DE102015221554B4 - Gearbox and method for operating such - Google Patents

Abstract

Transmission (A) with at least one transmission housing (B), at least a first and second partial transmission (4, 5), at least one first and second main clutch (2, 3), at least one summing planetary transmission (6), at least one transmission output shaft (8) and A transmission input shaft (1), the transmission input shaft (1) being connectable to the first partial transmission (4) at least by means of the first main clutch (2) and to the second partial transmission (5) by means of the second main clutch (3), each of the partial transmissions ( 4, 5) has an input shaft (VW1, HW1) and a parallel or coaxial output shaft (VW2, HW2, 14) which can be drive-connected by means of at least two shaft-fixed gearwheels (Z1 to Z6) which mesh with idler gears (L1 to L6) the idler gears (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) with different input modules of the summing tarpaulin Tengetriebes (6) are drive-connected, so that at least output rotary movements of the first and second sub-transmission (19, 20) are translated into a transmission output rotary movement (16), characterized in that the ring gear (13, 14) and the planet carrier (12) as input modules and that Sun gear (10) are designed as an output assembly of the summing planetary gear (6).

Description

The present invention relates to a transmission according to the preamble of claim 1 and a method for operating a transmission according to the preamble of claim 7.

Such transmissions and methods for operating such can be used in land and road vehicles. As a rule, a torque and a speed of rotation are provided by at least one drive unit, in particular an internal combustion engine. 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 speed are converted using a gearbox. Through the use of several partial transmissions and clutches, gear shifting can be carried out quickly and without interruption of traction. The powershift transmissions include, for example, double clutch transmissions or multi-planetary transmissions. It is often endeavored to implement a large number of gears that make it possible to deliver the greatest possible performance to the drive wheels and to operate a drive unit efficiently. It is important to design a gearbox in such a way that it is easy to control. As a rule, a step-up ratio can be achieved by means of two gear wheels, which mesh with one another and can each be firmly connected to a shaft. Analogously, several gear ratios can be implemented using two pairs of gearwheels by means of two parallel shafts, idler gears alternately coupled to the corresponding shaft. A planetary gear generally comprises at least one sun gear, a ring gear and a planet gear carrier, with planet gears mounted on the planet gear carrier. Depending on the arrangement of these modules, a planetary gear can be used to achieve a gear ratio, a direct gear by blocking two modules or a reverse gear by locking the bridge. A summing planetary gear is able to record two different rotary movements and output one rotary movement, so that two input rotary movements are converted into one. This requires a special arrangement of the components of a planetary gear. The modules of the planetary gear must be arranged in such a way that the input rotary movements that are to be summed are initiated by means of different input modules and the summed or resulting rotary movement is transmitted to an output module. For example, the sun and ring gear can be designed as an input assembly and the planet gear carrier as an output assembly. For the operating mode of a summation or superimposition of input rotary movements with different speeds, the input and output modules must not be coupled to each other in a rotationally rigid manner.

The disclosure DE 10 2012 021 293 A1 shows a shift arrangement for a double clutch transmission as a speed change transmission for motor vehicles, with two coaxially arranged input shafts, which can be activated via a clutch, with an axially parallel output shaft and with arranged on the shafts, by synchronous clutches gear sets to form several forward gears and one reverse gear, the gear sets being divided into a partial transmission with one input shaft and a partial transmission with the other input shaft, the partial transmission ( A ) and / or the partial transmission ( B ) at least one upstream and / or downstream unit which can be switched over in two transmission stages is assigned, the at least one upstream and / or downstream unit being a planetary gear which can be switched over in two transmission stages. The disadvantage here is that a planetary gear, which can be switched over in two gear ratios, does not offer the possibility of a gear from the sub-gear ( A ) with one gear from the partial transmission ( B ) to sum or superimpose. Since the planetary gear is not intended as a summing gear for the two sub-transmissions, there is also an increased load on the double clutch during each power shift.

In the DE 10 2011 005 028 A1 proposes a dual clutch transmission with two clutches, the input sides of which are connected to a drive shaft and the output sides of which are each connected to one of two transmission input shafts of partial transmissions arranged coaxially to one another. Furthermore, the double clutch transmission comprises two countershafts arranged coaxially to one another, each sub-transmission being assigned a plurality of switchable gear ratios, each of which can be coupled to the output shaft via the assigned countershaft and via a main shaft connected to an input element of a planetary gear designed as a range group, the output shaft being coaxial with the drive shaft is arranged. According to the invention, at least one switchable transmission stage of at least one of the sub-transmissions can be coupled to the output shaft independently of the range group. It is disadvantageous that the planetary gear is not designed as a summing planetary gear, so that here too it is not possible to operate a gear from one partial gear with a gear from another partial gear in a summing or superimposing manner.

The DE 20 2005 021 249 U1 shows a power split transmission for motor vehicles with an internal combustion engine which drives an input shaft of the power dissipation transmission, which Power split transmission several branches comprising at least one powershift transmission with a number of gears and an output shaft, at least one of the branches being provided with a control device with which the direction of rotation of the output shaft can be changed when the motor vehicle starts up, and during the starting process and the gears engaged with the input shaft connected powershift transmission via the control device, the speed of the output shaft is infinitely variable, the powershift transmission being designed in the manner of a double clutch transmission and the input shaft being connected to a first shift clutch and a second shift clutch, of which the first shift clutch with a first transmission shaft and the second shift clutch with a second Gear shaft is coupled, on which first and second gear shafts idler gears are mounted, the power shift transmission a first branch and the control device a second branch bi Identifies which control device cooperates with a third branch comprising a summation planetary gear. It is disadvantageous that the summation planetary gear does not offer the possibility of summing or superimposing different, fixed gear ratios of the individual partial transmissions. Furthermore, the third branch does not include a main clutch or a partial transmission with switchable fixed gears. The number of total gear ratios within the double clutch transmission is therefore not increased by the summation planetary gear.

From the DE 102 60 179 A1 is a multi-gear transmission in countershaft design with power split. This multi-speed transmission is provided with partial transmissions arranged in the respective power branches and a planetary gear set. To represent the overall transmission ratio, a partial transmission can be engaged and the planetary gear set can be blocked or the planetary gear set can be unlocked and both partial transmissions can be engaged.

DE 10 2005 018 978 A1 is one on DE 102 60 179 A1 constructing patent application and describes a multi-speed transmission with power split, in which arranged in the different power branches sub-transmissions are each coupled to different inputs of a planetary gear.

In DE 10 2004 006 732 A1 a staged power split automatic transmission with a double clutch is shown. This description includes gear units with integrated planetary gear units as partial gear units.

The disclosure DE 10 2012 000 652 A1 introduces a dual clutch transmission with main and secondary groups. In the subclaims it is mentioned that at least one of the shift groups can contain a planetary gear.

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

This object is achieved for a transmission by the features of claim 1 and for a method by the features of claim 7.

A transmission with at least one transmission housing, at least one first and second partial transmission, at least one first and second main clutch, at least one summing planetary transmission, at least one transmission output shaft and one transmission input shaft, the transmission input shaft being connected to the first partial transmission at least by means of the first main clutch and by means of the second main clutch can be coupled to the second sub-transmission, each of the sub-transmissions having an input shaft and a parallel or coaxial output shaft which can be drive-connected by means of at least two shaft-fixed gearwheels which mesh with idler gears, the idler gears being couplable by means of at least one clutch, the output shafts of the at least two sub-gears are drive-connected to different input assemblies of the summing planetary gear, so that at least output rotary movements of the first and second sub-gear units result in a gear output rotary movement ü be translated. The main clutches can be used, for example, as starting elements to bridge a speed difference between the drive unit and the transmission. This can e.g. be the case when operating the transmission with an internal combustion engine. However, a main clutch does not necessarily have to be provided as a starting element.

The fact that the summation planetary gear can optionally add up the torques from the sub-transmissions results in a significant increase in the possible total gear ratios in the case of a transmission with at least two sub-transmissions. Only one input torque can actually be present in one operating mode, and the possibility of summing two torques must be given. This is only the case with special arrangements of the components of a planetary gear. On the one hand, it is possible to use the gears from the first and second sub-transmissions separately with the respective gear ratio of the planetary gear, on the other hand, all gear combinations from the two sub-transmissions can be summed up. In the case of summation, output torques from the at least two sub-transmissions are transferred to the different input modules of the summing planetary gear, so that the output torques from the at least two sub-transmissions are translated into a transmission output torque. Each of the sub-transmissions should have at least one switchable gear ratio that enables sensible gear combinations with the other sub-transmission. However, a significant increase in the combinable overall gear ratios is only realized if at least two switchable gear ratios per sub-transmission are provided. When used separately, one of the partial transmissions is decoupled from the drive, so that an input torque of the summing planetary transmission is zero. In the event that there are n gear pairs in the first sub-gear and m gear pairs in the second sub-gear, the minimum number of gears results VG according to the following formula: $$\left(n+m\right)+\left(n\ast m\right)=VG$$

In the invention, the ring gear and the planet carrier are designed as input assemblies and the sun gear as the output assembly of the summing planetary gear. This arrangement has the advantage that negative total gear ratios are possible by means of the summation planetary gear even without the provision of a reverse gear in one of the sub-gears.

In a preferred embodiment, the output rotary movements of the first and second sub-transmission are translated into a transmission output rotary movement by closing the first and second main clutch. This is necessary in the event that two input torques, the amount of which is greater than zero, are applied to the summation planetary gear and are then summed accordingly. The torque is thus introduced into both partial transmissions. If an additional clutch is closed in each of the two partial transmissions, two input rotary movements are correspondingly obtained on the input assemblies of the summing planetary gear.

In a preferred embodiment, the summing planetary gear has a blocking device. By blocking the summation planetary gear, it acts like a direct gear with the translation 1 for the incoming torque. This results in new overall gear ratios. In the event that there are n gear pairs in the first sub-transmission and m gear pairs in the second sub-transmission, the total number of gears results VG according to the following formula: $$\mathrm{2nd}\left(n+m\right)+\left(n\ast m\right)=VG$$

In an alternative embodiment, a sun gear and a ring gear are designed as input assemblies and a planet gear carrier as an output assembly of the summing planetary gear. In this arrangement, a positive overall gear ratio is always guaranteed when engaging forward gears in the sub-transmissions. The ring gear can be constructed in a modified manner by providing several gear wheels on the outside of the ring gear or a hollow shaft. This is a particularly space-saving arrangement.

In an alternative embodiment, the sun gear and the planet gear carrier are designed as input assemblies and the ring gear as the output assembly of the summing planetary gear. Such an arrangement has the advantage that by means of the summing planetary gear, negative overall gear ratios are possible even without the provision of a reverse gear in one of the partial gears.

In a preferred embodiment, the summing planetary gear reverses the direction of rotation by fixing the planet gear carrier. This results in at least one reverse gear in a particularly advantageous manner, so that it is not necessary to provide a reverse gear within one of the partial transmissions.

In a preferred embodiment, at least one of the input assemblies of the summing 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, there is a blockage within the sub-transmission, so that no relative movement between the input and output shaft of the sub-transmission is possible without damaging the sub-transmission. This has the advantage that the brakes of the input modules of the summing planetary gear can be omitted.

In a preferred embodiment, the sun gear and / or the planet gear carrier and / or the ring gear comprises a brake. When the brake is closed, no relative movement of the respective assembly of the summing planetary gear to the housing is possible. By braking the components of the summation planetary gear, the torque flows can be transmitted in a targeted manner and without major losses through the planetary gear.

Braking must be coordinated accordingly with the main clutches and clutches so that there is no damage to 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

• - with the main clutch and clutch closed within one of the sub-transmissions, by closing a second main clutch and a clutch within one of the other sub-transmissions, the gear ratio for the transmission output rotary movement is changed or
• - With the at least two closed main clutches, by opening a main clutch and / or by opening a clutch, the translation for the transmission output rotary movement is changed.

By switching between these two shifting variants, gear shifting that is free of traction, low-wear and fast is possible. This results in a change between summation of the torques from the sub-transmissions and decoupling of one of the sub-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.

• 1 eine schematische Ansicht einer ersten möglichen Ausführungsvariante des Getriebes;
• 2 eine schematische Ansicht einer zweiten möglichen Ausführungsvariante des Getriebes;
• 3 eine schematische Ansicht einer dritten möglichen Ausführungsvariante des Getriebes.

In it show:

• 1 a schematic view of a first possible embodiment of the transmission;
• 2nd a schematic view of a second possible embodiment of the transmission;
• 3rd is a schematic view of a third possible embodiment of the transmission.

According to the 1 includes a transmission A a gearbox B , a transmission input shaft 1 , a first main clutch 2nd , a second main clutch 3rd , a first partial transmission 4th , a second sub-transmission 5 , a summing planetary gear 6 and a transmission output shaft 8th . The transmission input shaft 1 is with the first main clutch 2nd and with the second main clutch 3rd connected to the drive. The second sub-transmission 5 includes an output shaft VW2 , on the couplings G1 and G2 and idler gears L1 , L2 , L5 and L6 sit. The idler gears L1 , L2 , L5 and L6 comb with gears Z1 , Z2 , Z3 and Z4 that on an input shaft HW1 , which is designed as a hollow shaft, sit, the idler gear L1 and the gear Z1 Comb through an intermediate gear so that a reverse gear 7 is formed. The first partial transmission 4th includes an input shaft VW1 with a clutch G3 and on the input shaft VW1 mounted loose wheels L3 and L4 . The summing planetary gear includes a sun gear 10th , a planet carrier 12th with planet gears 11 , a modified ring gear 14 , a brake 21 for the sun gear 10th , a brake 22 for the modified ring gear 14 and an interlocking device 23 that the planet carrier 12th and the modified ring gear 14 blocked together. The first partial transmission 4th is by means of the input shaft VW1 with the first main clutch 2nd and by means of the release wheels L3 , L4 with the modified ring gear 14 drive connectable. The planet carrier 12th is with the transmission output shaft 8th connected to the drive. The second sub-transmission 5 is by means of the input shaft HW1 with the second main clutch 3rd and by means of the output shaft VW2 with the sun gear 10th drive connectable. A transmission input rotation 15 lies on the transmission input shaft 1 on and a transmission output rotation 16 lies on the transmission output shaft 8th on. An input rotary motion of the second sub-transmission 17th lies on the input shaft HW1 on and an input rotary movement of the first sub-transmission 18th lies on the input shaft VW1 on. An output rotary motion of the second sub-transmission 19th lies on the output shaft VW2 on and an output rotary motion of the first sub-transmission 20th is due to the modified ring gear 14 on.

Each of the at least two partial transmissions preferably comprises 4th and 5 at least two switchable gear ratios, the 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 2nd includes a transmission A a gearbox B , a transmission input shaft 1 , a first main clutch 2nd , a second main clutch 3rd , a first partial transmission 4th , a second sub-transmission 5 , a summing planetary gear 6 and a transmission output shaft 8th . The transmission input shaft 1 is with the first and second main clutch 2nd , 3rd connected to the drive. The second sub-transmission 5 includes an output shaft VW2 , on the couplings G1 and G2 and idler gears L1 , L2 and L5 sit. The idler gears L1 , L2 and L5 comb with gears Z1 , Z2 and Z3 that on an input shaft HW1 , which is designed as a hollow shaft. The first partial transmission 4th includes an input shaft VW1 , on the couplings G3 and G4 and idler gears L3 , L4 and L6 sit. The idler gears L3 , L4 and L6 comb with gears Z4 , Z5 , and Z6 that on an output shaft HW2 sit with the idler gear L6 and the gear Z6 Comb 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 summing planetary gear 6 includes a sun gear 10th , a planet carrier 12th with planet gears 11 , a ring gear 13 and an interlocking device 23 who the ring gear 13 and the planet carrier 12th can block together. The first partial transmission 4th is by means of the input shaft VW1 with the first main clutch 2nd and the output shaft HW2 with the ring gear 13 connected to the drive. Of the Planet carrier 12th is with the transmission output shaft 8th connected to the drive. The second sub-transmission 5 is by means of the input shaft HW1 with the second main clutch 3rd and by means of the output shaft VW2 with the sun gear 10th connected to the drive. A transmission input rotation 15 lies on the transmission input shaft 1 on and a transmission output rotation 16 lies on the transmission output shaft 8th on. An input rotary motion of the second sub-transmission 17th lies on the input shaft HW1 on and an input rotary movement of the first sub-transmission 18th lies on the input shaft VW1 on. An output rotary motion of the second sub-transmission 19th lies on the output shaft VW2 on and an output rotary motion of the first sub-transmission 20th lies on the output shaft HW2 on.

According to the 3rd includes a transmission A a gearbox B , a transmission input shaft 1 , a first main clutch 2nd , a second main clutch 3rd , a first partial transmission 4th , a second sub-transmission 5 , a summing planetary gear 6 and a transmission output shaft 8th . The transmission input shaft 1 is with the first main clutch 2nd and with the second main clutch 3rd connected to the drive. The second sub-transmission 5 includes an output shaft VW2 on which a clutch G1 and idler gears L1 and L2 sit. The idler gears L1 and L2 comb with gears Z1 and Z2 that on an input shaft HW1 , which is designed as a hollow shaft. The first partial transmission 4th includes an input shaft VW1 on which a clutch G3 and idler gears L3 and L4 sit. The idler gears L3 and L4 comb with gears Z3 and Z4 that on an output shaft HW2 sit. The output shaft HW2 is designed as a hollow shaft. The summing planetary gear 6 includes a sun gear 10th with a brake 21 , a planet carrier 12th with planet gears 11 and a brake 24th , a ring gear 13 and an interlocking device 23 that the planet carrier 12th with the ring gear 13 can block. The first partial transmission 4th is by means of the input shaft VW1 with the first main clutch 2nd and the output shaft HW2 with the planet carrier 12th connected to the drive. The ring gear 13 is with the transmission output shaft 8th connected to the drive. The second sub-transmission 5 is by means of the input shaft HW1 with the second main clutch 3rd and by means of the output shaft VW2 with the sun gear 10th connected to the drive. A transmission input rotation 15 lies on the transmission input shaft 1 on and a transmission output rotation 16 lies on the transmission output shaft 8th on. An input rotary motion of the second sub-transmission 17th lies on the input shaft HW1 on and an input rotary movement of the first sub-transmission 18th lies on the input shaft VW1 on. An output rotary motion of the second sub-transmission 19th lies on the output shaft VW2 on and an output rotary motion of the first sub-transmission 20th lies on the output shaft HW2 on.

Reference list

A

transmission

B

Gear housing

1

Transmission input shaft

2nd

first main clutch

3rd

second main clutch

4th

first partial transmission

5

second sub-transmission

6

Summation planetary gear

7

Reverse gear

8th

Transmission output shaft

10th

Sun gear

11

Planet gear

12th

Planet carrier

13

Ring gear

14

modified ring gear

15

Gearbox input rotation

16

Transmission output rotation

17th

Partial gearbox input rotary motion 1

18th

Partial gearbox input rotary motion 2nd

19th

Output rotary motion of the partial transmission 1

20th

Output rotary motion of the partial transmission 2nd

21

Brake sun gear

22

Brake ring gear

23

Interlocking device

24th

Brake planet carrier

G1

clutch

G2

clutch

G3

clutch

G4

clutch

L1

Idler gear

L2

Idler gear

L3

Idler gear

L4

Idler gear

L5

Idler gear

L6

Idler gear

Z1

gear

Z2

Gear,

Z3

gear

Z4

gear

Z5

gear

Z6

gear

HW1

Input shaft

HW2

Output shaft

VW1

Input shaft

VW2

Output shaft

Claims (7)

Transmission (A) with at least one transmission housing (B), at least a first and second partial transmission (4, 5), at least one first and second main clutch (2, 3), at least one summing planetary transmission (6), at least one transmission output shaft (8) and A transmission input shaft (1), the transmission input shaft (1) being connectable to the first partial transmission (4) at least by means of the first main clutch (2) and to the second partial transmission (5) by means of the second main clutch (3), each of the partial transmissions ( 4, 5) has an input shaft (VW1, HW1) and a parallel or coaxial output shaft (VW2, HW2, 14) which can be drive-connected by means of at least two shaft-fixed gearwheels (Z1 to Z6) which mesh with idler gears (L1 to L6) the idler gears (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) with different input modules of the summing tarpaulin Tengetriebes (6) are drive-connected, so that at least output rotary movements of the first and second sub-transmission (19, 20) are translated into a transmission output rotary movement (16), characterized in that the ring gear (13, 14) and the planet carrier (12) as input modules and that Sun gear (10) are designed as an output assembly of the summing planetary gear (6). Gearbox after Claim 1 , characterized in that the output rotary movements of the first and second partial transmission (19, 20) are translated into a transmission output rotary movement (16) by means of closing the first and second main clutch (2, 3). Transmission according to one of the preceding claims, characterized in that the summing planetary gear (6) has a blocking device (23). Transmission according to one of the preceding claims, characterized in that the summing planetary gear (6) reverses the direction of rotation by fixing the planet carrier (12). Transmission according to one of the preceding claims, characterized in that at least one of the input modules of the summing planetary gear (6) is blocked by closing the at least two clutches (G1, G2, G3, G4) within one of the at least two partial transmissions (4, 5). Transmission according to one of the preceding claims, characterized in that the sun gear (10) and / or the planet gear carrier (12) and / or the ring gear (13, 14) comprise a brake (21, 22, 24). Method for operating a transmission according to Claim 1 , characterized in that - with the main clutch (2) and clutch (G3, G4) closed 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 gear ratio for the transmission output rotational movement (16) is changed and thereby a summation of torques from the partial transmissions is set, or - for the at least two closed main clutches (2, 3), by opening a main clutch (2, 3) and / or by opening a clutch (G1, G2, G3, G4) the gear ratio for the transmission output rotary movement (16) is changed and thereby at least one partial transmission is decoupled.

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