Transmission, transmission assembly and powertrain

Abstract

A transmission, in particular a reducer transmission (34), which has two planetary sets and two shift elements (S1, S2). In addition, a transmission assembly which has a main transmission (32), of a planetary design, in particular a continuous power split transmission of a planetary design, and such a transmission which is coupled, as a reducer transmission (34), with the main transmission (32). Also, a powertrain (10) of a working machine with such a transmission assembly (30).

Claims

1. A transmission comprising: a first input shaft which is couplable with a main transmission, a second input shaft which is couplable with the main transmission, a primary planetary gear set, in a power flow direction, having a primary sun gear, a primary planet carrier, with at least a primary planet gear, and a first primary planetary gear set element, a secondary planetary gear set, downstream and following the primary planetary gear set, having a first secondary planetary gear set element, a second secondary planetary gear set element, and a third secondary planetary gear set element, at least a first shift element and a second shift element, and an output shaft, the first input shaft being rotationally fixedly connected to the primary sun gear, the second input shaft being rotationally fixedly connected to the primary planet carrier, the primary planet carrier being rotationally fixedly connected to the second secondary planetary gear set element, the output shaft being rotatably coupled to the second secondary planetary gear set element, the first primary planetary gear set element being rotationally fixedly connected to the first secondary planetary gear set element, the first primary planetary gear set element being connectable, in a rotationally fixed manner, to a transmission housing via the first shift element, the third secondary planetary gear set element being connectable, in a rotationally fixed manner, to the transmission housing via the second shift element, and the main transmission comprises: a main transmission-input shaft, a tertiary planetary gear set with a tertiary sun gear, a tertiary planet carrier, with at least one tertiary planet gear, and a tertiary ring gear, a quaternary planetary gear set with a quaternary sun gear, a quaternary planet carrier, at least one quaternary planet gear, and a quaternary ring gear, a fourth shift element, a fifth shift element, and a sixth shift element, and at least first and second adjustment units, which each are operationally connected to at least the one of the tertiary and the quaternary planetary gear sets of the main transmission.

2. The transmission according to claim 1, wherein the secondary planetary gear set is a minus planetary gear set, the second secondary planetary gear set element is a secondary planet carrier, and the third secondary planetary gear set element is a secondary ring gear.

3. The transmission according to claim 1, wherein the secondary planetary gear set is a plus planetary gear set, the second secondary planetary gear set element is a secondary ring gear, and the third secondary planetary gear set element is a secondary planet carrier.

4. The transmission according to claim 1, wherein the primary planet carrier and the secondary planet carrier are positioned next to each other along a transmission axis, the first primary planetary gear set element is a primary ring gear, and the first secondary planetary gear set element is a secondary sun gear.

5. The transmission according to claim 1, wherein the primary planetary gear set and the secondary planetary gear set are radially nested, with respect to a transmission axis, the first primary planetary gear set element and the first secondary planetary gear set element form an inner ring gear.

6. The transmission according to claim 1, wherein, with respect to a transmission axle, the first shift element is radially nested within the second shift element.

7. The transmission according to claim 1, wherein at least one of the first shift element and the second shift element is positioned along a transmission axis, between the primary planetary gear set and the secondary planetary gear set.

8. The transmission according to claim 1, wherein at least one of the first shift element and the second shift element is connected with the transmission enclosure, via an associated enclosure partition wall or a common enclosure partition wall.

9. The transmission according to claim 1, further comprising a third shift element, through which the primary planet carrier is rotatably connectable with the primary sun gear.

10. A transmission assembly comprising: a main transmission in a continuous power split transmission of a planetary design, and a reducer transmission being coupled with the main transmission, and the reducer transmission comprising a first input shaft which is couplable with a main transmission, a second input shaft being couplable with the main transmission, a primary planetary gear set, in a power flow direction, having a primary sun gear, a primary planet carrier, with at least a primary planet gear and a first primary planetary gear set element, a secondary planetary gear set, downstream and following the primary planetary gear set, having a first secondary planetary gear set element, a second secondary planetary gear set element, and a third secondary planetary gear set element, at least a first shift element and a second shift element, and an output shaft, the first input shaft being rotationally fixedly connected to the primary sun gear, the second input shaft being rotationally fixedly connected to the primary planet carrier, the primary planet carrier being rotationally fixedly connected to the second secondary planetary gear set element, the output shaft being rotatably coupled to the second secondary planetary gear set element, the first primary planetary gear set element being rotationally fixedly connected to the first secondary planetary gear set element, the first primary planetary gear set element being connectable, in a rotationally fixed manner, to a transmission housing via the first shift element, the third secondary planetary gear set element being connectable, in a rotationally fixed manner, to the transmission housing via the second shift element, and the main transmission comprises: a main transmission-input shaft, a tertiary planetary gear set with a tertiary sun gear, a tertiary planet carrier, with at least one tertiary planet gear, and a tertiary ring gear, a quaternary planetary gear set with a quaternary sun gear, a quaternary planet carrier, at least one quaternary planet gear, and a quaternary ring gear, a fourth shift element, a fifth shift element, and a sixth shift element, and at least first and second adjustment units, which each are operationally connected to at least the one of the tertiary and the questernary planetary gear sets of the main transmission.

11. The transmission assembly according to claim 10, wherein the main transmission-input shaft is rotationally fixedly connected to the quaternary planet carrier, the first adjustment unit is rotationally fixedly connected to the tertiary sun gear and the quaternary sun gear, the second adjustment unit is rotationally fixedly connected to the tertiary planet carrier, the tertiary ring gear is rotationally fixedly connected to the quaternary planet carrier, the second adjustment unit is rotatably couplable, via the fourth shift element, to the primary planet carrier, the quaternary ring gear is rotatably couplable, via the fifth shift element, to the primary sun gear, and the second adjustment unit is rotatably couplable, via the sixth shift element, to the primary sun gear.

12. The transmission assembly according to claim 10, wherein the main transmission comprises a quinary planetary gear set with a quinary sun gear and at least one quinary ring gear, a quinary planet carrier and at least one quinary planet gear, the main transmission-input shaft is rotationally fixedly connected to the tertiary ring gear and the quaternary planet carrier, the quaternary sun gear and the quinary sun gear are is rotationally fixedly connected, the first adjustment unit is rotationally fixedly connected to the main transmission-input shaft, the second adjustment unit is rotationally fixedly connected to the tertiary sun gear, the tertiary planet carrier is rotationally fixedly connected to the quaternary ring gear and the quinary planet carrier, at least one of the quinary planet carrier, the quaternary ring gear and the tertiary planet carrier is connectable, or is connected in a rotationally fixed manner, to the primary planet carrier via the fourth shift element, the quinary sun gear is connectable in a rotationally fixed manner, via the fifth shift element, to the primary sun gear, and the quinary ring gear is connectable in a rotationally fixed manner, via the sixth shift element, to the primary sun gear.

13. The transmission assembly according to claim 12, wherein, along a transmission axis, the primary, the secondary, the tertiary, the quaternary and the quinary planetary gear sets are positioned in an order of: the tertiary planetary gear set, the quaternary planetary gear set, the primary planetary gear set, and the secondary planetary gear set, and the quinary planetary gear set is positioned between the quaternary planetary gear set and the primary planetary gear set.

14. A powertrain of a mobile work machine, with a transmission assembly comprising: a main transmission in a continuous power split transmission of a planetary design, and a reducer transmission being coupled with the main transmission, and the reducer transmission comprising: a first input shaft which is couplable with a main transmission, a second input shaft which is couplable with the main transmission, a primary planetary gear set, in a power flow direction, having a primary sun gear, a primary planet carrier, with at least a primary planet gear and a first primary planetary gear set element, a secondary planetary gear set, downstream and following the primary planetary gear set, having a first secondary planetary gear set element, a second secondary planetary gear set element, and a third secondary planetary gear set element, at least a first shift element and a second shift element, and an output shaft, the first input shaft being rotationally fixedly connected to the primary sun gear, the second input shaft is being rotationally fixedly connected to the primary planet carrier, the primary planet carrier being rotationally fixedly connected to the second secondary planetary gear set element, the output shaft being rotatably coupled to the second secondary planetary gear set element, the first primary planetary gear set element being rotationally fixedly connected to the first secondary planetary gear set element, the first primary planetary gear set element being connectable, in a rotationally fixed manner, to a transmission housing via the first shift element, the third secondary planetary gear set element being connectable, in a rotationally fixed manner, to the transmission housing via the second shift element, and the main transmission comprises: a main transmission-input shaft, a tertiary planetary gear set with a tertiary sun gear, a tertiary planet carrier, with at least one tertiary planet gear, and a tertiary ring gear, a quaternary planetary gear set with a quaternary sun gear, a quaternary planet carrier, at least one quaternary planet gear, and a quaternary ring gear, a fourth shift element, a fifth shift element, and a sixth shift element, and at least first and second adjustment units, which each are operationally connected to at least the one of the tertiary and the quaternary planetary gear sets of the main transmission.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The invention is described based on different embodiments which are shown in the attached drawings. These show:

(2) FIG. 1 a powertrain according to the invention with a transmission assembly according to the invention and transmission according to the invention which is designed as a reducer transmission.

(3) FIG. 2 the transmission assembly in FIG. 1 in a detailed view,

(4) FIG. 3 an alternative embodiment of the transmission assembly according to the invention whereby, in reference to the transmission assembly in FIG. 2, just another reducer transmission is used,

(5) FIG. 4 another alternative embodiment of the transmission assembly according to the invention whereby, in reference to the transmission assemblies in FIGS. 2 and 3, just another reducer transmission is used,

(6) FIG. 5 a shifting schematic which applies to the transmission assemblies in FIGS. 2 to 4,

(7) FIG. 6 an alternative transmission assembly according to the invention, different to FIGS. 1 to 4, whereby in reference to the transmission assembly in FIG. 2, just the different main transmission is used,

(8) FIG. 7 an additional alternative transmission assembly, whereby the main transmission in FIG. 6 is combined with the reducer transmission in FIG. 3,

(9) FIG. 8 an additional alternative transmission assembly, whereby the main transmission in FIGS. 6 and 7 is combined with the reducer transmission in FIG. 4,

(10) FIG. 9 a transmission assembly according to the invention, whereby the reducer transmission in FIG. 2 is coupled with an arbitrary main transmission,

(11) FIG. 10 a transmission assembly according to the invention, whereby the reducer transmission in FIG. 4 is coupled with an arbitrary main transmission,

(12) FIG. 11 a transmission assembly according to the invention, whereby the reducer transmission in FIG. 3 is coupled with an arbitrary main transmission,

(13) FIG. 12 a shift schematic which refers to the reducer transmissions in FIGS. 9 to 11,

(14) FIGS. 13 to 18 transmission assemblies according to the invention, whereby the reducer transmissions are designed in accordance with additional embodiments and which are coupled with an arbitrary main transmission,

(15) FIG. 19 shifting schematics which reference the reducer transmissions in FIGS. 17 and 18.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

(16) FIG. 1 shows a powertrain 10 for a mobile work machine.

(17) It serves on one hand to drive a power take off for which a power take off transmission 14 is provided. On the other hand, the powertrain 10 serves as traction drive for the mobile work machine. An output shaft 16 is provided for this.

(18) By way of the output shaft 16, a front wheel drive 18 and a rear wheel drive 20 can be supplied with power in the form of a rotational speed and torque.

(19) In addition, the drive train 10 is used to drive additional aggregates and pumps which are just schematically shown in FIG. 1 and marked with the reference character 22.

(20) As energy source for the drive train 10 serves a drive motor 24 which is presently shown schematically as a combustion engine. It drives a main transmission-input shaft 12 via a vibration absorber 26.

(21) In the presented embodiments, the main transmission-input shaft 12, as well as the output shaft 16, are positioned on a transmission axis 27.

(22) The main transmission input shaft 12 and the output shaft 16 are interposed by an infinitely adjustable, mechanical-electrical power split transmission 28.

(23) The mechanical branch or power branch of this power split transmission 28 comprises a transmission assembly 30 which itself has again a main transmission 32 and a reducer transmission 34.

(24) The reducer transmission 34 is connected via a first input shaft E1 and a second input shaft E2 to the main transmission 32.

(25) The electrical branch or electrical power branch of the power split transmission 28 has a first adjustment unit 36 and a second adjustment unit 38, which each are designed as electrical machines and can be electrically coupled with each other.

(26) The two adjustment units 36, 38 are coupled in addition via a control unit 40 with an electrical storage unit 42.

(27) The transmission assembly 30, which comprises the main transmission 32 and the reducer transmission 34, is presented in detail in FIG. 2.

(28) The reducer transmission 34 is hereby coupled via a first input shaft E1 and a second input shaft E2 with the main transmission 32 and has a primary planetary gear set P1 and a secondary planetary gear set P2.

(29) An output shaft A of the reducer transmission 34 corresponds to the output shaft 16.

(30) The main transmission 32 comprises a tertiary planetary gear set P3, a quaternary planetary gear set P4 and a quinary planetary gear set P5.

(31) In the direction of power flow, i.e., from the main transmission input shaft 12 to the output shaft 16, the planetary gear sets are arranged in the order of the tertiary planetary gear set P3, the quaternary planetary gear set P4, the quinary planetary gear set P5, the primary planetary gear set P1, and the secondary planetary gear set P2, as is clear from FIG. 2.

(32) With reference to the reducer transmission 34, the primary planetary gear set P1 comprises a primary sun gear 11, a primary planet carrier P12, a primary planet gear P13, and a first primary planetary gear set element P14 which is designed as a ring gear, in accordance with the embodiment in FIGS. 1 and 2.

(33) The secondary planetary gear set P2 is designed in the embodiment of the FIGS. 1 and 2 as a so-called minus planetary gear set. It has a first secondary planetary gear set element P21, which is here a secondary sun gear. Also, it comprises a second, secondary planetary gear set element P22, which is here a secondary planet carrier. The secondary planet carrier P2 has also a secondary planet gear P23 and a third secondary planetary gear set element P24 which is here designed as a secondary ring gear, meaning a ring gear of the secondary planetary gear set P2.

(34) In reference to the main transmission 32, the tertiary planetary gear set P3 comprises a tertiary sun gear P31, a tertiary planet carrier P32, a tertiary planet gear P33, as well as a tertiary ring gear P34.

(35) The quaternary planetary gear set P4 has a quaternary sun gear P41, a quaternary planet carrier P42, a quaternary planet gear P43, as well as a quaternary ring gear P44.

(36) The quinary planetary gear set P5 has a quintery sun gear P51, a quinary planet carrier P52, a quinary planet gear P53, as well as a quinary ring gear P54.

(37) The previously mentioned elements of the transmission assembly 30 are coupled with each other as follows.

(38) The first adjustment unit 36 is connected rotationally fixed to the main transmission input shaft 12 and the second adjustment unit 38 is connected rotationally fixed to the tertiary sun gear P31.

(39) The tertiary ring gear P34 is connected rotationally fixed to the quaternary planet carrier P42, as well as to the main transmission input shaft 12.

(40) The quaternary sun gear P41 is connected rotationally fixed to the quinary sun gear P51.

(41) The quinary planet carrier P52 is connected rotationally fixed to the quaternary P44 ring gear and the tertiary planet carrier P32.

(42) The quaternary sun gear P41 and the quinary sun gear P51 are optionally coupled with the primary sun gear 11.

(43) The quinary ring gear P54 can optionally be rotatably coupled to the primary sun gear P11 via a sixth shift element S6.

(44) The assembly based on the tertiary planet carrier P32, the quaternary ring gear P44 and the planet carrier P52, can be optionally connected rotationally fixed to the primary planet carrier P12 by means of a fourth shift element S4.

(45) Also, the primary sun gear P11 can also optionally be rotatably to the planet carrier P12 via a third shift element S3.

(46) The primary ring gear P14 can be connected in a rotationally fixed manner, via a first shift element S1, to a transmission enclosure 44.

(47) Furthermore, the primary ring gear P14 is connected rotationally fixed to the first secondary planetary gear set element P21, which is here designed as secondary sun gear, meaning the sun gear of the secondary planetary gear set P2.

(48) The primary planet carrier P12 is connected rotationally fixed to the second secondary planet carrier element P22, meaning the secondary planet carrier, and the output shaft 16, A.

(49) The third secondary planet gear set element P24, here the secondary ring gear, can optionally be rotatably connected to the transmission housing 44 by means of a second shift element S2.

(50) FIG. 3 shows an additional embodiment of the transmission assembly 30.

(51) This differs from the embodiment in FIG. 2 only with regard to the reducer transmission 34. Therefore, it is only these differences that are discussed below.

(52) The secondary planetary gear set P2 is here designed as a plus planetary gear set.

(53) Accordingly, instead of the secondary planet gear P23, it comprises an inner planet gear P23i and an outer planet gear P23a.

(54) The third secondary planetary gear set element P24 is here a secondary planet carrier and is designed so as to accommodate both planetary gears P23i and P23a.

(55) Furthermore, the second secondary planetary gear set element P22 is now a secondary ring gear which is connected in a rotationally fixed manner to the output shaft 16, A.

(56) The third secondary planetary gear set element P24, meaning the secondary planet carrier, can be optionally connected to the transmission housing 44 in a rotationally fixed manner via the shift element S2.

(57) Apart from that, reference is made to description of the embodiment according to FIG. 2.

(58) The embodiment of the transmission assembly 30 shown in FIG. 4 also differs from the embodiment shown in FIG. 2 only with regard to reducer transmission 34. It is therefore explained based on the embodiment according to FIG. 2.

(59) In the embodiment according to FIG. 4, the primary planetary set P1 and the secondary planetary set P2 a radially nested.

(60) This means that, starting from the embodiment shown in FIG. 2, in which the primary planetary set P1 and the secondary planetary set P2 are arranged axially adjacent, the couplings between the primary planetary gear set P1 and the secondary planetary gear set P2 are the same, but the secondary planetary gear set P2 has been shifted to a position radially outside of the primary planetary gear set P1.

(61) In this context, the primary sun gear P11 now represents the sun gear of the nested planetary sets P1, P2.

(62) The primary planet gear P13 meshes with this radially to the outside (compare FIG. 2).

(63) Again, radially to the outside, there is an inner ring gear, for instance, which is created by a combination of the first primary planetary gear set element P14, which is formed in FIG. 2 as the primary ring gear, and the first secondary planetary gear set element P21, which is formed in FIG. 2 as a secondary sun gear, as a result of the radial nesting.

(64) This is followed radially outside by the secondary planet gear P23 (see FIG. 2).

(65) The third secondary planetary gear set element P24, which is a ring gear of the nested planetary gear sets, connects further radially outward.

(66) In other words, the previously first primary planetary gear set element P14 and the previously first secondary planetary gear set element P21 together form an inner ring gear which has an inner teething and an outer teething.

(67) Alternatively to the inner ring gear, the previously first primary planetary gear set element P14 and the previously first secondary planetary gear set element P21 can together form a gear wheel which is positioned between the two planet gears P13, P23, meaning between the primary planet gear P13 and the secondary planet gear P23.

(68) The shifting schematic shown in FIG. 5 can be implemented with the transmission assemblies 30 of FIGS. 1 to 4.

(69) Altogether, four forward drive ranges can now be realized, which are marked as FB-V1 to FB-V4, and two reverse drive ranges, which are marked as FB-R1 and FB-R2.

(70) Hereby, a first forward drive range FB-V1 is implemented when the first shift element S1 and the sixth shift element S6 are engaged. All remaining shift elements are disengaged.

(71) A second forward drive range FB-V2 is implemented when the first shift element S1 and the fifth shift element S5 are engaged. All remaining shift elements are disengaged.

(72) A third forward drive range FB-V3 is implemented when the fourth shift element S4 and the fifth shift element S5 are engaged. All remaining shift elements are disengaged.

(73) A fourth forward drive range FB-V4 is implemented when the third shift element S3 and the fifth shift element S5 are engaged. All remaining shift elements are disengaged.

(74) A first reverse drive range FB-R1 is implemented when the second shift element S2 and the sixth shift element S6 are engaged and the remaining shift elements are disengaged.

(75) A second reverse drive range FB-R2 is implemented when the second shift element S2 and the fifth shift element S5 are engaged and the remaining shift elements are disengaged.

(76) An additional embodiment of the transmission assembly 30 is shown in FIG. 6. It also comprises a main transmission 32 and a reducer transmission 34.

(77) The reducer transmission 34 used in the embodiment according to FIG. 6 corresponds to the reducer transmission 34 used in the embodiment according to FIG. 2. Reference is made to the comments thereof.

(78) The main transmission 32, however, differs from the main transmission 32 of the embodiments in FIGS. 1 to 4. It is understood that the transmission assembly 30 according to the embodiment in FIG. 6 can be integrated into the powertrain 10 instead of the transmission assembly 30 shown in FIG. 1.

(79) The main transmission 32 of the transmission assembly 30, in accordance with FIG. 6 comprises, and different to the main transmission 32 shown FIG. 1 to 4, just two planetary gear sets, namely the tertiary planetary gear set P3 and the quaternary planetary gear set P4. Insofar, the previously provided quinary planetary gear set is no longer provided, which was provided between the quaternary planetary gear set P4 and the reducer transmission 34.

(80) The elements of the tertiary planetary gear set P3 and of the quaternary planetary gear set P4 are named with the same system that was used for the description of FIG. 2 to 4. However, these elements are now coupled with each other differently.

(81) The first adjustment unit 36 is connected rotationally fixed to the tertiary sun gear P31 and the quaternary sun gear P41.

(82) The second adjustment unit 38 is connected rotationally fixed to the tertiary planet carrier P32.

(83) The main transmission-input shaft 12 is connected rotationally fixed to the quaternary planet carrier P42.

(84) Furthermore, the tertiary ring gear P34 is connected rotationally fixed to the quaternary planet carrier P42.

(85) The second adjustment unit 38 and therefore also the planet carrier P32, which is connected to it in a rotationally fixed manner, can optionally be connected rotationally fixed to the primary planet carrier P12 via the fourth switching element S4.

(86) Through the fifth shift element S5, the quaternary ring gear P44 can optionally be connected rotationally fixed to the primary sun gear P11.

(87) Furthermore, the second adjustment unit 38 and the tertiary planet carrier P32 can optionally be connected rotationally fixed to the sun gear P11 via the sixth shift element S5.

(88) Also, the primary sun gear P11 can optionally be connected in a rotationally fixed manner to the primary planet carrier P12 via the third shift element S3.

(89) FIG. 7 shows an additional embodiment of the transmission assembly 30, the main transmission 32 corresponds to the main transmission 32 of FIG. 6. The reducer transmission 34 corresponds to the reducer transmission 34 of FIG. 3. Reference is therefore made to the descriptions of the above described embodiments.

(90) FIG. 8 also shows an alternative transmission assembly 30, the reducer transmission 34 of which corresponds to the reducer transmission 34 in FIG. 4, and the main transmission 32 is identical to the main transmissions 32 from FIGS. 6 and 7. Therefore, reference is made to the above descriptions.

(91) The shifting schematic of FIG. 5 is also valid for the variants of the transmission assembly 30 which are presented in FIGS. 6 to 8. It is therefore also possible to implement these four forward drive ranges and two reverse drive ranges. Therefore, refer to the above descriptions.

(92) In the FIGS. 9 to 11 explained below, additional variations of the transmission assembly 30 are introduced.

(93) The only thing described in these is the design of the reducer transmission 34. It can be coupled with an arbitrary main transmission 32, i.e., the main transmission shown in FIGS. 1 to 4, and 6 to 8. Therefore and in reference to FIG. 9 to 11, only the reducer transmission 34 is described.

(94) The reducer transmission 34, in accordance with the embodiment of FIG. 9, corresponds to the previously described reducer transmission 34 as in FIG. 2. Therefore, reference is made to the related description.

(95) In the embodiment according to FIG. 10, the reducer transmission 34 corresponds to the reducer transmission 34 which has already been explained with reference to FIG. 4. Referenced to these description.

(96) In the embodiment in accordance with FIG. 11, the reducer transmission 34 is identical to the reducer transmission 34 in FIG. 3. Therefore, reference is made to the corresponding descriptions.

(97) The reducer transmissions 34 from FIGS. 9 to 11 are each designed as reversing units, meaning that in each case a forward drive range FB-V and a reverse drive range FB-R can be realized by means of this reducer transmission 34. The associated shift schematic can be seen in FIG. 12.

(98) Therefore, the forward drive range FB-V is implemented if the first shift element S1 is engaged and the second shift element S2 is disengaged.

(99) The reverse drive range FB-R is implemented if the first shift element S1 is disengaged and the second shift element S2 is engaged.

(100) FIGS. 13 to 16 show additional embodiments of the transmission assembly 30. Any main transmission 32 can again be used, in particular the main transmissions 32 as in FIGS. 1 to 4, and 6 to 8.

(101) In the embodiment in accordance with FIG. 13, the reducer transmission 34 has the same effect as the reducer transmission 34 in FIG. 9. However, the first shift element S1 and the second shift element S2 are now arranged differently.

(102) Both shift elements S1, S2 are now attached to a housing partition wall 44z.

(103) In addition, the first shift element S1 is located radially within the second shift element S2. In other words, the first shift element S1 and the second shift element S2 are radially nested.

(104) Also, the reducer transmission 34 of the embodiment in FIG. 14 corresponds to the reducer transmission 34 in FIG. 9 with regard to the components and the associated couplings. However, the two shift elements S1, S2 are now positioned directly adjacent to each other on the transmission housing 44.

(105) In addition, the two shift elements S1, S2 are now positioned between the primary planetary gear set P1 and the secondary planetary gear set P2.

(106) In the transmission assembly 30 as in FIG. 15, the reducer transmission 34 corresponds to the reducer transmission as in FIG. 10 with regard to its components and the respective couplings.

(107) However, the shift elements S1, S2 are now mounted on an enclosure or partition wall 44z.

(108) Hereby, the first shift element S1 is arranged radially within the second shift element S2. This configuration corresponds therefore with the radially nesting which has already been described in FIG. 13.

(109) In the variation of FIG. 16, a reducer transmission 34 is implemented which corresponds, with regard to its components and respective couplings, to the reducer transmission 34 of FIG. 15. However, the first shift element S1 and the second shift element S2 are each mounted to a separate housing partition wall 44z.

(110) In this case, the first shift element S1 is arranged, via the associated enclosure partition wall 44z, on the left hand side in the drawing of the planetary gear sets P1, P2, and the second shift element S2 is arranged, in the drawing, on the right side of the planetary gear sets P1, P2.

(111) With regard to their radial position, the first shift element S1 and the second shift element S2 of located approximately at the same height.

(112) Additional embodiments of the transmission assembly 30 are presented in FIGS. 17 and 18. The third shift element S3, which has already been described in connection with the main transmission 32, is designed as an integral part of the reducer transmission 34.

(113) Therefore, a reducer transmission 34 is shown in FIG. 17 which in its configuration corresponds with the reducer transmission 34 in FIG. 2. Via the third shift element S3, the primary planetary gear set P1 can be locked. Otherwise, it is described with reference to FIG. 2.

(114) The reducer transmission 34 in FIG. 18 corresponds to the reducer transmission 34 in FIG. 4. The third shift element S3 is again assigned to the reducer transmission 34.

(115) Consequently, two forward drive ranges FB-V1, FB-V2, and one reverse right range FB-R can be realized by means of the reducer transmission 34 as in FIGS. 17 and 18. A respective shifting schematic is presented in FIG. 19. The first forward drive range FB-V1 is hereby implemented when the first shift element S1 is engaged and all the remaining shift elements are disengaged.

(116) The second forward drive range FB-V2 is implemented when the third shift element S3 is engaged, meaning that the primary planetary gear set P1 is locked, and all remaining shift elements are disengaged.

(117) The reverse drive range FB-R is implemented when the second shift element S2 is engaged. The remaining shift elements are then disengaged.

(118) Such a reducer transmission 34 thus fulfills the functions of a reversing unit since it offers a forward drive range and a reverse drive range and also serves as a range group by offering two different forward drive ranges.

REFERENCE CHARACTERS

(119) 10 Powertrain 12 Main Transmission-Input Shaft 14 Power Take Off Transmission 16 Output Shaft 18 Front Wheel Drive 20 Rear Wheel Drive 22 Aggregates and Pumps 24 Drive Motor 26 Vibration Absorber 27 Transmission Axis 28 Power Split Transmission 30 Transmission Assembly 32 Main Transmission 34 Reducer Transmission 36 First Adjustment Unit 38 Second Adjustment Unit 40 Control Unit 42 Electrical Storage Unit 44 Transmission Housing 44z Housing Partition Wall E1 First Input Shaft of the Reducer Transmission E2 Second Input Shaft of the Reducer Transmission A Output Shaft of the Reducer Transmission P1 Primary Planetary Gear Set P12 Primary Planet carrier P13 Primary Planet Gear P14 First Primary Planetary Gear Set Element P2 Secondary Planetary Gear Set P21 First Secondary Planetary Gear Set Element P22 Second Secondary Planetary Gear Set Element P23 Secondary Planet Gear P23a Outer Planet Gear P23i Inner Planet Gear P24 Third Secondary Planetary Gear Set Element P3 Tertiary Planetary Gear Set P31 Tertiary Sun Gear P32 Tertiary Planet carrier P33 Tertiary Planet Gear P34 Tertiary Ring Gear P4 Quaternary Planetary Gear Set P41 Quaternary Sun Gear P42 Quaternary Planet carrier P43 Quaternary Planet Gear P44 Quaternary Ring Gear P5 Quinary Planetary Gear Set P51 Quinary Sun Gear P52 Quinary Planet carrier P53 Quinary Planet Gear P54 Quinary Ring Gear S1 First Shift Element S2 Second Shift Element S3 Third Shift Element S4 Fourth Shift Element S5 Fifth Shift Element S6 Sixth Shift Element