Center shaft transmission with planetary design for bicycles or electric mopeds

Abstract

The invention relates to a centre-axle transmission having a planetary design for a bicycle or an electric moped, comprising a pedal crankshaft (WAn) as a drive and a transmission output shaft (WAb) as an output, and comprising further shafts (W1, W2, W3, W4, W5, W6, W7), and comprising a first transmission shift group (3) and a second transmission shift group (4), which are coupled to one another for implementing a plurality of gears (G1, G2, G3, G4, G5, G6, G7, G8, G9, G10, G11, G12), the first transmission shift set (3) comprises a two-step planetary gear set (StRS1). A bicycle or electric moped (1) comprising a centre shaft transmission is also proposed.

Description

Technical Field

[0001] The invention relates to a central shaft transmission with a planetary design for a bicycle or electric assisted vehicle, which has a transmission input shaft or a pedal crankshaft as a drive and a transmission output shaft as an output, and has further shafts, and has a first transmission shift group and a second transmission shift group including a stepped planetary gear set, a plurality of shift elements being assigned to the first transmission shift group and the second transmission shift group. The invention also relates to a bicycle or electric assisted vehicle with a central shaft transmission. Background Art

[0002] For example, a transmission in a pedal crankshaft housing for a bicycle or electric power-assisted vehicle is disclosed in the publication DE102022203243B3. The transmission comprises a stepped planetary gear set and another planetary gear set arranged coaxially with the pedal crankshaft, and six shifting elements are assigned to these planetary gear sets to realize six gears. Summary of the invention

[0003] The object of the present invention is to provide a bottom bracket transmission and a bicycle or pedelec comprising the same, which bottom bracket transmission requires as little construction effort as possible and has improved properties compared to the prior art.

[0004] This object is achieved according to the invention by the features of claim 1 or 17. Advantageous and claimed developments are found in the dependent claims and in the description as well as in the drawings.

[0005] Therefore, a planetary-designed bottom-shaft transmission for bicycles or electric assisted vehicles is proposed. The bottom-shaft transmission has a pedal crankshaft as a drive and a transmission output shaft as an output as well as other shafts, wherein the output is preferably realized via a sprocket, a pulley or the like. In addition, the mid-shaft transmission includes a first transmission shift group and a second transmission shift group which are connected to each other to achieve multiple gears, wherein the first transmission shift group includes a two-stage stepped planetary gear set, three shift elements are assigned to the two-stage stepped planetary gear set, wherein the first shaft as the input shaft of the first stepped planetary gear set is connected to the second ring gear as an element of the first stepped planetary gear set, wherein the fifth shaft as the output shaft of the first stepped planetary gear set is connected to the first ring gear as an element of the first stepped planetary gear set, wherein the second sun gear as an element of the first stepped planetary gear set can be fixed to the housing or to a fixed component, etc. via the first shift element, wherein the first sun gear as an element of the first stepped planetary gear set can be fixed to the housing via the second shift element, wherein the stepped planetary gear carrier as an element of the first stepped planetary gear set is rotatably mounted, and wherein, in order to block the stepped planetary gear set, two elements of the first stepped planetary gear set can be connected to each other via the fifth shift element, so that theoretically ten equally effective blocking variants are possible.

[0006] In this way, a particularly simple and compact construction of the central shaft transmission is achieved by the above-mentioned connection of the first transmission shift group in the proposed central shaft transmission with the specified stepped planetary gear set and only three specified shifting elements. In addition, due to the geometric gear range in the central shaft transmission compared to known transmissions, there is a particularly low component load and an advantageously high transmission efficiency.

[0007] Preferably, in addition to the drive and the output, a further shaft or shaft-like element is used for the mechanical connection of elements (e.g. rotating elements etc.) of two planetary gear sets in two transmission shift groups, wherein the term shaft is not to be understood as referring solely to a cylindrically rotatably mounted machine element for transmitting torque, but is also to be understood as referring to a general connecting element which connects the individual gear set elements to one another for torque transmission.

[0008] In the proposed mid-shaft transmission, the axial order of the two transmission shift groups can be interchanged. Thus, between the transmission input shaft or pedal crankshaft of the mid-shaft transmission and the transmission output shaft, the first transmission shift group is connected upstream or downstream of the second transmission shift group. In the upstream arrangement of the first transmission shift group, the pedal crank of the mid-shaft transmission connected to the transmission input shaft or pedal crankshaft is effectively connected to the first shaft as the input shaft of the first transmission shift group, and the fifth shaft of the first transmission shift group is connected to the second transmission shift group on the input side. The pedal crankshaft and the first shaft can be designed as a single piece or even as multiple pieces. In the downstream arrangement of the first transmission shift group, the first shaft is connected to the second transmission shift group on the output side, and the fifth shaft of the first transmission shift group is connected to the transmission output shaft. The transmission output shaft and the fifth shaft can be designed as a single piece or as multiple pieces.

[0009] In the proposed mid-shaft transmission, any designed multi-speed second transmission shift group can be combined with the first transmission shift group as a mid-shaft transmission. Preferably, the second transmission shift group can be designed as a two-speed transmission or a two-speed group or as a three-speed transmission or a three-speed group or as a four-speed transmission or a four-speed group, and the first transmission shift group can be designed as a three-speed transmission or a three-speed group, so that, for example, a six-speed transmission or a nine-speed transmission or a ten-speed transmission or a twelve-speed transmission can be implemented as a mid-shaft transmission. However, other gear numbers can also be implemented in the transmission shift group, so that the mid-shaft transmission can also achieve a larger or smaller number of gears. Depending on the boundary conditions and requirements in the mid-shaft transmission, gears can also be omitted. In this way, the gear set can be optimized to the required transmission ratio (gear, range, etc.) or even to the type of shifting, and how many shifting elements are involved.

[0010] In order to connect the second transmission shift group and to achieve a particularly simple and compact construction of the mid-shaft transmission, it can be provided that: the second transmission shift group includes a first planetary gear set, a third shift element and a sixth shift element are assigned to the first planetary gear set, wherein in the second transmission shift group, the second element of the first planetary gear set is connected to the pedal crankshaft or to the fifth shaft serving as the output shaft of the first stepped planetary gear set, wherein the first element of the first planetary gear set can be fixed to the housing via the third shift element, wherein the third element of the first planetary gear set is connected to the transmission output shaft or to the first shaft serving as the input shaft of the first stepped planetary gear set, and wherein in order to block the first planetary gear set, two elements of the first planetary gear set can be connected to each other via the sixth shift element.

[0011] In order to achieve a particularly simple and compact construction of the mid-shaft transmission, a possible embodiment of the present invention for connecting the second transmission shift group can provide that the second transmission shift group includes a first planetary gear set and a second planetary gear set, a third shift element, a fourth shift element and a sixth shift element are assigned to the first planetary gear set and the second planetary gear set, wherein, in the second transmission shift group, the second element of the first planetary gear set is connected to the pedal crankshaft or to the fifth shaft as the output shaft of the first stepped planetary gear set, wherein the first element of the first planetary gear set and the first element of the second planetary gear set are connected to the transmission output shaft or to the first shaft as the input shaft of the first stepped planetary gear set, wherein the third element of the first planetary gear set can be fixed to the housing via the third shift element, wherein the third element of the first planetary gear set is connected to the second element of the second planetary gear set, wherein the third element of the second planetary gear set can be fixed to the housing via the fourth shift element, and wherein, in order to block the first planetary gear set and the second planetary gear set, the two elements of the planetary gear set can be connected to each other via the sixth shift element.

[0012] In order to achieve a particularly simple and compact construction of the mid-shaft transmission, another embodiment of the present invention for connecting the second transmission shift group can provide that: the second transmission shift group includes a second stepped planetary gear set, a third shift element, a fourth shift element and a sixth shift element are assigned to the second stepped planetary gear set, wherein in the second transmission shift group, the second ring gear as an element of the second stepped planetary gear set is connected to the pedal crankshaft or to the fifth shaft as the output shaft of the first stepped planetary gear set, wherein the second ring gear as an element of the second stepped planetary gear set is connected to the transmission output shaft or to the first shaft as the input shaft of the first stepped planetary gear set, wherein the stepped planetary gear carrier as an element of the second stepped planetary gear set can be fixed to the housing via the third shift element, wherein the sun gear as an element of the second stepped planetary gear set can be fixed to the housing via the fourth shift element, and wherein in order to block the second stepped planetary gear set, two elements of the second stepped planetary gear set can be connected to each other via the sixth shift element.

[0013] In order to achieve a particularly simple and compact construction of the mid-shaft transmission, another embodiment of the present invention for connecting the second transmission shift group can provide that the second transmission shift group includes a first planetary gear set and a second planetary gear set, a third shift element, a fourth shift element, a sixth shift element and a seventh shift element are assigned to the first planetary gear set and the second planetary gear set, wherein in the second transmission shift group, the second element of the first planetary gear set is connected to the pedal crankshaft or to the fifth shaft as the output shaft of the first stepped planetary gear set, wherein the first element of the first planetary gear set is connected to the transmission output shaft or to the fifth shaft as the output shaft of the first stepped planetary gear set The first shaft of the input shaft of the planetary gear set, wherein the third element of the first planetary gear set is connected to the second element of the second planetary gear set, wherein the third element of the second planetary gear set can be fixed to the housing via the third shift element and can be connected to the pedal crankshaft via the sixth shift element, or can be connected to the fifth shaft as the output shaft of the first stepped planetary gear set, and wherein the first element of the second planetary gear set can be fixed to the housing via the fourth shift element and can be connected to the transmission output shaft or to the first shaft as the input shaft of the first stepped planetary gear set via the seventh shift element.

[0014] In addition, in order to realize a particularly simple and compact construction of the central shaft transmission, another embodiment of the present invention for connecting the second transmission shift group can provide that: the second transmission shift group includes a first two-gear group and a second two-gear group, wherein the first two-gear group is assigned the third shift element and the sixth shift element, and wherein the second two-gear group is assigned the fourth shift element and the seventh shift element. It is also provided that: in the first two-gear group, the second element of the first planetary gear set is connected to the pedal crankshaft or to the fifth shaft as the output shaft of the first stepped planetary gear set; the third element of the first planetary gear set is connected to the second element of the second planetary gear set; the first element of the first planetary gear set can be fixed to the housing via the third shift element; in order to block the first planetary gear set, the two elements of the first planetary gear set can be connected to each other via the sixth shift element; the first element of the second planetary gear set is connected to the transmission output shaft or to the first shaft as the input shaft of the first stepped planetary gear set; the third element of the second planetary gear set can be fixed to the housing via the fourth shift element; and in order to block the second planetary gear set, the two elements of the second planetary gear set can be connected to each other via the seventh shift element. In addition to interchanging the order of the two transmission shift groups, an interchanging of the two gear groups is also effectively possible in the direction of the flux of force or in the axial direction.

[0015] Within the scope of the invention, in the proposed central shaft transmission with two transmission shift groups, it is provided that the specified shifting elements can be designed as brakes, flywheel brakes, clutches and / or flywheels. An advantageous variant of the invention provides that the first shifting element, the second shifting element, the third shifting element and the fourth shifting element are each designed as a positive-locking brake; and / or the fifth shifting element, the sixth shifting element and the seventh shifting element are each designed as a flywheel.

[0016] The shift element designed as a brake is preferably designed as a form-fitting shift element, such as a cost-effective brake pawl or shift pawl, etc., for example, with a toothed brake ring and a corresponding shift pawl. The brake as a shift element has the advantage that it can be easily approached from the outside for actuation. In a clutch designed as a flywheel, it is advantageous if the brake is designed as, for example, a one-way brake, so as to prevent blocking of the transmission when reversing the direction of rotation on the drive or output end. Preferably, a non-actively shiftable or actuable flywheel is used as a flywheel. This has the advantage that no shift actuation is required in a passive shift element. When the non-actuable flywheel is locked in the reverse direction state, it transmits torque. In the opposite direction of rotation, no torque is transmitted because the flywheel is not locked in the overrunning state. However, it is conceivable that an actively shiftable flywheel or even an actively shiftable flywheel brake can also be used.

[0017] A preferred embodiment of the invention can provide that at least one of the specified planetary gear sets is designed as a negative planetary gear set, resulting in a particularly space-saving arrangement. It is also conceivable that one of the planetary gear sets is designed as a positive planetary gear set.

[0018] If the planetary gear carrier and the ring gear connection to the gear set are interchanged with each other and the amount of fixed gear ratio is increased by 1, the negative planetary gear set can preferably be transferred to the positive planetary gear set. The negative planetary gear set has rotatably mounted planetary gears on its planetary gear carrier, which mesh with the sun gear and the ring gear of the planetary gear set, so that when the planetary gear carrier is fixed and the sun gear rotates, the ring gear rotates in a direction opposite to the direction of rotation of the sun gear. The positive planetary gear set has inner planetary gears and outer planetary gears, which are rotatably mounted on the planetary gear carrier of the positive planetary gear set and are tooth-engaged with each other, wherein the sun gear of the planetary gear set meshes with the inner planetary gears, and the ring gear of the planetary gear set meshes with the outer planetary gears, so that when the planetary gear carrier is fixed and the sun gear rotates, the ring gear rotates in the same direction of rotation as the direction of rotation of the sun gear.

[0019] For a person skilled in the art, this means that in the individual gear sets designed as negative planetary gear sets, the first element or gear set element is designed as a sun gear, the second element is designed as a planet gear carrier or web, and the third element is designed as a ring gear. This also means that in the individual gear sets designed as positive planetary gear sets, the first element is designed as a sun gear, the second element is designed as a ring gear, and the third element is designed as a planet gear carrier or web.

[0020] In order to further optimize the start-up of the proposed central shaft transmission, it is provided that at least one torque sensor or the like is arranged on the input and / or the output.

[0021] In order to provide electrical assistance to the drive in the proposed mid-axle transmission, at least one electric motor or the like may be connected or connectable or may be fixedly or releasably coupled to the drive or to the pedal crankshaft or the transmission input shaft and / or to the output or the transmission output shaft. Preferably, the electric motor may be arranged axially parallel to the pedal crankshaft or the transmission input shaft, while the planetary gear set is arranged coaxially with the pedal crankshaft or the transmission input shaft.

[0022] Another aspect of the present invention is to protect a bicycle or electric assisted vehicle having the above-mentioned middle shaft transmission, wherein the advantages already described and further advantages are found. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] The present invention is further explained below by means of the accompanying drawings, in which:

[0024] Figure 1 A schematic basic view of a bottom bracket transmission according to the invention on a bicycle or electric assisted vehicle is shown, which has a first transmission shift group with a stepped planetary gear set, which is connected upstream of a second transmission shift group in a first blocking variant;

[0025] Figure 2 A schematic basic view of a central shaft transmission according to the invention is shown, which has a first transmission shift group with a stepped planetary gear set, which is connected downstream of a second transmission shift group in a first block variant;

[0026] Figure 3 A schematic basic view of a central shaft transmission according to the invention is shown, which has a first transmission shift group with a stepped planetary gear set, which is connected upstream of a second transmission shift group in a second gearing variant;

[0027] Figure 4A schematic basic view of a central shaft transmission according to the invention is shown, which has a first transmission shift group with a stepped planetary gear set, which is connected upstream of a second transmission shift group in a third gear variation;

[0028] Figure 5 shows a schematic basic view of a central shaft transmission according to the invention, which has a first transmission shift group with a stepped planetary gear set, which is connected upstream of a second transmission shift group in a fourth gear variant;

[0029] Figure 6 A schematic basic view of a central shaft transmission according to the invention is shown, which has a first transmission shift group with a stepped planetary gear set, which is connected upstream of a second transmission shift group in a fifth gear variant;

[0030] Figure 7 shows a schematic basic view of a central shaft transmission according to the invention, which has a first transmission shift group with a stepped planetary gear set, which is connected upstream of a second transmission shift group in a sixth gear variation;

[0031] Figure 8 shows a schematic basic view of a central shaft transmission according to the invention, which has a first transmission shift group with a stepped planetary gear set, which is connected upstream of a second transmission shift group in a seventh gear variant;

[0032] Fig. 9 shows a schematic basic view of a central shaft transmission according to the invention, which has a first transmission shift group with a stepped planetary gear set, which is connected upstream of a second transmission shift group in an eighth gear variation;

[0033] Fig.10 A shift diagram of a first transmission shift group in a mid-shaft transmission having three shiftable gears is shown;

[0034] Fig.11 A schematic basic view of a central shaft transmission with an embodiment in which a second transmission shift group as a two-speed transmission is connected upstream of a first transmission shift group as a three-speed transmission is shown;

[0035] Fig.12 Shown according to Fig.11 Shift diagram for the six-speed mid-shaft transmission;

[0036] Fig.13shows a schematic basic view of a central shaft transmission with an embodiment in which a second transmission shift group with two planetary gear sets is connected downstream of a first transmission shift group as a three-speed transmission;

[0037] Fig.14 shows a schematic basic view of a central shaft transmission with an embodiment in which a second transmission shift group with a second stepped planetary gear set is connected downstream of a first transmission shift group as a three-speed transmission;

[0038] Fig.15 Shown according to Fig.13 and Fig.14 The shift diagram of the nine-speed mid-shaft transmission;

[0039] Fig.16 shows a schematic basic view of a central shaft transmission with an embodiment in which a second transmission shift group with two planetary gear sets is connected downstream of a first transmission shift group as a three-speed transmission;

[0040] Fig.17 Shown according to Fig.16 The shift diagram of the ten-speed mid-shaft transmission;

[0041] Fig.18 A schematic basic view of a central shaft transmission with an embodiment in which a second transmission shift group with two two-speed groups is connected downstream of a first transmission shift group as a three-speed transmission is shown;

[0042] Fig.19 Shown according to Fig.18 Shift diagram for the twelve-speed mid-shaft transmission;

[0043] Fig. 20 Shown according to Figure 1 Schematic basic view of a mid-shaft transmission, wherein a torque sensor on the drive is indicated by way of example;

[0044] Fig.21 Shown according to Fig. 20 Schematic basic view of a central shaft transmission, wherein the electric machine is arranged on the drive as an example;

[0045] Fig. 22 Shown according to Fig. 20 A schematic basic view of a mid-shaft transmission of , wherein the electric machine is arranged at the output as an example; and

[0046] Fig.23 Shown according to Fig. 20 Schematic basic view of a mid-shaft transmission with the flywheel upstream of the pedal crankshaft. DETAILED DESCRIPTION

[0047] The different variants and embodiments or shifting diagrams of the central shaft transmission with a planetary design according to the invention are described merely by way of example. Figures 1 to 23 Shown in. Figure 1 By way of example, a bicycle or pedelec 1 is shown, wherein a bottom bracket transmission is only shown schematically.

[0048] The bottom shaft transmission is shown in a housing or bottom shaft housing 2 with a pedal crank, wherein the pedal crank with a pedal serves as a pedal crankshaft WAn, wherein the pedal crankshaft WAn is connected on the input side to one of the transmission shift groups 3, 4. The bottom shaft transmission also includes a transmission output shaft WAb as an output, which has a sprocket or a pulley (not further shown), which is connected on the output side to one of the transmission shift groups 3, 4. The bottom shaft transmission includes a multi-speed first transmission shift group 3 and a multi-speed second transmission shift group 4, wherein the first transmission shift group 3 has a two-stage stepped planetary gear set StRS1, a first shift element B1 as a form-fitting brake, a second shift element B2 as a form-fitting brake, and a fifth shift element F1 as a flywheel. I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII Assigned to the two-stage stepped planetary gear set StRS1. The two transmission shift groups 3, 4 effectively form two sub-transmissions which can be interconnected with one another in any order with respect to the direction of the flow of force between the pedal crankshaft WAn and the transmission output shaft WAb.

[0049] Independently of the corresponding variant, in the mid-shaft transmission, it is provided that: the first shaft W1 is connected as the input shaft of the first stepped planetary gear set StRS1 to the second ring gear HR1.2 as an element of the first stepped planetary gear set StRS1, the fifth shaft W5 as the output shaft of the first stepped planetary gear set StRS1 is connected to the first ring gear HR1.1 as an element of the first stepped planetary gear set StRS1, the second sun gear SR1.2 as an element of the first stepped planetary gear set StRS1 can be fixed to the housing 2 via the first shift element B1, the first sun gear SR1.1 as an element of the first stepped planetary gear set StRS1 can be fixed to the housing 2 via the second shift element B2, the stepped planetary gear carrier SPT1 as an element of the first stepped planetary gear set StRS1 is rotatably mounted, and in order to block the stepped planetary gear set StRS1, two elements of the first stepped planetary gear set StRS1 can be shifted via the fifth shift element F1 I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII Connect with each other.

[0050] exist Fig.11 , Fig.13 , Fig.14 , Fig.16 and Fig.18 In the example, the designated planetary gear sets RS1, RS2 are designed in each case as space-saving negative planetary gear sets. It is provided here that in each case, in the planetary gear sets RS1, RS2, a sun gear SR1, SR2 is provided as the first element, a web or planetary gear carrier PT1, PT2 is provided as the second element, and a ring gear HR1, HR2 is provided as the third element.

[0051] exist Figure 1 In FIG. 1 , a variant of a mid-shaft transmission is shown, in which a first transmission shift group 3 is connected upstream of a second transmission shift group 4. Figure 1In the first variant, it is stipulated that: the first shaft W1 as the input shaft of the first stepped planetary gear set StRS1 of the first transmission shift group 3 is connected to the pedal crankshaft WAn or is constructed as an integral part with the pedal crankshaft WAn; the first shaft W1 is connected to the second ring gear HR1.2 of the first stepped planetary gear set StRS1; the first ring gear HR1.1 of the first stepped planetary gear set StRS1 is connected to the second transmission shift group 4 on the input side via the fifth shaft W5; the stepped planetary gear carrier SPT1 of the first stepped planetary gear set StRS1 is rotatably mounted via the fourth shaft W4; when the first shift element B1 is engaged, the second sun gear SR1.2 of the first stepped planetary gear set StRS1 can be fixed to the housing 2 via the second shaft W2; when the second shift element B2 is engaged, the first sun gear SR1.1 of the first stepped planetary gear set StRS1 can be fixed to the housing 2 via the third shaft W3; and in order to block the first stepped planetary gear set StRS1 as the first blocking variant, when in the fifth shift element F1 I In the first arrangement variant of the fifth shifting element F1 I When locked, the first sun gear SR1.1 can be connected to the first ring gear HR1.1.

[0052] exist Figure 2 In FIG. 1 , a variant of a mid-axle transmission is shown, in which a first transmission shift group 3 is connected downstream of a second transmission shift group 4. Figure 2 In a variant, it is stipulated that: the first shaft W1 as the input shaft of the first stepped planetary gear set StRS1 is connected to the second transmission shift group 4 on the output side; the first shaft W1 is connected to the second ring gear HR1.2 of the stepped planetary gear set StRS1; the first ring gear HR1.1 of the first stepped planetary gear set StRS1 is connected to the fifth shaft W5; the fifth shaft W5 as the output shaft of the first transmission shift group is connected to the transmission output shaft WAb or is constructed as an integral part with the transmission output shaft WAb; the stepped planetary gear carrier SPT1 of the first stepped planetary gear set StRS1 is rotatably mounted via the fourth shaft W4; when the first shift element B1 is engaged, the second sun gear SR1.2 of the first stepped planetary gear set StRS1 can be fixed to the housing 2 via the second shaft W2; when the second shift element B2 is engaged, the first sun gear SR1.1 of the first stepped planetary gear set StRS1 can be fixed to the housing 2 via the third shaft W3; and at the fifth shift element F1 I In the first arrangement variant, in order to block the first stepped planetary gear set StRS1 as the first blocking variant, when the fifth shifting element F1 I When locked, the first sun gear SR1.1 can be connected to the first ring gear HR1.1.

[0053] exist Figure 3 , a second blocking variant of the first stepped planetary gear set StRS1 is shown, wherein the first transmission shift group 3 is connected upstream of the second transmission shift group 4. In the context of the second blocking variant, in the second arrangement variant, when the fifth shift element F1 II When engaged, the second sun gear SR1.2 is connected to the second ring gear HR1.2 of the first stepped planetary gear set StR1.

[0054] exist Figure 4 , a third blocking variant of the first stepped planetary gear set StRS1 is shown, wherein the first transmission shift group 3 is connected upstream of the second transmission shift group 4. In the context of the third blocking variant, in the third arrangement variant, when the fifth shift element F1 III When engaged, the stepped planetary gear carrier SPT1 is connected to the second ring gear HR1 . 2 of the first stepped planetary gear set StR1 .

[0055] exist Figure 5 , a fourth blocking variant of the first stepped planetary gear set StRS1 is shown, wherein the first transmission shift group 3 is connected upstream of the second transmission shift group 4. In the context of the fourth blocking variant, in the fourth arrangement variant, when the fifth shift element F1 IV When engaged, the first ring gear HR1 . 1 is connected to the second ring gear HR1 . 2 of the first stepped planetary gear set StR1 .

[0056] exist Figure 6 , the fifth blocking variant of the first stepped planetary gear set StRS1 is shown, wherein the first transmission shift group 3 is connected upstream of the second transmission shift group 4. In the context of the fifth blocking variant, in the fifth arrangement variant, when the fifth shift element F1 V When engaged, the first sun gear SR1.1 is connected to the second sun gear SR1.2 of the first stepped planetary gear set StR1.

[0057] exist Figure 7 , the sixth blocking variant of the first stepped planetary gear set StRS1 is shown, in which the first transmission shift group 3 is connected upstream of the second transmission shift group 4. In the context of the sixth blocking variant, in the sixth arrangement variant, when the fifth shift element F1 VI When engaged, the second sun gear SR1.2 is connected to the stepped planetary gear carrier SPT1 of the first stepped planetary gear set StR1.

[0058] exist Figure 8, the seventh blocking variant of the first stepped planetary gear set StRS1 is shown, in which the first transmission shift group 3 is connected upstream of the second transmission shift group 4. In the context of the seventh blocking variant, in the seventh arrangement variant, when the fifth shift element F1 VII When engaged, the first sun gear SR1.1 is connected to the stepped planet gear carrier SPT1 of the first stepped planetary gear set StR1.

[0059] exist Fig. 9 , the eighth blocking variant of the first stepped planetary gear set StRS1 is shown, in which the first transmission shift group 3 is connected upstream of the second transmission shift group 4. In the context of the eighth blocking variant, in the eighth arrangement variant, when the fifth shift element F1 VIII When engaged, the first ring gear HR1 . 1 is connected to the stepped planet carrier SPT1 of the first stepped planetary gear set StR1 .

[0060] exist Fig.10 , a shift diagram for the first transmission shift group 3 as a three-speed transmission is shown. It follows that three gears G1, G2, G3 can be achieved by the first transmission shift group 3. The shift diagram specifies the shift elements B1, B2, F1 for the corresponding gears G1, G2, G3. I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII Here, the flywheel F1 as the shift element in the shift diagram I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII The X in means that the flywheel is locked. This takes effect automatically without external actuation. In addition, the X in the shift diagram for the brakes B1, B2 as shift elements means that the brakes B1, B2 are engaged. This takes effect via a suitable actuator system. Flywheel F1 I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII Empty fields in means the flywheel is not locked. Empty fields in brakes B1, B2 means the brakes are disengaged.

[0061] In detail, according to Fig.10 The shift diagram shows that in order to realize or shift the first gear G1, the first shifting element F1 designed as a flywheel I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII Locking; in order to achieve the second gear G2, the second shifting element B2 designed as a brake is engaged; and / or in order to achieve the third gear G3, the first shifting element B1 designed as a brake is engaged.

[0062] exist Fig.11 In the figure, it is shown by way of example that the intermediate shaft transmission has a first transmission shift group 3 as a three-speed transmission group and has a second transmission shift group 4 as a two-speed transmission group, the second transmission shift group 4 having a first planetary gear set RS1, to which a third shift element B3 as a brake and a sixth shift element F2 as a flywheel are assigned. In detail, in order to connect the second transmission shift group 4 to the first transmission shift group 3, it is provided that: the planetary gear carrier PT1 of the first planetary gear set RS1 is connected to the fifth shaft W5 as the output shaft of the first stepped planetary gear set StRS1; when the third shift element B3 is engaged, the sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via the sixth shaft W6; the ring gear HR1 of the first planetary gear set RS1 is connected to the transmission output shaft WAb; and in order to block the first planetary gear set RS1, in the first blocking variant, when the sixth shift element F2 is locked, the ring gear HR1 can be connected to the sun gear of the first planetary gear set RS1. Two further blocking variants are achieved by further connection options of the elements of the first planetary gear set RS1 . The connection of the first stepped planetary gear set StRS1 in the first transmission shift group 3 has already been described above.

[0063] exist Fig.12 In the figure, the Fig.11 The shift diagram of the central shaft transmission with the first transmission shift group 3 as a three-speed transmission and the second transmission shift group 4 as a two-speed transmission is shown in FIG. It can be seen from this that 4x2, i.e., six gears G1, G2, G3, G4, G5, G6 can be realized. The shift diagram specifies the shift elements B1, B2, B3, F1 for the corresponding gears G1, G2, G3, G4, G5, G6. I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1VI 、F1 VII 、F1 VIII Here, the flywheel F1 as the shift element in the shift diagram I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII The X in F1, F2 means that the flywheel is locked. This takes effect automatically without external actuation. In addition, the X in the brakes B1, B2, B3 as shift elements in the shift diagram means that the brakes B1, B2, B3 are engaged. This takes effect via a suitable actuator system. Flywheel F1 I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII Empty fields in F1, F2 mean the flywheel is not locked. Empty fields in brakes B1, B2, B3 mean the brakes are disengaged.

[0064] In detail, according to Fig.12 The shift diagram shows that in order to realize or shift the first gear G1, the fifth shifting element F1 designed as a flywheel I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII and the sixth shifting element F2 designed as a flywheel are locked; to achieve the second gear G2, the second shifting element B2 designed as a brake is engaged, and the sixth shifting element F2 designed as a flywheel is locked; to achieve the third gear G3, the first shifting element B1 designed as a brake is engaged, and the sixth shifting element F2 designed as a flywheel is locked; to achieve the fourth gear G4, the third shifting element B3 designed as a brake is engaged, and the fifth shifting element F1 designed as a flywheel is engaged. I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIIILocked; in order to achieve the fifth gear G5, the second shift element B2 designed as a brake and the third shift element B3 designed as a brake are engaged; and / or in order to achieve the sixth gear G6, the first shift element B1 designed as a brake and the third shift element B3 designed as a brake are engaged.

[0065] exist Fig.13 In the figure, it is shown by way of example that the intermediate shaft transmission has a first transmission shift group 3 as a three-speed transmission group and has a second transmission shift group 4 as a three-speed transmission group, the second transmission shift group 4 has a first planetary gear set RS1 and a second planetary gear set RS2, and a third shift element B3 as a brake, a fourth shift element B4 as a brake, and a sixth shift element F2 as a flywheel are assigned to the first planetary gear set RS1 and the second planetary gear set RS2. In detail, in order to connect the second transmission shift group 4 to the first transmission shift group 3, it is stipulated that: the planetary gear carrier PT1 of the first planetary gear set RS1 is connected to the fifth shaft W5 as the output shaft of the first stepped planetary gear set StRS1; the sun gear SR1 of the first planetary gear set RS1 and the sun gear SR2 of the second planetary gear set RS2 are connected together to the transmission output shaft WAb; when the third shift element B3 is engaged, the ring gear HR1 of the first planetary gear set RS1 can be fixed to the housing 2 via the sixth shaft W6; the ring gear HR1 of the first planetary gear set RS1 is fixedly connected to the housing 2 via the sixth shaft W6 connected to the planetary gear carrier PT2 of the second planetary gear set RS2; when the fourth shift element B4 is engaged, the ring gear HR2 of the second planetary gear set RS2 can be fixed to the housing 2 via the seventh shaft W7; and in order to block the first planetary gear set RS1 and the second planetary gear set RS2, in the context of the first blocking variant, the transmission output shaft WAb connected to the two sun gears SR1 and SR2 of the two planetary gear sets RS1 and RS2 when the sixth shift element F2 is blocked in the first arrangement variant can be connected to the seventh shaft W7, and the seventh shaft W7 is connected to the ring gear HR2 of the second planetary gear set RS2. In order to realize further blocking variants, more of the six elements of the two planetary gear sets RS1, RS2 are connected to each other via the sixth shift element F2. The connection of the first stepped planetary gear set StRS1 in the first transmission shift group 3 has been described above.

[0066] exist Fig.14In the figure, it is shown by way of example that the mid-shaft transmission has a first transmission shift group 3 as a three-speed transmission group and a second transmission shift group 4 as a three-speed transmission group, the second transmission shift group 4 has a second stepped planetary gear set StRS2, a third shift element B3 as a brake, a fourth shift element B4 as a brake and a sixth shift element F2 as a flywheel are assigned to the second stepped planetary gear set StRS2. In detail, in order to connect the second transmission shift group 4 to the first transmission shift group 3, it is stipulated that: the second ring gear HR2.2, which is an element of the second stepped planetary gear set StRS2, is connected to the fifth shaft W5, which is the output shaft of the first stepped planetary gear set StRS1; the first ring gear HR2.1, which is an element of the second stepped planetary gear set StRS2, is connected to the transmission output shaft WAb; when the third shift element B3 is engaged, the stepped planetary gear carrier SPT2, which is an element of the second stepped planetary gear set StRS2, can be fixed to the housing 2 via the sixth shaft W6; when the fourth shift element B4 is engaged, the sun gear SR2.1, which is an element of the second stepped planetary gear set StRS2, can be fixed to the housing 2 via the seventh shaft W7; and in order to block the second stepped planetary gear set StRS2, in the context of the first blocking variant, in the first arrangement variant, when the sixth shift element F2 is locked, the sun gear SR2.1 can be connected to the first ring gear HR2.1 of the second stepped planetary gear set StRS2. Further blocking variants are achieved by further connection options of the four elements of the second stepped planetary gear set StRS2 . The connection of the first stepped planetary gear set StRS1 in the first transmission shift group 3 has already been described above.

[0067] exist Fig.15 In the figure, the Fig.13 and Fig.14 The shift diagram of the central shaft transmission with the first transmission shift group 3 as a three-speed transmission and the second transmission shift group 4 as a three-speed transmission shown in FIG. It can be seen that 3x3, i.e., nine gears G1, G2, G3, G4, G5, G6, G7, G8, G9 can be realized. The shift diagram specifies the shift elements B1, B2, B3, B4, F1 for the corresponding gears G1, G2, G3, G4, G5, G6, G7, G8, G9. I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII Here, the flywheel F1 as the shift element in the shift diagram I 、F1 II 、F1III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII The X in F1, F2 means that the flywheel is locked. This takes effect automatically without external actuation. In addition, the X in the brakes B1, B2, B3, B4 as shift elements in the shift diagram means that the brakes B1, B2, B3, B4 are engaged. This takes effect via a suitable actuator system. Flywheel F1 I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII Empty fields in F1, F2 mean that the flywheel is not locked. Empty fields in brakes B1, B2, B3, B4 mean that the brakes are disengaged.

[0068] In detail, according to Fig.15 The shift diagram shows that in order to realize or shift the first gear G1, the fifth shifting element F1 designed as a flywheel I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII and the sixth shifting element F2 designed as a flywheel is locked; to achieve the second gear G2, the second shifting element B2 designed as a brake is engaged, and the sixth shifting element F2 designed as a flywheel is locked; to achieve the third gear G3, the first shifting element B1 designed as a brake is engaged, and the sixth shifting element F2 designed as a flywheel is locked; to achieve the fourth gear G4, the fourth shifting element B4 designed as a brake is engaged, and the fifth shifting element F1 designed as a flywheel is engaged. I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII Lock; to achieve the fifth gear G5, the second shift element B2 designed as a brake and the fourth shift element B4 designed as a brake are engaged; to achieve the sixth gear G6, the first shift element B1 designed as a brake and the fourth shift element B4 designed as a brake are engaged; to achieve the seventh gear G7, the third shift element B3 designed as a brake is engaged, and the fifth shift element F1 designed as a flywheel is engagedI 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII Locked; in order to achieve the eighth gear G8, the second shift element B2 designed as a brake and the third shift element B3 designed as a brake are engaged; and / or in order to achieve the ninth gear G9, the first shift element B1 designed as a brake and the third shift element B3 designed as a brake are engaged.

[0069] exist Fig.16 In the figure, it is shown by way of example that the mid-shaft transmission has a first transmission shift group 3 as a three-speed transmission group and a second transmission shift group 4, wherein the second transmission shift group 4 has a first planetary gear set RS1 and a second planetary gear set RS2, and a third shift element B3 as a brake, a fourth shift element B4 as a brake, a sixth shift element F2 as a flywheel and a seventh shift element F3 as a flywheel are assigned to the first planetary gear set RS1 and the second planetary gear set RS2. In detail, in order to connect the second transmission shift group 4 to the first transmission shift group 3, it is stipulated that: the planetary gear carrier PT1 of the first planetary gear set RS1 is connected to the fifth shaft W5 which is the output shaft of the first stepped planetary gear set StRS1; the sun gear SR1 of the first planetary gear set RS1 is connected to the transmission output shaft WAb; the ring gear HR1 of the first planetary gear set RS1 is fixedly connected to the planetary gear carrier PT2 of the second planetary gear set RS2 via the sixth shaft W6; when the third shift element B3 is engaged, the ring gear HR2 of the second planetary gear set RS2 can be fixed to the housing 2 via the seventh shaft W7, and when the sixth shift element F2 is locked, the ring gear HR2 of the second planetary gear set RS2 can be connected to the fifth shaft W5 which is the output shaft of the first stepped planetary gear set StRS1; and when the fourth shift element B4 is engaged, the sun gear SR2 of the second planetary gear set RS2 can be fixed to the housing 2 via the eighth shaft W8, and when the seventh shift element F3 is locked, the sun gear SR2 of the second planetary gear set RS2 can be connected to the transmission output shaft WAb. The connection of the first stepped planetary gear set StRS1 in the first transmission shift group 3 has been described above.

[0070] exist Fig.17 In the figure, the Fig.16The shift diagram of the central shaft transmission with the first transmission shift group 3 as a three-speed transmission and the second transmission shift group 4 is shown in FIG. It follows that ten gears G1, G2, G3, G4, G5, G6, G7, G8, G9, G10 can be realized. In this shift diagram, the shift elements B1, B2, B3, B4, F1 for the corresponding gears G1, G2, G3, G4, G5, G6, G7, G8, G9, G10 are specified. I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII , F2, F3. Here, the flywheel F1 as the shift element in the shift diagram I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII , F2, F3 means that the flywheel is locked. This takes effect automatically without external actuation. In addition, the X in the shift diagram for the brakes B1, B2, B3, B4 as shift elements means that the brakes B1, B2, B3, B4 are engaged. This takes effect via a suitable actuator system. Flywheel F1 I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII Empty fields in F1, F2, F3 mean that the flywheel is not locked. Empty fields in brakes B1, B2, B3, B4 mean that the brakes are disengaged.

[0071] In detail, according to Fig.17 The shift diagram shows that in order to realize or shift the first gear G1, the fifth shifting element F1 designed as a flywheel I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII, the sixth shifting element F2 designed as a flywheel and the seventh shifting element F3 designed as a flywheel are locked; in order to achieve the second gear G2, the second shifting element B2 designed as a brake is engaged, and the sixth shifting element F2 designed as a flywheel and the seventh shifting element F3 designed as a flywheel are locked; in order to achieve the third gear G3, the first shifting element B1 designed as a brake and the sixth shifting element F2 designed as a flywheel and the seventh shifting element F3 designed as a flywheel are locked; in order to achieve the fourth gear G4, the fourth shifting element B4 designed as a brake is engaged, and the fifth shifting element F1 designed as a flywheel is locked. I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII and the sixth shifting element F2 designed as a flywheel is locked; in order to achieve the fifth gear G5, the third shifting element B3 designed as a brake is engaged, and the fifth shifting element F1 designed as a flywheel I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII and the seventh shifting element F3 designed as a flywheel is locked; to achieve the sixth gear G6, the second shifting element B2 designed as a brake and the third shifting element B3 designed as a brake are engaged, and the seventh shifting element F3 designed as a flywheel is locked; to achieve the seventh gear G7, the first shifting element B1 designed as a brake and the third shifting element B3 designed as a brake are engaged, and the seventh shifting element F3 designed as a flywheel is locked; to achieve the eighth gear G8, the third shifting element B3 designed as a brake and the fourth shifting element B4 designed as a brake are engaged, and the fifth shifting element F1 designed as a flywheel is locked. I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII Lock; in order to achieve the ninth gear G9, the second shift element B2 designed as a brake, the third shift element B3 designed as a brake and the fourth shift element B4 designed as a brake are engaged; and / or in order to achieve the tenth gear G10, the first shift element B1 designed as a brake, the third shift element B3 designed as a brake and the fourth shift element B4 designed as a brake are engaged.

[0072] exist Fig.18 In the figure, it is shown by way of example that the mid-shaft transmission has a first transmission shift group 3 as a three-speed transmission group and a second transmission shift group 4 as a first two-speed group and as a second two-speed group, the second transmission shift group 4 has a first planetary gear set RS1 and a second planetary gear set RS2, and the third shift element B3 as a brake, the fourth shift element B4 as a brake, the sixth shift element F2 as a flywheel and the seventh shift element F3 as a flywheel are assigned to the first planetary gear set RS1 and the second planetary gear set RS2. In detail, in order to connect the second transmission shift group 4 to the first transmission shift group 3, it is stipulated that: in the first two-speed group, the planetary gear carrier PT1 of the first planetary gear set RS1 is connected to the fifth shaft W5 which is the output shaft of the first stepped planetary gear set StRS1; the ring gear HR1 of the first planetary gear set RS1 is connected to the planetary gear carrier PT2 of the second planetary gear set RS2 via the seventh shaft W7; when the third shift element B3 is engaged, the sun gear SR1 of the first planetary gear set RS1 can be fixed to the housing 2 via the sixth shaft W6; in order to block the first planetary gear set RS1, in the context of the first blocking variant, in the first arrangement variant, when the sixth shift element F2 is locked, the sun gear SR1 can be connected to the ring gear of the first planetary gear set RS1 gear HR1, wherein further blocking variants are achieved by using other elements in the first planetary gear set RS1 via the sixth shift element F2; in the second two-speed group, the sun gear SR2 of the second planetary gear set RS2 is connected to the transmission output shaft WAb; when the fourth shift element B4 is engaged, the ring gear HR3 of the second planetary gear set RS2 can be fixed to the housing 2 via the eighth shaft W8; and in order to block the second planetary gear set RS2, in the context of the first blocking variant, in the first arrangement variant, when the seventh shift element F3 is locked, the sun gear SR2 can be connected to the ring gear HR2 of the second planetary gear set R2, wherein further blocking variants are achieved by using other elements in the second planetary gear set RS2 via the seventh shift element F3. The connection of the first stepped planetary gear set StRS1 in the first transmission shift group 3 has been described above.

[0073] exist Fig.19 In the figure, the Fig.18The shift diagram of the central shaft transmission shown in the figure has a first transmission shift group 3 as a three-speed transmission and a second transmission shift group 4, the second transmission shift group 4 having two two-speed groups. It follows that 3x2x2, i.e., twelve gears G1, G2, G3, G4, G5, G6, G7, G8, G9, G10, G11, G12 can be realized. The shift diagram specifies the shift elements B1, B2, B3, B4, F1 for the corresponding gears G1, G2, G3, G4, G5, G6, G7, G8, G9, G10, G11, G12. I 、F1 II 、F1 III 、F1 IV 、F1 VI 、F1 VI 、F1 VIII , F2, F3. Here, the flywheel F1 as the shift element in the shift diagram I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII , F2, F3 means that the flywheel is locked. This takes effect automatically without external actuation. In addition, the X in the shift diagram for the brakes B1, B2, B3, B4 as shift elements means that the brakes B1, B2, B3, B4 are engaged. This takes effect via a suitable actuator system. Flywheel F1 I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII Empty fields in F1, F2, F3 mean that the flywheel is not locked. Empty fields in brakes B1, B2, B3, B4 mean that the brakes are disengaged.

[0074] In detail, according to Fig.19 The shift diagram shows that in order to realize or shift the first gear G1, the fifth shifting element F1 designed as a flywheel I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII, the sixth shifting element F2 designed as a flywheel and the seventh shifting element F3 designed as a flywheel are locked; to achieve the second gear G2, the second shifting element B2 designed as a brake is engaged, and the sixth shifting element F2 designed as a flywheel and the seventh shifting element F3 designed as a flywheel are locked; to achieve the third gear G3, the first shifting element B1 designed as a brake is engaged, and the sixth shifting element F2 designed as a flywheel and the seventh shifting element F3 designed as a flywheel are locked; to achieve the fourth gear G4, the third shifting element B3 designed as a brake is engaged, and the fifth shifting element F1 designed as a flywheel is locked. I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII and the seventh shifting element F3 designed as a flywheel are locked; to achieve the fifth gear G5, the second shifting element B2 designed as a brake, the third shifting element B3 designed as a brake, and the seventh shifting element F3 designed as a flywheel are locked; to achieve the sixth gear G6, the first shifting element B1 designed as a brake and the third shifting element B3 designed as a brake are engaged, and the seventh shifting element F3 designed as a flywheel is locked; to achieve the seventh gear G7, the fourth shifting element B4 designed as a brake is engaged, and the fifth shifting element F1 designed as a flywheel is engaged. I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII and the sixth shifting element F2 designed as a flywheel is locked; to achieve the eighth gear G8, the second shifting element B2 designed as a brake and the fourth shifting element B4 designed as a brake are engaged, and the sixth shifting element F2 designed as a flywheel is locked; to achieve the ninth gear G9, the first shifting element B1 designed as a brake and the fourth shifting element B4 designed as a brake are engaged, and the sixth shifting element F2 designed as a flywheel is locked; to achieve the tenth gear G10, the third shifting element B3 designed as a brake and the fourth shifting element B4 designed as a brake are engaged, and the fifth shifting element F1 designed as a flywheel is locked. I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIIILock; in order to achieve the eleventh gear G11, the second shift element B2 designed as a brake, the third shift element B3 designed as a brake and the fourth shift element B4 designed as a brake are engaged; and / or in order to achieve the twelfth gear G12, the first shift element B1 designed as a brake, the third shift element B3 designed as a brake and the fourth shift element B4 designed as a brake are engaged.

[0075] exist Fig. 20 In, reference Figure 1 An embodiment of a mid-axle transmission according to the invention is shown, in which the torque sensor 5 is connected or can be connected to the pedal crankshaft or the transmission input shaft WAn. For example, a disk-shaped torque sensor 5 can be arranged on the gear input. However, the torque sensor 5 can also be designed in a different way.

[0076] exist Fig.21 and Fig. 22 In, refer to Fig. 20 An embodiment of a mid-shaft transmission according to the invention is shown, in each case with an additional electric motor EM. The electric motor EM can be connected to a pedal crankshaft WAn, such as Fig.21 It is also conceivable that the electric machine EM is connected to the transmission output shaft WAb, such as Fig. 22 The electric motor EM is preferably arranged axially parallel to the pedal crankshaft or the transmission input shaft WAn. However, a coaxial arrangement of the electric motor EM and the pedal crankshaft is also possible. In any case, it is advantageous to connect the electric motor EM via a flywheel F0 or the like so that during operation without the electric motor EM, the electric motor EM rotates with it without causing losses.

[0077] exist Fig.23 In, reference Fig. 20 An embodiment of a bottom bracket transmission according to the invention is shown with an additional flywheel F between the pedal crank and the transmission input of the bottom bracket transmission. In this way, when pedaling is interrupted, the flywheel is able to open the pedal crank and decouple it from the inertial masses of the transmission gear set (and in particular the electric machine EM) so that no inertial forces are felt on the pedals.

[0078] Reference numerals

[0079] 1 Bicycle or electric assisted bicycle

[0080] 2 Shell or bottom bracket shell

[0081] 3 First transmission shift group

[0082] 4 Second transmission shift group

[0083] 5. Torque sensor

[0084] EM Motor

[0085] F0 Flywheel for electric motor

[0086] F Additional flywheel

[0087] SR1 Sun gear of the first planetary gear set

[0088] PT1 Planetary gear carrier of the first planetary gear set

[0089] HR1 Ring gear of the first planetary gear set

[0090] SR2 Sun gear of the second planetary gear set

[0091] PT2 Planetary gear carrier for the second planetary gear set

[0092] HR2 Ring gear of the second planetary gear set

[0093] SR1.1 The first sun gear with a larger number of teeth of the first stepped planetary gear set

[0094] SR1.2 The second sun gear with the smaller number of teeth of the first stepped planetary gear set

[0095] HR1.1 The first ring gear with the larger number of teeth of the first stepped planetary gear set

[0096] HR1.2 Second ring gear with smaller number of teeth of the first stepped planetary gear set

[0097] SPT1 Stepped planetary gear carrier for the first stepped planetary gear set

[0098] SR2.1 Sun gear of the second step planetary gear set

[0099] HR2.1 The first ring gear with a larger number of teeth of the second stepped planetary gear set

[0100] HR2.2 The second ring gear with the smaller number of teeth of the second stepped planetary gear set

[0101] SPT2 Stepped planetary gear carrier for the second stepped planetary gear set

[0102] RS1 1st planetary gear set

[0103] RS2 Second planetary gear set

[0104] StRS1 First step planetary gear set

[0105] StRS2 Second step planetary gear set

[0106] WAn Transmission input shaft or pedal crankshaft

[0107] WAb Transmission Output Shaft

[0108] W1 First axis

[0109] W2 Second axis

[0110] W3 Third Axis

[0111] W4 Fourth Axis

[0112] W5 Fifth Axis

[0113] W6 Sixth Axis

[0114] W7 Seventh Axis

[0115] W8 Eighth Axis

[0116] G1 1st gear

[0117] G2 2nd Gear

[0118] G3 3rd gear

[0119] G4 Fourth gear

[0120] G5 Fifth gear

[0121] G6 Sixth gear

[0122] G7 Seventh Gear

[0123] G8 Eighth gear

[0124] G9 Ninth Gear

[0125] G10 Tenth gear

[0126] G11 Eleventh gear

[0127] G12 12th gear

[0128] B1 is designed as the first shifting element for the brake

[0129] B2 is designed as the second shifting element for the brake

[0130] B3 is designed as the third shifting element for the brake

[0131] B4 is designed as the fourth shifting element for the brake

[0132] F1 I The fifth shifting element designed as a flywheel in the first arrangement position

[0133] F1 II The fifth shifting element designed as a flywheel in the second arrangement position

[0134] F1 III The fifth shifting element designed as a flywheel in the third arrangement position

[0135] F1 IV The fifth shifting element designed as a flywheel in the fourth arrangement position

[0136] F1 V The fifth shifting element designed as a flywheel in the fifth arrangement position

[0137] F1 VI The fifth shifting element designed as a flywheel in the sixth arrangement position

[0138] F1 VII The fifth shifting element designed as a flywheel in the seventh arrangement position

[0139] F1 VIII The fifth shifting element designed as a flywheel in the eighth arrangement position

[0140] F2 is designed as the sixth shifting element of the flywheel

[0141] F3 is designed as the seventh shifting element on the flywheel.

Claims

1. A planetary-designed central shaft transmission for a bicycle or electric assisted vehicle (1), the central shaft transmission having a pedal crankshaft (WAn) as a drive and a transmission output shaft (WAb) as an output, and having further shafts (W1, W2, W3, W4, W5, W6, W7), and having a first transmission shift group (3) and a second transmission shift group (4), the first transmission shift group (3) and the second transmission shift group (4) being coupled to each other for realizing a plurality of gears (G1, G2, G3, G4, G5, G6, G7, G8, G9, G10, G11, G12), in, The first transmission shift group (3) comprises a two-stage stepped planetary gear set (StRS1), three shift elements (B1, B2, F1 I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII ) is assigned to the two-stage stepped planetary gear set (StRS1), wherein a first shaft (W1) as an input shaft of the first stepped planetary gear set (StRS1) is connected to a second ring gear (HR1.2) as an element of the first stepped planetary gear set (StRS1), wherein a fifth shaft (W5) as an output shaft of the first stepped planetary gear set (StRS1) is connected to a first ring gear (HR1.1) as an element of the first stepped planetary gear set (StRS1), wherein the second sun gear (SR1.2) as an element of the first stepped planetary gear set (StRS1) can be fixed to the housing (2) via a first shifting element (B1), wherein the first sun gear (SR1.1) as an element of the first stepped planetary gear set (StRS1) can be fixed to the housing (2) via a second shift element (B2), wherein a stepped planetary gear carrier (SPT1) as an element of the first stepped planetary gear set (StRS1) is rotatably mounted, and In order to block the stepped planetary gear set (StRS1), two elements of the first stepped planetary gear set (StRS1) can be shifted via the fifth shift element (F1 I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII ) are connected to each other.

2. The mid-shaft transmission according to claim 1, characterized in that: The first transmission shift group (3) is connected upstream or downstream of the second transmission shift group (4).

3. The mid-shaft transmission according to one of the preceding claims, characterized in that The second transmission shift group (4) comprises a first planetary gear set (RS1), a third shift element (B3) and a sixth shift element (F2) are assigned to the first planetary gear set (RS1), wherein in the second transmission shift group (4), the second element of the first planetary gear set (RS1) is connected to the pedal crankshaft (WAn) or to the fifth shaft (W5) which is the output shaft of the first stepped planetary gear set (StRS1), wherein the first element of the first planetary gear set (RS1) can be fixed to the housing (2) via the third shift element (B3), wherein the third element of the first planetary gear set (RS1) is connected to the transmission output shaft (WAb) or to the first shaft (W1) which is the input shaft of the first stepped planetary gear set (StRS1), and In order to block the first planetary gear set (RS1), two elements of the first planetary gear set (RS1) can be connected to one another via the sixth shifting element (F2).

4. The mid-shaft transmission according to claim 1, characterized in that The second transmission shift group (4) includes a first planetary gear set (RS1) and a second planetary gear set (RS2), a third shift element (B3), a fourth shift element (B4) and a sixth shift element (F2) are assigned to the first planetary gear set (RS1) and the second planetary gear set (RS2), wherein, in the second transmission shift group (4), the second element of the first planetary gear set (RS1) is connected to the pedal crankshaft (WAn) or to the fifth shaft (W5) which is the output shaft of the first stepped planetary gear set (StRS1), wherein the first element of the first planetary gear set (RS1) and the first element of the second planetary gear set (RS2) are connected to the transmission output shaft (WAb) or to the first shaft (W1) which is the input shaft of the first stepped planetary gear set (StRS1), wherein the third element of the first planetary gear set (RS1) can be fixed to the housing (2) via the third shift element (B3), wherein the third element of the first planetary gear set (RS1) is connected to the second element of the second planetary gear set (RS2), wherein the third element of the second planetary gear set (RS2) can be fixed to the housing (2) via the fourth shift element (B4), and In order to block the first planetary gear set (RS1) and the second planetary gear set (RS2), two shafts connected to the elements of the planetary gear sets (RS1, RS2) can be connected to each other via the sixth shift element (F2).

5. The mid-shaft transmission according to claim 1, characterized in that The second transmission shift group (4) includes a second stepped planetary gear set (StRS2), to which a third shift element (B3), a fourth shift element (B4) and a sixth shift element (F2) are assigned, wherein in the second transmission shift group (4), the second ring gear (HR2.2) as an element of the second stepped planetary gear set (StRS2) is connected to the pedal crankshaft (WAn) or to the fifth shaft (W5) as an output shaft of the first stepped planetary gear set (StRS1), wherein the first ring gear (HR2.1) as an element of the second stepped planetary gear set (StRS2) is connected to the transmission output shaft (WAb) or to the first shaft (W1) as an input shaft of the first stepped planetary gear set (StRS1), wherein a stepped planetary gear carrier (SPT2) as an element of the second stepped planetary gear set (StRS2) can be fixed to the housing (2) via the third shift element (B3), wherein the sun gear (SR2.1) as an element of the second stepped planetary gear set (StRS2) can be fixed to the housing (2) via the fourth shift element (B4), and In order to block the second stepped planetary gear set (StRS2), two elements of the second stepped planetary gear set (StRS2) can be connected to one another via the sixth shifting element (F2).

6. The mid-shaft transmission according to claim 1, characterized in that The second transmission shift group (4) includes a first planetary gear set (RS1) and a second planetary gear set (RS2), a third shift element (B3), a fourth shift element (B4), a sixth shift element (F2) and a seventh shift element (F3) are assigned to the first planetary gear set (RS1) and the second planetary gear set (RS2), wherein, in the second transmission shift group (4), the second element of the first planetary gear set (RS1) is connected to the pedal crankshaft (WAn) or to the fifth shaft (W5) which is the output shaft of the first stepped planetary gear set (StRS1), wherein the first element of the first planetary gear set (RS1) is connected to the transmission output shaft (WAb) or to the first shaft (W1) which is the input shaft of the first stepped planetary gear set (StRS1), wherein the third element of the first planetary gear set (RS1) is connected to the second element of the second planetary gear set (RS2), wherein the third element of the second planetary gear set (RS2) can be fixed to the housing (2) via the third shift element (B3), and can be connected to the pedal crankshaft (WAn) via the sixth shift element (B3), or can be connected to the fifth shaft (W5) which is the output shaft of the first stepped planetary gear set (StRS1), and In which, the first element of the second planetary gear set (RS2) can be fixed to the housing (2) via the fourth shift element (B4), and can be connected to the transmission output shaft (WAb) or to the first shaft (W1) which is the input shaft of the first stepped planetary gear set (StRS1) via the seventh shift element (F3).

7. The mid-shaft transmission according to claim 1, characterized in that The second transmission shift group (4) comprises a first two-gear group and a second two-gear group, The first two gear groups are assigned the third shift element (B3) and the sixth shift element (F2), and The second two-gear group is assigned the fourth shifting element (B4) and the seventh shifting element (F3).

8. The mid-shaft transmission according to claim 7, characterized in that: In the first two-speed gear set, the second element of the first planetary gear set (RS1) is connected to the pedal crankshaft (WAn) or to the fifth shaft (W5) which is the output shaft of the first stepped planetary gear set (StRS1); The third element of the first planetary gear set (RS1) is connected to the second element of the second planetary gear set (RS2); The first element of the first planetary gear set (RS1) can be fixed to the housing (2) via the third shift element (B3); In order to block the first planetary gear set (RS1), two elements of the first planetary gear set (RS1) can be connected to each other via the sixth shift element (F2); In the first two-speed group, the first element of the second planetary gear set (RS2) is connected to the transmission output shaft (WAb) or to the first shaft (W1) which is the input shaft of the first stepped planetary gear set (StRS1); The third element of the second planetary gear set (RS2) can be fixed to the housing (2) via the fourth shift element (B4); and In order to block the second planetary gear set (RS2), two elements of the second planetary gear set (RS2) can be connected to one another via the seventh shifting element (F3).

9. The midshaft transmission according to one of the preceding claims, characterized in that The first shift element (B1), the second shift element (B2), the third shift element (B3) and the fourth shift element (B4) are each designed as a positive-locking brake; and / or The fifth shifting element (F1 I 、F1 II 、F1 III 、F1 IV 、F1 V 、F1 VI 、F1 VII 、F1 VIII ), the sixth shifting element (F2) and the seventh shifting element (F3) are each designed as a flywheel.

10. The midshaft transmission according to one of the preceding claims, characterized in that The first planetary gear set (RS1) and / or the second planetary gear set (RS2) are in each case designed as a minus planetary gear set.

11. The mid-shaft transmission according to claim 10, characterized in that: In the negative planetary gear set, the first element is designed as a sun gear (SR1, SR2), the second element is designed as a planetary gear carrier (PT1, PT2), and the third element is designed as a ring gear (HR1, HR2).

12. The midshaft transmission according to one of the preceding claims, characterized in that The first planetary gear set (RS1) and / or the second planetary gear set (RS2) are in each case designed as spur gear sets.

13. The mid-shaft transmission according to claim 12, characterized in that: In the spur planetary gear set, the first element is designed as a sun gear (SR1, SR2), the second element is designed as a ring gear (HR1, HR2), and the third element is designed as a planetary gear carrier (PT1, PT2).

14. The midshaft transmission according to one of the preceding claims, characterized in that A torque sensor (5) is connected to the pedal crankshaft (WAn).

15. The mid-shaft transmission according to one of the preceding claims, characterized in that At least one electric machine (EM) is connected or connectable to the pedal crankshaft (WAn) or to the transmission output shaft (WAb).

16. The mid-shaft transmission according to claim 15, characterized in that: The electric motor (EM) is arranged parallel to the pedal crankshaft (WAn) in an axial direction.

17. A bicycle or pedelec (1) comprising a bottom bracket transmission according to one of the preceding claims.

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