Multi-stage gearbox

Abstract

Multi-stage transmission with a drive shaft (1), with an output shaft (2), with a first intermediate gear set (VS1), a second intermediate gear set (VS2) and a third intermediate gear set (VS3), as well as a first secondary gear set (NS1) and a second secondary gear set (NS2), each designed as a planetary gear set, and with six switching elements (A, B, C, D, E, F), by selectively switching these elements a drive speed of the drive shaft (1) and output speeds generated in the intermediate gear sets (VS1, VS2, VS3) can be selectively transferred to the output shaft (2) as an output speed for shifting at least 12 forward gears (G1 to G12) and at least one reverse gear (R) via at least one of the secondary gear sets (NS1, NS2), wherein four switching elements (A, B, C, D) are assigned to the intermediate gear sets (VS1, VS2, VS3), wherein The two downstream gear sets (NS1, NS2) are each assigned two switching elements (E, F), with at least one of the upstream gear sets (VS1,VS2, VS3) is rigidly connected to an element of the downstream gear sets (NS1, NS2) such that six different output speeds of the upstream gear sets (VS1, VS2, VS3) can be transmitted to at least one of the downstream gear sets (NS1, NS2), wherein the drive shaft (1) is connected to a planet carrier (PT2) of the second upstream gear set (VS2) and to a ring gear (HR1) of the first upstream gear set (VS1) when the fourth switching element (D) is closed, wherein the drive shaft (1) and the planet carrier (PT2) of the second upstream gear set (VS2) and the ring gear (HR1) of the first upstream gear set (VS1) are connected to a ring gear (HR2) of the second upstream gear set (VS2) and to a planet carrier (PT3) of the third upstream gear set (VS3) when the third switching element (C) is closed and when the fourth switching element (D) is closed, wherein the drive shaft (1) is connected to a sun gear (SR3) of the third intermediate gear set (VS3),wherein a sun gear (SR1) of the first intermediate gear set (VS1) is connected to a housing (3) of the transmission when the first switching element (A) is closed, wherein a sun gear (SR2) of the second intermediate gear set (VS2) is connected to the housing (3) when the second switching element (B) is closed, wherein a planet carrier (PT1) of the first intermediate gear set (VS1) is connected to a ring gear (HR3) of the third intermediate gear set (VS3), wherein the planet carrier (PT3) of the third intermediate gear set (VS3) is connected to a sun gear (SR5) of the second secondary gear set (NS2), wherein a sun gear (SR4) of the first secondary gear set (NS1) is connected to the housing (3) when the sixth switching element (F) is closed, wherein a planet carrier (PT4) of the first secondary gear set (NS1) is connected to a ring gear (HR5) of the second secondary gear set (NS2) and to the output shaft (2) is connected,and wherein a ring gear (HR4) of the first secondary gear set (NS1) is connected to a planet carrier (PT5) of the second secondary gear set (NS2), wherein the ring gear (HR4) of the first secondary gear set (NS1) and the planet carrier (PT5) of the second secondary gear set (NS2) are connected to the drive shaft (1) when the fifth switching element (E) is closed.

Description

[0001] The present invention relates to a multi-stage transmission of the type defined in more detail in the preamble of claim 1.

[0002] For example, a multi-stage automatic transmission is known from publication EP 1 373 756 B1, in which, for instance, two pre-selector gear sets and two secondary gear sets are provided, to which seven shift elements are assigned, but only eleven forward gears and one reverse gear are selectable. The pre-selector gear sets are permanently connected to the secondary gear sets via a connecting shaft. Furthermore, the secondary gear sets can be connected to the input shaft via a shaft and a clutch as a shift element, and locked in place via another shaft and a brake as a further shift element, so that in at least three of the forward gears, the two secondary gear sets simultaneously transmit torque. This limits the number of gears despite the large number of components required, such as the seven shift elements.

[0003] From the publication DE 10 2014 117 679 A1, a planetary gear unit with a drive shaft and an output shaft, as well as with five planetary gear sets and six switching elements for realizing twelve forward gears and one reverse gear, is known.

[0004] The present invention is based on the objective of proposing a multi-stage transmission of the type described above with a maximum number of gears and a design that is as simple as possible.

[0005] This problem is solved according to the invention by the features of claim 1 or 2 or 3, with advantageous embodiments arising from the dependent claims and the description as well as the drawings.

[0006] Thus, a multi-stage transmission is proposed as an automatic transmission, particularly for vehicles, which comprises a drive shaft and an output shaft, as well as a first, second, and third intermediate gear set. Furthermore, a first and a second intermediate gear set are provided. The drive and intermediate gear sets are each designed as planetary gear sets. In addition, the multi-stage transmission has only six shift elements, through the selective shifting of which a drive speed of the drive shaft and the speeds generated in the drive gear sets can be selectively transmitted to the output shaft as the output speed for shifting at least 12 forward gears and at least one reverse gear via at least one of the intermediate gear sets. Four shift elements are assigned to the two drive gear sets and two shift elements to the two intermediate gear sets.At least one of the upstream gear sets is rigidly connected to an element of the downstream gear sets, so that six different output speeds of the upstream gear sets can be transferred to at least one of the downstream gear sets, where, normalized to the drive speed of the drive shaft, one of the output speeds is less than 0, three output speeds are between 0 and 1, one output speed is equal to 1 and one output speed is greater than 1.

[0007] In this way, a multi-stage automatic transmission is proposed that provides at least twelve forward gears and one reverse gear with minimal structural complexity. Furthermore, a particularly short and a particularly long forward gear are achievable, with a maximum of five individual gear sets and a maximum of six shift elements. Thus, in contrast to known multi-stage transmissions, more gear ratios are realized while simultaneously reducing the number of shift elements. Consequently, the proposed multi-stage transmission enables a maximum number of gears with the simplest possible design and optimized gear ratios.

[0008] Preferably, in the multi-stage transmission according to the invention, only three of the switching elements are designed as clutches and three as brakes. This results in a further space saving, since brakes are significantly simpler in design than clutches.

[0009] The construction effort is further reduced by preferably designing the three intermediate gear sets as 3-spindle, 5-shaft transmissions and assigning four switching elements to each intermediate gear set. This is achieved by connecting one element of the first intermediate gear set to an element of the second intermediate gear set, another element of the second intermediate gear set to an element of the third intermediate gear set, and another element of the third intermediate gear set to an element of the first intermediate gear set.

[0010] The two secondary gear sets are preferably designed as 2-web-4-shaft transmissions or arrangements. In a 2-web-4-shaft transmission or arrangement, two elements of each gear set are connected, so that instead of the usual six shafts, only four shafts are required. Each secondary gear set is assigned two shift elements. This further simplifies the design of the proposed multi-stage transmission and reduces overall manufacturing costs.

[0011] The multi-stage transmission proposed according to the invention can generally be used in vehicles. A preferred application is that the multi-stage transmission is used in vehicles that require a particularly short first gear or a so-called creeper gear, such as off-road vehicles or commercial vehicles, such as buses or the like. The fact that a long gear ratio is also possible with the multi-stage transmission results in improved efficiency during driving.

[0012] The present invention will now be explained in more detail with reference to the drawings. The drawings show: Fig. 1 a schematic view of a first embodiment of a multi-stage transmission according to the invention; Fig. 2 a schematic view of a second design variant of the multi-stage transmission with downstream sets designed as a Simpson gear set; Fig. 3 a schematic view of a third embodiment of the multi-stage transmission according to the invention with secondary gear sets designed as a modified Simpson gear set; and Fig. 4 an exemplary circuit diagram for the in the Fig. 1 to 3 wheelsets shown.

[0013] In the Fig. Figures 1 to 3 are exemplary gear set diagrams of a multi-stage transmission of a vehicle with, for example, 12 forward gears G1 to G12 and at least one reverse gear R, wherein Fig. 4 shows a possible switching matrix or switching scheme only as an example for the wheelset schemes.

[0014] The multi-stage transmission, designed as an automatic transmission, comprises a drive shaft 1 and an output shaft 2, wherein the drive shaft 1 is preferably coupleable via a torque converter 4 to a drive motor of the vehicle, for example an internal combustion engine or the like, as is the case, for example, in Fig. 1 is shown as an example. In Fig. Figure 2 shows the connection between the drive motor and the drive shaft 1 in the multi-stage transmission via a torsional damper K and a disconnect clutch K0. Fig. Figure 3 shows the same coupling between the drive motor and the drive shaft 1, with the additional feature of an electric machine EM coupled to the drive shaft 1 to illustrate a hybrid variant. The coupling options shown between the drive motor, an electric machine, and the drive shaft 1 of the multi-stage gearbox are merely examples and can be combined in any way.

[0015] Regardless of the specific design variant, the multi-stage transmission also includes a first pre-selector gear set VS1, a second pre-selector gear set VS2, and a third pre-selector gear set VS3, as well as a first secondary gear set NS1 and a second secondary gear set NS2, each designed as a planetary gear set. Furthermore, only six switching elements A, B, C, D, E, and F are provided, the selective engagement of which allows the drive speed of the drive shaft 1 and the speeds generated in the pre-selector gear sets VS1, VS2, and VS3 to be selectively transmitted to the output shaft 2 as the output speed for shifting at least twelve forward gears G1 to G12 and at least one reverse gear via at least one of the secondary gear sets NS1 and NS2.

[0016] In the multi-stage transmission according to the invention, four switching elements A, B, C, D are assigned to the upstream gear sets VS1, VS2, VS3, and two switching elements E, F are assigned to the two downstream gear sets NS1, NS2. The upstream gear sets VS2 and VS3 are rigidly connected to one element of the downstream gear sets NS1, NS2, such that six different output speeds of the upstream gear sets VS1, VS2, VS3 can be transmitted to at least one of the downstream gear sets NS1, NS2. The output speeds of the upstream gear sets VS1, VS2, VS3 are normalized or referenced to the drive speed of the drive shaft 1. One of the output speeds is less than 0. Three further output speeds are between 0 and 1. One further output speed is equal to 1, and one further output speed is greater than 1.

[0017] With a value of 1, the output speed equals the input speed. A reduction gear set therefore delivers a normalized speed that lies between 0 and 1. An overdrive gear set therefore delivers a normalized speed that is greater than 1. A reversing gear set therefore delivers a normalized speed that is less than 0.

[0018] Regardless of the various design variants, it is provided that the pre-selector gear sets VS1, VS2, VS3 are assigned a first switching element A as a brake, a second switching element B as a brake, a third switching element C as a clutch, and a fourth switching element D as a clutch, and that the secondary gear sets NS1, NS2 are assigned a fifth switching element E as a clutch and a sixth switching element F as a brake. Furthermore, the pre-selector gear sets VS1, VS2, VS3 are designed as 3-spindle, 5-shaft transmissions, and the two secondary gear sets NS1, NS2 are designed as 2-spindle, 4-shaft transmissions.

[0019] At the in Fig. In the first embodiment shown in Figure 1, it is provided in detail that, when the fourth switching element D is closed, the drive shaft 1 is connected to a planetary gear carrier PT2 of the second intermediate gear set VS2 and to a ring gear HR1 of the first intermediate gear set VS1. Furthermore, when the third switching element C and the fourth switching element D are closed, the drive shaft can be connected to both a ring gear HR2 of the second intermediate gear set VS2 and a planetary gear carrier PT3 of the third intermediate gear set VS3. Additionally, the drive shaft 1 is connected to a sun gear SR3 of the third intermediate gear set VS3. Moreover, when the first switching element A is closed, a sun gear SR1 of the first intermediate gear set VS1 is connected to a housing 3 of the multi-stage transmission. When the second switching element B is closed, a sun gear SR2 of the second intermediate gear set VS2 is connected to the housing 3.Furthermore, a planetary gear carrier PT1 of the first intermediate gear set VS1 is connected to a ring gear HR3 of the third intermediate gear set VS3. Additionally, the ring gear HR1 of the first intermediate gear set VS1 is connected to the planetary gear carrier PT2 of the second intermediate gear set VS2. Finally, the ring gear HR2 of the second intermediate gear set VS2 is connected to the planetary gear carrier PT3 of the third intermediate gear set VS3.

[0020] Furthermore, in the first embodiment, the planetary gear carrier PT3 of the third intermediate gear set VS3 is connected to a sun gear SR5 of the second intermediate gear set NS2. A sun gear SR4 of the first intermediate gear set NS1 is connected to the housing 3 when the sixth switching element F is closed. Additionally, a planetary gear carrier PT4 of the first intermediate gear set NS1 is connected to a ring gear HR5 of the second intermediate gear set NS2 and to the output shaft 2. Furthermore, a ring gear HR4 of the first intermediate gear set NS1 is connected to a planetary gear carrier PT5 of the second intermediate gear set NS2. When the fifth switching element E is closed, the ring gear HR4 and the planetary gear carrier PT5 are connected to the input shaft 1.

[0021] The in Fig. The first exemplary embodiment, shown in Figure 1, thus illustrates the third switching element C, advantageously located on a large diameter between the planet carrier or web PT2 and the ring gear HR2 of the second intermediate gear set VS2, and designed as a clutch. Furthermore, in the first embodiment, a planet-speed-optimized 2-web-4-shaft gear arrangement designed as CR-CR is implemented as secondary gear sets NS1, NS2.

[0022] In Fig. Figure 2 shows a second embodiment of the multi-stage transmission, in which the drive shaft 1, when the fourth shift element D is closed, is connected to a planet carrier PT2 of the second intermediate gear set VS2 and a ring gear HR1 of the first intermediate gear set VS1. When the third shift element C and the fourth shift element D are closed, the drive shaft 1, the ring gear HR1, and the planet carrier PT2 are also connected to a sun gear SR2 of the second intermediate gear set VS2. Furthermore, the drive shaft 1 is connected to a sun gear SR3 of the third intermediate gear set VS3. Additionally, when the first shift element A is closed, a sun gear SR1 of the first intermediate gear set VS1 is connected to the housing 3 of the transmission. A planet carrier PT1 of the first intermediate gear set VS1 is connected to a ring gear HR3 of the third intermediate gear set VS3.The ring gear HR1 of the first intermediate gear set VS1 is connected to the planet carrier PT2 of the second intermediate gear set VS2. Furthermore, the sun gear SR2 of the second intermediate gear set VS2 is connected to the housing 3 when the second switching element B is closed. Finally, the ring gear HR2 of the second intermediate gear set VS2 is connected to the planet carrier PT3 of the third intermediate gear set VS3.

[0023] Furthermore, in the second version variant according to Fig. 2. It is provided that the planetary gear carrier PT3 of the third intermediate gear set VS3 is connected to a sun gear SR4 of the first intermediate gear set NS1 and a sun gear SR5 of the second intermediate gear set NS2. Furthermore, a planetary gear carrier PT4 of the first intermediate gear set NS1 is connected to a ring gear HR5 of the second intermediate gear set NS2 and to the output shaft 2. A ring gear HR4 of the first intermediate gear set NS1 is connected to the housing when the sixth switching element F is closed. Furthermore, a planetary gear carrier PT5 of the second intermediate gear set NS2 is connected to the input shaft 1 when the fifth switching element E is closed.

[0024] Therefore, in the second execution variant, according to Fig. 2. Compared to the first version, the third switching element C, designed as a clutch, is actuated in a more economical manner. This element couples the planet carrier PT2 and the sun gear SR2 of the second intermediate gear set VS2. Furthermore, the two secondary gear sets NS1 and NS2 are designed as Simpson gear sets, resulting in significantly lower component loads.

[0025] In Fig. Figure 3 shows a third embodiment in which the drive shaft 1 is connected to a sun gear SR3 of the third intermediate gear set VS3. Furthermore, when the fourth switching element D is closed, the drive shaft 1 is connected to a planet carrier PT2 of the second intermediate gear set VS2 and to a ring gear HR1 of the first intermediate gear set VS1. When the first switching element A is closed, a sun gear SR1 of the first intermediate gear set VS1 is connected to the housing 3 of the transmission. Additionally, a planet carrier PT1 of the first intermediate gear set VS1 is connected to a ring gear HR3 of the third intermediate gear set VS3. A ring gear HR2 of the second intermediate gear set VS2 is connected to a planet carrier PT3 of the third intermediate gear set VS3.Furthermore, when the second switching element B is closed, a sun gear SR2 of the second intermediate gear set VS2 is connected to the housing 3, while when the third switching element C is closed, the sun gear SR2 of the second intermediate gear set VS2 is connected to the planet carrier PT2 of the second intermediate gear set VS2 and to the ring gear HR1 of the first intermediate gear set VS1. If the fourth switching element D is also closed, a connection to the drive shaft 1 can also be established.

[0026] Furthermore, in the third embodiment, the planetary gear carrier PT3 of the third intermediate gear set VS3 is connected to both a sun gear SR4 of the first intermediate gear set NS1 and a sun gear SR5 of the second intermediate gear set NS2. A planetary gear carrier PT4 of the first intermediate gear set NS1 is connected to the output shaft 2. Additionally, when the fifth switching element E is closed, a ring gear HR5 of the second intermediate gear set NS2 is also connected to the output shaft 2 and to the planetary gear carrier PT4 of the first intermediate gear set NS1. Furthermore, a planetary gear carrier PT5 of the second intermediate gear set NS2 is connected to the input shaft 1. Finally, when the sixth switching element F is closed, a ring gear HR4 of the first intermediate gear set NS1 is connected to the housing 3.

[0027] Accordingly, in the third version variant, a modified Simpson wheelset is provided as the main wheelset or as secondary wheelsets NS1, NS2 compared to the second version variant, whereby a lower support factor is realized on the fifth switching element E, which is designed as a clutch, compared to the first two versions variants.

[0028] In Fig. 4 is exemplary of those in the Fig. Figures 1 to 3 of the gear set diagrams of the multi-stage transmission according to the invention illustrate a shifting diagram. The shifting diagram indicates which of the shifting elements A, B, C, D, E, F are closed or engaged to implement the respective gear stage. Furthermore, the respective gear ratio, efficiency, and gear step are specified in the shifting diagram.

[0029] In the multi-stage transmission according to the invention, the first forward gear G1 has a short ratio, i.e., it has a high ratio and can therefore be used as a creeper gear. Furthermore, the eighth forward gear G8 is designed as a direct drive. In addition, the twelfth forward gear G12 has a long ratio, i.e., it has a low ratio and can be used as a so-called overdrive gear.

[0030] Depending on the application, the multi-stage transmission can be configured with 12 normally spaced forward gears (G1 to G12) and one reverse gear. Alternatively, as mentioned previously, it is also possible to have 11 normally spaced forward gears, a creeper gear, and a reverse gear. By skipping, for example, the third-highest gear, 11 gears with optimized spacing are achieved. By skipping the third-highest and fifth-highest gears, 10 gears with optimized gear ratios in the higher gears can be implemented.

[0031] In detail, the following results from the exemplary circuit diagram shown according to Fig.4, that to engage first forward gear G1, the first shift element A, the second shift element B, and the sixth shift element F are closed. To engage second forward gear G2, the first shift element A, the third shift element C, and the sixth shift element F are closed. To engage third forward gear G3, the first shift element A, the fourth shift element D, and the sixth shift element F are closed. To engage fourth forward gear G4, the third shift element C, the fourth shift element D, and the sixth shift element F are closed. To engage fifth forward gear G5, the second shift element B, the fourth shift element D, and the sixth shift element F are closed. To engage sixth forward gear G6, the second shift element B, the fifth shift element E, and the sixth shift element F are closed.To engage a seventh forward gear G7, the second shift element B, the fourth shift element D, and the fifth shift element E are closed. To engage an eighth forward gear G8, the third shift element C, the fourth shift element D, and the fifth shift element E are closed. To engage a ninth forward gear G9, the first shift element A, the fourth shift element D, and the fifth shift element E are closed. To engage a tenth forward gear G10, the first shift element A, the third shift element C, and the fifth shift element E are closed. To engage an eleventh forward gear G11, the first shift element A, the second shift element B, and the fifth shift element E are closed. Finally, to engage a twelfth forward gear G12, the second shift element B, the third shift element C, and the fifth shift element E are closed.

[0032] To engage a first alternative of the sixth forward gear G6, the first switching element A, the fifth switching element E, and the sixth switching element F are closed. To engage a second alternative of the sixth forward gear G6, the third switching element C, the fifth switching element E, and the sixth switching element F are closed. Finally, to engage a third alternative of the sixth forward gear G6, the fourth switching element D, the fifth switching element E, and the sixth switching element F are closed.

[0033] Thus, to switch to any gear stage, three of the switching elements A, B, C, D, E, F are closed.

[0034] In neutral (N) or idle, the second switching element B and the sixth switching element F are preferably closed. This offers the advantage that only one additional switching element needs to be closed to engage reverse (R) or a forward gear. Reference sign 1 drive shaft 2 Output shaft 3 cases 4 torque converters EM electric machine K Torsion damper K0 disconnect coupling between electric machine and drive machine VS1 first gear set VS2 second gear set VS3 third gear set NS1 first secondary gear set NS2 second downstream gear set G1 first forward gear G2 second forward gear G3 third forward gear G4 fourth forward gear G5 fifth forward gear G6 sixth forward gear G7 seventh forward gear G8 eighth forward gear G9 ninth forward gear G10 tenth forward gear G11 eleventh forward gear G12 twelfth forward gear R Reverse gear N Neutral or Idle A first switching element as a brake B second switching element as brake C third switching element as clutch The fourth switching element acts as a clutch. E fifth switching element as clutch F sixth switching element as brake SR1 Sun gear of the first intermediate gear set PT1 planetary gear carrier of the first intermediate gear set HR1 Ring gear of the first intermediate gear set SR2 Sun gear of the second intermediate gear set PT2 planetary gear carrier of the second intermediate gear set HR2 ring gear of the second intermediate gear set SR3 Sun gear of the third intermediate gear set PT3 planetary gear carrier of the third intermediate gear set HR3 ring gear of the third intermediate gear set SR4 Sun gear of the first downstream set PT4 planetary gear carrier of the first downstream set HR4 ring gear of the first downstream set SR5 Sun gear of the second downstream set PT5 planetary gear carrier of the second downstream set HR5 ring gear of the second downstream set

Claims

[1] Multi-stage transmission with a drive shaft (1), with an output shaft (2), with a first intermediate gear set (VS1), a second intermediate gear set (VS2) and a third intermediate gear set (VS3), as well as a first secondary gear set (NS1) and a second secondary gear set (NS2), each of which is designed as a planetary gear set, and with six switching elements (A, B, C, D, E, F), by the selective switching of which a drive speed of the drive shaft (1) and output speeds generated in the intermediate gear sets (VS1, VS2, VS3) can be selectively transmitted to the output shaft (2) as an output speed for switching at least 12 forward gears (G1 to G12) and at least one reverse gear (R) via at least one of the secondary gear sets (NS1, NS2), wherein four switching elements (A, B, C, D) are assigned to the intermediate gear sets (VS1, VS2, VS3). are, wherein the two downstream gear sets (NS1, NS2) are assigned two switching elements (E, F), wherein at least one of the upstream gear sets (VS1,VS2, VS3) is rigidly connected to an element of the secondary gear sets (NS1, NS2) such that six different output speeds of the secondary gear sets (VS1, VS2, VS3) can be transmitted to at least one of the secondary gear sets (NS1, NS2), wherein the drive shaft (1) is connected to a planet carrier (PT2) of the second secondary gear set (VS2) and to a ring gear (HR1) of the first secondary gear set (VS1) when the fourth switching element (D) is closed, wherein the drive shaft (1) and the planet carrier (PT2) of the second secondary gear set (VS2) and the ring gear (HR1) of the first secondary gear set (VS1) are connected to a ring gear (HR2) of the second secondary gear set (VS2) and to a planet carrier (PT3) of the third secondary gear set (VS3) when the third switching element (C) is closed and when the fourth switching element (D) is closed. wherein the drive shaft (1) is connected to a sun gear (SR3) of the third intermediate gear set (VS3),wherein a sun gear (SR1) of the first intermediate gear set (VS1) is connected to a housing (3) of the transmission when the first switching element (A) is closed, wherein a sun gear (SR2) of the second intermediate gear set (VS2) is connected to the housing (3) when the second switching element (B) is closed, wherein a planet carrier (PT1) of the first intermediate gear set (VS1) is connected to a ring gear (HR3) of the third intermediate gear set (VS3), wherein the planet carrier (PT3) of the third intermediate gear set (VS3) is connected to a sun gear (SR5) of the second secondary gear set (NS2), wherein a sun gear (SR4) of the first secondary gear set (NS1) is connected to the housing (3) when the sixth switching element (F) is closed, wherein a planet carrier (PT4) of the first secondary gear set (NS1) is connected to a ring gear (HR5) of the second secondary gear set (NS2) and to the output shaft (2) is connected,and wherein a ring gear (HR4) of the first secondary gear set (NS1) is connected to a planet carrier (PT5) of the second secondary gear set (NS2), wherein the ring gear (HR4) of the first secondary gear set (NS1) and the planet carrier (PT5) of the second secondary gear set (NS2) are connected to the drive shaft (1) when the fifth switching element (E) is closed. [2] Multi-stage transmission with a drive shaft (1), with an output shaft (2), with a first intermediate gear set (VS1), a second intermediate gear set (VS2) and a third intermediate gear set (VS3), as well as a first secondary gear set (NS1) and a second secondary gear set (NS2), each of which is designed as a planetary gear set, and with six switching elements (A, B, C, D, E, F), by the selective switching of which a drive speed of the drive shaft (1) and output speeds generated in the intermediate gear sets (VS1, VS2, VS3) can be selectively transmitted to the output shaft (2) as an output speed for switching at least 12 forward gears (G1 to G12) and at least one reverse gear (R) via at least one of the secondary gear sets (NS1, NS2), wherein four switching elements (A, B, C, D) are assigned to the intermediate gear sets (VS1, VS2, VS3). are, wherein the two downstream gear sets (NS1, NS2) are assigned two switching elements (E, F), wherein at least one of the upstream gear sets (VS1,VS2, VS3) is rigidly connected to an element of the downstream gear sets (NS1, NS2) such that six different output speeds of the upstream gear sets (VS1, VS2, VS3) can be transmitted to at least one of the downstream gear sets (NS1, NS2), wherein the drive shaft (1) is connected to a planet carrier (PT2) of the second upstream gear set (VS2) and to a ring gear (HR1) of the first upstream gear set (VS1) when the fourth switching element (D) is closed, wherein the drive shaft (1), the ring gear (HR1) of the first upstream gear set (VS1) and the planet carrier (PT2) of the second upstream gear set (VS2) are connected to a sun gear (SR2) of the second upstream gear set (VS2) when the third switching element (C) is closed and when the fourth switching element (D) is closed, and wherein the drive shaft (1) is connected to a sun gear (SR3) of the third upstream gear set (VS3) is connectedwherein a sun gear (SR1) of the first intermediate gear set (VS1) is connected to a housing (3) of the transmission when the first switching element (A) is closed, wherein a planet carrier (PT1) of the first intermediate gear set (VS1) is connected to a ring gear (HR3) of the third intermediate gear set (VS3), wherein the sun gear (SR2) of the second intermediate gear set (VS2) is connected to the housing (3) when the second switching element (B) is closed, wherein a ring gear (HR2) of the second intermediate gear set (VS2) is connected to a planet carrier (PT3) of the third intermediate gear set (VS3), wherein the planet carrier (PT3) of the third intermediate gear set (VS3) is connected to a sun gear (SR4) of the first secondary gear set (NS1) and to a sun gear (SR5) of the second secondary gear set (NS2), wherein a planet carrier (PT4) of the first secondary gear set (NS1) is connected to a ring gear (HR5) of the second downstream gear set (NS2) and to the output shaft (2),wherein a ring gear (HR4) of the first secondary gear set (NS1) is connected to the housing (3) when the sixth switching element (F) is closed, and wherein a planetary gear carrier (PT5) of the second secondary gear set (NS2) is connected to the drive shaft (1) when the fifth switching element (E) is closed. [3] Multi-stage transmission with a drive shaft (1), with an output shaft (2), with a first intermediate gear set (VS1), a second intermediate gear set (VS2) and a third intermediate gear set (VS3) as well as a first secondary gear set (NS1) and a second secondary gear set (NS2), each of which is designed as a planetary gear set, and with six switching elements (A, B, C, D, E, F), by the selective switching of which a drive speed of the drive shaft (1) and output speeds generated in the intermediate gear sets (VS1, VS2, VS3) can be selectively transferred to the output shaft (2) as an output speed for switching at least 12 forward gears (G1 to G12) and at least one reverse gear (R) via at least one of the secondary gear sets (NS1, NS2), wherein four switching elements (A, B, C, D) are assigned to the intermediate gear sets (VS1, VS2, VS3). are, wherein the two downstream gear sets (NS1, NS2) are assigned two switching elements (E, F), wherein at least one of the upstream gear sets (VS1,VS2, VS3) is rigidly connected to an element of the downstream gear sets (NS1, NS2) such that six different output speeds of the upstream gear sets (VS1, VS2, VS3) can be transmitted to at least one of the downstream gear sets (NS1, NS2), wherein the drive shaft (1) is connected to a planet carrier (PT2) of the second upstream gear set (VS2) and to a ring gear (HR1) of the first upstream gear set (VS1) when the fourth switching element (D) is closed, wherein the drive shaft (1), the ring gear (HR1) of the first upstream gear set (VS1) and the planet carrier (PT2) of the second upstream gear set (VS2) are connected to a sun gear (SR2) of the second upstream gear set (VS2) when the third switching element (C) and fourth switching element (D) are closed, and wherein the drive shaft (1) is connected to a sun gear (SR3) of the third upstream gear set (VS3) is connectedwherein a sun gear (SR1) of the first intermediate gear set (VS1) is connected to a housing (3) of the transmission when the first switching element (A) is closed, wherein a planet carrier (PT1) of the first intermediate gear set (VS1) is connected to a ring gear (HR3) of the third intermediate gear set (VS3), wherein the sun gear (SR2) of the second intermediate gear set (VS2) is connected to the housing (3) when the second switching element (B) is closed, wherein a ring gear (HR2) of the second intermediate gear set (VS2) is connected to a planet carrier (PT3) of the third intermediate gear set (VS3), wherein the planet carrier (PT3) of the third intermediate gear set (VS3) is connected to a sun gear (SR4) of the first secondary gear set (NS1) and to a sun gear (SR5) of the second secondary gear set (NS2), wherein a planet carrier (PT4) of the first secondary gear set (NS1) is connected to the output shaft (2),wherein a ring gear (HR5) of the second secondary gear set (NS2) is connected to the output shaft (2) and to the planet carrier (PT4) of the first secondary gear set (NS1) when the fifth switching element (E) is closed, wherein a ring gear (HR4) of the first secondary gear set (NS1) is connected to the housing (3) when the sixth switching element (F) is closed, and wherein a planet carrier (PT5) of the second secondary gear set (NS2) is connected to the input shaft (1). [4] Multi-stage transmission according to any of the preceding claims, characterized by , that the upstream gear sets (VS1, VS2, VS3) are assigned a first switching element (A) as a brake, a second switching element (B) as a brake, a third switching element (C) as a clutch and a fourth switching element (D) as a clutch and that the downstream gear sets (NS1, NS2) are assigned a fifth switching element (E) as a clutch and a sixth switching element (F) as a brake. [5] Multi-stage transmission according to any of the preceding claims, characterized by , that the first auxiliary gear set (VS1), the second auxiliary gear set (VS2) and the third auxiliary gear set (VS3) are designed as 3-web 5-shaft gearboxes. [6] Multi-stage transmission according to claim 1 or 2, characterized by , that the first secondary gear set (NS1) and the second secondary gear set (NS2) are designed as 2-strip 4-shaft gearboxes. [7] Multi-stage transmission according to one of the preceding claims, characterized bythat to engage reverse gear (R) the second shift element (B), the third shift element (C) and the sixth shift element (F) are closed; that to engage first forward gear (G1) the first shift element (A), the second shift element (B) and the sixth shift element (F) are closed; that to engage second forward gear (G2) the first shift element (A), the third shift element (C) and the sixth shift element (F) are closed; that to engage third forward gear (G3) the first shift element (A), the fourth shift element (D) and the sixth shift element (F) are closed; that to engage fourth forward gear (G4) the third shift element (C), the fourth shift element (D) and the sixth shift element (F) are closed; that to engage fifth forward gear (G5) the second shift element (B), the fourth shift element (D) and the sixth shift element (F) are closed.that to engage a sixth forward gear (G6), the second shift element (B), the fifth shift element (E), and the sixth shift element (F) are closed; that to engage a seventh forward gear (G7), the second shift element (B), the fourth shift element (D), and the fifth shift element (E) are closed; that to engage an eighth forward gear (G8), the third shift element (C), the fourth shift element (D), and the fifth shift element (E) are closed; that to engage a ninth forward gear (G9), the first shift element (A), the fourth shift element (D), and the fifth shift element (E) are closed; that to engage a tenth forward gear (G10), the first shift element (A), the third shift element (C), and the fifth shift element (E) are closed; that to engage an eleventh forward gear (G11), the first shift element (A), the second shift element (B), and the fifth shift element (E) are closed are,and that to engage a twelfth forward gear (G12), the second switching element (B), the third switching element (C) and the fifth switching element (E) are closed. [8] Multi-stage transmission according to any one of claims 1 to 7, characterized by , that to switch a first alternative of a sixth forward gear (G6) the first switching element (A), the fifth switching element (E) and the sixth switching element (F) are closed. [9] Multi-stage transmission according to any one of claims 1 to 7, characterized by , that to switch a second alternative of a sixth forward gear (G6) the third switching element (C), the fifth switching element (E) and the sixth switching element (F) are closed. [10] Multi-stage transmission according to any one of claims 1 to 7, characterized by , that to switch a third alternative of a sixth forward gear (G6) the fourth switching element (D), the fifth switching element (E) and the sixth switching element (F) are closed.

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