DE102010003943A1 - Gear box device for drive train of tractor, has clutch system provided in gearbox region for switch-on and off gearbox power paths, where parts of clutch system and switching elements represent paths on axle stitch of output shaft - Google Patents

Gear box device for drive train of tractor, has clutch system provided in gearbox region for switch-on and off gearbox power paths, where parts of clutch system and switching elements represent paths on axle stitch of output shaft

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Publication number
DE102010003943A1
DE102010003943A1 DE102010003943A DE102010003943A DE102010003943A1 DE 102010003943 A1 DE102010003943 A1 DE 102010003943A1 DE 102010003943 A DE102010003943 A DE 102010003943A DE 102010003943 A DE102010003943 A DE 102010003943A DE 102010003943 A1 DE102010003943 A1 DE 102010003943A1
Authority
DE
Germany
Prior art keywords
transmission
switching
variator
clutch
output shaft
Prior art date
Legal status (The legal status 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 status listed.)
Pending
Application number
DE102010003943A
Other languages
German (de)
Inventor
Gerhard Bailly
Helmut Konrad
Jürgen Pohlenz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen 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 ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Priority to DE102010003943A priority Critical patent/DE102010003943A1/en
Publication of DE102010003943A1 publication Critical patent/DE102010003943A1/en
Pending legal-status Critical Current

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H47/00Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/02Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H37/00Combinations of mechanical gearings, not hereinbefore provided for
    • F16H37/02Combinations of mechanical gearings, not hereinbefore provided for comprising essentially only toothed or friction gearings
    • F16H37/06Combinations of mechanical gearings, not hereinbefore provided for comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08Combinations of mechanical gearings, not hereinbefore provided for comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833Combinations of mechanical gearings, not hereinbefore provided for comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084Combinations of mechanical gearings, not hereinbefore provided for comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/0866Power split variators with distributing differentials, with the output of the CVT connected or connectable to the output shaft
    • F16H2037/0873Power split variators with distributing differentials, with the output of the CVT connected or connectable to the output shaft with switching, e.g. to change ranges
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H2200/00Transmissions for multiple ratios
    • F16H2200/20Transmissions using gears with orbital motion
    • F16H2200/2002Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2005Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one sets of orbital gears

Abstract

The device (3) has a variator (9) for continuously varying translation in translation regions. A planetary gear device (12) i.e. stage planetary gear, is coupled with a gear box input (10), a gearbox (37) and the variator. A dual clutch system (33) is provided in a gearbox region for switching-on and off power paths of the gearbox. Parts of the clutch system and positive switching elements (29, 30) are arranged to represent the power paths on an axle stitch of a transmission output shaft (5). The clutch system has frictional switching elements (31, 32) spatially arranged from each other.

Description

  • The invention relates to a transmission device with at least one variator for infinitely varying a ratio according to the closer defined in Oberbebegriff of claim 1. Art.
  • From the EP 1 541 898 A2 a continuously variable transmission device with power split and primary coupling is known. The power split takes place in the region of a planetary gear device, which is coupled to a transmission input and a variator and a transmission, in the area in connection with the variator more translation areas are displayed. Within the transmission ranges, the ratio of the transmission device via the variator is continuously variable. In addition, a dual-clutch system is provided in the region of the transmission device, by means of which respective power paths of the gearbox are switched on and off.
  • The known continuously variable transmission device is disadvantageously characterized both in the radial direction and in the axial direction by a high space requirement, since the dual clutch system and provided for displaying the power paths interlocking shift element are each arranged on two parallel countershafts and a transmission output shaft via a spur gear with the countershaft is operatively connected, on which the double-coupling system is arranged. In addition, the stepless transmission device causes high manufacturing costs due to the large design effort, but this is undesirable.
  • The present invention is therefore an object of the invention to provide a cost-continuous variable transmission device available, which is characterized by a small space requirement.
  • According to the invention, this object is achieved with a transmission device having the features of patent claim 1.
  • In the transmission device according to the invention with at least one variator for infinitely varying a ratio with preferably secondary power split, the planetary gear device is coupled to a transmission input and the variator and to a manual transmission. In the gearbox range, several transmission ranges can be displayed in conjunction with the variator, with the transmission ratio being infinitely variable within the transmission ranges via the variator. In addition, a dual-clutch system is provided in the region of the transmission device, by means of which each power paths of the transmission area are switched on and off.
  • Characterized in that at least parts of the dual clutch system and switching elements for displaying the power paths are arranged on a Achsstich a transmission output shaft, the transmission device according to the invention compared to the known from the prior art solution both in the radial direction and in the axial direction compared to that State of the art known solutions characterized by a smaller space requirement and cheaper to produce with less design effort. This results from the fact that essential parts of the transmission device are mounted on a shaft, i. H. preferably on the transmission output shaft of the transmission device can be arranged and this shaft, for example, without an additional space-requiring, gear output side arranged spur gear teeth with the output of a vehicle drive train is connectable.
  • Both the features specified in the claims and the features specified in the following embodiments of the transmission device according to the invention are each suitable for training alone or in any combination with each other to further develop the subject invention. The respective feature combinations represent no limitation with respect to the development of the subject matter according to the invention, but essentially have only an exemplary character.
  • Further advantages and advantageous embodiments of the transmission device according to the invention will become apparent from the claims and the embodiments described in principle below with reference to the drawings, the same reference numerals are used in the description of the various embodiments in favor of clarity for construction and functionally identical components.
  • It shows:
  • 1 a highly schematic representation of a drive train of a vehicle, preferably a tractor, with a wheel diagram of a first embodiment of the transmission device according to the invention;
  • 2 a second embodiment of the transmission device according to the invention with a dual-clutch system, by means of which two synchronously changeable transmission ranges and a reverse gear can be displayed;
  • 3 A third embodiment of the transmission device according to the invention, via the three synchronously switchable driving ranges and a reverse gear can be displayed;
  • 4 a fourth embodiment of the transmission device according to the invention, which in the axial direction requires less space than the transmission device according to 3 having;
  • 5 a fifth embodiment of the transmission device according to the invention with spatially separated double clutch system;
  • 6 a sixth embodiment of the transmission device according to the invention;
  • 7 a seventh embodiment of the transmission device according to the invention, by means of which four synchronously switchable driving ranges and one reverse gear can be displayed;
  • 8th an eighth embodiment of the transmission device according to the invention;
  • 9 a ninth embodiment comprising a stepped planetary gear device;
  • 10 A tenth embodiment of the transmission device according to the invention, in which a switching element is provided for coupling a drivable vehicle axle in the region of a variator of the transmission device;
  • 11 an eleventh embodiment of the transmission device according to the invention, with which two transmission ranges and one reverse gear can be displayed;
  • 12 a twelfth embodiment of the transmission device according to the invention;
  • 13 a further embodiment of the transmission device according to the invention, via which two synchronously switchable driving ranges and one reverse gear are available.
  • In 1 is a powertrain 1 a vehicle, preferably a tractor or the like, with a prime mover 2 , a transmission device 3 and a downforce 4 shown in a very schematic way. The downforce 4 includes one via a transmission output shaft 5 with the prime mover 2 Actively connected first drive axle 6 , Which in this case is the vehicle rear axle. In addition, the downforce 4 a second via a switching element 7 to the transmission output shaft 5 connectable second drivable vehicle axle 8th on, which in this case is the vehicle front axle. Depending on the particular application, however, there is also the possibility that the first drivable vehicle axle 6 the vehicle front axle and the second drivable vehicle axle 8th the vehicle rear axle is. In addition, there is also the possibility that the first drivable vehicle axle 6 also a switching element, if necessary, to the drive train 1 can be coupled or separated from this.
  • The transmission device 3 is with a presently designed as a hydrostatic device variator 9 for continuously varying a transmission ratio of the transmission device 3 executed. One of the engine designed as an engine 2 provided torque is in the range of a transmission input 10 into the transmission device 3 introduced and in the range of the transmission output shaft 5 from the transmission device 3 in the direction of the output 4 directed.
  • That in the area of the transmission input 10 applied torque of the prime mover 2 is via a first wave designed as a planetary ridge 11 a planetary gear device 12 into the transmission device 3 initiated. With the help of the planetary gear device 12 becomes a so-called power split of the drive torque of the prime mover 2 performed, with the torque from the first shaft 11 the planetary gear device 12 on rotatable on the shaft 11 stored planet gears 13 is forwarded. The planet wheels 13 combing with a second shaft designed as a sun gear 14 the planetary gear device 12 and with one as a ring gear 15 executed third shaft of the planetary gear device 12 ,
  • The sun wheel 14 the planetary gear device 12 is with a first wave 16 of the variator 9 coupled while a second wave 17 of the variator 9 over a spur gear 18 with an external toothing 19 of the ring gear 15 the planetary gear device 12 is actively connected. The ring gear 15 and another spur gear 20 are rotatable on the fixed with the sun gear 14 connected first wave 16 of the variator 9 stored, wherein the further spur gear 20 with a rotatable on the transmission output shaft 5 stored loose wheel 21 combs.
  • The variator 9 or the hydrostatic unit of the transmission device 3 is with two each operable as a pump and as a motor hydraulic devices 9A and 9B executed in Schrägachsenbauart, which has a common pivoting part 22 or a so-called double yoke are positively coupled, and thus has a simple and inexpensive control over only one adjusting mechanism. As a function of a setting angle of the common pivoting part 22 between the engine 9A respectively. 9B and the pump 9B respectively. 9A of the variator 5 change the speeds of the first wave 16 and the second wave 17 of the variator 9 in the end positions of the pivoting part 22 each between a shaft standstill and a maximum speed. In addition, however, there is also the possibility that the variator 9 is formed with independently adjustable hydraulic devices.
  • Another also rotatably with the first wave 16 of the variator 9 connected spur gear 23 meshes with one on the transmission output shaft 5 rotatably mounted idler gear 24 while non-rotatable with the second shaft 17 of the variator 9 connected spur gears 25 . 26 each with rotatable on the transmission output shaft 5 stored further loose wheels 27 and 28 engage.
  • The loose wheels 21 and 25 are about one between the loose wheels 21 and 25 arranged positive switching element 29 alternately with the transmission output shaft 5 rotatably connectable while the idler gears 24 and 28 via another positive switching element 30 also alternately with the transmission output shaft 5 rotatably coupled.
  • Both the positive switching element 29 as well as the other positive switching element 30 are rotatable on the transmission output shaft 5 arranged and in turn alternately via a present two frictional switching elements 31 . 32 comprehensive double clutch system 33 with the transmission output shaft 5 rotatably engageable in operative connection.
  • In addition, gearbox output side is on the transmission output shaft 5 another festival bike 34 provided, which with one on another shaft 35 the transmission device 3 rotatably mounted idler gear 36 combs. The idler wheel 36 is about the frictional switching element 7 rotatably with the other wave 35 connectable, bringing one to the transmission output shaft 5 applied torque partially in the direction of the second drivable vehicle axle 8th of the drive train 1 is feasible.
  • The planetary gear device 12 is present next to the transmission input 10 and the variator 9 also with a double clutch system 33 and the positive switching elements 29 and 30 comprehensive manual transmission 37 operatively connected, using the dual-clutch system 33 in the area of the manual transmission 37 and the positive switching elements 29 and 30 each power paths of the gearbox 37 for displaying each synchronously switchable three driving ranges for forward drive and a driving range for reversing in a power flow of the transmission device 1 can be switched on and off from this, within the translation of the transmission device 3 over the variator 9 each is infinitely variable.
  • At the in 1 illustrated first embodiment of the transmission device according to the invention 1 are both the dual clutch system 33 as well as the form-locking switching elements 29 and 30 on the Achsstich the transmission output shaft 5 arranged, bringing the transmission device 3 characterized in the radial direction by a small space requirement, due to the low wave number is inexpensive to produce and has low overall weight.
  • In addition, via the transmission device 3 a so-called shuttle function is available, by means of which between a first driving range for forward drive and the driving range for reverse driving during a load circuit traction interruption free interchangeable.
  • A so-called PTO wave 38 (Power take-off shaft) is present directly with an engine output shaft of the prime mover 2 coupled and provides in the execution of the drive train 1 trained tractor tractor as a PTO. One in the area of the transmission input 10 rotatably with the engine output shaft or the PTO shaft 38 rotatably connected fixed wheel 39 meshes with another spur gear 40 that in turn with a wave 41 rotatably connected. The wave 41 provides a drive shaft for a hydraulic pump system 42 represents, over which hydraulic consumers of the vehicle are supplied with working pressure.
  • To illustrate the first driving range for forward drive in the transmission device 3 becomes the first loose wheel 21 over the positive switching element 29 with an inner disc carrier 31A the frictional switching element 31 of the double clutch system 33 coupled. Will the frictional switching element 31 transferred by appropriate operation in its closed operating state, the idler gear 21 non-rotatably with the transmission output shaft 5 connected. At the same time open operating state of the second frictional switching element 32 is then in the transmission device 3 the first driving range for forward travel is engaged.
  • Starting from the first driving range for forward drive according to the requirements in the transmission device 3 the second driving range for forward drive are inserted, first the idler gear 24 over the positive switching element 30 rotatably with an inner disk carrier 32A of the second frictional switching element 32 of the double clutch system 33 rotatably connected. This is in the transmission device 3 first on the further positive switching element 30 a preselection of the second driving range for forward drive performed.
  • Subsequently, the variator 9 swiveled as needed and the second frictional switching element 32 converted into a synchronous operating state. Upon reaching the synchronous operating state of the second frictional switching element 32 of the double clutch system 33 becomes the first frictional switching element 31 converted into its open operating state and the second frictional switching element 32 closed, bringing in the transmission device 3 the second driving range for forward drive is engaged.
  • If there is a corresponding requirement for inserting the third driving range for forward travel, starting from the second driving range for forward driving, the idler gear first becomes 27 over the positive switching element 29 with the inner disk carrier 31A of the first frictional switching element 31 rotatably coupled and the frictional switching element 31 by appropriate operation of the variator 9 converted into its synchronous operating state.
  • In the synchronization point of the first frictional switching element 31 becomes the second frictional switching element 32 of the double clutch system 33 opened and the first frictional switching element 31 closed, bringing in the transmission device 3 the third driving range for forward drive is engaged.
  • If there is a request to engage the reverse drive range starting from the first drive range for forward travel, the idler gear becomes 28 over the positive switching element 30 rotatably with the inner disk carrier 32A of the second frictional switching element 32 rotatably connected and then the transmission capacity of the second frictional switching element 32 raised while the transmission capability of the first frictional switching element 31 is reduced accordingly. This leads to that in the region of the second frictional switching element 32 increasingly a load transfer takes place and that with the drive train 1 vehicle is braked and then moved in the reverse direction. The ratio change between the first driving range for forward driving and the driving range for reversing is at fully open first frictional switching element 31 and complete load transfer of the second frictional switching element 32 of the double clutch system 33 completed.
  • At the in 1 illustrated first embodiment of the transmission device 3 is the ring gear 15 the planetary gear mechanism 12 , which are for displaying the third driving range for forward drive and also required to represent the driving range for reverse driving gear elements via a common shaft of the transmission device 3 with the variator 9 operatively connected.
  • At the in 1 illustrated first embodiment of the transmission device 3 is the hydraulic device 9B together with the second wave 17 of the variator 9 opposite the first hydraulic device 9A with any tilt angle around the first shaft 16 of the variator 9 opposite the first hydraulic device 9A in an in 1 Not shown housing of the transmission device 3 can be arranged with high degree of freedom, bringing the transmission device 3 optimized in each case can be adapted to existing space in a vehicle and the available space available in the vehicle.
  • The common shaft for connecting the ring gear 15 the planetary gear device 12 , the transmission elements for displaying the third range for forward travel and the transmission elements for displaying the driving range for reverse drive advantageously offers the possibility of the transmission device 3 to perform with less tooth intervention and operate at a higher efficiency.
  • In 2 to 13 are further embodiments of the drive device according to the invention 3 represented, which in each case only in partial areas of the in 1 differ in the following description, essentially only to the differences between the other embodiments of the transmission device 3 according to 2 to 13 and the in 1 illustrated first embodiment is received and with respect to the further operation of the transmission device 3 to the above description 1 is referenced.
  • This in 2 shown second embodiment of the transmission device 3 provides two translations for forward and one reverse translation. In this case, driving range changes between the first driving range and the second driving range for forward driving are in each case in the synchronized state of the frictionally engaged shifting elements 31 and 32 of the double clutch system 33 at low loads in the field of frictional switching elements 31 and 32 of the double clutch system 33 feasible.
  • Lies in the transmission device 3 according to 2 inlaid first driving range for forward drive a corresponding requirement for inserting the second driving range before, first becomes the idler gear 23 over the positive switching element 30 with the inner disk carrier 32A the further frictional switching element 32 rotatably connected. Subsequently, by appropriate adjustment of the variator 9 the frictional switching element 32 converted into its synchronous operating state and closed in the synchronization point, while the first frictional switching element 31 of the double clutch system 33 is opened. With open first frictional switching element 31 and closed frictional switching element 32 is in the transmission device 3 the second driving range for forward travel is engaged.
  • If there is a corresponding driver-side request for the change, starting from the first driving range for forward travel in the driving range for reversing, is via the interlocking switching element 30 the idler wheel 26 rotatably with the inner disk carrier 32A the frictional switching element 32 rotatably coupled and then the transmission capacity of the frictional switching element 32 increases, while the transmission capability of the first frictional switching element 31 is reduced. With increasing load transfer in the region of the second frictional switching element 32 the speed of the vehicle is reduced in the forward direction and ultimately operated in the reverse direction, this process can be displayed as a load circuit and the vehicle is operated in a shuttle operation.
  • This in 3 illustrated third embodiment of the transmission device 3 also includes the dual clutch system 33 and the two positive switching elements 29 and 30 all on the transmission output shaft 5 are arranged. About the transmission device 3 are three synchronously switchable driving ranges for forward drive and an insertable in shuttle mode by a load circuit driving range for reversing representable.
  • The for displaying the third driving range for forward drive provided spur gear 25 and the foreseen for displaying the driving range for reverse drive spur gear 26 is each on a parallel to the second wave 17 of the variator 9 arranged countershaft 43 respectively. 44 arranged, with a fixed wheel of the countershaft 43 with the spur gear 18 the second wave 17 of the variator 9 combs while a fixed wheel 46 the countershaft 44 with the external teeth 19 of the ring gear 15 the planetary gear device 12 engaged.
  • The compared to the in 1 illustrated transmission device 1 separate embodiment of the transmission elements provided for displaying the third driving range for forward travel and the transmission elements of the transmission device provided for representing the driving range for reverse driving 3 according to 3 offers the possibility of the respective connecting shafts performing countershafts 43 and 44 between the planetary gear device 12 and the downforce 4 to freely arrange in the room and thus to make optimal use of available space in a vehicle. In addition, the third embodiment is the transmission device 3 according to 3 compared to the first embodiment of the transmission device 3 according to 1 characterized by a smaller axial space requirement.
  • In the 4 illustrated further embodiment of the transmission device according to the invention 3 is essentially the same as in 3 shown transmission device 3 and differs from this only in the area of the double clutch system 33 , In the execution of the transmission device 3 according to 4 are the two frictional switching elements 31 and 32 spatially separated from each other on the transmission output shaft 5 arranged.
  • The spatially separated executed dual-clutch system is in a cost effective manner of two identical frictionally engaged shift elements 31 and 32 produced. In this embodiment of the transmission device 3 are wavelengths as well as an arrangement of bearings of the transmission output shaft 5 adaptable to the respective load case. The latter adaptation offers the possibility of the diameter of the transmission output shaft 5 perform as small as possible by a load-oriented positioning of the bearings and both the manufacturing costs and the total weight of the transmission device 3 to lower. Here is the distance between the bearings of the transmission output shaft 5 preferably as small as possible.
  • At the in 5 illustrated further embodiment of the transmission device 3 are the two frictional switching elements 31 and 32 of the double clutch system 33 also spatially separated from each other on the transmission output shaft 5 arranged, wherein between the frictional switching elements 31 and 32 the two positive switching elements 29 and 30 are provided.
  • Again, alternatively, the two are spatially separated from each other on the transmission output shaft 5 arranged frictional switching elements 31 and 32 the dual clutch system between the two positive switching elements 29 and 30 arranged. Otherwise corresponds to the structural design of the transmission device 3 according to 6 essentially the structural design of the transmission device according to 5 ,
  • 7 shows a development of the transmission device 3 according to 1 to 3 , with which four synchronously switchable driving ranges for forward drive and for reverse drive can be displayed. About that In addition, the transmission device 3 according to 7 with three positive switching elements 29 . 30 and 47 formed, wherein on the two form-locking switching elements 29 and 30 in the manner described above, each of the four driving ranges for forward and reverse travel initially preselected and via corresponding actuation of the two frictional switching elements 31 and 32 of the double clutch system 33 are inserted accordingly. The switchover between the forward drive mode and the reverse drive mode is only possible in vehicle standstill, with which no shuttle function can be displayed.
  • If there is a corresponding requirement for a change, for example, from the first driving range for forward travel in the direction of the first driving range for reverse driving, the vehicle is first to decelerate to zero and then a fixed gear 48 in the region of the positive switching element 47 from the transmission output shaft 5 to decouple and one on the transmission output shaft 5 rotatably mounted idler gear 49 rotatably on the form-locking switching element 47 with the transmission output shaft 5 connect to. In this operating state of the positive switching element 47 becomes one of the planetary gear device 12 over the first frictional switching element 29 , the fixed wheel 48 , an intermeshing wheel 50 and a fixed wheel engaged therewith 51 a countershaft 52 as well as another fixed gear of the countershaft 52 on the loose wheel 49 and thus on the thus on the positive switching element 47 non-rotatably connected transmission output shaft 5 forwarded.
  • If there is a corresponding requirement for a changeover from the first transmission range to the second transmission range, first in the region of the second positive-locking switching element 30 the idler wheel 24 with the inner disk carrier 32A of the second frictional switching element 32 of the double clutch system 33 rotatably connected. Subsequently, the translation of the variator 9 changed so that the second frictional switching element 32 goes into a synchronous operating state. In the synchronization point of the second frictional switching element 32 this is closed while the first frictional switching element 31 is opened. In the closed operating state of the second frictional switching element 32 is the planetary gear device 12 with one with the transmission output shaft 5 aligned shaft over the further spur gear 23 and the idler wheel meshing with it 24 operatively connected.
  • If it is desired to switch over from the second driving range to the third driving range in accordance with a requirement, the first interlocking shifting element becomes 29 pressed and the idler wheel 21 from the inner disk carrier 31A of the first frictional switching element 31 of the double clutch system 33 decoupled and the other loose wheel 27 rotatably with the inner disk carrier 31A connected. Subsequently, in the presence of the synchronous operating state of the first frictional switching element 31 the second frictional switching element 32 opened and the first frictional switching element 31 closed at the same time, bringing in the transmission device 3 the third driving range is engaged.
  • For a transition from the third driving range to the fourth driving range, turn on the shaft 54 rotatably mounted idler gear 55 over the positive switching element 30 rotatably with the inner disk carrier 32A of the second frictional switching element 32 rotatably connected while the idler gear 24 is decoupled from this. Subsequently, the second frictional switching element 32 closed at its point of synchronization, while the first frictional switching element 31 is opened. In the latter operating state of the transmission device 3 is inserted in this the fourth driving range.
  • Because of the over the transmission device 3 according to 7 representable four driving ranges for both forward drive and reverse drive is one with the transmission device 3 executed vehicle with higher drive powers available. In addition, the countershaft transmission disposed on the transmission output side for displaying the forward drive ranges and the reverse drive ranges offers the possibility of the transmission device 3 run with low radial space requirements.
  • In the 8th illustrated further embodiment of the transmission device 3 essentially corresponds to the design of the transmission device 3 according to 7 , wherein the transmission device 3 according to 8th without the second positive switching element 30 and executed without the fourth driving range and characterized by a smaller space requirement and lower production costs.
  • The planetary gear device 12 is at the in 9 illustrated embodiment of the transmission device 3 in contrast to the other illustrated in the drawings embodiments of the transmission device 3 designed as a stepped planetary set, with the sun gear 14 the planetary gear device 12 with the first wave 16 of the variator 9 is operatively connected while another sun gear 56 the planetary gear device 12 with one with the first wave 16 of the variator 9 aligned shaft 57 rotatably connected. The ring gear 15 the planetary gear device 12 In the present case, it meshes with the second shaft in a rotationally fixed manner 17 of the variator 9 connected spur gear 18 that in turn with the fixed gear 45 the countershaft 43 engaged. In the area of another external toothing 58 the ring gear meshes 15 the planetary gear device 12 with the loose wheel 21 , via the corresponding actuation of the positive switching element 29 and the first frictional switching element 31 of the double clutch system 33 the first driving range for forward or reverse travel is displayed.
  • The two frictional switching elements 31 and 32 of the double clutch system 33 are present again spatially separated from each other, wherein the first frictional switching element 31 on the with the transmission output shaft 5 in alignment 54 and the second frictional switching element 32 as the only switching element of the transmission device 3 on the first wave 16 of the variator 9 aligned shaft 57 is installed.
  • About the transmission device 3 according to 9 each three synchronously switchable driving ranges for forward and reverse travel can be displayed, wherein between forward drive and reverse drive in the region of the transmission output side arranged countershaft transmission with appropriate actuation of the positive switching element 47 can be switched to the vehicle standstill.
  • By the execution of the planetary gear device 12 as a stepped planetary gearset is the over the transmission device 3 feasible drive power with reduced radial space requirements higher than in the above-described embodiments of the transmission device 3 , Wherein, depending on the particular application, the above-described embodiments according to 1 to 8th and the further embodiments of the transmission device 3 according to 10 to 13 instead of using a simple planetary gear set, also with a stepped planetary gear set are executable to those via the gear device 3 each to be able to increase feasible drive power as needed.
  • At the in 10 illustrated further embodiment of the transmission device 3 is that for the application of the drive axle 8th provided frictional switching element 37 below the variator 9 arranged, bringing the transmission device 3 in comparison to the above-described embodiments of the transmission device 3 is characterized by a smaller axial space requirement.
  • In addition, the transmission device 3 according to 10 , on the three driving ranges for forward travel and a driving range for reverse travel can be displayed, even a small radial space requirement, as provided for the representation of the third driving range for forward drive idler gear 25 , the fixed wheel 46 the countershaft 44 and the spur gear 18 the second shaft of the variator 9 directly with the external teeth 19 of the ring gear 15 the planetary gear device 12 comb without additional intermediate shaft.
  • Depending on the operation of the first positive switching element 29 is in the transmission device 3 when the first frictional switching element is closed 31 either the first or the third driving range for forward drive inserted while in response to the actuation of the second positive switching element 30 at closed second frictional switching element 32 of the double clutch system 33 either the second range for forward drive or the drive range for reverse drive is engaged.
  • 11 essentially shows in the in 10 illustrated embodiment of the transmission device 3 corresponding embodiment of the transmission device 3 , which are essentially only in the area of the connection of the countershaft 44 to the planetary gear device 12 from the transmission device 3 out 10 different. The fixed wheel 46 the countershaft 44 meshes with the transmission device 3 according to 11 with the rotation with the ring gear 15 the planetary gear device 12 connected further spur gear 20 , bringing the countershaft 44 the transmission device 3 according to 11 shorter than the countershaft 44 the transmission device 3 according to 10 is executable and additional space preferably for the arrangement of the positive switching element 7 and the associated spur gear 36 is available.
  • 12 shows a further embodiment of the transmission device 3 in which the second positive switching element 30 the above-described embodiments of the transmission device 3 according to 1 to 11 by two spatially separated from each other form-fitting switching elements 59 and 60 is replaced, in addition to the first wave 16 of the variator 9 are arranged. About the transmission device 3 according to 12 are three synchronously switchable driving ranges for forward drive and a driving range for reversing representable, which can throw changed between forward drive and reverse in shuttle mode. Furthermore, the loose wheels 25 and 27 over the positive switching element 29 with an outer disc carrier 31B of the first frictional switching element 31 of the double clutch system 33 connectable.
  • The main advantage of in 12 shown design variant of the transmission device 3 is the small axial space requirement, due to the resolved design of the switching elements 31 and 32 of the double clutch system 33 and the positive switching element 30 that through the positive switching elements 59 and 60 replaced, achieved.
  • In the 13 illustrated further construction variant of the transmission device 3 is essentially the same as in 11 shown embodiment of the transmission device 3 , wherein via the transmission device 3 according to 13 only two synchronously switchable driving ranges for forward drive and a driving range for reversing can be displayed and the idler gears 24 and 28 over the positive switching element 30 to an outer disk carrier 32B of the second frictional switching element 32 of the double clutch system 33 be coupled.
  • The frictional couplings 31 and 32 the dual clutch system and the positive switching element 29 are all on the transmission output shaft 5 arranged, between forward drive and reverse in shuttle mode can be changed.
  • The special component arrangement of the design variant of the transmission device 3 according to 13 again offers the possibility of the transmission device 3 execute both in the axial and in the radial direction with a small space requirement.
  • Notwithstanding the above description, the variator can also be embodied as a friction gear or as any other gear unit, via which the ratio of the transmission device according to the invention in the different driving ranges is continuously variable. In addition, it is also possible to design the transmission device according to the invention as a function of the respective application also with primary coupling in the region of the variator, wherein the transmission device can be used in various agricultural vehicles, such as tractors, combine harvesters or the like, as well as in construction vehicles.
  • At the in 1 to 6 and 10 to 13 illustrated embodiments of the transmission device 3 is in each case a driving range for reversing representable and changeable between forward drive and reverse each in shuttle mode via a load circuit. In the 7 to 9 shown embodiments of the transmission device 3 have both in the forward direction and in the reverse direction, the same number of driving ranges, with a change between forward and reverse each in the vehicle standstill is feasible.
  • The interlocking shift elements of the transmission device according to the invention can be executed in each case as claw shift elements or as synchronizers, depending on the respective application case.
  • LIST OF REFERENCE NUMBERS
  • 1
    powertrain
    2
    prime mover
    3
    transmission device
    4
    output
    5
    Transmission output shaft
    6
    Drive shaft, rear axle
    7
    switching element
    8th
    Drive shaft, front axle
    9
    variator
    9A
    hydraulic device
    9B
    hydraulic device
    10
    transmission input
    11
    first shaft of the planetary gear device
    12
    Planetary gear set
    13
    planet
    14
    second wave, sun gear
    15
    third shaft, ring gear
    16
    first wave of the variator
    17
    second shaft of the variator
    18
    spur gear
    19
    External toothing of the ring gear
    20
    another spur gear
    21
    Losrad
    22
    pivoting part
    23
    another spur gear
    24
    Losrad
    25
    spur gear
    26
    spur gear
    27
    logRAD
    28
    logRAD
    29
    positive switching element
    30
    another positive switching element
    31
    frictional switching element
    31A
    Inner disk carrier
    31B
    External disk carrier
    32
    frictional switching element
    32A
    Inner disk carrier
    33
    Dual Clutch System
    34
    fixed gear
    35
    another wave
    36
    Losrad
    37
    manual transmission
    38
    PTO shaft
    39
    fixed gear
    40
    spur gear
    41
    wave
    42
    Hydraulic pump system
    43
    Countershaft
    44
    Countershaft
    45
    fixed gear
    46
    fixed gear
    47
    positive switching element
    48
    fixed gear
    49
    Losrad
    50
    idler
    51
    fixed gear
    52
    Countershaft
    53
    another festrad
    54
    wave
    55
    Losrad
    56
    sun
    57
    wave
    58
    further external toothing of the ring gear
    59
    positive switching element
    60
    positive switching element
  • 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
    • EP 1541898 A2 [0002]

Claims (15)

  1. Transmission device ( 3 ) with at least one variator ( 9 ) for continuously varying a ratio and preferably with secondary power split, wherein a planetary gear device ( 12 ) with a transmission input ( 10 ) and the variator ( 9 ) and a manual transmission ( 37 ) in the area in connection with the variator ( 9 ) can be represented, wherein the translation within the transmission ranges via the variator ( 9 ) is each infinitely variable, and wherein in the region of the gearbox ( 37 ) a dual clutch system ( 33 ) is provided, by means of which respective power paths of the gearbox ( 37 ) are switched on and off, characterized in that at least parts of the double clutch system ( 33 ) and switching elements ( 29 . 30 ) for displaying the power paths on the Achsstich a transmission output shaft ( 5 ) are arranged.
  2. Transmission device according to claim 1, characterized in that in the region of the power paths in each case at least one positive-locking switching element ( 29 . 30 ) is provided, over which for representing the power paths idler gears ( 21 . 24 . 27 . 28 ) with waves ( 5 ) are connectable.
  3. Transmission device according to claim 1 or 2, characterized in that the double clutch system ( 33 ) at least two a frictional unit forming frictional switching elements ( 31 . 32 ).
  4. Transmission device according to claim 1 or 2, characterized in that the double clutch system ( 33 ) at least two spatially separated frictionally engaged switching elements ( 31 . 32 ) having.
  5. Transmission device according to one of claims 1 to 4, characterized in that the planetary gear device ( 12 ) is designed as a stepped planetary gear.
  6. Transmission device according to one of claims 1 to 5, characterized in that a switching element ( 30 . 32 ) is provided for inserting a driving range for reversing.
  7. Transmission device according to one of claims 4 to 6, characterized in that the switching elements ( 31 . 32 ) of the dual clutch system ( 33 ) on a common wave ( 5 ) are arranged.
  8. Transmission device according to one of claims 4 to 6, characterized in that the switching elements ( 31 . 32 ) of the dual clutch system ( 33 ) on different contractions ( 5 . 57 ) are arranged.
  9. Transmission device according to one of claims 4 to 8, characterized in that the switching elements ( 29 . 30 ) of the power paths and the switching elements ( 31 . 32 ) of the dual clutch system ( 33 ) on a common wave ( 5 ) are arranged.
  10. Transmission device according to one of claims 1 to 9, characterized in that the transmission output shaft ( 5 ) with a vehicle front axle ( 8th ) can be brought into operative connection, wherein the vehicle front axle ( 8th ) via a switching element ( 47 ) can be coupled to the power flow.
  11. Transmission device according to claim 10, characterized in that for coupling the vehicle front axle ( 8th ) on the transmission output shaft ( 5 ) provided switching element ( 37 ) axially adjacent to the switching elements ( 29 . 30 . 31 . 32 ) of the power paths and the dual clutch system ( 33 ) is positioned.
  12. Transmission device according to claim 10 or 11, characterized in that for coupling the vehicle front axle ( 8th ) on the transmission output shaft ( 5 ) provided switching element ( 47 ) radially adjacent to the switching elements ( 29 . 30 . 31 . 32 ) of the power paths and the dual clutch system ( 33 ) is positioned.
  13. Transmission device according to one of claims 1 to 12, characterized in that a change between a power path for forward travel and a power path for reverse travel via the dual clutch system ( 33 ) traction interruption free feasible.
  14. Transmission device according to one of claims 1 to 13, characterized in that the variator ( 9 ) as a hydrostatic unit with two preferably operated as a pump and as a motor hydraulic devices ( 9A . 9B ) is executed in Schrägachsenbauart.
  15. Transmission device according to claim 14, characterized in that the variator ( 9 ) has an adjusting mechanism, wherein the hydraulic devices ( 9A . 9B ) of the variator ( 9 ) via a common pivoting part ( 22 ) positively coupled and are formed jointly pivotable about this.
DE102010003943A 2010-04-14 2010-04-14 Gear box device for drive train of tractor, has clutch system provided in gearbox region for switch-on and off gearbox power paths, where parts of clutch system and switching elements represent paths on axle stitch of output shaft Pending DE102010003943A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE102010003943A DE102010003943A1 (en) 2010-04-14 2010-04-14 Gear box device for drive train of tractor, has clutch system provided in gearbox region for switch-on and off gearbox power paths, where parts of clutch system and switching elements represent paths on axle stitch of output shaft

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102010003943A DE102010003943A1 (en) 2010-04-14 2010-04-14 Gear box device for drive train of tractor, has clutch system provided in gearbox region for switch-on and off gearbox power paths, where parts of clutch system and switching elements represent paths on axle stitch of output shaft

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Publication Number Publication Date
DE102010003943A1 true DE102010003943A1 (en) 2011-12-15

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DE102010003943A Pending DE102010003943A1 (en) 2010-04-14 2010-04-14 Gear box device for drive train of tractor, has clutch system provided in gearbox region for switch-on and off gearbox power paths, where parts of clutch system and switching elements represent paths on axle stitch of output shaft

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Citations (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4563914A (en) * 1982-01-10 1986-01-14 Industries Development Corporation (International Services) Continuously variable transmission with auxiliary drive
DE3903876C1 (en) * 1989-02-10 1990-09-13 Friedrich Prof. Dr.-Ing. 4300 Essen De Jarchow Transmission with a continuously variable action, a starting clutch and gears for hydrostatic-mechanical operation or hydrostatic operation
EP0465752A1 (en) * 1990-06-20 1992-01-15 Aragonesa De Equipamientos Para Automoviles, S.A. Continuous gear change mechanism
DE4236671C1 (en) * 1992-10-30 1993-11-18 Jarchow Friedrich Staglessly working hydrostatic-mechanical load switch gear - comprises four-shaft gearwheel circulating gear, stagelessly adjustable hydrostatic gear comprising gearwheel switch stages, and switch couplings
DE4323358C1 (en) * 1993-05-28 1994-05-26 Jarchow Friedrich Five-shaft gearwheel planetary gear - has parallel arranged steplessly adjustable hydrostatic gear, with gearwheel switch stages and switch couplings
WO1994021941A1 (en) * 1993-03-19 1994-09-29 Zf Friedrichshafen Ag Continuously variable transmission with wide transmission ratio range
DE4443267A1 (en) * 1994-12-05 1996-06-13 Claas Ohg Powershift transmission with 5-shaft epicyclic gear
US5868640A (en) * 1996-12-04 1999-02-09 Caterpillar Inc. Hydromechanical transmission having four members and two planetaries
DE19843069A1 (en) * 1997-09-20 1999-05-06 Michael Meyerle Continuously variable transmission, especially with power branching
DE10113177C1 (en) * 2001-03-19 2002-04-04 Friedrich Jarchow Planetary cogwheel gearing, for continuously variable hydrostatic transmission, has drive shaft, coupling shaft, high-speed and low-speed coupling shafts and connection shaft for variable hydrostatic drive
DE10319252A1 (en) * 2003-04-28 2004-11-18 Claas Industrietechnik Gmbh Infinitely variable torque division gearbox for agricultural tractors and utility vehicles has a continuously adjustable ratio of speeds, two engaging/disengaging clutches and a driven shaft
EP1541898A2 (en) 2003-12-12 2005-06-15 CNH Italia S.p.A. CVT transmission for motor vehicles, in particular for tractors
WO2006042434A1 (en) * 2004-10-20 2006-04-27 Markus Liebherr International Ag Power-branched transmission and method for the operation of such a transmission
EP1855029A2 (en) * 2006-05-11 2007-11-14 CNH Italia S.p.A. CVT hydromechanical drive, in particular for a farm tractor.
DE102008040446A1 (en) * 2008-07-16 2010-01-21 Zf Friedrichshafen Ag Transmission device for vehicle, has variator spaciously arranged between planetary gear unit and manual gear unit, where orientation of pivot axis of variator corresponds to orientation of vehicle vertical axis
DE102008040450A1 (en) * 2008-07-16 2010-01-21 Zf Friedrichshafen Ag Variable transmission device for vehicle, has variator, planetary gear unit, and manual gear unit, which are arranged in transmission housing
DE102008040441A1 (en) * 2008-07-16 2010-02-18 Zf Friedrichshafen Ag Transmission device for use in vehicle power train, has planetary gear unit and variator whose shafts are connected to transmission output via switching elements for illustrating transmission regions, respectively

Patent Citations (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4563914A (en) * 1982-01-10 1986-01-14 Industries Development Corporation (International Services) Continuously variable transmission with auxiliary drive
DE3903876C1 (en) * 1989-02-10 1990-09-13 Friedrich Prof. Dr.-Ing. 4300 Essen De Jarchow Transmission with a continuously variable action, a starting clutch and gears for hydrostatic-mechanical operation or hydrostatic operation
EP0465752A1 (en) * 1990-06-20 1992-01-15 Aragonesa De Equipamientos Para Automoviles, S.A. Continuous gear change mechanism
DE4236671C1 (en) * 1992-10-30 1993-11-18 Jarchow Friedrich Staglessly working hydrostatic-mechanical load switch gear - comprises four-shaft gearwheel circulating gear, stagelessly adjustable hydrostatic gear comprising gearwheel switch stages, and switch couplings
WO1994021941A1 (en) * 1993-03-19 1994-09-29 Zf Friedrichshafen Ag Continuously variable transmission with wide transmission ratio range
DE4323358C1 (en) * 1993-05-28 1994-05-26 Jarchow Friedrich Five-shaft gearwheel planetary gear - has parallel arranged steplessly adjustable hydrostatic gear, with gearwheel switch stages and switch couplings
DE4443267A1 (en) * 1994-12-05 1996-06-13 Claas Ohg Powershift transmission with 5-shaft epicyclic gear
US5868640A (en) * 1996-12-04 1999-02-09 Caterpillar Inc. Hydromechanical transmission having four members and two planetaries
DE19843069A1 (en) * 1997-09-20 1999-05-06 Michael Meyerle Continuously variable transmission, especially with power branching
DE10113177C1 (en) * 2001-03-19 2002-04-04 Friedrich Jarchow Planetary cogwheel gearing, for continuously variable hydrostatic transmission, has drive shaft, coupling shaft, high-speed and low-speed coupling shafts and connection shaft for variable hydrostatic drive
DE10319252A1 (en) * 2003-04-28 2004-11-18 Claas Industrietechnik Gmbh Infinitely variable torque division gearbox for agricultural tractors and utility vehicles has a continuously adjustable ratio of speeds, two engaging/disengaging clutches and a driven shaft
EP1541898A2 (en) 2003-12-12 2005-06-15 CNH Italia S.p.A. CVT transmission for motor vehicles, in particular for tractors
WO2006042434A1 (en) * 2004-10-20 2006-04-27 Markus Liebherr International Ag Power-branched transmission and method for the operation of such a transmission
EP1855029A2 (en) * 2006-05-11 2007-11-14 CNH Italia S.p.A. CVT hydromechanical drive, in particular for a farm tractor.
DE102008040446A1 (en) * 2008-07-16 2010-01-21 Zf Friedrichshafen Ag Transmission device for vehicle, has variator spaciously arranged between planetary gear unit and manual gear unit, where orientation of pivot axis of variator corresponds to orientation of vehicle vertical axis
DE102008040450A1 (en) * 2008-07-16 2010-01-21 Zf Friedrichshafen Ag Variable transmission device for vehicle, has variator, planetary gear unit, and manual gear unit, which are arranged in transmission housing
DE102008040441A1 (en) * 2008-07-16 2010-02-18 Zf Friedrichshafen Ag Transmission device for use in vehicle power train, has planetary gear unit and variator whose shafts are connected to transmission output via switching elements for illustrating transmission regions, respectively

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