DE102015221554A1 - Transmission and method for operating such - Google Patents

Abstract

Transmission (A) having at least one transmission housing (B), at least one first and second partial transmission (4, 5), at least one first and second main clutch (2, 3), at least one Summierplanetengetriebe (6), at least one transmission output shaft (8) and a transmission input shaft (1), wherein the transmission input shaft (1) at least by means of the first main clutch (2) with the first partial transmission (4) and by means of the second main clutch (3) with the second partial transmission (5) can be coupled, each of the partial transmission ( 4, 5) has an input shaft (VW1, HW1) and a parallel or coaxial output shaft (VW2, HW2, 14), which by means of at least two shaft-fixed gears (Z1 to Z6) combing with loose wheels (L1 to L6) are drive-connected, wherein the loose wheels (L1 to L6) can be coupled by means of at least one clutch (G1 to G4), the output shafts (VW2, HW2, 14) of the at least two partial transmissions (4, 5) having different input modules of the summing plane are geared so that at least output rotational movements of the first and second partial transmission (19, 20) are translated to a Getriebeausgansdrehbewegung (16), and a method for operating a transmission.

Description

The present invention relates to a transmission according to the preamble of patent claim 1 and a method for operating a transmission according to the preamble of patent claim 10.

Such transmissions and methods of operating such may be used in land and road vehicles. As a rule, a torque and a rotational speed of at least one drive unit, in particular an internal combustion engine, are provided. In principle, it is possible to provide one or more electric motors in a drive train, so that there is a plug-in hybrid, micro, mild, full or mixed hybrid. The torque and the speed are converted by means of a gearbox. Through the use of multiple partial transmissions and clutches traction interruption-free and can be switched quickly. The powershift transmissions include, for example, dual-clutch transmissions or multi-web planetary transmissions. It is often endeavored to realize a large number of gears, which make it possible to direct the maximum power to the drive wheels and operate a drive unit efficiently. It is important to design a gearbox so that it is easy to control in terms of control technology. In general, a translation stage by means of two gears, which mesh with each other and are each firmly connected to a shaft, can be realized. Analog can be implemented by means of two parallel waves of several gear ratios by means of several pairs of gears, with idler gears are alternately coupled to the corresponding shaft. A planetary gear usually comprises at least one sun gear, a ring gear and a planet carrier, wherein mounted on the planet carrier planet gears are arranged. Depending on the arrangement of these modules can be realized with a planetary gear a gear ratio, a direct gear by blocking two modules or a reverse gear by locking the web. A summation planetary gear is able to take two different rotational movements and output a rotational movement, so that two input rotational movements are converted to one. For this purpose, a special arrangement of the components of a planetary gear is required. In this case, the assemblies of the planetary gear must be arranged so that the input rotational movements to be summed, are introduced by means of different input modules and the summed or resulting rotational movement is transmitted to an output module. For example, the sun gear and ring gear can be designed as input intake hubs and the planet carrier as the output assembly. For the operating mode of a summation or superimposition of input rotary motions with different speeds, the input and output modules must not be coupled in a torsionally rigid manner.

The publication DE 10 2012 021 293 A1 shows a switching arrangement for a dual-clutch transmission as a speed change gearbox for motor vehicles, with two coaxially arranged input shafts, which are activated via one clutch, with an axially parallel output shaft and arranged on the shafts, switchable by means of synchronous clutches gear sets to form a plurality of forward gears and one reverse gear, wherein the gear sets are divided into a partial transmission with the one input shaft and a partial transmission with the other input shaft, wherein the partial transmission (A) and / or the partial transmission (B) is associated with at least one switchable in two transmission stages forward and / or Nachschalteinheit, wherein the at least one pre-and / or Nachschalteinheit is a switchable in two gear ratios planetary gear. The disadvantage here is that a switchable in two gear ratios planetary gear as a forward and / or Nachschalteinheit not the possibility offers a gear from the partial transmission (A) to sum with a gear from the partial transmission (B) or to superimpose. Since the planetary gear is not provided as a summing gear for the two partial transmissions, there is also an increased stress on the double clutch at each load switching operation.

In the DE 10 2011 005 028 A1 a dual-clutch transmission with two clutches is proposed, whose input sides are connected to a drive shaft and whose output sides are each connected to one of two coaxial transmission input shafts of partial transmissions. Furthermore, the dual-clutch transmission comprises two countershafts arranged coaxially with one another, wherein each partial transmission is assigned a plurality of shiftable gear ratios which can be coupled respectively to the output shaft via the associated countershaft and via a main shaft connected to an input member of a planetary gear formed as a range group, the output shaft being coaxial with the drive shaft is arranged. According to the invention, at least one shiftable ratio stage of at least one of the partial transmissions can be coupled to the output shaft independently of the range group. The disadvantage is that the planetary gear is not designed as a summation planetary gear, so that even here not offered the opportunity to operate a gear from a partial transmission with a gear from another sub-transmission summing or superimposing.

The DE 20 2005 021 249 U1 shows a power split transmission for motor vehicles with an internal combustion engine that drives an input shaft of the Leistungsverveygetriebes, which Power split transmission more at least one powershift transmission with a number of gears comprehensive branches and an output shaft, wherein at least one of the branches is provided with a control device with which the direction of rotation of the output shaft is variable during the starting process of the motor vehicle, and the start-up process and switched gears of the input shaft connected via the control device, the speed of the output shaft is steplessly influenced, wherein the powershift transmission formed in the manner of a dual-clutch transmission and the input shaft is connected to a first clutch and a second clutch, of which the first clutch with a first transmission shaft and the second clutch with a second Gear shaft is coupled, on which first and second transmission shafts loose wheels are mounted, wherein the power shift transmission a first branch and the control means a second branch bi which control means cooperates with a third branch comprising a summation planetary gear. The disadvantage is that the Summierplanetengetriebe, not the possibility offers different, fixed gear ratios of the individual partial transmission to sum up, or superimpose. Furthermore, the third branch does not comprise a main clutch and a partial transmission with switchable fixed gears. Thus, the number of total gear ratios within the dual clutch transmission is not increased by the summing planetary gear.

Object of the present invention is to provide a transmission and method for operating such, which make it possible despite a structurally compact gear design and a few switching elements to allow a large gear spread and an increased number of gears.

This object is achieved for a transmission by the features of patent claim 1 and for a method by the features of claim 10.

A transmission having at least one transmission housing, at least one first and second partial transmission, at least one first and second master clutch, at least one summation, at least one transmission output shaft and a transmission input shaft, wherein the transmission input shaft at least by means of the first main clutch with the first partial transmission and by means of the second main clutch the second partial transmission can be coupled, wherein each of the partial transmission has an input shaft and a parallel or coaxial output shaft which are driveably connected by means of at least two shaft-fixed gears which mesh with idler gears, wherein the idler gears are coupled by means of at least one clutch, wherein the output shafts of the at least two partial transmissions are drive-connected with different input modules of the Summierplanetengetriebes, so that at least output rotational movements of the first and second partial transmission to a Getriebeausgansdrehbewegung ü be translated. The main clutches can be used for example as starting elements for bridging a speed difference between the drive unit and the transmission. This can e.g. when operating the transmission with an internal combustion engine to be the case. However, a main clutch does not necessarily have to be provided as a starting element.

By summing up the torques from the partial transmissions optionally, the summation planetary gearbox, in the case of a transmission with at least two partial transmissions, results in a significant increase in the possible overall ratios. In fact, only one input torque may be present in one operating mode, with the possibility of summing two torques being given. This is the case only with special arrangements of the assemblies of a planetary gear. So it is on the one hand possible to use the gears from the first and second partial transmission with the respective translation of the planetary gear separately, on the other hand, all gear combinations can be summed from the two partial transmissions. In the summation case, output torques from the at least two subtransmissions are transmitted to the different input modules of the summation planetary gear, so that the output torques from the at least two subtransmissions are translated to a transmission output torque. Each of the sub-transmission should have at least one shiftable gear ratio that allows meaningful gear combinations with the other sub-transmission. However, a significant increase in the total combinations that can be combined is only realized if at least two shiftable gear ratios are provided per sub-transmission. In the case of separate use, one of the partial transmissions is decoupled from the drive in such a way that an input torque of the summation planetary gear is zero. In the event that n pairs of gears are present in the first partial transmission and m pairs of gears in the second partial transmission, the minimum number of gears VG is given by the following formula: n + m) + (n · m) = VG

In a preferred embodiment, the output rotational movements of the first and second partial transmissions are translated by closing the first and second master clutches to a transmission output rotary motion. This is necessary in the event that two input torques, the amount of which is greater than zero, are applied to the totalizer gearbox and then summed accordingly become. Thus, the torque is introduced into both partial transmissions. If, in addition, a respective clutch is closed in both partial transmissions, then correspondingly two input rotary movements are obtained at the input modules of the summing-type planetary gearbox.

In a preferred embodiment, the Summierplanetengetriebe on a Verblockvorrichtung. By blocking the summing planetary gear, it acts like a direct gear with the ratio 1 for the incoming torque. Consequently, new overall ratios for the transmission arise. In the event that n pairs of gears are present in the first partial transmission and m pairs of gears in the second partial transmission, the overall minimum number of gears VG is given by the following formula: 2 (n + m) + (n · m) = VG

In a preferred embodiment, a sun gear and a ring gear are formed as input modules and a planet carrier as the output module of the Summierplanetengetriebes. In this arrangement, a positive total gear ratio is always guaranteed when inserting forward gears in the partial transmissions. The ring gear may be modified by providing a plurality of gears on the outside of the ring gear and a hollow shaft, respectively. This is a particularly space-saving arrangement.

In a preferred embodiment, the sun gear and the planet carrier are designed as input modules and the ring gear as the output module of the Summierplanetengetriebes. Such an arrangement has the advantage that negative Gesamtübersetzungsverhältnisse are possible by means of the Summierplaninetgetriebes without the provision of a reverse gear in one of the partial transmissions.

In a preferred embodiment, the ring gear and the planet carrier are designed as input modules and the sun gear as the output module of the Summierplanetengetriebes. This arrangement also has the advantage that negative total gear ratios are possible by means of the summation planetary gear without the provision of a reverse gear in one of the partial transmissions.

In a preferred embodiment, the summation planetary gear reverses the direction of rotation by means of setting the planet carrier. Thus, at least one reverse gear results in a particularly advantageous manner, so that the provision of a reverse gear within one of the partial transmission is not necessary.

In a preferred embodiment, at least one of the input modules of the summation planetary gear is blocked by closing the at least two clutches within one of the at least two partial transmissions. By inserting two gear ratios within one of the sub-transmissions, a blockage arises within the sub-transmission, so that between the input and output shaft of the sub-transmission no relative movement, without damaging the sub-transmission, is possible. This has the advantage that the brakes of the input modules of the Summierplanetengetriebes can be omitted.

In a preferred embodiment, the sun gear and / or the planet carrier and / or the ring gear comprises a brake. When the brake is closed, no relative movement of the respective assembly of the summation planetary gear to the housing is possible. By braking assemblies of the summation planetary gear, the torque flows can be targeted and transmitted without major losses by the planetary gear. The brakes must be adjusted accordingly with the main clutches and clutches so that no damage occurs in the transmission.

• – bei geschlossener Hauptkupplung und geschlossener Kupplung innerhalb eines der Teilgetriebe, durch Schließen einer zweiten Hauptkupplung und einer Kupplung innerhalb eines der anderen Teilgetriebe die Übersetzung für die Getriebeausgangsdrehbewegung verändert wird oder
• – bei den mindestens zwei geschlossenen Hauptkupplungen, durch Öffnen einer Hauptkupplung und/oder durch Öffnen einer Kupplung die Übersetzung für die Getriebeausgangsdrehbewegung verändert wird.

A method of operating a transmission, wherein

• - When the main clutch and the clutch is closed within one of the sub-transmission, by closing a second main clutch and a clutch within one of the other sub-transmission, the ratio for the transmission output rotational movement is changed or
• - In the at least two closed main clutches, by opening a main clutch and / or by opening a clutch, the ratio for the transmission output rotational movement is changed.

By switching between these two switching variants, traction interruption-free, low-wear and fast switching becomes possible. This results in a change between the summation of the torques from the partial transmissions and decoupling of one of the partial transmissions.

Further details and features of the present invention will become apparent from the following description of a preferred embodiment with reference to the drawings.

Show:

1 a schematic view of a first possible embodiment of the transmission;

2 a schematic view of a second possible embodiment of the transmission;

3 a schematic view of a third possible embodiment of the transmission.

According to the 1 A transmission A comprises a transmission housing B, a transmission input shaft 1 , a first main clutch 2 , a second main clutch 3 , a first partial transmission 4 , a second partial transmission 5 , a summation planetary gearbox 6 and a transmission output shaft 8th , The transmission input shaft 1 is with the first main clutch 2 and with the second main clutch 3 drive-connected. The second partial transmission 5 includes an output shaft VW2, sit on the clutches G1 and G2 and idler gears L1, L2, L5 and L6. The idler gears L1, L2, L5 and L6 mesh with gears Z1, Z2, Z3 and Z4, which sit on an input shaft HW1, which is designed as a hollow shaft, wherein the idler gear L1 and the gear Z1 mesh with each other via an intermediate gear, so that a reverse gear 7 is formed. The first partial transmission 4 comprises an input shaft VW1 with a clutch G3 and idler gears L3 and L4 mounted on the input shaft VW1. The summation planetary gear includes a sun gear 10 , a planet carrier 12 with planet wheels 11 , a modified ring gear 14 , a brake 21 for the sun wheel 10 , a brake 22 for the modified ring gear 14 and a blocking device 23 that the planet carrier 12 and the modified ring gear 14 locked together. The first partial transmission 4 is by means of the input shaft VW1 with the first main clutch 2 and by means of the release wheels L3, L4 with the modified ring gear 14 drivingly. The planet carrier 12 is with the transmission output shaft 8th drive-connected. The second partial transmission 5 is by means of the input shaft HW1 with the second main clutch 3 and by means of the output shaft VW2 with the sun gear 10 drivingly. A transmission input rotary motion 15 lies on the transmission input shaft 1 on and a transmission exhaust rotary motion 16 is located on the transmission output shaft 8th at. An input rotational movement of the second partial transmission 17 is applied to the input shaft HW1 and an input rotational movement of the first sub-transmission 18 is applied to the input shaft VW1. An output rotary motion of the second partial transmission 19 is applied to the output shaft VW2 and an output rotational movement of the first partial transmission 20 is located on the modified ring gear 14 at. Preferably, each of the at least two partial transmissions 4 and 5 at least two shiftable gear ratios comprising at least two idler gears L1 to L6 which mesh with at least two other gears, a clutch G1 to G4 which can fix the idler gears with the shaft on which they are mounted, an input and an output shaft.

According to the 2 A transmission A comprises a transmission housing B, a transmission input shaft 1 , a first main clutch 2 , a second main clutch 3 , a first partial transmission 4 , a second partial transmission 5 , a summation planetary gearbox 6 and a transmission output shaft 8th , The transmission input shaft 1 is with the first and second main clutch 2 . 3 drive-connected. The second partial transmission 5 comprises an output shaft VW2, sit on the clutches G1 and G2 and idler gears L1, L2 and L5. The idler gears L1, L2 and L5 mesh with gears Z1, Z2 and Z3, which sit on an input shaft HW1, which is designed as a hollow shaft. The first partial transmission 4 comprises an input shaft VW1, sit on the clutches G3 and G4 and idler gears L3, L4 and L6. The idler gears L3, L4 and L6 mesh with gears Z4, Z5, and Z6, which sit on an output shaft HW2, wherein the idler gear L6 and the gear Z6 mesh with each other by means of an intermediate gear, so that a reverse gear 7 is formed. The output shaft HW2 is designed as a hollow shaft. The summation planetary gearbox 6 includes a sun wheel 10 , a planet carrier 12 with planet wheels 11 , a ring gear 13 and a blocking device 23 that the ring gear 13 and the planet carrier 12 can interlock with each other. The first partial transmission 4 is by means of the input shaft VW1 with the first main clutch 2 and the output shaft HW2 with the ring gear 13 drive-connected. The planet carrier 12 is with the transmission output shaft 8th drive-connected. The second partial transmission 5 is by means of the input shaft HW1 with the second main clutch 3 and by means of the output shaft VW2 with the sun gear 10 drive-connected. A transmission input rotary motion 15 lies on the transmission input shaft 1 on and a transmission exhaust rotary motion 16 is located on the transmission output shaft 8th at. An input rotational movement of the second partial transmission 17 is applied to the input shaft HW1 and an input rotational movement of the first sub-transmission 18 is applied to the input shaft VW1. An output rotary motion of the second partial transmission 19 is applied to the output shaft VW2 and an output rotational movement of the first partial transmission 20 is applied to the output shaft HW2.

According to the 3 For example, a transmission A includes a transmission case B, a transmission input shaft 1 , a first main clutch 2 , a second main clutch 3 , a first partial transmission 4 , a second partial transmission 5 , a summation planetary gearbox 6 and a transmission output shaft 8th , The transmission input shaft 1 is with the first main clutch 2 and with the second main clutch 3 drive-connected. The second partial transmission 5 comprises an output shaft VW2, on which a clutch G1 and idler gears L1 and L2 sit. The idler gears L1 and L2 mesh with gears Z1 and Z2, which sit on an input shaft HW1, which is designed as a hollow shaft. The first partial transmission 4 comprises an input shaft VW1, on which a Clutch G3 and idler gears L3 and L4 sit. The idler gears L3 and L4 mesh with gears Z3 and Z4, which sit on an output shaft HW2. The output shaft HW2 is designed as a hollow shaft. The summation planetary gearbox 6 includes a sun wheel 10 with a brake 21 , a planet carrier 12 with planet wheels 11 and a brake 24 , a ring gear 13 and a blocking device 23 that the planet carrier 12 with the ring gear 13 can lock. The first partial transmission 4 is by means of the input shaft VW1 with the first main clutch 2 and the output shaft HW2 with the planet carrier 12 drive-connected. The ring gear 13 is with the transmission output shaft 8th drive-connected. The second partial transmission 5 is by means of the input shaft HW1 with the second main clutch 3 and by means of the output shaft VW2 with the sun gear 10 drive-connected. A transmission input rotary motion 15 lies on the transmission input shaft 1 on and a transmission exhaust rotary motion 16 is located on the transmission output shaft 8th at. An input rotational movement of the second partial transmission 17 is applied to the input shaft HW1 and an input rotational movement of the first sub-transmission 18 is applied to the input shaft VW1. An output rotary motion of the second partial transmission 19 is applied to the output shaft VW2 and an output rotational movement of the first partial transmission 20 is applied to the output shaft HW2.

LIST OF REFERENCE NUMBERS

A

transmission

B

gearbox

1

Transmission input shaft

2

first main clutch

3

second main clutch

4

first partial transmission

5

second partial transmission

6

planetary transmission

7

reverse gear

8th

Transmission output shaft

10

sun

11

planet

12

planet

13

ring gear

14

modified ring gear

15

Transmission input rotational movement

16

Getriebeausgansdrehbewegung

17

Input rotary motion partial transmission 1

18

Input rotary motion partial transmission 2

19

Output rotary motion partial transmission 1

20

Output rotary motion partial transmission 2

21

Brake sun gear

22

Brake ring gear

23

Verblockeinrichtung

24

Brake planet carrier

G1

clutch

G2

clutch

G3

clutch

G4

clutch

L1

Losrad

L2

Losrad

L3

Losrad

L4

Losrad

L5

Losrad

L6

Losrad

Z1

gear

Z2

Gear,

Z3

gear

Z4

gear

Z5

gear

Z6

gear

HW1

input shaft

HW2

output shaft

VW1

input shaft

VW2

output shaft

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102012021293 A1 [0003]
• DE 102011005028 A1 [0004]
• DE 202005021249 U1 [0005]

Claims (10)

Transmission (A) with at least one transmission housing (B), at least one first and second partial transmission ( 4 . 5 ), at least one first and second main clutch ( 2 . 3 ), at least one summation planetary gear ( 6 ), at least one transmission output shaft ( 8th ) and a transmission input shaft ( 1 ), wherein the transmission input shaft ( 1 ) at least by means of the first main clutch ( 2 ) with the first partial transmission ( 4 ) and by means of the second main clutch ( 3 ) with the second partial transmission ( 5 ), wherein each of the partial transmissions ( 4 . 5 ) an input shaft (VW1, HW1) and a parallel or coaxial output shaft (VW2, HW2, 14 ) which are driveably connectable by means of at least two shaft-fixed gears (Z1 to Z6) which mesh with idler gears (L1 to L6), wherein the idler gears (L1 to L6) can be coupled by means of at least one clutch (G1 to G4), characterized in that the output shafts (VW2, HW2, 14 ) of the at least two partial transmissions ( 4 . 5 ) with different input modules of the summation planetary gear ( 6 ) are drivingly connected, so that at least output rotational movements of the first and second partial transmission ( 19 . 20 ) to a transmission output rotary motion ( 16 ) are translated. Transmission according to claim 1, characterized in that the output rotational movements of the first and second partial transmission ( 19 . 20 ), by closing the first and second main clutch ( 2 . 3 ), to a transmission output rotary motion ( 16 ) are translated. Transmission according to one of the preceding claims, characterized in that the summation planetary gear ( 6 ) a blocking device ( 23 ) having. Transmission according to one of the preceding claims, characterized in that a sun gear ( 10 ) and a ring gear ( 13 . 14 ) as input modules and a planet carrier ( 12 ) as the output module of the summation planetary gear ( 6 ) are formed. Transmission according to one of the preceding claims, characterized in that the sun gear ( 10 ) and the planet carrier ( 12 ) as input modules and the ring gear ( 13 . 14 ) as the output module of the summation planetary gear ( 6 ) are formed. Transmission according to one of the preceding claims, characterized in that the ring gear ( 13 . 14 ) and the planet carrier ( 12 ) as input modules and the sun gear ( 10 ) as the output module of the summation planetary gear ( 6 ) are formed. Transmission according to one of the preceding claims, characterized in that the summation planetary gear ( 6 ) the direction of rotation, by means of setting the planet carrier, reverses. Transmission according to one of the preceding claims, characterized in that by closing the at least two clutches (G1, G2, G3, G4) within one of the at least two partial transmissions ( 4 . 5 ) at least one of the input modules of the summation planetary gear ( 6 ) is blocked. Transmission according to one of the preceding claims, characterized in that the sun gear ( 10 ) and / or the planet carrier ( 12 ) and / or the ring gear ( 13 . 14 ) a brake ( 21 . 22 . 24 ). Method for operating a transmission according to claim 1, characterized in that - with the main clutch closed ( 2 ) and closed clutch (G3, G4) within one of the partial transmissions ( 5 ), by closing a second main clutch ( 3 ) and a clutch (G1, G2) within one of the other partial transmissions ( 4 ) the transmission output rotary motion ( 16 ) or, for the at least two closed main couplings ( 2 . 3 ), by opening a main clutch ( 2 . 3 ) and / or by opening a clutch (G1, G2, G3, G4) the transmission output rotational movement ( 16 ) is changed.

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