FR2787852A1 - GEAR GEARBOX COMPRISING TWO PARTS COMPLETELY ALLOWED IN THE FORCE TRANSMISSION FLOW, AND METHODS OF SWITCHING SUCH A BOX - Google Patents

Abstract

In this gearbox in which an input shaft (10) is connected to an output shaft by two parts (12, 13) of the gearbox, the intermediate shaft of the part (12) of the gearbox gear is connected to the output shaft and to a constant transmission unit (C1) of the gearbox having a secondary shaft parallel to the output shaft, the intermediate shaft (15) of the other part (13 ) of the gearbox is connected by a constant transmission unit (C2) of the gearbox to another secondary shaft (16) connected to the output shaft, and pinion stages (ZIV, ZIV *, ZIII ) intended for the reduction of a gear are associated with the parts (12, 13) of the gearbox in an alternating sequence of gears. Application to gearboxes making it possible to change gears by skipping gears.

Description

The present invention relates to a gearbox with gears, in

  which an input shaft is connected to a coaxial output shaft by means of two parts of the gearbox arranged parallel to each other in the force transmission flow and which comprise gear stages respectively associated with a speed of the gearbox, due to their gear ratio, as well as the respective intermediate shafts, and in which the intermediate shafts are arranged concentrically

  between them and are connected by respective friction clutches of

  load on the input coaxial shaft, and in which the input shaft

  a first part of the gearbox can be brought, by means of the stages of associated gears, to actively cooperate with the output shaft in a drive link made to the choice, and in which a secondary shaft arranged parallel to the the input shaft can be made to cooperate with the stages of sprockets associated with the other part of the gearbox, according to a motor linkage made to the choice, and also be brought to cooperate, by means of a transmission unit. gearbox constant, with one of the other shafts coaxial with each other, according to a permanent drive link, and in particular in which the output shaft is connected by a direct drive clutch that can be engaged and disengaged, for the setting a forward gearing speed of the gearbox to the secondary shaft of the first part of the gearbox

  speeds, and also concerns gearboxes.

  The invention furthermore relates to methods for switching a

  such a gearbox with gears.

  From US Pat. No. 4,658,663 there is known a gearbox, which corresponds to the gearbox mentioned above. In this known gearbox, the gear stages for the forward gears I, III and IV as well as for the reverse speed belong to a first part of the gearbox, in which the fourth gear is arranged. as a direct drive speed - which means that by means of the engagement of a direct drive clutch, a switch can be made between the output shaft and the intermediate shaft of this first part of the gearbox

speeds.

  The other part of the gearbox contains the gears stages of forward gears II and V and an additional stage of gears, the gear ratio of which is equal to the reduction of the third gear, including the gears stage. belongs to the first part of the gearbox featuring the direct-drive clutch for the IVth speed of

  direct catch. In this first part of the gearbox, the embra-

  The gears for the third speed and the direct drive clutch for the fourth speed are combined to form a switching clutch comprising a sliding sleeve of common commutation and which can be coupled to the idle gear of the third gear stage. speed or

the output shaft.

  In the known gearbox, a common secondary shaft is used for both parts of the gearbox, which is connected by a gearbox permanent transmission unit.

  speeds at the output shaft according to a permanent drive link.

  Because of this arrangement, in the known gearbox, in general all double downshifts, ie downshifts by skipping a gear, are possible - but the most important gear changes because the most frequent, between the fourth direct speed and the speeds I and II whose gears stages also belong to the first part of the gearbox, as well as the speed of direct catch, require, when these speeds must be engaged without interruption of the transmission of the torque - that is to say according to a switching load - the engagement

  intermediate of the additional stage of gears of the third speed.

  The problem underlying the present invention consists in being able to carry out speed changes between the direct drive speed and the speeds which belong, by their stages of gears, to the first part of the gearbox comprising the engagement clutch. direct, as switching load without interrupting the flow of force, without the need to engage an additional stage of gears. The problem explained is advantageously solved in accordance with a first aspect of the present invention by virtue of the fact that the constant transmission unit of the gearbox is connected to the intermediate shaft of the other part of the gearbox. intermediate shaft of the first part of the gearbox is connected by a constant transmission unit of the gearbox, which can be inserted into the force flow, to another secondary shaft parallel to the input shaft and which can be made to cooperate, by means of gear stages associated with the first part of the gearbox, the output shaft, according to a drive link made to the choice, and that the unit of constant transmission of the box of speeds connected to the intermediate shaft of the first part of the gearbox can be

  connected to the choice to one of two or two intermediate trees.

  In this gearbox according to the invention, in

  because of the presence of the secondary shaft which can be activated, a third

  the second torque transmission path is created between the input shaft and the output shaft, which can be used alternately with the torque transmission path of the direct drive clutch, by switching the two load switching clutches, for load switching between direct drive speed and speeds also belonging to the first part of the gearbox through their gear stages. When the speed distribution in the gearbox between two parts of the gearbox, and in the case of the gearbox in which the gears stages of the parts of the gearbox are associated in an alternating sequence gearbox speeds, all single passes at a higher speed and at a lower speed

  can be executed by alternating directly between the two

  Switching modes in load - that is, in a direct way. This is also valid for the speed or speeds close to the direct drive speed, in accordance with the gear ratio, even if in the gearbox according to the invention the direct drive speed is designed

  as the highest speed second.

  In the gearbox according to the present invention, double passages at a higher speed and double downshifts are possible between the direct drive speed and the sprocket speeds or stages, which belong to the first part of the gear box. speeds, which has the intermediate shaft connected to the direct drive clutch. In the gearbox according to the present invention, double passages at a higher speed and double downshifts between gears or gears stages, which belong to the other part of the gearbox, are allowed when the first part of the gearbox has an additional stage of pinions whose gear ratio is equal to the reduction of a gear stage of the other part of the gearbox, associated with the speed of the gearbox, or when the gearbox gear stage of the other part of the gearbox, the gear ratio of which is equal to the reduction of the additional stage of gears, is associated with the highest speed in

  third row of the gearbox.

  In the gearbox according to the present invention, the two secondary shafts of the two parts of the gearbox can be arranged for example by being parallel to each other. In the case where the available mounting space is not sufficient in the directions perpendicular to the axis, it can be provided that the additional shafts

  are arranged by being reciprocally coaxial.

  In the known gearbox, for the gear stages of two neighboring speeds on the basis of the gear ratio, among which the gear stage for the third gear belongs to the first part of the gearbox, which includes the gearbox. intermediate shaft connected to the direct drive clutch, and the gears stage for the second gear belongs to the other part of the gearbox, respectively used

  a main shaft gear connected to the respective and respective secondary shaft

  a secondary shaft gear connected to the common secondary shaft -

  that is to say a total of four gears.

  This explained complexity of the gearbox is advantageously reduced by the second aspect of the present invention relating to a gearbox in which an input shaft is connected to a coaxial output shaft by means of two parts of the gearbox. shifters arranged parallel to each other in the force transmission stream and which comprise stages of gearwheels associated respectively with a speed of the gearbox, due to their gear ratio, as well as respective intermediate shafts, and wherein the intermediate shafts are disposed concentrically with each other and are connected by respective frictionally engaged friction clutches to the input coaxial shaft, and wherein the intermediate shaft of a first gearbox portion can be brought, by means of the stages of associated gears, actively cooperate with the output shaft in a driving link optionally, and in which a secondary shaft arranged parallel to the input shaft can be made to cooperate with the gear stages associated with the other part of the gearbox, according to a motor link made to the choice, and it is also necessary to cooperate, by means of a unit with constant transmission of the gearbox, with one of the other shafts coaxial with each other, in a permanent drive link, thanks to the fact that the unit with constant transmission of the gearbox is permanently connected to the intermediate shaft of the other part of the gearbox, that the intermediate shaft of the first part of the gearbox is connected by another gearbox constant transmission unit speeds to another secondary shaft parallel to the input shaft, that the secondary shaft of the first part of the gearbox can be actively connected, by the stages of associated gears, to the output shaft according to a drive link made to the choice, that the stages of gears, which are associated with neighboring speeds in the gearbox and one of which belongs to the first part of the gearbox, and whose other belongs to the other part of the gearbox, comprise both a main shaft common gear, which is mounted coaxially with the output shaft and in a manner locked in rotation on the shaft, that a respective gear clutch, which is respectively connected to one of the two secondary shafts and to an associated secondary shaft gear. That is, for the two stages of sprockets - regardless of whether the two secondary shafts are coaxial or parallel to each other and furthermore regardless of whether the invention is used according to its first aspect indicated at the beginning , in the gearbox of the type just indicated, or not - it is necessary to provide a maximum of three gears, namely a main shaft common gear on the output shaft and respectively a gear pinion secondary shaft on the associated secondary shaft, the two secondary shaft gears meshing with the main shaft common gear and which can also be arranged in a plane

  common crankcase, perpendicular to the axis of rotation.

  In the gearbox according to the second aspect of the invention, the reduction ratio of the two gear stages, which work with a main shaft common gear, can be determined by the distance of the axes of the secondary shafts relative to to that of

the output shaft.

  In an advantageous embodiment of the gearbox according to the second aspect of the invention, the secondary shafts are located at the same distance between the axes of the output shaft and the constant transmission units of the gearbox. have different gear ratios, that is, the gear ratio of the two indicated gear stages is determined by the gear ratio of the two gearbox constant transmission units for the same distance between the secondary gear shafts. and the output shaft. This embodiment allows both parallel mounting

  than a coaxial assembly of the secondary trees.

  In another advantageous embodiment of the gearbox according to the second aspect of the invention, both the construction expense and the space expense are greatly reduced by virtue of the fact that the secondary shafts are arranged coaxially with each other and that the gears stages, which are associated with two speeds close to the gearbox and work with a main shaft common gear, also comprise a secondary shaft common gear, which is connected to both gear clutches each connected to a secondary shaft, since for the two specified stages of gears, only two gears are still generally necessary.

  The two embodiments, indicated in both para-

  graphs of the gearbox according to the second aspect of the invention may be used separately or in conjunction with

  the arrangements according to the first aspect of the invention.

  In another aspect, the invention relates to a method of

  a gearbox according to the invention, characterized in that in the case of the switching on the direct speed, which occurs from a lower speed of the gearbox, whose stage of associated pinions belongs to the first part of the gearbox, whose intermediate shaft is connected to the direct drive clutch, by means of the jump of a speed in the gearbox, first of all the trans unit - constant mission, which can be switched to the choice, the first part of the gearbox is further connected to the intermediate shaft of the other part of the gearbox, and then a control of overlapping transmission capacity of two switching clutches in

  charge is triggered so that the sum of the transmission capabilities

  mission is kept approximately constant and that the transmission capacity of the load switching clutch, which is connected to the intermediate shaft of the first part of the gearbox, tends to zero, and in that, when the capacity transmission of this switching clutch in load tends to zero, the direct-drive clutch is

  triggered, then a command to overlap the transmission capabilities

  mission of the two load-switching clutches is triggered so that the sum of the transmission capacities is maintained

  approximately constant and that the transmission capacity of the embra-

  the load switching mode, which is connected to the intermediate shaft of the other part of the gearbox, tends to zero and in that, when the transmission capacity of this load switching clutch tends to zero, the link between the gearbox's constant transmission unit, which can be switched on as desired, and the intermediate shaft of the other part of the gearbox is removed and the gearbox clutch is removed

  the lower speed of the gearbox is engaged.

  According to another aspect the invention relates to a method for switching a gearbox according to the invention, characterized

  in that in the case of a downshift from the mean direct speed

  the speed of the gearbox to a lower speed in the gearbox, including the associated gear stage

  belongs to the first part of the gearbox, whose internal shaft

  intermediate is connected to the direct drive clutch, first the gears clutch of the gears stage of the lower speed of the gearbox is engaged and the constant transmission unit of the gearbox, which can be engaged as desired, is further connected to the intermediate shaft of the other part of the gearbox and then an overlap control of the transmission capacity of the two switching clutches is triggered so that the the sum of the transmission capacities is kept approximately constant and that the transmission capacity of the load switching clutch, which is connected to the intermediate shaft of the first part of the gearbox, tends to zero, and in that when the transmission capacity of this load switching clutch tends to zero, the direct drive clutch is disengaged and the constant transmission unit of the fast gearbox which can be switched on as desired, is further connected to the intermediate shaft of the first part of the gearbox, and that subsequently an overlap control of the transmission capacities of the two load switching clutches is triggered from such

  so that the sum of transmission capacities is kept approximately

  constant and that the transmission capacity of the switching clutch in load, which is connected to the intermediate shaft of the other part of the gearbox, tends to zero and in that the connection between I ' constant gearbox transmission unit, which can be switched on as desired, and the intermediate shaft of the other part of the gearbox.

speeds is removed.

  The provisions indicated in the two preceding paragraphs relate to advantageous methods for the double passage at a higher speed or a double downshift, and that respectively by skipping a speed and this between the speed of direct catch and another speed, whose stage of gables also belongs to a part of the box of

  speeds, of which the intermediate shaft is connected to the direct drive clutch.

  According to another aspect of the invention, there is provided a method for switching a gearbox according to the invention, characterized in that, in the case of the passage of a lower speed of the gearbox, with jump of a speed in the gearbox, at the higher speed in the gearbox, which is associated with the gears stage of the other part of the gearbox and whose gear ratio is equal to the gear ratio of the additional stage of gears of the first part of the gearbox, firstly the gears clutch of the additional gears stage is switched on, then an overlap control of the transmission capacities of the two switching clutches load is triggered so that the sum of the transmission capacitances is kept approximately constant and the transmission capacity of the switching clutch under load, which is connected to the arbr e intermediate the other part of the gearbox, tende

  to zero, and in that, when the transmission capacity of that embra-

  In the load switching mode tends to zero, the clutch gear of the gears stage of the higher speed of the gearbox is engaged and then an overlap command of the transmission capabilities of the two switching clutches in load is triggered so that the sum of the transmission capacities is kept approximately constant and the transmission capacity of the load switching clutch, which is connected to the intermediate shaft of the first part of the gearbox, tends to zero and in that then the gear clutches of the additional stage of gables and the floor

  lower speed gears are disengaged.

  According to another aspect of the invention there is provided a method for switching a gearbox according to the invention, characterized in that in the case of a downshift from the higher speed of the gearbox, of which The associated gearset stage is part of the other part of the gearbox and has the same reduction ratio as the additional gears stage of the first part of the gearbox, with a speed jump in the gear box. speeds, to switch to a lower speed in the gearbox, whose associated gearcase stage belongs to the other part of the gearbox, first the gears clutch of the additional stage of gears is switched on, then an overlap control of the transmission capacities of the two load switching clutches is performed so that the sum of the transmission capacities is maintained approximately

  constant and that the transmission capacity of the switching clutch

  load which is connected to the intermediate shaft of the other part of the

  gearbox tends to zero and that, when the transmission capacity

  This load-switching clutch's mission tends to zero, the gearset of the gearset stage of the lower speed of the gearbox is engaged and then a control of overlapping of the transmission capacities of the two Load switching clutches are triggered such that the sum of the transmission capacities is kept approximately constant and the transmission capacity of the load switching clutch, which is connected to the intermediate shaft of the first part of the gearbox, tends to zero, and in that then the gears clutches of the additional stage of gears and the gears stage of the gear

  higher gearbox are disengaged.

  The arrangements described in the previous two paragraphs relate to advantageous methods for a double pass at a higher speed and a double downshift by jumping respectively a speed in a gearbox and that on the one hand to the speed, of which the Sprocket stage belongs to the other part of the gearbox and has the same gear ratio as the additional sprocket stage of the first gearbox part, the intermediate shaft of which is connected to the direct drive clutch , and secondly from

of this speed.

  According to another aspect of the invention, there is provided a method for switching a gearbox according to the invention, characterized in that in the case of the passage from a lower speed of the gearbox, of which the The associated gearbox stage belongs to the other part of the gearbox and has the same gear ratio as that of the additional gearset stage of the first gearbox part, with a speed jump in the gear box. speeds, to achieve a higher speed in the gearbox, whose associated gearcase stage belongs to the other part of the gearbox, first the pinion clutch of the additional stage of gears is triggered, then an overlap command of the transmission capabilities of the two load-switching clutches is triggered in such a way

  that the sum of transmission capacities should be kept approximately

  It is consistent and the transmission capacity of the load switching clutch, which is connected to the intermediate shaft of the other part of the gearbox, tends to zero and in that, when the transmission capacity of the gearbox this load-switching clutch tends to zero, the gearset of the gearset of the higher speed of the gearbox is engaged, and then an overlap control of the transmission capacities of the two switching clutches under load is triggered such that the sum of the transmission capacitances is kept approximately constant and the transmission capacity of the switching clutch under load, which is connected to the intermediate clutch of the first part of the gearbox, tends towards zero, and in that then the gears clutch of the additional stage of

gears is disengaged.

  According to another aspect of the invention, there is provided a method for switching a gearbox according to the invention, characterized in that in the case of a downshift from a higher speed of the gearbox, of which the The associated gearset stage belongs to the other part of the gearbox, with a gearbox jumping a gear, to switch to a lower speed in the gearbox, the associated gearset of which belongs to the gearbox. to the other part of the gearbox and which has the same gear ratio as the additional gear stage of the first part of the gearbox, first of all the gears clutch of the additional gears stage is switched on, then an overlap command of the transmission capabilities of the two switching clutches under load is triggered so

  that the sum of transmission capacities should be kept approximately

  the constant transmission capacity and transmission capacity of the switching clutch.

  under load, which is connected to the intermediate shaft of the other part of the

  gearbox, tends towards zero and that, when the transmission capacity

  mission of this load-switching clutch tends to zero, the gears clutch of the gears stage of the lower speed of the gearbox is engaged, then an overlap control of the transmission capabilities of the two switching clutches load is triggered so that the sum of the transmission capacities is kept approximately constant and the transmission capacity of the load switching clutch, which is connected to the intermediate shaft of the first gearbox part , tends towards zero and in that then the pinion clutch of the additional stage of gears is disengaged. The provisions indicated in the two preceding paragraphs relate to advantageous methods for the double pass at a higher speed and for a double downshift by jumping respectively a speed in the case of a gearbox of the type indicated above, a starts from the speed, whose gear stage belongs to the other part of the gearbox and which has the same gear ratio as the additional stage of gears of the first part of the gearbox, of which the intermediate shaft is connected to

  the direct drive clutch, and secondly to achieve this speed.

  Other features and benefits of these different aspects of

  the present invention will emerge from the description given below taken in

  reference to the accompanying drawings, in which: - Figure 1 shows a longitudinal section of a gearbox gear according to the first and second aspects of the invention indicated above; FIG. 2 represents a signal transmission flowchart for a type of commutation of the gearbox of FIG. 1; Figure 3 shows a signal transmission flowchart for another switching method of the gearbox of Figure 1; Figure 4 shows a signal transmission flowchart for another switching method of the gearbox of Figure 1; Figure 5 shows a signal transmission flowchart for another switching method of the gearbox of Figure 1; Figure 6 shows a signal transmission flowchart for another switching method of the gearbox of Figure 1; and FIG. 7 represents a signal transmission flow chart for another method of switching the gearbox to

gears of Figure 1.

  Referring now to Figure 1, an input shaft 10 and a coaxial output shaft 11 are interconnected through the two parts 12 and 13 of a gearbox which are arranged parallel between

  they in the flow of force transmission.

  The parts 12 and 13 of the gearbox each comprise

  respective intermediate shafts 14 and 15, which are arranged concentrically

  to each other and coaxially to the input shaft 10, and are connected to this

  last through load switching clutches in accordance with

  Ki and K2 can be engaged and disengaged.

  The intermediate shaft 14 of the first part 12 of the gearbox is connected on the one hand to the output shaft 11 via a direct engagement clutch 17 which can be engaged and disengaged, for the establishment of a fifth direct speed V and secondly to a secondary shaft 16, which is parallel to the output shaft 11 and is arranged

  in the form of a hollow shaft, by means of a transmission unit

  aunt Cl of the gearbox, which can be engaged and disengaged.

  The secondary shaft 16 of the first portion 12 of the gearbox is connected by a gear stage ZI, for setting the forward speed of the weakest I, to the output shaft 11, the idler gear of this gear stage ZI being arranged in a concentric manner with the possibility of rotation on the output shaft 11, and being connected thereto by

  a gear clutch 26 that can be engaged and disengaged.

  The secondary shaft 16 of the first part 12 of the gearbox is furthermore connected to the output shaft 11 by an additional stage of ZIV * gears, the idler gear of which is mounted in a concentric manner and with the possibility of rotation on the secondary shaft 16 and can be coupled thereto by a pinion clutch 23 can be engaged and disengaged. Finally, the secondary shaft 16 of the first portion 12 of the gearbox is further connected by a gear stage ZIII / IV for setting the third gear III and the fourth gear IV to the output shaft 11, the fixed gear 19 of this gear stage ZIII / IV being concentrically mounted with rotational locking on the output shaft 11, while the idle gear 20 of this gear stage ZIII / IV is mounted concentrically and in a manner to be rotatable on another secondary shaft 18 parallel to the output shaft 11 and can be coupled to this

  last by the gear clutch 22 that can be triggered and disengaged

  on the contrary to the secondary shaft 16 by a geared clutch

  21 can be engaged and disengaged.

  The other secondary shaft 18 passes through the secondary shaft 16 of the first part 12 of the gearbox with a certain clearance and is connected to the intermediate shaft 15 of the other part 13 of the gearbox, which is arranged in the form of a hollow shaft and is traversed with a certain clearance by the intermediate shaft 14 of the first part 12 of the gearbox, by means of a constant transmission unit C2 of the gearbox which acts to permanently. The other secondary shaft 18, which in this way belongs to the other part 13 of the gearbox, is connected to the output shaft 11 by other stages of sprockets ZVI and ZII as well as ZR, which belong naturally. also to the other part 13 of the gearbox. The idle gear of the gear stage ZVI, which is designed to realize the reduction of the maximum forward speed ZI, is concentrically and rotatably mounted on the secondary shaft 18 and can be coupled to the latter by means of a clutch

  with gears 25 can be engaged and disengaged.

  On the contrary, the idle gear of the gear stage ZII, which is used to establish the gear ratio of the second lowest forward gait speed II, is mounted in a concentric manner and with the possibility of rotation on the shaft. 11 and can be coupled to the latter by a

  gear clutch 24 that can be engaged and disengaged.

  While the fixed gear 8 of the gear stage ZR for setting the reverse speed R is concentrically mounted with rotational locking on the secondary shaft 18 and meshes with an intermediate gear, which is not further shown, for the reversal of the direction of rotation, the idle gear 19, which also meshes with the intermediate gear, of this gear stage is concentrically and rotatably mounted on the output shaft 11, to which it can be coupled by means of a pinion clutch 21 which can be engaged and disengaged. The constant transmission unit Cl of the gearbox comprises a fixed pinion gear 28 which is mounted in a concentric manner and with rotational locking on the secondary shaft 16 and which meshes with a pinion gear 29 which is mounted with a gear. concentrically with possibility of rotation on the intermediate shaft 14 and which can be connected, by a pinion clutch S- C1 / K1 can be engaged and disengaged, to the intermediate shaft 14 and thus to the switching clutch in charge K1 and by means of a pinion clutch s-C1 / K2, which can be engaged and disengaged, to the intermediate shaft 15 and therefore to

  the switching clutch in load K2.

  The ratios of the gear stage ZIII / IV and the constant transmission units C1 and C2 of the gearbox are tuned together so that, on the one hand, in the case of a force flow from the gearbox switching clutch in load K1, via the constant transmission unit C1 of the gearbox, at the gear stage

  ZIII / IV and consequently to the output shaft 11, we obtain the reduction

  application of the HIIth speed while on the other hand in the case of a force flow from the switching clutch load K2 via the constant transmission unit C2 of the gearbox to reach the ZIII / IV gear stage and consequently to the output shaft 11

  obtain the reduction of the first gear.

  The gear ratios of the constant transmission unit Cl of the gearbox and the additional gear stage ZIV * are tuned together so that in the case of a force flow from the switching clutch to load K1 through the constant transmission unit Cl of the gearbox to reach the additional stage ZIV * pinions and therefore the output shaft 11, we

  obtain also the multiplication of the IVth speed.

  It follows from the preceding description that the speeds I (by means of

  the gear clutch 26 of the gear stage ZI) and III (by means of the gear clutch 21 of the gear stage ZIII / IV) and V (by means of the direct drive clutch 17 ) are associated with the first part 12 of the gearbox and that the speeds II (by means of the pinion clutch 24 of the gear stage ZII) and IV (by means of the pinion clutch 22 of the gearbox 22). ZIII / IV sprocket stage) and VI (by means of the pinion clutch 25 of the ZVI sprocket stage) are associated with the other part 13 of the gearbox. As a result, all the simple commutations (passages at a higher speed and at a lower speed and between two speeds close to

  forward operation) can be performed in a known manner as a com-

  mutations under load by means of a respective override command

  the two load switching clutches K1 and K2 so that the sum of the transmission capacities of the two load switching clutches is kept approximately constant and that the transmission capacity of the switching clutch in load of the speed in front of to be disengaged tends to zero. The load switching IIIzIV and IVzIII are then carried out in such a way that the two

  pinion clutches 21 and 22 of the ZIII / IV gear stage are respectively

  switched on during the overlap command.

  Naturally, with the described combination of gears stages at the two parts 12 and 13 of the gearbox, all the multiple commutations, that is to say the passages at a higher speed or a lower speed with jump of one or more speeds, are possible as load switching, between speeds whose associated gear stages do not belong to the same part of the gearbox. This includes triple crossing at a higher speed I => IV, passing five times at a higher speed I =, VI, triple crossing at a higher speed II = V, triple crossing at a higher speed IIIZVI, triple IV = I demotion, triple VZII retrogression, demotion

  quintuple VI> I and triple demotion VIzIII.

  According to the first aspect of the invention, it is also possible to perform multiple gear changes between the direct drive speed V, which can be switched by means of the direct drive clutch 17, and one of the two other speeds I or III, also associated with the first part 12 of the gearbox, and that respectively as

  that switching in charge. As an example for this purpose, we will describe below

  after the gear changes involving the third gear according to a method according to the invention. The corresponding switching or speed changes involving the first gear are carried out

corresponding.

  Double pass at a higher speed IIIV according to Figure 2

  In the steady state of the third gear, the clutch of

  load bearing KS and the sprocket clutch 21 of the ZIII / IV gear stage and the gear clutch s-C1 / K1 of the gear unit

  Cl constant of the gearbox are engaged.

  When a shift signal 30 occurs, firstly, during a first operating step 31, the other gear clutch s-C1 / K2 of the constant transmission unit Cl of the gearbox is engaged, then, during another operating step 32, a

  Overlap command is executed for K1 => 0.

  In a next operating step 33, the gear clutch s-

  Ci / Kl of the Cl constant transmission unit of the gearbox is

  disengaged and the direct engagement clutch 17 is engaged.

  Then intervenes, during another operating step 34, an overlap control for K2 => 0, following which the clutch to

  pinions 21 of the ZIII / IV sprocket stage and the other gear clutch s-

  C1 / K2 of the C1 constant transmission unit of the gearbox are

  triggered during a terminal surgical step 35.

  Double V = III downgrading according to Figure 3

  In the steady state of the 5th gear, the shift clutch

  KS as well as the direct drive clutch 17 are engaged.

  During the appearance of a switching system 36, firstly during a first operating step 37, the gear clutch 21 of the gear stage ZIII / IV and the other gear clutch s -Cl / K2 of the constant transmission unit C1 of the gearbox are switched on, then an overlap command for K1> 0 is executed during a

other operating stage 38.

  In a subsequent operating step 39, the direct drive clutch 17 is disengaged and the gear clutch s-C1 / K1 of the drive unit.

  constant transmission C1 of the gearbox is engaged.

  The next operating step 40 is to execute an overlap command for K2 = 0 with an end operative step 41 for the disengagement of the other gear clutch s-C1 / K2 of the drive unit.

  constant transmission C1 of the gearbox.

  In an alternative embodiment of the gearbox in the first aspect of the invention, in which the first part of the gearbox

  speeds comprises an additional stage of gears, the multiplication of which

  cation is equal to the reduction of a gear stage of the other part of the gearbox, associated with the speed of the gearbox, or in which the gears stage of the other part of the gearbox speeds, whose gear ratio is equal to the reduction of the additional stage of gears, is associated with the highest speed in the third gearbox, double speed changes are possible between the speed of the other part 13 of the gearbox, whose gear ratio corresponds to that of the additional gear stage ZIV * of the first part 12 of the gearbox, and the other gear, also belonging to the other part 13 of the gearbox in accordance with gearbox switching processes, such as that

will be described below.

  Double shift at higher speed IIJIV in accordance with Figure 4: In the stationary state of the 2nd gear, the pinion clutch 24 of the ZII gear stage and the load switching clutch

K2 are engaged.

  During the variation of a speed change signal 42, firstly during a first operating step 43, the gear clutch 23

  the additional ZIV * sprocket stage and the pinion gear clutch

  C1 / K1 of the constant transmission unit C1 of the gearbox are switched on and, during a subsequent operating step 44, a control of

  overlap for K2 => 0 is executed.

  Then, during another operating step 45, the gear clutch 22 of the gear stage ZIII / IV is engaged and in a subsequent operating step 46, an overlap command for Ki = 0 is executed. During a final operating stage 47, the gear clutch 24 of the gear stage ZII and the gear clutch 23 of the stage

  additional ZIV * sprockets are engaged.

  Dual IV downshift: II in accordance with Figure 5 In the steady state of the 4th gear, the gear clutch 22 of the ZIII / IV gear stage and the load switching clutch

K2 are engaged.

  When a shift signal 48 appears, firstly during a first operating stage 49 the gear clutch 23

  the additional ZIV * sprocket stage and the pinion gear clutch

  C1 / K1 of the constancy C1 of the gearbox are switched on and, during a subsequent operation, an overlap command for K2 = 0

is executed.

  Then, in another operating step 51, the gear clutch 24 of the gear stage ZII is engaged and, in a subsequent operating step 52, an overlap command for K10 is executed. In a final operating step 53, the gear clutch 23 of the additional gear stage ZIV * as well as the gear clutch s-C1 / K1 of the constant transmission unit C1 of the gearbox are disengaged. Double shift at a higher speed IV = VI according to Figure 6 In the steady state of the 4th gear, the gear clutch 22 of the ZIII / IV gear stage and the load switching clutch

K2 are engaged.

  During the appearance of a gearshift system 54, firstly during a first operating step 55 the gear clutch

  23 of the additional ZIV * sprocket stage and the pinion gear clutch.

  C1 / K1 of the constant transmission unit C1 of the gearbox and in a subsequent operation 56, an overlap control for

K2 = 0 is executed.

  Then, during another operating step 57, the pinion clutch 25 of the ZVI gear stage is switched on and, during a subsequent operating step 58, an overlap command is executed.

for KlO0.

  In a final operating step 59, the gear clutch 23 of the additional gear stage ZIV * and the gear clutch s-C1 / K1 of the constant transmission unit C1 of the gearbox are disengaged. . Double VI = IV demotion according to Figure 7 In the steady state of the VIth gear, the ZVI pinion gear pinion clutch as well as the gear shift clutch.

K2 load are switched on.

  Firstly, when a gear change signal 60 appears, the gear clutch 23 of the additional gear stage ZIV * and the gear clutch s-C1 / K1 of the gear unit with constant transmission C1 of the gearbox are engaged during a first operating step 61 and an overlap command for K2 => 0 is executed during a next operating step 62. Then, during another operating step 63 the gear clutch 22 of the gear stage ZIII / IV is engaged and in a subsequent operating step 64 an overlap command for Kli0 is executed. In a final operating step 65, the gear clutch 23 of the additional gear stage ZIV * and the gear clutch s-C1 / K1 of the gear unit

  C1 of the gearbox are disengaged.

  The gear clutch s-C1 / K1 of the constant transmission unit C1 of the gearbox can remain engaged outside the gearshift processes, in which, under the effect of the disengagement of this clutch and the engagement of the other gears clutch C1 / K2 of the constant transmission unit C1 of the gearbox, it is necessary to have a transmission path of the torque, parallel to the clutch of

  direct drive 17, in the first part 12 of the gearbox.

Claims (16)

CLAIMS S   A gearbox in which an input shaft is connected to a coaxial output shaft by means of two parts of the gearbox arranged parallel to each other in the force transmission flow and which comprise gears stages respectively associated with a speed of the gearbox, due to their gear ratio, as well as the respective intermediate shafts, and in which the intermediate shafts are arranged concentrically between them and are connected by friction clutches respective load-switching arrangements at the input coaxial shaft, and wherein the intermediate shaft of a first part of the gearbox can be driven, by means of the associated gear stages, to actively cooperate with the shaft an output shaft according to a drive connection made in the choice, and in which a secondary shaft arranged parallel to the input shaft can be made to cooperate with the stages of sprockets associated with the other part of the gearbox, according to a drive link made to the choice, and also be brought to cooperate, by means of a constant transmission unit of the gearbox, with one of the other shafts coaxial with each other, in a permanent drive link, and in which the output shaft is connected by a drive-in clutch which can be engaged and disengaged, for the establishment of a gear-shift speed of the gearbox , to the secondary shaft of the first part of the gearbox, characterized in that the constant transmission unit (C2) of the gearbox is connected to the intermediate shaft (15) of the other part ( 13) of the gearbox, that the intermediate shaft (14) of the first part (12) of the gearbox is connected by a transmission unit (C1) of the gearbox that can be inserted into the gearbox. force, to another tree s econdaire (16) parallel to the input shaft (10) and which can be made to cooperate, by means of the gear stages (ZI, ZIV *, ZIII) associated with the first part (12) of the gearbox , to the output shaft (11), according to a drive linkage made optionally, and that the constant transmission unit (C1) of the gearbox connected to the intermediate shaft (16) of the first part (12). ) of the gearbox may be connected to one of the two   or to the two intermediate shafts (14, 15).   2. A gearbox according to claim 1, characterized   in that the gear stages (Z1-ZVI) of the gearbox parts (12, 13) are associated in an alternating sequence of speeds (I- VI) of the gearbox.   Gearbox according to any one of the claims   1 and 2, characterized in that the direct drive speed (V) of the   gearbox is the highest speed second gearbox.   4. Gearbox according to any one of   Claims 1 to 3, characterized in that the first part (12) of the   gearbox comprises an additional stage of gears (ZIV *) whose gear ratio is equal to the reduction of a gearset stage (ZIV) of the other part (13) of the gearbox, associated with the speed (IV ) of the gearbox.   Gearbox according to claim 4, characterized   in that the gear stage (ZIV) of the other part (13) of the gearbox, whose reduction ratio is equal to the reduction of the additional gears stage (ZIV *), is associated with the highest speed in   third row (IV) of the gearbox.   Gearbox according to any one of the   1 to 5, characterized in that a number (six) of gable stages is provided which corresponds to the sum, minus one, of the number (six) of   non-direct forward speeds and a reverse gear.   7. Gearbox according to any one of   Claims 1 to 6, characterized in that the additional shafts (14,   ) are arranged by being reciprocally coaxial.   8. Gearbox in which an input shaft is connected to a coaxial output shaft by means of two parts of the gearbox   parallel to each other in the transmission stream.   of force and which have associated pinion stages respectively   at a speed of the gearbox, because of their multiplier-   and respective intermediate shafts, and wherein the intermediate shafts are arranged concentrically therebetween and are connected by respective frictionally engaged friction clutches to the input coaxial shaft, and wherein the intermediate shaft a first part of the gearbox can be brought, by means of the associated gear stages, to actively cooperate with the output shaft according to a drive link made to the choice, and in which a secondary shaft arranged parallel to the input shaft can be brought to cooperate with the gear stages associated with the other part of the gearbox, according to a drive link made to the choice, and also be brought to cooperate, by means of a unit with constant transmission of the gearbox, with one of the other shafts coaxial with each other, according to a permanent drive link, in particular according to claim 1, characterized in that that the constant transmission unit (C2) of the gearbox is permanently connected to the intermediate shaft (15) of the other part (13) of the gearbox, that the intermediate shaft (14) of the first part (12) of the gearbox is connected by another constant transmission unit (C1) of the gearbox to another secondary shaft (16) parallel to the input shaft (10), which the secondary shaft (16) of the first part (12) of the gearbox can be actively connected, by the associated gear stages, to the output shaft (11) according to a motor connection made to the choice, that the stages of gears (ZIII / ZIV), which are associated with neighboring speeds (III, IV) in the gearbox and one of which (ZIII) belongs to the first part (12) of the gearbox, and of which the other (ZIV) belongs to the other part (13) of the gearbox, both comprise a main shaft common gear (19), which is coaxially mounted to the output shaft (11) and in a rotationally locked manner on said shaft, that a respective pinion clutch (21, 22), which is respectively connected to one of the two secondary shafts ( 16, 18) and an associated secondary shaft gear (20).   9. A gearbox according to claim 8, characterized   in that the secondary shafts (16, 18) are located at the same distance between the axes of the output shaft (11) and the constant transmission units (C1 / C2) of the gearbox have ratios of different gear ratios.   Gearbox according to claim 9,   characterized in that the secondary shafts (16, 18) are coaxially arranged   between them and that the pinion stages (ZIII / ZIV), which are associated with two adjacent speeds (III / IV) of the gearbox and work with a main shaft common gear (19), also comprise a pinion common secondary shaft (20), which is connected to the two clutches at   gears (21, 22) each connected to a secondary shaft (16, 18).   11. Method of switching a gearbox with gears   according to any one of claims i to 10, characterized in that   in the case of switching to the direct speed (V), which occurs from a lower speed (III) of the gearbox, whose associated gear stage (ZIII) belongs to the first part (12) ) of the gearbox, the intermediate shaft (14) of which is connected to the direct drive clutch (17), by the jump of a speed in the gearbox, first of all the transmission unit constant (C1), which can be switched on, the first part (12) of the gearbox is further connected to the intermediate shaft (15) of the other part (13) of the gearbox, and then an overlap control of the transmission capacities of the two load switching clutches (K1, K2) is triggered such that the sum of the transmission capacities is maintained   approximately constant and that the transmission capacity of the embra-   load switching yoke (K1), which is connected to the intermediate shaft (14) of the first part (12) of the gearbox, tends to zero, and in that, when the transmission capacity of this clutch switching mode (K1) tends to zero, the direct drive clutch (17) is switched on, then an overlap command of the transmission capacities of the two load switching clutches (K1 / K2) is triggered so that the sum of the transmission capacities   be kept approximately constant and that the transmission capacity   mission of the load switching clutch (K2), which is connected to the intermediate shaft (15) of the other part (13) of the gearbox, tends to zero and in that, when the transmission of this   load switching clutch (K1) tends to zero, the link (S-   K1 / K2) between the constant transmission unit (C1) of the gearbox, which can be switched on optionally, and the intermediate shaft (15) of the other part (13) of the gearbox is removed and the gear clutch   (ZIII) of the lower speed (III) of the gearbox is engaged.   12. Process for switching a gearbox   according to any one of claims 1 to 10, characterized in that   in the case of a downshift from the direct speed (V) by the jump of a speed in the gearbox, to a lower speed (III) in the gearbox, including the associated gear stage ( ZIII) belongs to the first part (12) of the gearbox, the intermediate shaft (ZIV) of which is connected to the direct drive clutch (17), first of all the gear clutch (21) of gear stage (ZIII) of the lower speed (III) of the gearbox is switched on and the gear unit   constant transmission (C1) of the gearbox, which can be   choice, is further connected to the intermediate shaft (15) of the other   part (13) of the gearbox and then a control of   transmission capacities of the two switching clutches   (K1 / K2) is triggered so that the sum of the transmission capacitors is kept approximately constant and the transmission capacity of the load switching clutch (K1), which is connected to the intermediate shaft (14). ) of the first portion (12) of the gearbox, tends to zero, and in that, when the transmission capacity of this load switching clutch (K1) tends to zero, the direct drive clutch (17) ) is disengaged and the unit   constant transmission (C1) of the gearbox, which can be   optionally, is further connected to the intermediate shaft (14) of the first part (12) of the gearbox, and that subsequently an overlap control of the transmission capacities of the two switching clutches under load (K1 / K2) is triggered so that the sum of the transmission capacities is kept approximately constant and the transmission capacity of the load switching clutch (K2), which is connected to the intermediate shaft (15). the other part (13) of the gearbox, tends towards zero and in that then the connection between the constant transmission unit (C1) of the gearbox, which can be engaged as desired, and the intermediate shaft (15) of the other part (13) of the gearbox is removed.   13. Method for switching a gearbox   according to any one of claims 4 to 10, characterized in that,   in the case of the transition from a lower speed (II) of the gearbox, with a jump of a speed in the gearbox, to the higher speed (IV) in the gearbox, to which is associated the gear stage (ZIV) of the other part (13) of the gearbox and whose reduction is equal to the reduction of the additional gears stage (ZIV *) of the first part (12) of the gearbox gearbox, first the pinion clutch (23) of the additional gear stage (ZIV *) is switched on, then an overlap command of the transmission capacities of the two switching clutches under load (K1 / K2 ) is triggered such that the sum of the transmission capacities is kept approximately constant and the transmission capacity of the load switching clutch (K2), which is connected to the intermediate shaft (15) of the other part (13) of the gearbox, tends to zero, and in that when the transmission capacity of this load switching clutch (K2) tends to zero, the sprocket clutch (22) of the gearbox stage (ZIV) of the higher speed (IV) of the gearbox is switched on and then an overlap command of the transmission capacities of the two load switching clutches (K1 / K2) is triggered so that the sum of the transmission capacities is kept approximately constant and the transmission capacity of   the load switching clutch (K1), which is connected to the intermediate shaft   (14) of the first portion (12) of the gearbox tends to zero   and then that the gear clutches (23 and 24) of the additional stage   sprockets (ZIV *) and the sprocket floor (ZII) of the speed of   lower forward (II) are disengaged.   14. Process for switching a gearbox   according to any one of claims 4 to 10, characterized in that   in the case of a downshift from the higher speed (IV) of the gearbox, whose associated gear stage (ZIV) is part of the other part (13) of the gearbox and which has the same gear ratio as the additional gear stage (ZIV *) of the first gearbox part (12), with a gearbox jump, to switch to a lower speed (II) in the gearbox. gearbox, the associated gearbox stage (ZII) belonging to the other part (13) of the gearbox, firstly the gear clutch (23) of the additional gear stage (ZIV *) is switched on, then an overlap control of the transmission capacities of the two load switching clutches (K1 / K2) is carried out so that the sum of the transmission capacities is kept approximately constant and the transmission capacity of the load switching clutch (K2) which is connected to the intermediate shaft (15) of the other part (13) of the gearbox tends to zero and in that, when the transmission capacity of this load switching clutch (K2) tends to zero, the pinion clutch (24) of the gear stage (ZII) of the lower speed (II) of the   gearbox is engaged and that subsequently a control of   transmission capacities of the two switching clutches   load (K1 / K2) is triggered so that the sum of the transmission capacities is kept approximately constant and the transmission capacity of the load switching clutch (K1), which is connected to the intermediate shaft (14) of the first portion (12) of the gearbox, tends to zero, and that then the pinion clutches (23 and 22) of the additional gear stage (ZIV *) and the sprocket stage (ZIV) of the higher speed (IV) of the box speeds are disengaged.   15. Process for switching a gearbox   according to any one of claims 4 to 10, characterized in that   in the case of the passage from a lower speed (IV) of the gearbox, the associated gear stage (ZIV) belongs to the other part (13) of the gearbox and has the same gear ratio as that of the additional gears stage (ZIV *) of the first part (12) of the gearbox, with a gear shift in the gearbox, to result in a higher speed (VI) in the gearbox of gear, whose associated gearwheel stage (ZVI) belongs to the other part (13) of the gearbox   first gear clutch (23) of the auxiliary stage   The gearbox (ZIV *) is engaged, then an overlap control of the transmission capacities of the two load switching clutches (K1 / K2) is triggered so that the sum of the transmission capacities is kept approximately constant and the capacitance for transmitting the load switching clutch (K2), which is connected to the intermediate shaft (15) of the other gearbox part (13), tends to zero and in that, when the capacity transmission of this load-switching clutch (K2) tends to zero, the sprocket clutch (25) of the gearbox stage (ZVI) of the higher speed (VI) of the gearbox is engaged, then an overlap control of the transmission capacities of the two load switching clutches (K1 / K2) is triggered so that the sum of the transmission capacities is kept approximately constant and the transmission capacity of the gear load switching geode (K1), which is connected to the intermediate clutch (14) of the first transmission part (12), tends to zero, and in that then the gear clutch (23) ) the additional sprocket stage (ZIV *) is disengaged. 16. Process for switching a gearbox   according to any one of claims 4 to 10, characterized in that   in the case of a downshift from a higher speed (VI) of the gearbox, whose associated gear stage (ZVI) belongs to the other part (13) of the gearbox, with a jump of a speed in the gearbox, to switch to a lower speed (IV) in the gearbox, whose associated gear stage (ZIV) belongs to the other part (13) of the gearbox and which has the same reduction ratio as the additional sprocket stage (ZIV *) of the first gearbox part (12), first of all the gear clutch (23) of the additional sprocket stage (ZIV *) ) is engaged, then an overlap command of the transmission capacities of the two load switching clutches (K1 / K2) is triggered so that the sum of the transmission capacities is kept approximately constant and the transmission capacity of the clutch switching load (K2), which is connected the intermediate shaft (15) of the other part (13) of the gearbox tends   to zero and in that, when the transmission capacity of that embra-   Load switching (K2) tends to zero, the sprocket gear (ZIV) pinion clutch (22) of the lower speed (IV) of the gearbox is engaged, and then an overlap command Transmission capabilities of both switching clutches under load   (K1 / K2) is triggered so that the sum of the transmission capacities   the mission is kept approximately constant and the transmission capacity of the load switching clutch (K1), which is connected to the intermediate shaft (14) of the first gearbox part (12), tends to zero and then that the gear clutch (23) of the stage   additional sprockets (ZIV *) is disengaged.