 and C3 and the third brake B3 are arranged in such a coaxial manner that one encircles another. Furthermore, the first brake B1 is arranged coaxially around the second planetary gear set 22. Therefore, it is possible to reduce the axial length of the planetary gear system considerably. The planetary gear system is superior especially when used for a transaxle of a front engine front wheel drive automobile. In this embodiment, the second planetary gear set 22 and the first brake B1 are disposed axially between the first planetary gear set 20 and the coaxial arrangement of the friction devices C1, C2, C3 and B3. A second embodiment of the present invention is shown in Fig. 3. A planetary gear system 110 of the second embodiment is used for an automatic transmission of an F.R. vehicle. In the second embodiment, input and output shafts 112 and 114 are aligned in a straight line. First, second and third planetary gear sets 120, 122 and 126 are all arranged around the above-mentioned straight line which serves as a common axis. The first planetary gear set 120 is placed axially between the second and third planetary gear sets 122 and 126. The first and second planetary gear sets 120 and 122 are of the single pinion type, and the third planetary gear set 126 is of the double pinion type, as in the first embodiment. The first planet carrier 120pc of the first planetary gear set 120 is connected with the second ring gear 122r so that they rotate as a unit. The first planet carrier 120pc is further connected with the third ring gear 126s of the third planetary gear set 126 so that they rotate as a unit. The third sun gear 126s is connected with the output shaft 114 so that they rotate as a unit. The second planet carrier 122pc is connected with the first ring gear 120r so that they rotate as a unit. The first ring gear 120r is connected with the third ring gear 126r of the third planetary gear set 126 so that they rotate as a unit. The input shaft 112 is connected to the first sun gear 120s through a first clutch c1, to the second planet carrier 122pc through a second clutch c2, and to the second sun gear 122s through a third clutch c3. The transmission case (housing) is connected to the first ring gear 120r through a first brake b1, to the third planet carrier 126pc through a second brake b2, and to the second sun gear 122s through a third brake b3. As explained above, the compound combination of three planetary gear sets according to the present invention can reduce shift shock because the three planetary gear sets are not controlled independently, reduce the axial dimension of the planetary gear system, reduce the number of friction devices, and permit a wide choice of gear ratio values. Especially, the final output speed is determined by the first planet carrier. Therefore, it is possible to set the final speed ratio of each speed freely, as compared with the conventional arrangement in which the final speed ratio is equal to the product obtained by multiplying the speed ratio of the first gear train on the input shaft's side, by the speed ratio of the gear train on the output shaft's side.

Claims: A planetary gear system comprising: an input element (12, 112) for receiving an input rotation; an output element (14, 114) for delivering an output rotation; a first planetary gear train which is connected with the input element and which includes a first planetary gear set (20, 120) having three active elements which are a first sun gear (20s, 120s), a first planet carrier (20pc, 120pc) and a first ring gear (20r, 120r), and a second planetary gear set (22, 122) having three active elements which are a second sun gear (22s, 122s), a second planet carrier (22pc, 122pc) and a second ring gear (22r, 122r); a second planetary gear train which is connected with the output element and which includes a third planetary gear set (26, 126) having three active elements which are a third sun gear (26s, 126s), a third planet carrier (26pc, 126pc) and a third ring gear (26r, 126r); a connecting means which connects one active element (20pc, 120pc) of the first planetary gear set and one active element (22r, 122r) of the second planetary gear set together so that both elements rotate as a unit, which connects another active element (20r, 120r) of the first planetary gear set and another active element (22pc, 122pc) of the second planetary gear set together so that both elements rotate as a unit, and which comprises a first connecting means (24) for connecting one active element (20pc, 22r, 120pc, 122r) of the first planetary gear train with one active element (26s, 126s) of the second planetary gear train, and a second connecting means (28) for connecting another active element (20r, 22pc. 120r, 122pc) of the first planetary gear train with another active element (26r, 126r) of the second planetary gear train; and a device group comprising selective engaging devices (C1, C2, C3, B1, B2, B3, c1, c2, c3, b1, b2, b3) for driving and holding a plurality of the active elements of the first, second and third planetary gear sets, the device group comprising a first clutch (C1, c1) for connecting the first sun gear (20s, 120s) with the input element; characterized in that the first connecting means (24) connects the first planet carrier (20pc, 120pc) with the output element (14, 114) so that rotation can be transmitted therebetween; and in that the first connecting means (24) further connects the first planet carrier (20pc, 120pc) with the third sun gear (26r, 126r) so that rotation can be transmitted therebetween. A planetary gear system according to Claim 1 wherein the first, second and third planetary gear sets (20, 22, 26) and the device group (C1, C2, C3, B1, B2, B3, c1, c2, c3, b1, b2, b3) are so arranged to provide five different forward speeds and one reverse speed. A planetary gear system according to Claim 2 wherein the second connecting means (28) connects the first ring gear (20r, 120r) with the third ring gear (26r, 126r) so that rotation can be transmitted therebetween. A planetary gear system according to Claim 3 wherein the device group further comprises a first brake (B1, b1) for holding the first ring gear (20r, 120r), and a second brake (B2, b2) for holding the third planet carrier (26pc, 126pc). A planetary gear system according to Claim 4 wherein the first ring gear (20r, 120r) is connected with the second planet carrier (22pc, 122pc) by the connecting means so that both active elements rotate as a unit; the first planet carrier (20pc, 120pc) is connected with the second ring gear (22r, 122r) by the connecting means so that both active elements rotate as a unit; and the device group further comprises a second clutch (C2, c2) for connecting the second planet carrier (22pc, 122pc) with the input element (12, 112), and a third brake (B3, b3) for holding the second sun gear (22s, 122s). A planetary gear system according to Claim 5 wherein each of the first and second planetary gear sets (20, 22, 120, 122) is a single pinion type planetary gear set; the third planetary gear set (26, 126) is a double pinion type planetary gear set; and the device group further comprises a third clutch (C3, c3) for connecting the second sun gear (22s, 122s) with the input element (12, 112). A planetary gear system according to any of Claims 1-6 wherein the third planetary gear set (26, 126) and one (B2, b2) of the engaging devices are mounted on the output element which is in the form of an output shaft (14, 114), and none of the remaining devices and the first and second planetary gear sets are mounted on the output shaft. A planetary gear system according to any of Claims 1-7 wherein the second planetary gear set (22, 122) is located axially between the input element (12, 112) and the first planetary gear set (20, 120). A planetary gear system according to any of Claims 1-8 wherein the second -planetary gear set (22, 126) is surrounded by one (B1, b1) of the engaging devices, and placed axially between a subgroup of four (C1, C2, C3, B3; c1, c2, c3, b3) of the engaging devices and the first planetary gear set (20, 120). A planetary gear system according to any of Claims 5-9 wherein the first, second and third clutches (C1, C2, C3, c1, c2, c3) and the third brake (B3, b3) are arranged coaxially; the first clutch is surrounded by the second clutch, the second clutch is surrounded by the third clutch; and the third clutch is surrounded by the third brake. A planetary gear system according to any of Claims 1-10 wherein the input and output elements are in the form of input and output shafts (12, 14) which are parallel to each other; the first connecting means (24) comprises a first input shaft's side gear (24a) which is coaxial with the input shaft, and connected with one active element of the first planetary gear train, and a first output shaft's side gear (24b) which is mounted on the output shaft (14) and which is directly engaged with the first input shaft's side gear; and the second connecting means (28) comprises a second input shaft side's gear (28a) formed on a periphery of the first ring gear (20r), and a second output shaft's side gear (28b) which is formed on a periphery of the third ring gear (26r) and which is directly engaged with the second input shaft's side gear. A planetary gear system according to Claim 11 wherein the first, second and third planetary gear sets (20, 22, 26) are placed axially between a first end of the planetary gear system (10) and the first connecting means (24); and the first connecting means is placed at a second end of the planetary gear system. A planetary gear system according to any of Claims 1-10 wherein the input and output elements are in the form of input and output shafts (112, 114) which are in alignment with each other; the first connecting means connects the first planet carrier (120pc) with the third sun gear (126s) so that both active elements rotate as a unit; and the second connecting means connects the first ring gear (120r) and the third ring gear (126r) so that both active elements rotate as a unit. A planetary gear system according to Claim 13 wherein the first, second and third planetary gear sets (120, 122, 126) are coaxial with one another, and the first planetary gear set (120) is placed axially between the second and third planetary gear sets (122, 126).

Inventors: OTSUKA KUNIO, OTSUKA, KUNIO
Applicants: NISSAN MOTOR, NISSAN MOTOR CO., LTD.
Application year: 1990
Main classification: F16H3
IPC codes: F16H3, F16H1