WO2012016656A1 - Dispositif de train d'engrenages - Google Patents

Dispositif de train d'engrenages Download PDF

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Publication number
WO2012016656A1
WO2012016656A1 PCT/EP2011/003728 EP2011003728W WO2012016656A1 WO 2012016656 A1 WO2012016656 A1 WO 2012016656A1 EP 2011003728 W EP2011003728 W EP 2011003728W WO 2012016656 A1 WO2012016656 A1 WO 2012016656A1
Authority
WO
WIPO (PCT)
Prior art keywords
transmission
group
gear
switching
planetary gear
Prior art date
Application number
PCT/EP2011/003728
Other languages
German (de)
English (en)
Inventor
Carsten Bergelt
Jens Luckmann
Original Assignee
Daimler Ag
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daimler Ag filed Critical Daimler Ag
Publication of WO2012016656A1 publication Critical patent/WO2012016656A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/64—Gearings having three or more central gears composed of a number of gear trains, the drive always passing through all the trains, each train having not more than one connection for driving another train
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing

Definitions

  • the invention relates to a group transmission device according to the preamble of claim 1.
  • EP 1 532 383 B1 is already a group transmission device, in particular a motor vehicle group transmission device, with at least one transmission group, which is provided for switching at least two different transmission ratios, and with at least one downstream in the power flow further transmission group, the circuit for at least two further transmission ratios a planetary gear and at least one switching unit, known.
  • the invention is in particular the object of providing a compact and simple transmission for a motor vehicle. It is achieved according to the invention by the features of claim 1. Further embodiments emerge from the subclaims.
  • the invention relates to a group transmission device, in particular a motor vehicle group transmission device, with at least one transmission group, which is provided for switching at least two different transmission ratios, and at least one downstream in the power flow further transmission group, the circuit for at least two further ratios a Planetenradge - gear and has at least one switching unit.
  • the front transmission group comprises a planetary gear and at least one switching unit.
  • a group transmission device can be provided which has at least two transmission units connected in series with a planetary gear, whereby a compact and simple transmission for a motor vehicle can be realized.
  • this can be provided by means of which a large number of gears are switchable.
  • a “transmission group” is to be understood as meaning, in particular, an assembly intended to switch at least two different transmission ratios, the at least two transmission ratios of the one transmission group and the at least two transmission ratios of the downstream transmission group superimposed to form a total transmission ratio
  • a transmission group connected downstream of the power flow is understood to mean, in particular, a transmission group which is generated with respect to a transmission of a drive torque which is generated by a drive machine and forwarded to drive wheels via the group transmission device , located behind the first gear group.
  • the ratios of the two transmission groups are superimposed preferably to a total gear ratio.
  • a "planetary gearbox” is to be understood as meaning, in particular, a toothed gearwheel which has a sun gear, a ring gear, a planet carrier and at least one planet gear guided in a circular path about the sun gear by the planet carrier a unit are understood, which has at least two mutually rotatable elements and at least one coupling element which is provided to selectively connect the at least two mutually rotatable elements rotatably with each other or to decouple from each other.
  • the transmission device comprises a single transmission shaft, which is provided to connect the at least two group transmission directly to each other.
  • a simple connection of the individual transmission groups can be realized.
  • a "single gear shaft” is to be understood in particular as meaning that only a single gear shaft is connected between two gear groups, which connects the two gear groups with each other is connected to a group input shaft of the other transmission group.
  • the transmission shaft preferably forms the transmission output shaft of the first transmission group and the transmission input shaft of the second transmission group in one piece.
  • At least one of the transmission groups has at least one further switching unit which is provided to switch a third transmission ratio.
  • a number of total shiftable transmission gears can be increased without the need for another planetary gear.
  • “Further switching unit” is to be understood in particular an independently operable by the first switching unit switching unit.
  • At least one of the transmission groups has a planetary gear bypass, which is provided to connect a group input shaft and a group output shaft of the transmission group directly to each other in a rotationally fixed manner.
  • the planetary gear can be unlocked, which in particular drag torques can be reduced in the transmission group.
  • An "unlocked planetary gear” is to be understood that at least one speed in the planetary gear, ie a speed of the sun gear, a speed of the ring gear or a speed of the planet wheel carrier, for example, bes due to the drag torques of Planetenradgetrie- bes free.
  • at most one of the rotational speeds of the planetary gear for example, by a rotationally fixed connection to a transmission housing or a transmission shaft is defined.
  • the group transmission device has a third transmission group, which comprises a planetary gear and at least one switching unit. Thereby, a number of the gears can be further increased, whereby flexibility can be improved.
  • the transmission groups have at most one planetary gear.
  • all transmission groups have exactly one planetary gear.
  • the Having arranged on the input side gear group has a gear set with at least two differently translated spur gear.
  • transmission structure is to be understood in particular an embodiment of non-rotatable, rotatable and switchable connections within the transmission group, as they can be represented in particular in a schematic transmission scheme.
  • a further advantageous embodiment which in particular allows a high number of identical components, can be achieved if at least two of the transmission groups have the same transmission structures.
  • the group transmission device has a modular design which is formed by the individual transmission groups.
  • the transmission device can be easily adapted to different requirements.
  • a "modular design" is to be understood in particular as meaning that the at least two transmission groups can be connected to one another, in particular in different sequences and / or different combinations.
  • the switching unit of at least one of the transmission groups has a sliding sleeve with at least two coupling elements, which are intended to simultaneously produce at least two different non-rotatable connections.
  • the coupling elements are axially fixed to each other and provided to be actuated jointly by means of an actuator.
  • a simple operation unit for the switching unit can be formed.
  • the switching unit is provided for switching the planetary gear bypass.
  • the planetary gear of at least one of the transmission groups comprises a sun gear, a ring gear and a planet carrier and the shift gear
  • the unit is intended to connect the group input shaft directly to the group output shaft in a first switching position and to directly connect the group input shaft to one of the transmission elements in a second switching position.
  • the group transmission device include an additional input-side transmission group having a planetary gear provided to provide two different input ratios.
  • This can advantageously be provided a split group.
  • the input-side transmission group can also be realized without planetary gear, wherein in particular an embodiment of the input-side transmission group with a countershaft and at least one arranged between a group input shaft and the countershaft spur gear is advantageous.
  • the input side arranged transmission group further comprises a starting unit.
  • the starter unit can basically have a single clutch, a double clutch or a converter. If the starting unit comprises a single clutch, the gear group arranged on the input side preferably has a switching unit which is provided to switch gear ratios of the input-side gear group. If the starting unit has a double clutch, the dual clutch preferably comprises two partial clutches which are provided to shift the transmission ratios of the input-side transmission group.
  • FIG. 4 shows a switching logic for the group transmission device from FIG. 1
  • FIG. 5 shows a further embodiment of a group transmission device according to the invention
  • FIG. 6 shows a module of the group transmission device for forming a transmission group
  • Fig. 7 shows a switching logic for the group transmission device of Fig. 5 and
  • Fig. 8 shows a third embodiment of a group transmission device according to the invention.
  • FIGS. 1 to 4 show a group transmission device according to the invention.
  • the group transmission device is configured as a motor vehicle group transmission device.
  • One of the group transmission device upstream drive machine is not shown in detail.
  • the drive machine may be designed, for example, as an internal combustion engine. In principle, however, the group transmission device can also be preceded by other types of drive machines.
  • the group transmission device is provided in total for the transmission of 14 gears V1a-V14a.
  • the group transmission device comprises a total of four transmission groups 10a, 14a, 18a, 26a.
  • the transmission groups 10a, 14a, 18a, 26a are arranged in series with a force flow.
  • Each of the transmission groups 10a, 14a, 18a, 26a is provided for switching at least two transmission ratios.
  • the gear ratios of the individual gear groups 10a, 14a, 18a, 26a are changed.
  • a shift logic of the gears V1a-V14a, which are switchable by means of the group transmission device is shown in Figure 4. Due to the arrangement of the transmission groups 10a, 14a, 18a, 26a, the transmission ratios of the individual transmission groups 10a, 14a, 18a, 26a overlap to a transmission gear ratio, which has the corresponding gear V1a-V14a.
  • the group transmission device has a modular construction formed by the transmission groups 10a, 14a, 18a, 26a.
  • the modules of the group transmission device are arranged in a common transmission housing 39a.
  • the transmission groups 10a, 14a, 18a, 26a are configured as the individual modules which, connected in series, form the group transmission device.
  • the two transmission groups 14a, 18a are of similar design.
  • the two other transmission groups 10a, 26a are formed differently.
  • the group transmission device thus comprises a total of three different modules (see Figure 1).
  • the transmission group 26a comprises a starting unit 40a, which is arranged upstream of the transmission groups 10a, 14a, 18a, and has a transmission input shaft 41a.
  • the transmission input shaft 41a is rotatably connected to the drive machine.
  • the starting unit 40a is provided to produce a slipping connection for starting and a rotationally fixed connection for a driving operation between the drive machine and the transmission input shaft 41a.
  • the starting unit 40a comprises a starting clutch, which is connected upstream of the transmission groups 10a, 14a, 18a, 26a.
  • the starting element is designed as a single clutch.
  • the transmission input shaft 41a forms a group input shaft of the first transmission section 26a.
  • the transmission group 26a comprises exactly one switching unit 28a and exactly one planetary gear 27a.
  • the planetary gear 27a includes a sun gear 43a, a planet carrier 44a, and a ring gear 45a.
  • the planet gear carrier 44a guides planetary gears meshing with the sun gear 43a and the ring gear 45a on a circular path around the sun gear 43a.
  • the sun gear 43a of the planetary gear 27a is rotatably connected to the transmission housing 39a.
  • the transmission section 26a further includes a sun gear shaft 47a penetrating the sun gear 43a.
  • the first transmission section 26a is arranged as an input-side transmission section. As input-side transmission group, the transmission group 26a is provided for connecting the starter unit 40a. To connect the starter unit 40a to the planetary gear 27a of the first gear groups 26a, the gear group 26a comprises a single gear shaft 42a.
  • the transmission shaft 42a is the only connection shaft between the starter unit 40a and the planetary gear 27a, by means of which torque can be transmitted from the starter unit 40a to the planetary gear 27a.
  • the switching unit 28a includes an input member non-rotatably connected to the transmission shaft 42a, a first output member rotatably connected to the sun gear shaft 47a, and a second output member rotatably connected to the ring gear 45a.
  • the planet carrier 44a of the planetary gear 27a is rotatably connected to the sun gear shaft 47a.
  • the switching unit 28a comprises an axially displaceable sliding sleeve.
  • the sliding sleeve forms a coupling element 48a, which can be switched in two switching positions.
  • the coupling element 48a rotatably connects the input element to the second output element.
  • the first output element is rotatable relative to the input element in the first switching position.
  • the second switching position connects the Coupling element 48a, the input member rotationally fixed to the first output element.
  • the second output element is rotatable relative to the input element in the second switching position.
  • the coupling element 48a of the switching unit 28a has for connection to the input element on an extended toothing, which establishes a rotationally fixed connection with the input element both in the first switching position and in the second switching position.
  • the coupling element 48a is thus always connected rotationally fixed to the transmission shaft 42a.
  • the coupling element 48a comprises a toothing, which is shortened in comparison to the toothing for connecting the input element.
  • the coupling element 48a is thereby selectively connected in rotation with either the sun gear shaft 47a or the ring gear 45a depending on its switching position.
  • the two gear ratios of the transmission section 26a are switchable.
  • the gear group 26a In the first switching position of the switching unit 28a, the gear group 26a, the gear ratio 1, 00 on.
  • the gear ratio provided by the gear group 26a corresponds to a stationary gear ratio of the planetary gear 27a with the sun gear 43a fixed.
  • the transmission section 26a In the second switching position of the switching unit 28a, the transmission section 26a has the transmission ratio 1, 28.
  • the gear device For connecting the first gear group 26a to the second gear group 10a, the gear device comprises a single gear shaft 49a.
  • the gear shaft 49a is formed integrally with the sun gear shaft 47a of the first gear group 26a.
  • the transmission shaft 49a forms a group output shaft of the first transmission section 26a and a group input shaft of the second transmission section 10a.
  • the second transmission group 10a comprises exactly two switching units 2a, 13a and exactly one planetary gear 11a (see FIG.
  • the planetary gear 11a includes a sun gear 50a, a planet carrier 51a, and a ring gear 52a.
  • the planet carrier 51a guides planetary gears which mesh with the sun gear 50a and the ring gear 52a in a circular orbit around the sun gear 50a.
  • the transmission section 10a further comprises a planetary gear bypass 23a, by means of which the planetary gear 11 a can be unlocked.
  • the planetary gear bypass 23a includes a bypass gear shaft 53a passing through the sun gear 50a.
  • the first switching unit 12a is arranged on the input side of the planetary gear 11 a.
  • the first switching unit 12a includes a housing connecting member rotatably connected to the gear housing 39a, an input member rotatably connected to the gear shaft 49a, a first output member rotatably connected to the bypass gear shaft 53a, a second output member non-rotatably is connected to the planet 51 a, and a third output member which is rotatably connected to the ring gear 52 a.
  • the switching unit 12a comprises an axially displaceable sliding sleeve.
  • the sliding sleeve comprises two coupling elements 29a, 30a, which can simultaneously produce two different non-rotatable connections.
  • the relatively rotatable coupling elements 29a, 30a are axially fixed to each other. They are switched together by means of an actuator.
  • the sliding sleeve and thus the two coupling elements 29a, 30a are switchable in two switching positions.
  • the first coupling element 29a rotatably connects the housing connecting element with the third output element.
  • the second coupling element 30a connects the input element to the first output element.
  • the second output element is rotatable in the first switching position relative to the input element and the output elements.
  • the first coupling element 29a rotatably connects the input element to the third output element.
  • the second coupling element 30a rotatably connects the first output element to the second output element.
  • the housing connecting element, the input element and the two output elements have teeth, which are arranged on a radially inner level.
  • the third output element has a toothing, which is arranged with respect to the remaining teeth on a radially outer level.
  • the first coupling element 29a has a toothing which lies on the radially inner level.
  • the first coupling element comprises a toothing which lies on the radially outer level. The toothing for connection to the third output element is executed extended with respect to the toothing for connection to the input element or to the housing connection element.
  • the coupling element 29a is thus always connected in a rotationally fixed manner to the ring gear 52a.
  • the second coupling element 30a is arranged radially nested within the first coupling element 29a.
  • the first coupling element 29a and the second coupling element 30a are fixedly connected to one another via a form-locking connection for a switching movement along an axial direction.
  • the form-fitting connection allows relative rotation of the first coupling element 29a with respect to the second coupling element 30a.
  • the not shown Akuator for common switching of the two coupling elements 29a, 30a engages the first coupling element 29a.
  • the second coupling element 30a is taken along by the first coupling element 29a.
  • the second switching unit 13a is arranged on the output side of the planetary gear 11a.
  • the second switching unit 13a includes a first input member rotatably connected to the Planetenradtrager 51a, a second input member which is rotatably connected to the sun gear 50a, a third input member, which is rotatably connected to the bypass gear shaft 53a, an output member and a housing connecting member rotatably connected to the transmission housing 39 a.
  • the ring gear 52a is rotatably connected to the transmission housing 39a.
  • the transmission shaft 42a is non-rotatably connected to the bypass transmission shaft 53a.
  • the transmission shaft 42a is rotatably connected to the ring gear 52a.
  • the planetary carrier 51a is non-rotatably connected to the bypass gear shaft 53a.
  • the switching unit 13a comprises an axially displaceable sliding sleeve.
  • the sliding sleeve comprises two coupling elements 31a, 32a, which can simultaneously produce two different non-rotatable connections.
  • the mutually rotatable coupling elements 31a, 32a are axially fixed to each other. They are switched together by means of an actuator.
  • the sliding sleeve and thus the two coupling elements 31a, 32a are switchable in two switching positions.
  • the first coupling element 31a connects the first input element to the output element.
  • the second coupling element 32a connects the second input element to the third input element.
  • the first coupling element 31a rotatably connects the second input element to the housing connecting element.
  • the second coupling element 32a rotatably connects the third input element to the output element.
  • the first input element is rotatable relative to the input elements and the output element in the second switching position.
  • the second coupling element 32a is arranged radially nested within the first coupling element 31a.
  • the first coupling element 31a and the second coupling element 32a are firmly connected to one another via a form-locking connection for a switching movement along an axial direction.
  • the positive connection allows a relative rotation of the first coupling element 31a with respect to the second coupling element 32a.
  • the not shown Akuator for switching the two coupling elements 31 a, 32 a engages the first coupling element 31 a.
  • the second coupling element 32a is taken along by the first coupling element 31a.
  • the gear device For connecting the second gear group 10a to the third gear group 14a, the gear device comprises a single gear shaft 21a.
  • the output element of the second switching unit 13a of the second transmission section 10a is non-rotatably connected to the transmission shaft 21a.
  • the transmission shaft 21a forms a group output shaft of the second transmission section 10a.
  • the planet carrier 51a In the first switching position of the switching unit 13a, the planet carrier 51a is thus connected in a rotationally fixed manner to the gear shaft 21a. At the same time, the sun gear 50a is rotatably connected to the bypass gear shaft 53a. In the second switching position of the switching unit 13a, the sun gear 50a is non-rotatably connected to the transmission housing 39a. At the same time, the bypass gear shaft 53a is non-rotatably connected to the gear shaft 21a.
  • the three gear ratios of the gear group 10a are switched by means of the switching units 12a, 13a. If both switching units 12a, 13a are switched to the first switching position, the gear group 10a has the gear ratio 2.64, which corresponds to a gear ratio of the planetary gear 11a with the ring gear 52a fixed. If both switching units 12a, 13a are switched to the second switching position, the transmission group 10a has the transmission ratio 1, 61, which corresponds to a steady-state transmission ratio of the planetary gear 11a with the sun gear 50a fixed. If the switching unit 12a is switched to the first switching position and the second switching unit 13a is switched to the second switching position, the transmission group 10a has the transmission ratio 1, 00.
  • the transmission shaft 21a forms a group input shaft of the third transmission section 14a.
  • the third transmission group 14a is executed analogously to the second transmission group 10a. According to the odulbauweise finds the module that the second gear group 10a forms, in the third transmission section 14a again.
  • the third transmission group 14a comprises exactly two shifting units 16a, 17a and exactly one planetary gear 15a with a sun gear 54a, a planet carrier 55a and a ring gear 56a.
  • the transmission group 14a further comprises a planetary gear bypass 24a for releasing the planetary gear 15a, which has a bypass gear shaft 57a, which passes through the sun gear 54a of the planetary gear 15a.
  • the first switching unit 16a is arranged on the input side of the planetary gear 15a.
  • the first switching unit 16a includes a housing connecting member rotatably connected to the gear housing 39a, an input member rotatably connected to the gear shaft 21a, a first output member rotatably connected to the bypass gear shaft 57a, a second output member non-rotatably is connected to the planet carrier 55a, and a third output member which is rotatably connected to the ring gear 56a.
  • the switching unit 16a comprises an axially displaceable sliding sleeve with two coupling elements 33a, 34a which are axially fixed and rotatably coupled to one another and which can produce two different non-rotatable connections at the same time and which are switched together by means of an actuator.
  • the ring gear 56a is rotatably connected to the transmission housing 39a.
  • the transmission shaft 21a is non-rotatably connected to the bypass transmission shaft 57a.
  • the transmission shaft 21a is non-rotatably connected to the ring gear 56a.
  • the planet carrier 55a is non-rotatably connected to the bypass gear shaft 57a.
  • the second switching unit 17a is arranged on the output side of the planetary gear 15a.
  • the second switching unit 17a includes a first input member non-rotatably connected to the planet carrier 55a, a second input member rotatably connected to the sun gear 54a, a third input member rotatably connected to the bypass transmission shaft 57a, an output member and a Housing connection element which is rotatably connected to the transmission housing 39a.
  • the switching unit 17a likewise comprises an axially displaceable sliding sleeve with two coupling elements 35a, 36a, which are axially fixed and rotatable with each other and which can simultaneously produce two different non-rotatable connections and which are switched together by means of an actuator.
  • the gear device For connecting the third gear group 14a to the fourth gear group 18a, the gear device comprises a single gear shaft 22a.
  • the output element of the second switching unit 17a of the third transmission section 14a is non-rotatably connected to the transmission shaft 22a.
  • the transmission shaft 22a forms a group output shaft of the third transmission section 14a.
  • the planet carrier 55a In the first switching position of the switching unit 17a, the planet carrier 55a is thus connected in a rotationally fixed manner to the transmission shaft 22a. At the same time, the sun gear 54a is non-rotatably connected to the bypass gear shaft 57a. In the second switching position of the switching unit 17a, the sun gear 54a is non-rotatably connected to the transmission housing 39a. At the same time, the bypass gear shaft 57a is non-rotatably connected to the gear shaft 22a.
  • the three gear ratios of the transmission section 14a are switched by means of the switching units 16a, 17a. If both switching units 16a, 17a are switched to the first switching position, the gear group 14a has the gear ratio 2.64, which corresponds to a stationary gear ratio of the planetary gear 15a with the ring gear 56a fixed. If both switching units 16a, 7a are switched to the second switching position, the transmission group 14a has the transmission ratio 1, 61, which corresponds to a steady-state ratio of the planetary gear 15a with the sun gear 54a fixed. If the switching unit 16a is switched into the first switching position and the second switching unit 17a into the second switching position, the transmission group 14a has the transmission ratio 1, 00.
  • the transmission shaft 22a forms a group input shaft of the fourth transmission section 18a.
  • the fourth transmission group 8a comprises exactly one switching unit 20a and exactly one planetary gear 19a (see FIG.
  • the planetary gear 19a includes a sun gear 58a, a planet carrier 59a, and a ring gear 60a.
  • the planet gear carrier 59a guides planet gears meshing with the sun gear 58a and the ring gear 60a on a circular path around the sun gear 58a.
  • the ring gear 60a of the planetary gear 19a is rotatably connected to the transmission housing 39a.
  • a toothing for the ring gear 60a is inserted directly into the gear housing 39a. To minimize axial forces, the toothing is designed as an arrow toothing.
  • the transmission group 18a includes a planetary gear bypass 25a, by means of which the planetary gear 19a can be unlocked.
  • the planetary gear bypass 25a includes a bypass gear shaft 6a, which passes through the sun gear 58a.
  • the transmission shaft 22a, which the Group input shaft is formed integrally with the bypass gear shaft 61 a.
  • the switching unit 20a is arranged on the output side of the planetary gear 19a.
  • the switching unit 20a includes a first input member non-rotatably connected to the planetary gear carrier 59a, a second input member rotatably connected to the sun gear 58a, a third input member rotatably connected to the bypass transmission shaft 61a, and an output member ,
  • the switching unit 20a comprises an axially displaceable sliding sleeve.
  • the sliding sleeve comprises two coupling elements 37a, 38a, which can simultaneously produce two different non-rotatable connections.
  • the mutually rotatable coupling elements 37a, 38a are axially fixed to each other. They are switched together by means of an actuator.
  • the sliding sleeve and thus the two coupling elements 37a, 38a are switchable in two switching positions.
  • the first coupling element 37a connects the first input element to the output element.
  • the second coupling element 38a connects the second input element to the third input element.
  • the second coupling element 38a rotatably connects the third input element with the output element.
  • the first coupling element 37a is connected in the second switching position only with the second input element.
  • the first input element and the second input element are rotatable in the second switching position relative to the third input element and the output element.
  • the second coupling element 38a is arranged radially nested within the first coupling element 37a.
  • the first coupling element 37a and the second coupling element 38a are fixedly connected to one another via a form-locking connection for a switching movement along an axial direction.
  • the form-fitting connection allows a relative rotation of the first coupling element 37a with respect to the second coupling element 38a.
  • the not shown Akuator for switching the two coupling elements 37a, 38a engages the first coupling element 37a.
  • the second coupling element 38a is taken along by the first coupling element 37a.
  • the transmission device comprises a transmission output shaft 62a.
  • the output element of the switching unit 20a of the fourth transmission group 18a is rotatably connected to the transmission output shaft 62a.
  • the transmission output shaft 62a forms a group output shaft of the fourth transmission section 18a.
  • the planet carrier 59a In the first switching position of the switching unit 20a, the planet carrier 59a is thus connected in a rotationally fixed manner to the transmission output shaft 62a. At the same time, the sun gear 58a is non-rotatably connected to the bypass gear shaft 61a. In the second switching position of the switching unit 17a only the bypass gear shaft 61a is rotatably connected to the transmission output shaft 62a.
  • the two transmission ratios of the transmission group 18a are switchable.
  • the gear ratio provided by the gear group 18a corresponds to a stationary gear ratio of the planetary gear 9a with the ring gear 56a fixed.
  • the transmission group 18a In the second switching position of the switching unit 20a, the transmission group 18a has the transmission ratio 2.64.
  • the transmission group 18a In the first switching position of the switching unit 20a, the transmission group 18a, the transmission ratio 1, 00 on.
  • the fourteenth gear V14a is formed as a direct gear. It has a gear ratio of 1, 000. In the fourteenth gear V14a all planetary gear 1a, 15a, 19a, 27a of the individual gear groups 10a, 14a, 18a, 26a are released. The Planentenradgetriebe 11 a, 15 a, 19 a, 27 a are free of load. A power flow for the fourteenth transmission gear V14a is transmitted through the transmission shafts 21a, 22a, 42a, 49a, the sun gear shaft 47a, and the bypass gear shafts 53a, 57a, 61a. The remaining gears V1a-V13a have a gear ratio greater than 1.00.
  • the transmission groups 10a, 14a, 18a, 26a are provided for switching gear ratios equal to or greater than 1, 00.
  • Such a transmission group 0a, 14a, 18a, 26a can be realized, for example, by conversely using the module constituting the second transmission section 10a and the third transmission section 14a. Structurally, such a module corresponds to the transmission group 10a. Only one power flow direction through the module is reversed, ie input or input side and output or output side are reversed.
  • the switching unit which is arranged in the second or third gear group 10a, 14a on the output side of the planetary gear, would be used as an input-side switching unit, while the switching unit, in the second or third gear group 10a, 14a on the input side of the Planetenradgetriebes is arranged to be used as an output-side switching unit.
  • the input elements of the switching units would then form output elements, while the output elements would form input elements.
  • the actuating unit comprises five actuators for actuating the switching units 12a, 13a, 16a, 17a, 20a, 28a and a clutch actuator for actuating the single clutch of the starter unit 40a.
  • actuators of the switching units 13a, 16a can be made partially in one piece.
  • the two switching units 13a, 6a are switched in three different combinations according to the switching logic (see FIG.
  • the actuators of the switching units 13a, 16a may be combined with each other in an actuator having three switch positions.
  • Such an actuating unit can be switched by means of 14 solenoid valves.
  • FIGS. 5 to 8 show two further exemplary embodiments of the invention.
  • the following descriptions are essentially limited to the differences between the exemplary embodiments, reference being made to the description of the other exemplary embodiments, in particular FIGS. 1 to 4, with regard to components, features and functions remaining the same.
  • identically designated components in particular with regard to components having the same reference numerals, reference may in principle also be made to the drawings and / or the description of the other exemplary embodiments, in particular FIGS. 1 to 4.
  • FIGS. 5 to 7 show a further exemplary embodiment of a group transmission device according to the invention.
  • the group transmission device is provided in total to the circuit of 12 gears V1 b -V12b.
  • the group transmission device comprises a total of four transmission groups 10b, 14b, 18b, 26b.
  • the transmission groups 10b, 14b, 18b, 26b are arranged in series in a force flow.
  • Each of the transmission groups 0b, 14b, 18b, 26b is provided for switching at least two transmission ratios.
  • the gear ratios of the individual gear groups 10b, 14b, 18b, 26b are changed.
  • a shift logic of the gears V1 b -V12b, which are switchable by means of the group transmission device is shown in Figure 7. Due to the arrangement of the transmission groups 10b, 14b, 18b, 26b, the transmission ratios of the individual transmission groups 10b, 14b, 18b, 26b are superimposed to form a transmission gear ratio which has the corresponding transmission V1b-V12b.
  • the transmission groups 14b, 8b, 26b are executed analogously to the preceding embodiment. They each comprise exactly one planetary gear 15b, 19b, 27b.
  • the transmission groups 18b, 26b each have a switching unit 20b, 28b and are provided for switching two transmission ratios.
  • the transmission group 14b comprises two switching units 16b, 17b and is provided for switching three transmission ratios.
  • the transmission section 10b comprises exactly one planetary gear 11b and exactly one switching unit 12b (see FIG.
  • the planetary gear 11 b includes a sun gear 50 b, a planet carrier 51 b and a ring gear 52 b.
  • the planet carrier 51b guides planetary gears which mesh with the sun gear 50ab and the ring gear 52b on a circular path around the sun gear 50b.
  • the sun gear 50b of the planetary gear 11b is rotatably connected to a transmission housing 39b.
  • the transmission section 10b further comprises a planetary gear bypass 23b, by means of which the planetary gear 1 1 b can be unlocked.
  • the planetary gear bypass 23b includes a bypass gear shaft 53b that passes through the sun gear 50b.
  • the switching unit 12b is arranged on the input side of the planetary gear 11b.
  • the switching unit 12b comprises a housing connecting member rotatably connected to the transmission housing 39b, an input member rotatably connected to a transmission shaft 49b, a first output member rotatably connected to the bypass gear shaft 53b, a second output member rotatably with the planet carrier 51 b is connected, and a third output member which is rotatably connected to the ring gear 52b.
  • the switching unit 12b comprises an axially displaceable sliding sleeve.
  • the sliding sleeve comprises two coupling elements 29b, 30b, which can simultaneously produce two different non-rotatable connections.
  • the relatively rotatable coupling elements 29b, 30b are axially fixed to each other. They are switched together by means of an actuator.
  • the sliding sleeve and thus the two coupling elements 29b, 30b are in two Switch positions switchable.
  • the first coupling element 29b rotatably connects the housing connecting element with the third output element.
  • the second coupling element 30b connects the input element to the first output element.
  • the second output element is rotatable in the first switching position relative to the input element and the output elements.
  • the first coupling element 29b rotatably connects the input element to the third output element.
  • the second coupling element 30b rotatably connects the first output element to the second output element.
  • the housing connecting element, the input element and the two output elements have teeth, which are arranged on a radially inner level.
  • the third output element has a toothing, which is arranged with respect to the remaining teeth on a radially outer level.
  • the first coupling element 29b has a toothing which lies on the radially inner level.
  • the first coupling element 29b has a toothing which lies on the radially outer level.
  • the toothing for connection to the third output element is executed extended with respect to the toothing for connection to the input element or to the housing connection element.
  • the coupling element 29b is thus always connected in a rotationally fixed manner to the ring gear 52b. At the same time, depending on its switching position, it is optionally connected in a rotationally fixed manner either to the transmission housing 39b or to the transmission shaft 49b.
  • the second coupling element 30b is arranged radially nested within the first coupling element 29b.
  • the first coupling element 29b and the second coupling element 30b are fixedly connected to each other via a positive connection for a switching movement along an axial direction.
  • the form-locking connection permits a relative rotation of the first coupling element 29b with respect to the second coupling element 30b.
  • the not shown Akuator for common switching of the two coupling elements 29b, 30b engages the first coupling element 29b.
  • the second coupling element 30b is carried along by the first coupling element 29b.
  • the transmission device For connecting the second transmission group 10b to the third transmission group 14b, the transmission device comprises a single transmission shaft 2.
  • the bypass gear shaft 53b is made in one piece with the transmission shaft 21b.
  • the transmission shaft 21b forms a group output shaft of the second transmission section 10b.
  • the two gear ratios of the transmission section 10b are switched by means of the switching unit 12b. If the switching unit 12b is switched to the first switching position, the transmission group 10b has the transmission ratio 1, 61, which corresponds to a steady state ratio of the planetary gear 11b with the sun gear 50b fixed. If the switching unit 12b is switched to the second switching position, the transmission group 10a has the transmission ratio 1, 00.
  • FIG. 8 shows a third exemplary embodiment of a group transmission device according to the invention.
  • the group transmission device is provided in total for the transmission of 4 gears V1c-V 4c.
  • the group transmission device comprises a total of four transmission groups 10 c, 14 c, 18 c, 26 c.
  • the transmission groups 10c, 14c, 18c, 26c are arranged in series in a force flow.
  • Each of the transmission groups 10c, 14c, 18c, 26c is provided for switching at least two transmission ratios.
  • the gear ratios of the individual Getnebeitati 10c, 14c, 18c, 26c are changed.
  • the transmission ratios of the individual transmission groups 10c, 14c, 18c, 26c overlap to a transmission gear ratio, which has the corresponding gear V1c-V14c.
  • a shift logic of the gears V1c-V14c with respect to the gear groups 10c, 14c, 18c corresponds to the first embodiment.
  • the transmission groups 10c, 14c, 18c are executed analogously to the preceding embodiment. They each comprise exactly one planetary gear 11c, 15c, 19c, 27c.
  • the gear group 18c has a switching unit 20c and is provided for switching two gear ratios.
  • the transmission groups 10c, 14c each comprise two switching units 12c, 13c, 16c, 17c and are provided for switching three gear ratios.
  • the transmission section 26c comprises a starting unit 40c, which has a double clutch.
  • the input-side transmission section 26c comprises exactly one planetary gear 27c, which is connected to the starter unit 40c.
  • the planetary gear 27c includes a sun gear 43c, a planet carrier 44c, and a ring gear 45c.
  • the planet gear carrier 44c guides planet gears meshing with the sun gear 43c and the ring gear 45c on a circular path around the sun gear 43c.
  • the sun gear 43c of the planetary gear gear 27c is rotatably connected to a transmission housing 39c.
  • the transmission section 26c further includes a sun gear shaft 47c penetrating the sun gear 43c.
  • the starting unit 40c comprises two partial clutches 63c, 64c.
  • the group gear device For connecting the starter unit 40c to the planetary gear 27a of the input-side gear group 26c, the group gear device comprises two gear part shafts 65c, 66c, which are arranged parallel to one another in the force flow. In each case one of the transmission part shafts 65c, 66c connects in the power flow to one of the partial clutches 63c, 64c.
  • the transmission part shaft 65c which adjoins the part-coupling 63c, is non-rotatably connected to the ring gear 45c of the planetary gear 27c of the transmission section 26c.
  • the transmission part shaft 66c which connects to the part clutch 64c, is rotatably connected to the sun gear shaft 47c and the planet carrier 44c.
  • the sun gear shaft 47c is integrally formed with a transmission shaft 49c which forms a group output shaft of the transmission section 26c.
  • a switching logic of the group transmission device is substantially analogous to that of the first embodiment.
  • a switching functionality for switching the gear ratios of the input-side gear group 26 c is realized by means of the starter unit 40 c.
  • the gear ratio of the transmission section 26c is switched by closing the sub-clutch 63c.
  • the other transmission ratio of the transmission section 26c is switched by closing the partial clutch 64c.
  • the gear ratio of the gear group 26c is defined by the stationary gear ratio of the planetary gear 27c with the sun gear 43c fixed.
  • the partial clutch 63c is closed, the transmission ratio is 1, 28. If the partial clutch 64c is closed, the transmission ratio of the transmission group 26c is 1.00.
  • the gears V1c-V14c are at least sequentially power shiftable. Adjacent gear trains V1c-V14c are each assigned alternately to one of the partial clutches 63c, 64c.
  • a device for switching a reverse gear In the exemplary embodiments not shown in detail is a device for switching a reverse gear.
  • a transmission group in the group transmission device additional a transmission group can be introduced, which is provided only for a reversal of direction. It is also conceivable to provide a gear group for switching at least two gear ratios without reversing the direction of rotation and for switching a gear ratio with reversal of direction.
  • a such transmission group can be easily formed, in particular with a planetary gear.
  • the group transmission device can have different auxiliary drives.
  • the ring gears of the planetary gear of the individual transmission groups are suitable for connection of auxiliary drives. Basically, however, other connections are conceivable.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

L'invention concerne un dispositif de train d'engrenages, en particulier un dispositif de train d'engrenages de véhicule automobile, comportant au moins un groupe d'engrenages (10a, 14a; 10b, 14b; 10c, 14c) pour le passage d'au moins deux rapports de démultiplication différents et au moins un autre groupe d'engrenages (18a; 18b; 18c) monté en aval dans la chaîne cinématique et présentant, pour le passage d'au moins deux autres rapports de démultiplication, un engrenage planétaire (19a; 19b; 19c) et au moins une unité de sélection de rapports (20a; 20b; 20c). Selon l'invention, le groupe d'engrenages avant (10a, 14a; 10b, 14b; 10c, 14c) comprend un engrenage planétaire (11a, 15a; 11b, 15b; 11c, 15c) et une unité de sélection de rapports (12a, 13a, 16a, 17a; 12b, 13b, 16b, 17b; 12c, 13c, 16c, 17c).
PCT/EP2011/003728 2010-08-06 2011-07-26 Dispositif de train d'engrenages WO2012016656A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010033590.8 2010-08-06
DE201010033590 DE102010033590A1 (de) 2010-08-06 2010-08-06 Gruppengetriebevorrichtung

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Publication number Priority date Publication date Assignee Title
DE102012216228A1 (de) * 2012-09-13 2014-03-13 Zf Friedrichshafen Ag Erweiterungsstufe, Getriebe und Antriebsstrang für ein Fahrzeug sowie Verfahren zum Einstellen einer Zusatzübersetzung für ein Getriebe
DE102014215156B4 (de) * 2014-08-01 2020-11-19 Zf Friedrichshafen Ag Gruppengetriebe eines Kraftfahrzeugs
DE102016015302A1 (de) 2016-12-22 2018-06-28 Daimler Ag Gruppengetriebevorrichtung

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4043225A (en) * 1973-12-29 1977-08-23 Aisin Seiki Kabushiki Kaisha Power shift transmission for motor vehicles
US5213551A (en) * 1990-02-28 1993-05-25 Mat Holdings B.V. Variable-ratio transmission device, especially for motor vehicles
EP0618382A1 (fr) * 1993-03-29 1994-10-05 Eaton Corporation Unité auxiliaire d'une transmission
US20050059521A1 (en) * 2003-09-16 2005-03-17 Komatsu Ltd. Control system for a hydro-mechanical transmission
EP1532383B1 (fr) 2002-08-28 2006-08-23 ZF FRIEDRICHSHAFEN Aktiengesellschaft Boite de vitesses a prise directe
RU2298713C1 (ru) * 2005-12-23 2007-05-10 Виктор Владимирович Становской Модульная планетарная коробка передач
CN101769365A (zh) * 2009-10-23 2010-07-07 陈国庆 一种可直接换挡的行星齿轮变速箱

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4043225A (en) * 1973-12-29 1977-08-23 Aisin Seiki Kabushiki Kaisha Power shift transmission for motor vehicles
US5213551A (en) * 1990-02-28 1993-05-25 Mat Holdings B.V. Variable-ratio transmission device, especially for motor vehicles
EP0618382A1 (fr) * 1993-03-29 1994-10-05 Eaton Corporation Unité auxiliaire d'une transmission
EP1532383B1 (fr) 2002-08-28 2006-08-23 ZF FRIEDRICHSHAFEN Aktiengesellschaft Boite de vitesses a prise directe
US20050059521A1 (en) * 2003-09-16 2005-03-17 Komatsu Ltd. Control system for a hydro-mechanical transmission
RU2298713C1 (ru) * 2005-12-23 2007-05-10 Виктор Владимирович Становской Модульная планетарная коробка передач
CN101769365A (zh) * 2009-10-23 2010-07-07 陈国庆 一种可直接换挡的行星齿轮变速箱

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