DE102011084623A1 - Power takeoff gear box e.g. four-level power takeoff gear box, for tractor, has spur gear stages for switching transmission stages, where each gear stage comprises gear wheels arranged on power-takeoff axles and shaft axle - Google Patents

Power takeoff gear box e.g. four-level power takeoff gear box, for tractor, has spur gear stages for switching transmission stages, where each gear stage comprises gear wheels arranged on power-takeoff axles and shaft axle

Info

Publication number
DE102011084623A1
DE102011084623A1 DE102011084623A DE102011084623A DE102011084623A1 DE 102011084623 A1 DE102011084623 A1 DE 102011084623A1 DE 102011084623 A DE102011084623 A DE 102011084623A DE 102011084623 A DE102011084623 A DE 102011084623A DE 102011084623 A1 DE102011084623 A1 DE 102011084623A1
Authority
DE
Germany
Prior art keywords
pto
gear
input shaft
shaft
stages
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
DE102011084623A
Other languages
German (de)
Inventor
Stefan Igl
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 DE102011084623A priority Critical patent/DE102011084623A1/en
Publication of DE102011084623A1 publication Critical patent/DE102011084623A1/en
Pending legal-status Critical Current

Links

Images

Classifications

    • BPERFORMING OPERATIONS; TRANSPORTING
    • B60VEHICLES IN GENERAL
    • B60KARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00Arrangement or mounting of transmissions in vehicles
    • B60K17/28Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or type of power take-off
    • 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
    • F16H3/00Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/006Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
    • 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
    • F16H3/00Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/089Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B60VEHICLES IN GENERAL
    • B60YINDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2200/00Type of vehicle
    • B60Y2200/20Off-Road Vehicles
    • B60Y2200/22Agricultural vehicles
    • 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
    • F16H3/00Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H2003/0807Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with gear ratios in which the power is transferred by axially coupling idle gears
    • 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
    • F16H2200/003Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0043Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds

Abstract

The gear box has input shafts (2, 3) and a drive shaft (1) coaxially mounted on an input shaft axle. A power takeoff (PTO) shaft is arranged offset from the input shaft axle. Spur gear stages (6, 7, 8, 9) are provided for switching of read-switchable transmission stages, where each spur gear stage comprises gear wheels (10-17) arranged on PTO axles and the input shaft axle. One of the input shafts is designed as a sleeve shaft in which the other input shaft is fed, and a dual clutch device (4) is arranged between the input shaft and the drive shaft. An independent claim is also included for an agricultural commercial vehicle.

Description

  • The present invention relates to a power take-off, which is provided in agricultural and / or building economics usable motor vehicles to make the torque of a drive motor of the vehicle at a usually exposed to the vehicle PTO with a desired speed can be tapped. The PTO shaft exposed on the vehicle usually has a serrated cross-sectional shape, so that a propshaft for connecting the power take-off shaft to a drive shaft of an agricultural implement such as a tedder, a loader wagon, or a fertilizer spreader can be connected substantially by being pushed onto the PTO shaft. The PTO is usually coupled in the prior art directly to the engine, so that the rotational speed of the PTO directly correlates with the rotational speed of the engine. By means of wheelsets, the actual rotational speed of the engine output shaft to be expected during operation of the equipment can be adapted to the desired rotational speed of the power take-off shaft.
  • In the prior art PTO are known, which are designed as a two-stage gear and which can be switched without load. Often, this switching is done manually. However, it is not possible to switch the power take-off under load. Solutions are known from the prior art, which reduce disadvantages due to the dependence of the PTO shaft on the engine rotational speed. So revealed the DE 26 47 141 A1 a drive for the PTO of an agriculturally usable vehicle, wherein the PTO shaft with both an output shaft for the vehicle drive, ie a transmission to the switching of the driving gears of the commercial vehicle, and with a directly coupled to the engine output shaft is coupled. Accordingly, it is possible to operate the PTO both with engine-dependent speed, as well as with path-dependent speed. For engine-dependent operation two wheelsets are provided. In this case, the directly coupled to the engine shaft carries two fixed wheels, which can be brought into engagement with slidably mounted on an input shaft of the PTO spur gears spur gears when these gears are brought with a dog clutch to the height of the associated fixed wheel. The input shaft is in turn connectable via a multi-plate clutch of the power take-off with the PTO shaft, wherein the input shaft is provided coaxially with said PTO. The dog clutch to the input or disengagement of the spur gears of the two wheelsets can only be operated without load.
  • An alternative solution is from the DE 20 51 556 C2 in which one, designed as a hollow shaft input shaft of the drive gear passing through and directly connected to the output shaft of the motor input shaft of the PTO is connected to a dual clutch, which carries at opposite ends gears of two different spur gears. The PTO shaft extends axially parallel to the drive shaft and a countershaft whose two fixed gears mesh with the input shaft associated with and coupled via the dual clutch gears. One of the fixed gears of the countershaft meshes with a idler gear associated with the PTO shaft. By pressing the dual-clutch transmission, one of the gears associated with the input shaft can be respectively coupled with the latter and the torque can be transmitted via the output constant between the PTO shaft of the countershaft.
  • The previously known PTO can indeed be switched under load. But it is a two-stage gearbox. In particular, the consumption-optimized operation of agricultural vehicles with power take-off makes it necessary to match the voltage applied to the PTO shaft speed in an improved manner to an economical operation of the drive motor resulting speed. Certain agricultural implements that are driven by the PTO require different speed ranges.
  • In general, the rated speeds of known PTO are now standardized. Adjusted to the different devices to be operated with such PTOs, PTOs with different rated speeds are available on the market. Typically, these rated speeds are 540 rpm, 750 rpm, 1000 rpm and 1400 rpm. Accordingly, the PTO transmissions the gear ratios 450, 750, 1000 or 1400 assigned. At these standard gear ratios, the corresponding nominal PTO speed is not in the range of the rated engine speed (maximum power). PTO gearboxes with so-called economy gear ratios have been available for some time (eg 540E, 750E, 1000E or 1400E). At these PTOs, the rated speeds are already reached at reduced engine speed, usually in the vicinity of the highest engine torque at about 1400 to 1600 rev / min. Devices with a low power consumption can thus be operated fuel-efficient.
  • Depending on the particular work situations, different transmission stages are expediently used for the operation of a device. For example, it is often the case that a device connected to the PTO requires little power at the beginning of the operation and therefore Translation stage of the PTO can be operated. If, in the further course of work, a higher performance must be called up, it is necessary to switch to a standard translation stage. For the ideal coordination of the gear ratio to the respective requirements, a frequent switching between individual gear ratios is required today.
  • In non-load switchable PTO, there is the problem that the operator of the agricultural equipment, d. H. the tractor operator must set the appropriate gear ratio on the PTO before starting a job. If this is a translation stage that is favorable under full load, then there is the problem that at the beginning of the work process, ie. H. In the partial load range, resulting in an inappropriate translation with low torque, which is disadvantageous both for the operation of agricultural equipment, as well as for the load of the engine. It is not possible to change the gear ratio under load during the operation.
  • The present invention is based on the problem to provide an improved power take-off gear, which satisfies the practical requirements described above in an improved manner.
  • To solve this problem, the present invention provides a power take-off with the features of claim 1. This PTO has a drive shaft and a first and second input shaft, which are provided coaxially with each other on an input shaft axis. The drive shaft may be formed by both the output shaft of the engine, but it is also possible that this is an output constant coupled to this output shaft drive shaft of the PTO transmission. Furthermore, it is possible to connect the drive shaft with a shaft of a transmission unit of an agricultural vehicle. Downstream of the drive shaft and coaxial with this, the two input shafts are provided in extension of the drive shaft.
  • It is preferable to provide one of the input shafts as a hollow shaft, in which the other input shaft is guided. Usually, accordingly, the second input shaft is a solid shaft. In particular, however, it may alternatively also be provided to provide both input shafts as solid shafts arranged axially one after the other.
  • Furthermore, an offset from the input shaft axis arranged PTO shaft is provided. As the input shaft axis that axis is considered on which the drive shaft and the two input shafts are provided. The PTO shaft is offset and arranged parallel to the input shaft axis. The PTO usually towers on one side a gear housing, so about this z. B. by means of a propeller shaft, the connection can be made to an agricultural device.
  • The PTO has at least three spur gears that define individual gear ratios (gears). Each spur gear includes a set of two off-axis arranged, meshed with each other gears. In particular, one of the gears input shaft side and the other PTO shaft side is provided. The diameter of the two gears of a spur gear determines the translation of the speed between the drive shaft and PTO. At a high gear ratio, the PTO shaft speed is lowered more than a low gear ratio compared to the input shaft input speed. Inversely, a small translation level indicates a high translation and a large translation level indicates a lower translation.
  • With gear ratio in particular the rated speed of the PTO shaft is designated. If z. B. input shaft side, a speed of 4000 U / min (rated motor speed) is applied, is at a standard gear ratio 540 at the PTO a speed of 540 U / min. A standard gear ratio of 1000 indicates a nominal PTO speed of 1000 rpm at full load engine speed. The smaller of these two translation stages is the translation stage 540, which has the higher ratio in comparison. The terminology of small and large gear ratios applies only to PTO gearboxes which are uniformly equipped with standard or economy gear ratios only.
  • The two gears of a spur gear can be mounted in different ways on the respective shafts. For a compact design, however, it is preferred to provide one of the gears as a fixed gear and the other of the gears as idler gear. It is preferred according to an alternative development that both gears of a spur gear to perform as a fixed wheels.
  • The translation stages are also referred to as gears, which are consecutively numbered beginning with the smallest translation stage. This results in even and odd gear ratios (gears). In a PTO, with three spur gears accordingly three gears are provided. In particular, it is provided that the gears of the power take-off in the numerical order are full load switchable. This means, in particular, that it is possible to change between two consecutive gear ratios under load.
  • The PTO invention has only three spur gears, each comprising two gears, one of which is assigned to the input shaft axis and the other of the output shaft axis. Furthermore, the PTO transmission according to the invention comes with waves that are arranged solely on these two axes, so that the power take-off can be made relatively compact.
  • According to a preferred embodiment, the power take-off according to the invention has four switchable under load gear ratios. To achieve these four under load switchable translation stages regularly two double switching devices are sufficient. This preferred embodiment allows at least the switching of two in each case in numerical order successively provided aisles.
  • In a compact PTO this power shift of four gear ratios is preferably achieved in that one of the input shafts as a hollow shaft and the other input shaft is provided as this enforcing arranged solid shaft. The two input shafts are drivingly connected to a dual clutch device disposed between the input shafts and the drive shaft. In this case, the wheelsets that are associated with the straight gear ratios associated with an input shaft and the odd gear ratios assigned wheelsets of the other input shaft. Accordingly, in the upshift or downshift the next gear can already be pre-set and switched by simultaneous disengagement of the coupling element associated with the old gear and engagement of the other clutch element of the dual clutch device associated with the new gear. The dual clutch device is not only designed so that the drive shaft can be selectively coupled to the first or second input shaft. Rather, the dual clutch device is also preferably provided for starting the connected to the PTO agricultural implement. To start, d. H. Startup of this device preferably both coupling elements of the coupling device are closed at the same time, so that the friction torque is transmitted to start the device via both coupling elements until the PTO rotational speed in the selected gear has the desired speed of rotation, d. H. the PTO is synchronized in the selected gear ratio. At this moment, the supportively connected coupling element is disengaged, so that the load flow is transmitted solely through the components of the transmission which are intended to be involved in the respective power stage in the respective gear stage.
  • The design of the dual clutch device as a starting clutch makes it possible to form the PTO without separate starting clutch for the connected agricultural equipment. The design requires, however, a corresponding dimensioning of the double clutch and a cooling provided for this purpose. Accordingly, the load flow required for starting is divided into two different coupling elements, so that each individual coupling element must be designed in a reduced manner for passing the high starting load flow. The friction surface of two coupling elements used in this case corresponds approximately to the friction surface of a starting clutch known from the prior art. In a corresponding manner, coupling devices are also designed with regard to the lubricant supply in order to derive the necessary waste heat from the friction work when starting up. When starting the friction work on the two simultaneously switched coupling elements of the dual clutch device is divided in a predetermined manner. The division does not necessarily have to be made in half. Rather, space-related, dimensional deviations of the friction surface of the individual coupling elements and / or their lubrication can be taken into account in the distribution of the load flow to the two coupling elements.
  • According to a preferred refinement, the power take-off gearbox according to the invention has a first double-shifting device provided between two spur gear stages, by means of which idler gears assigned to the straight gears can be coupled to the one input shaft or the power take-off shaft. The odd gears associated idler gears can be coupled via a second double switching device to the other input shaft or the PTO. In this case, the two double switching devices may be jointly assigned to the power take-off shaft axis or jointly to the input shaft axis. Alternatively, one of the double switching devices of the PTO axis and the other of the input shaft axis may be assigned. Accordingly, loose wheels can be assigned to the two input shafts or solely to the PTO shaft. If idler gears are to be assigned for reasons of space, the input shaft axis and the PTO shaft, these are uniform in a sub-transmission either the PTO shaft or the input shaft axis assigned. In this case, a partial transmission in each case contains the second spur gear stages assigned to the straight gears, another partial transmission the spur gear stages associated with the odd gears. Each of the partial transmission has in the preferred embodiment of one of said double switching devices.
  • The four power shift PTO providing PTO offers the user or the tractor driver the ability between the Gears 1, 2, 3 and 4 to be able to switch under load, in which - as previously described - by Voreinlegen the gear, ie coupling the gear stage associated spur gear with its input shaft and the PTO with disengaged coupling element - when switching only the new Gear stage assigned coupling element engaged and at the same time the old gear ratio associated coupling element is disengaged. In this case, the power take-off gear according to the invention may have a control unit, which determines due to the driving style or the operation of the user, possibly due to the evaluation of constantly acquired measurement data of the driving situation, which gear stage the user intends to turn next. By this control unit, the double switching device is controlled such that in the respective part transmissions already always the gear required by the tractorist is preset.
  • The dual clutch device and / or the double shift device are preferably to be switched hydraulically, wherein the actuator to the switching can be done mechanically or hydraulically, in particular electro-hydraulically. A mechanical solution is given for example by a Seilzugaktuatorik. In view of improved handling, however, a hydraulic, in particular an electro-hydraulic actuator, is preferred, in which by switching an electric switch hydraulically acting on the switching device. Preferably, the double switching device is designed as a shift sleeve, which is arranged axially displaceably on the shaft between the spur gear. This shift sleeve may also include synchronization means for synchronizing the gears with the shaft.
  • According to an alternative preferred development, it is provided that the PTO transmission includes two individual coupling devices. In that case, an input-shaft-side coupling device should couple the first input shaft to the drive shaft. A second input shaft-side coupling device preferably couples the second input shaft via the first input shaft to the drive shaft. In this development, the input shafts are regularly formed as solid shafts and coaxial with each other, but provided in the axial direction one behind the other. Between the first countershaft and the second countershaft, a first PTO-side coupling device and between the second countershaft and the PTO shaft, a second PTO-side coupling device is provided. About the coupling means each provided adjacent to the coupling means shafts are coupled together.
  • The individual coupling devices can be designed as non-positive or positive coupling devices. In particular, it is advantageous to provide the individual coupling devices as non-positive coupling elements, in particular as multi-plate clutches. All four coupling devices are preferably designed as starting clutches, so that this alternative development of the PTO transmission according to the invention does not require a separate starting clutch.
  • In the alternative embodiment, a first spur gear has fixed gears on the drive shaft and the first countershaft. The second spur gear has fixed gears on the first input shaft and the second countershaft. The third spur gear finally has fixed gears on the second input shaft and the PTO. By appropriate switching of the coupling devices provided between the individual shafts different gears can be realized. Accordingly, the transmission according to the invention is in any case simply shaped with regard to the mounting of the individual gears of the gear stages. All provided for switching the PTO gear wheels are fixed wheels of the corresponding wheels.
  • In general, the PTO can be provided with different gear ratios. Particularly useful it is a PTO with the standard speeds, d. H. to equip the standard gear ratios, as well as the economy gear ratios. Preferably, the first gear is associated with a standard gear stage 450 or an economy gear stage 450E. The second gear is preferably associated with the standard translation stage 750 or the economy translation stage 750E. The third gear is advantageously associated with the standard gear stage 1000 or the economy gear stage 1000E, and the fourth gear is advantageously associated with the standard gear stage 1400 or the economy gear stage 1400E. Also, partially standard and partially economy gear ratios may be realized in the transmission.
  • In particular, it is preferred that four-speed transmissions with the standard gear ratios 450, 750, 1000, 1400 be provided in the order of first, second, third, fourth gear. As a result, a load switchability between the following translation stages is possible.
  • In order to solve the aforementioned problem, the present invention further provides, according to its independent aspect, an agricultural utility vehicle having the features of claim 11. According to this, the present invention proposes an agricultural utility vehicle, in particular a tractor, with a motor, the drive shaft of which is coupled to a gear before. The agricultural utility vehicle is equipped with the PTO transmission according to the invention. In particular, the drive shaft of the PTO transmission is formed by the output shaft of the engine or at least coupled thereto. The coupling can follow via an output constant part. The aforementioned transmission is the transmission to the switching of the gear stages for the forward and backward movement of the agricultural utility vehicle.
  • Further details and advantages of the present invention will become apparent from the following description of three embodiments in conjunction with the drawings. In these show:
  • 1 a wheel diagram of a first embodiment of a four-stage power take-off,
  • 2 a wheel diagram of a second embodiment of a four-stage power take-off,
  • 3 a gear diagram of another embodiment of a three-stage power take-off, with four powershift gears / ratio stages.
  • In 1 is an embodiment of a designed as a double clutch transmission PTO shown. Between a drive shaft 1 and two coaxially provided input shafts 2 . 3 is a double clutch device 4 provided, which is the first input shaft 2 with the drive shaft 1 or the second input shaft 3 with the drive shaft 1 about the switching of two coupling elements 4.1 . 4.2 can couple. With the first coupling element 4.1 can be the first input shaft 2 with the drive shaft 1 coupled with the second coupling element 4.2 can be the second input shaft 3 with the drive shaft 1 be coupled. The drive shaft 1 lies together with the input shafts 2 . 3 on an input shaft axis. Axle offset and parallel to it extends a PTO shaft of a PTO 5 , One end of the PTO 5 protrudes from a housing not shown. At this end of the PTO 5 In general, a toothed cross-sectional shape is provided, over which the drive shaft of an agricultural device rotatably connected to the PTO 5 can be connected.
  • Both coupling elements 4.1 . 4.2 the double clutch device 4 are designed as non-positive coupling elements, in this case multi-plate clutches. Both coupling elements 4.1 and 4.2 can be simultaneously engaged such that the dual clutch device 4 can be used. When starting accordingly both coupling elements 4.1 and 4.2 Enables the load flow through both coupling elements on the two input shafts 2 . 3 to transmit until at the selected gear stage, the power flow transmitting input shaft has reached its target speed. At this time, the other coupling element is disengaged.
  • The first input shaft 2 passes through the second input shaft designed as a hollow shaft 3 and towers over the second input shaft 3 in the axial direction on the double clutch device 4 opposite side. At the input shafts 2 . 3 and the PTO 5 are as spur gears 6 . 7 . 8th . 9 designated wheelsets of gear pairs 10 / 14 . 11 / 15 . 12 / 16 . 13 / 17 intended. Each of the spur gears 6 . 7 . 8th . 9 contains a wheelset 10 / 14 . 11 / 15 . 12 / 16 . 13 / 17 whose gears mesh with each other. Drive shaft side started the spur gear as the first spur gear 6 , second spur gear 7 , third spur gear 8th and fourth spur gear stage 9 designated. The first and second spur gears 6 . 7 are the second input shaft 3 assigned. The third and fourth spur gears 8th . 9 are the first input shaft 2 assigned.
  • The first spur gear stage 6 is a first fixed bike 10 the second input shaft 3 and a first idler gear 14 the PTO 5 assigned. The second spur gear 7 has a second fixed wheel 11 the second input shaft and a second idler gear 15 the PTO 5 , The third spur gear stage 8th has a third fixed wheel 12 , which is connected to the first input shaft 2 is provided, and a third loose wheel 16 the PTO 5 , A fourth fixed wheel 13 the first input shaft 2 is engaged with a fourth idler gear 17 and forms the fourth spur gear stage 9 ,
  • The first and second spur gears 6 . 7 are a first partial transmission 18 , the third and fourth spur gear 8th . 9 a second partial transmission 19 assigned. Both partial transmissions 18 . 19 can via the dual clutch device 4 with the drive shaft 1 be coupled. PTO shaft side is in each case between the first and second spur gear 6 . 7 and the third and fourth spur gears 8th . 9 a double switching device 20 . 20 ' intended. The one of the double switching devices 20 is designed as an axially movable shift sleeve with synchronization elements, which optionally the first idler gear 14 the first spur gear 6 with the PTO 5 or the second idler gear 15 the second spur gear 7 with the PTO 5 coupled. In a middle position of the shift sleeve 20 is not one of the two spur gears 6 . 7 with the PTO 5 coupled. Likewise, between the third and fourth spur gear 8th . 9 PTO shaft side a double switching device 20 ' , provided in this case an axially displaceable sliding sleeve with synchronization elements. This optionally couples the third spur gear 8th or the fourth spur gear stage 9 with the PTO 5 ,
  • In a coupled spur gear is a transmission and translation of the speed of the input shaft 2 . 3 on the PTO 5 possible. A coupled spur gear is referred to as a preset gear or preset gear ratio. The ratio of the input speed to an output speed depends on the ratio of the wheel diameter of the wheelsets of the spur gears 6 . 7 . 8th . 9 from. The first idler gear 14 has the largest diameter in relation to the other loose wheels 15 . 16 . 17 such that the coupling of the first spur gear provides the highest ratio. However, there is also the possibility to form the highest gear in another spur gear. The translation stage at the highest ratio is inverse to the translation then the smallest gear ratio, because this is defined by the rated speed of the PTO. The individual translation stages are provided with increasing numerical value with a consecutive numbering (1), (2), (3), (4). The smallest gear ratio or the smallest gear is accordingly in the embodiment of the first spur gear 6 formed first course (1).
  • Since the gears one (1) and two (2) the first partial transmission 18 assigned and the gears are two (2) and four (4) associated with the second partial transmission, the embodiment according to 1 when switching in the numerical order under load are switched.
  • In 2 a second embodiment of a four-stage PTO transmission is shown. Between a drive shaft 101 and two input shafts 102 . 103 Coaxially provided on a common input shaft axis is a double clutch device 104 intended. The double clutch device 104 contains a first coupling element 104.1 and a second coupling element 104.2 , wherein the first coupling element 104.1 the first input shaft 102 with the drive shaft 101 couples and the second coupling element 104.2 the second input shaft 103 with the drive shaft 101 coupled.
  • Analogous to the embodiment according to 1 are four spur gears 106 . 107 . 108 . 109 provided with different translations. The first spur gear stage 106 is located closest to the drive shaft. Axial following are the second, third and fourth spur gear 107 . 108 . 109 intended. The second input shaft 103 is designed as a hollow shaft, in which the first input shaft 102 is performed as a full wave. Input shaft side is in each case between the first and second spur gear 106 . 107 , as well as the third and fourth spur gear 108 . 109 one double switching device each 120 ' . 120 acting as a sliding sleeve 120 ' . 120 is executed, provided.
  • As with the in 1 embodiment shown is about the shift sleeve 120 ' the second input shaft 103 over the first and second spur gear 106 . 107 with the PTO 105 coupled. By actuating the other shift sleeve with synchronization elements 120 becomes the first input shaft 102 with the PTO 105 over the third spur gear 108 or the fourth spur gear stage 109 coupled. The third spur gear stage 108 defines a first gear (1), the fourth spur gear 109 a third gear (3), the second spur gear 107 a second gear (2) and the first spur gear 106 defines a fourth gear (4). The gears or gear stages one (1) and three (3) are the first input shaft 102 and a first partial transmission 118 assigned. The gears two (2) and four (4) are designed as a hollow shaft second input shaft 103 and a second partial transmission 119 assigned.
  • One each spur gear stage 106 . 107 . 108 . 109 contains exactly two gears 110 / 114 . 111 / 115 . 112 / 116 . 113 / 117 , The assignment of the fixed or loose wheels is compared to the embodiment according to 1 exactly reversed. In 1 the PTO 5 assigned loose wheels 14 . 15 . 16 . 17 are in the embodiment after 2 loose wheels 111 . 115 . 116 and 117 assigned to the input shaft axis. Here is the first idler gear 114 and the second idler gear 115 the second input shaft 103 whereas the third idler gear is assigned 116 and the fourth idler gear 117 the first input shaft 102 assigned. The first fixed wheel 110 as well as the first loose wheel 114 is the first spur gear 106 , the second fixed wheel 111 and the second idler gear 115 is the second spur gear 107 , the third festival bike 112 and the third idler gear 116 is the third spur gear 108 and the fourth fixed wheel 113 and the fourth idler gear 117 is the fourth spur gear stage 109 assigned.
  • The switching of the gears or gear ratios is carried out in the same manner as previously with reference to the embodiment according to 1 has been described.
  • In 3 a further embodiment of a PTO transmission is shown. A drive shaft 201 , a first input shaft 202 and a second input shaft 203 are coaxial with each other on a common input shaft axis. Axle offset parallel to it on a PTO axle is a PTO 205 , a first countershaft 221 and a second countershaft 222 intended. The input shafts 202 . 203 and the counter waves 221 . 222 are designed as full waves. The PTO transmission includes four clutch devices 223 . 224 . 225 . 226 which are arranged between different waves and can couple adjacent waves. The first coupling device 223 is input shaft side between the drive shaft 201 and the first input shaft 202 arranged. The second coupling device 224 is between the first input shaft 202 and the second input shaft 203 arranged. The third coupling device 225 is PTO side between the first countershaft 221 and the second countershaft 222 and the fourth clutch device 226 is between the second countershaft 222 and the PTO 205 intended.
  • The PTO has four gears that through three spur gears 206 . 207 . 208 are defined. The spur gears 206 . 207 . 208 each contain a wheelset 210 / 211 . 212 / 213 . 227 / 228 from two gears, all of which are designed as fixed wheels. One of the gears 210 . 212 . 227 each spur gear stage 206 . 207 . 208 lies respectively on the input shaft axis, the other gear 211 . 213 . 228 is provided on the PTO axis. Following in the direction of power flow from the drive side to the dispensing side one after the other is the first spur gear stage 206 , the second spur gear 207 and the third spur gear 208 intended. The first spur gear includes a first and second fixed gear 210 . 211 , the second spur gear 207 contains a third and fourth fixed wheel 212 . 213 , the third spur gear 208 contains a fifth and sixth fixed wheel 227 . 228 , The fixed wheels 210 . 211 the first spur gear 206 lie on the drive shaft 201 or on the first countershaft 221 , The fixed wheels 212 . 213 the second spur gear 207 are on the first input shaft 202 and the second countershaft 222 intended. The fixed wheels 227 . 228 the third spur gear stage 208 are corresponding to the second input shaft 203 and the PTO 205 intended.
  • The three spur gears define analogous to the embodiments of the 1 and 2 Translation stages. In this case, four gears with three gear ratios are to be realized.
  • When engaged first gear (1) is the first coupling device 223 and the second clutch device 224 engaged and third and fourth clutch means 225 . 226 are disengaged. This is the drive shaft 201 over the first input shaft 202 , the second input shaft 203 and the third spur gear 208 with the PTO 205 coupled. In the second gear (2), the power flow from the drive shaft 101 through the first coupling device 223 to the first input shaft 202 , from there via the second spur gear 207 on the PTO axis. The power flow is from the second countershaft 222 via the fourth coupling device 226 on the PTO 205 transfer. In the third gear (3), the power flow takes place from the drive shaft 201 over their fixed wheel 210 and on the second fixed wheel 211 to the first countershaft 221 , About the third and fourth clutch device 225 . 226 and the second countershaft 222 the power flow is finally on the PTO 205 transfer. In the second gear (2) are second and third clutch means 224 . 225 disengaged. In the third gear (3) are the first and second clutch means 223 . 224 disengaged. In addition, via an intelligent circuit of the coupling elements 223 to 226 a fourth gear can be realized. In the fourth gear, the first and fourth clutch means 223 . 226 disengaged (open). The coupling device 224 and 225 are indented (closed). Thus, a fourth gear with only three gear ratios can be realized.
  • When changing from the first gear (1) to the second gear (2) is simultaneously the second clutch device 224 disengaged and the fourth coupling device 226 indented. If, however, switched from the first gear to the third gear under load, there is a simultaneous disengagement of the first and second clutch devices 223 . 224 with simultaneous engagement of the third and fourth coupling devices 225 . 226 , Correspondingly, under load from the second gear (2) in the first or the third gear (1), (3) can be switched or from the third gear (3) to the second gear (2) or another gear deeper be switched directly into the first gear (1). Analogously, a change to the fourth gear from each of the described gears 1, 2, 3 is possible. A change from the fourth gear in one of the gears 1, 2, 3 is possible by appropriate coupling circuit. When changing from the fourth gear to the first gear (1) at the same time the coupling element 223 disengaged and 225 indented. By the engagement of coupling elements 223 and 225 is a self-locking PTO shaft created. Thus, one obtains a PTO brake without additional actuators and / or components. All circuits can be carried out under load by simultaneously driving the coupling device active in the old gear while at the same time closing the coupling device (s) transmitting the load in the target gear.
  • LIST OF REFERENCE NUMBERS
  • 1, 101, 201
    drive shaft
    2, 102, 202
    first input shaft
    3, 103, 203
    second input shaft
    4, 104
    Dual clutch assembly
    4.1, 104.1
    first coupling element
    4.2, 104.2
    second coupling element
    5, 105, 205
    PTO
    6, 106, 206
    first spur gear
    7, 107, 207
    second spur gear
    8, 108, 208
    third spur gear
    9, 109
    fourth spur gear
    10, 110, 210
    first fixed bike
    11, 111, 211
    second fixed wheel
    12, 112, 212
    third fixed wheel
    13, 113, 213
    fourth fixed wheel
    14, 114
    first idler gear
    15, 115
    second idler gear
    16, 116
    third idler gear
    17, 117
    fourth idler gear
    18, 118
    first partial transmission
    19, 119
    second partial transmission
    20, 20 ', 120, 120'
    Double switching device (sliding sleeve)
    221
    first countershaft
    222
    second countershaft
    223
    first clutch device (first input shaft-side clutch device)
    224
    second clutch device (second input shaft-side clutch device)
    225
    third clutch device (first PTO-side clutch device)
    226
    fourth clutch device (second PTO-side clutch device)
    227
    fifth fixed wheel
    228
    sixth fixed wheel
  • QUOTES INCLUDE IN THE DESCRIPTION
  • This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.
  • Cited patent literature
    • DE 2647141 A1 [0002]
    • DE 2051556 C2 [0003]

Claims (11)

  1. PTO transmission with a drive shaft ( 1 . 101 . 201 ), a first and second input shaft ( 2 . 102 . 202 . 3 . 103 . 203 ), wherein the drive shaft ( 1 . 101 . 201 ) and the two input shafts ( 2 . 102 . 202 . 3 . 103 . 203 ) are provided coaxially on an input shaft axis, a PTO ( 5 . 105 . 205 ) arranged on a PTO axis provided offset from the input shaft axis and at least three spur gear stages (FIG. 6 . 106 . 206 . 7 . 107 . 207 . 8th . 108 . 208 . 9 . 109 ), each of which is arranged on the input shaft axis and on the PTO axis gear ( 10 . 110 . 210 . 11 . 111 . 211 . 12 . 112 . 212 . 13 . 113 . 213 . 14 . 114 . 15 . 115 . 16 . 116 . 17 . 117 . 227 . 228 ).
  2. PTO transmission according to claim 1, characterized in that four powershift transmission stages are switchable.
  3. PTO transmission according to claim 1 or 2, characterized in that one of the input shafts ( 3 . 103 ) is formed as a hollow shaft and the other input shaft ( 2 . 102 ) passing through it, that between the input shafts ( 2 . 102 . 3 . 103 ) and the drive shaft ( 1 . 101 ) a dual clutch device ( 4 . 104 ) and that the even translation stages ( 8th . 9 . 106 . 107 ) assigned wheelsets ( 12 / 16 . 13 / 17 . 110 / 114 . 111 / 115 ) of an input shaft ( 2 . 103 ) and the odd translation stages ( 6 . 7 . 108 . 109 ) assigned wheelsets ( 10 / 14 . 11 / 15 . 112 / 116 . 113 / 117 ) of the other input shaft ( 3 . 102 ) assigned.
  4. PTO transmission according to claim 3, characterized by a between two spur gear stages ( 8th . 9 . 106 . 107 ) provided first double switching device ( 20 ' . 120 ' ), by which the straight gears assigned idler gears ( 16 . 17 . 114 . 115 ) to the one input shaft ( 103 ) or the PTO shaft ( 5 ) and one between two other spur gear stages ( 6 . 7 . 108 . 109 ) provided second double switching device ( 20 . 120 ), by which idler gears ( 14 . 15 . 116 . 117 ) to the other input shaft ( 102 ) or the PTO shaft ( 5 ) can be coupled.
  5. PTO transmission according to claim 1, characterized in that between the drive shaft ( 201 ) and the first input shaft ( 202 ) a first input shaft side coupling device ( 223 ) and between the first input shaft ( 202 ) and the second input shaft ( 203 ) a second input shaft side coupling device ( 224 ) is provided that coaxially on the PTO shaft axis first and second countershafts ( 221 . 222 ) are arranged, wherein between the first countershaft ( 221 ) and the second countershaft ( 222 ) a first PTO-side coupling device ( 225 ) and between the second countershaft ( 222 ) and the PTO ( 205 ) a second PTO-side coupling device ( 226 ) is provided, and that a first spur gear stage ( 206 ) with fixed wheels ( 210 . 211 ) on the drive shaft ( 201 ) and the first counter-wave ( 221 ), a second spur gear stage ( 207 ) with fixed wheels ( 212 . 213 ) on the first input shaft ( 202 ) and the second countershaft ( 222 ) and a third spur gear stage ( 208 ) with fixed wheels ( 227 . 228 ) on the second input shaft ( 203 ) and the PTO ( 205 ) intended.
  6. PTO transmission according to claim 5, characterized in that three power-shift stages are switchable.
  7. PTO transmission according to one of the preceding claims, characterized in that the first gear is associated with a transmission stage 450 or 450E.
  8. PTO transmission according to one of the preceding claims, characterized in that the second gear is associated with a transmission stage 750 or 750E.
  9. PTO transmission according to one of the preceding claims, characterized in that the third gear is associated with a transmission stage 1000 or 1000E.
  10. PTO transmission according to one of claims 1 to 4, characterized in that the fourth gear is assigned to a translation stage 1400 or 1400E.
  11. Agricultural commercial vehicle with a motor whose output shaft is coupled to a transmission, characterized by a PTO transmission according to one of the preceding claims, whose drive shaft is the output shaft of the motor or is coupled thereto.
DE102011084623A 2011-10-17 2011-10-17 Power takeoff gear box e.g. four-level power takeoff gear box, for tractor, has spur gear stages for switching transmission stages, where each gear stage comprises gear wheels arranged on power-takeoff axles and shaft axle Pending DE102011084623A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE102011084623A DE102011084623A1 (en) 2011-10-17 2011-10-17 Power takeoff gear box e.g. four-level power takeoff gear box, for tractor, has spur gear stages for switching transmission stages, where each gear stage comprises gear wheels arranged on power-takeoff axles and shaft axle

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102011084623A DE102011084623A1 (en) 2011-10-17 2011-10-17 Power takeoff gear box e.g. four-level power takeoff gear box, for tractor, has spur gear stages for switching transmission stages, where each gear stage comprises gear wheels arranged on power-takeoff axles and shaft axle

Publications (1)

Publication Number Publication Date
DE102011084623A1 true DE102011084623A1 (en) 2013-04-18

Family

ID=47990577

Family Applications (1)

Application Number Title Priority Date Filing Date
DE102011084623A Pending DE102011084623A1 (en) 2011-10-17 2011-10-17 Power takeoff gear box e.g. four-level power takeoff gear box, for tractor, has spur gear stages for switching transmission stages, where each gear stage comprises gear wheels arranged on power-takeoff axles and shaft axle

Country Status (1)

Country Link
DE (1) DE102011084623A1 (en)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013217646A1 (en) 2013-09-04 2015-03-05 Zf Friedrichshafen Ag Power take-off gear for a motor vehicle
DE102013217644A1 (en) 2013-09-04 2015-03-05 Zf Friedrichshafen Ag Power take-off gear for a motor vehicle
DE102013217643A1 (en) 2013-09-04 2015-03-05 Zf Friedrichshafen Ag Power take-off gear for a motor vehicle
DE102013217645A1 (en) 2013-09-04 2015-03-05 Zf Friedrichshafen Ag Power take-off gear for a motor vehicle
DE102013110316A1 (en) 2013-09-19 2015-03-19 Claas Tractor Sas PTO transmission for an agricultural machine
DE102013110315A1 (en) 2013-09-19 2015-03-19 Claas Tractor Sas Agricultural working machine
DE102014203352A1 (en) 2014-02-25 2015-08-27 Zf Friedrichshafen Ag Pto
DE102015212047A1 (en) 2015-04-20 2016-10-20 Zf Friedrichshafen Ag Power take-off gearbox and agricultural working machine
EP3085567A2 (en) 2015-04-20 2016-10-26 ZF Friedrichshafen AG Auxiliary output transmission and agricultural working machine
WO2017201359A1 (en) * 2016-05-19 2017-11-23 Dana Limited Planetary powertrain configurations with a ball variator continuously variable transmission used as a powersplit
EP3279511A1 (en) * 2016-08-03 2018-02-07 CNH Industrial America LLC Transmission system for a work vehicle
DE102016220130A1 (en) 2016-10-14 2018-04-19 Deere & Company Pto
EP3543058A1 (en) 2018-03-22 2019-09-25 Deere & Company Power take-off shaft transmission

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1223264B (en) * 1963-03-01 1966-08-18 Zahnradfabrik Friedrichshafen Gears change gearbox for motor vehicles, particularly agricultural tractors
DE1680674A1 (en) * 1965-12-07 1970-06-04 Fendt & Co Xaver od driving device for side shoots on agricultural tractors. like.
DE2647141A1 (en) 1976-10-19 1978-04-20 Fendt & Co Xaver Take=off shaft drive for agricultural vehicles - has friction clutch at point behind step=up stage in power flow for both types of drive
DE2051556C2 (en) 1970-10-21 1983-02-03 Kloeckner-Humboldt-Deutz Ag, 5000 Koeln, De Gearbox for agricultural and earthmoving vehicles - has drive shaft optionally connectable to non-travel drive or to power take=off shaft

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1223264B (en) * 1963-03-01 1966-08-18 Zahnradfabrik Friedrichshafen Gears change gearbox for motor vehicles, particularly agricultural tractors
DE1680674A1 (en) * 1965-12-07 1970-06-04 Fendt & Co Xaver od driving device for side shoots on agricultural tractors. like.
DE2051556C2 (en) 1970-10-21 1983-02-03 Kloeckner-Humboldt-Deutz Ag, 5000 Koeln, De Gearbox for agricultural and earthmoving vehicles - has drive shaft optionally connectable to non-travel drive or to power take=off shaft
DE2647141A1 (en) 1976-10-19 1978-04-20 Fendt & Co Xaver Take=off shaft drive for agricultural vehicles - has friction clutch at point behind step=up stage in power flow for both types of drive

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013217646A1 (en) 2013-09-04 2015-03-05 Zf Friedrichshafen Ag Power take-off gear for a motor vehicle
DE102013217644A1 (en) 2013-09-04 2015-03-05 Zf Friedrichshafen Ag Power take-off gear for a motor vehicle
DE102013217643A1 (en) 2013-09-04 2015-03-05 Zf Friedrichshafen Ag Power take-off gear for a motor vehicle
DE102013217645A1 (en) 2013-09-04 2015-03-05 Zf Friedrichshafen Ag Power take-off gear for a motor vehicle
DE102013110316A1 (en) 2013-09-19 2015-03-19 Claas Tractor Sas PTO transmission for an agricultural machine
DE102013110315A1 (en) 2013-09-19 2015-03-19 Claas Tractor Sas Agricultural working machine
EP2853431A2 (en) 2013-09-19 2015-04-01 CLAAS Tractor S.A.S. Power take-off shaft drive for an agricultural work machine
EP2857246A2 (en) 2013-09-19 2015-04-08 CLAAS Tractor S.A.S. Agricultural work machine
DE102014203352A1 (en) 2014-02-25 2015-08-27 Zf Friedrichshafen Ag Pto
DE102015212047A1 (en) 2015-04-20 2016-10-20 Zf Friedrichshafen Ag Power take-off gearbox and agricultural working machine
EP3085567A2 (en) 2015-04-20 2016-10-26 ZF Friedrichshafen AG Auxiliary output transmission and agricultural working machine
WO2017201359A1 (en) * 2016-05-19 2017-11-23 Dana Limited Planetary powertrain configurations with a ball variator continuously variable transmission used as a powersplit
EP3279511A1 (en) * 2016-08-03 2018-02-07 CNH Industrial America LLC Transmission system for a work vehicle
DE102016220130A1 (en) 2016-10-14 2018-04-19 Deere & Company Pto
EP3543058A1 (en) 2018-03-22 2019-09-25 Deere & Company Power take-off shaft transmission
DE102018204405A1 (en) 2018-03-22 2019-09-26 Deere & Company Pto

Similar Documents

Publication Publication Date Title
US9546721B2 (en) Transmission for vehicle and method for operation of a transmission
EP2681464B1 (en) Dual clutch gearbox
EP2652358B1 (en) Transmission system, as well as method for changing a transmission ratio
EP1367294B1 (en) Toothed speed-changing gearing with two parallel transmission paths
US5125282A (en) Motor vehicle two countershaft transmission change-speed gearbox and method
CN104709079B (en) Double clutch seven speed transmission equipment for hybrid vehicle
US7246536B2 (en) Dual clutch kinematic arrangements with wide span
CN100425868C (en) Double clutch transmission
DE102008009728B4 (en) Multi-speed transmission with countershaft gear arrangement
DE102004022413B4 (en) Double clutch
US7950302B2 (en) Step variable transmission for a motor vehicle
US6958028B2 (en) Ranged dual clutch transmission for motor vehicles
US7621839B2 (en) Dual clutch transmission with multiple range gearing
JP5156008B2 (en) Multi-group transmission and method for shifting in a multi-group transmission
US7155994B2 (en) Six-gear or seven-gear dual-clutch transmission
US9476461B2 (en) Electric hybrid module for a dual clutch transmission
CN101501365B (en) Output shaft speed reduction-type dual clutch transmission
US10584769B2 (en) Heavy duty transmission architecture
US7469609B2 (en) Output reduction dual clutch transmission with clutch coupler
DE102010004140B4 (en) Hybrid powertrain and dual clutch transmission
US7377191B2 (en) Double clutch transmission
EP2462365B1 (en) Method for operating a transmission device of a vehicle drivetrain
DE102005016588B9 (en) Multi-speed transmission
DE102004011142B4 (en) Transmission with two gear ratios in the slow
DE102004032498B4 (en) Double clutch

Legal Events

Date Code Title Description
R163 Identified publications notified
R012 Request for examination validly filed