FR2644866A1 - TRAINING DEVICE WITH SEVERAL FLOORS - Google Patents

Abstract

The invention relates to a multi-stage drive device, in particular for auxiliary equipment of a motor vehicle. The drive device comprises a base casing 1, a casing 5 surrounding a planetary transmission and a disc brake 22, 23; for switching the transmission as a function of the speed of rotation of the engine, there is provided inside the transmission a control system comprising in particular centrifugal weights in the form of balls 28, which move, as a function of the speed of rotation of the engine, at least one valve lifter 32, which controls the supply of pressurized oil to a piston 35 ensuring the application or release of the transmission brake.

Description

The present invention relates to a multi-drive device

floors, including a device

  two-stage auxiliary drive, coupling a crankcase,

  planetary gear, consisting of at least one central pinion, an outer body arranged as a hollow ring and planet gears mounted on a planet carrier, the central pinion being connected to a shaft, as the driven shaft, and the gate -satellites being non-rotatably connected to another shaft, such as the driving shaft, for example by means of an intermediate shaft, and in which there is further provided a toothed annular element non-rotatably connected to the outer body as well as a brake provided with multiple disks which are driven by the intermediary of a

  hydraulic device. For example, this training device -

  can be used for ancillary equipment

of a motor vehicle.

  A drive device of this kind is known in the prior art from German Patent No. 31 03 397. For a modification of the ratio between the rotational speeds

  of the leading part and the driven part, a hy-

  hydraulics is driven by a pulley forming the driven portion and thereby produces in the hydraulic fluid different pressures for clamping and loosening of a brake, which immobilizes or releases the central gear of a planetary transmission. When the central gear is locked, it establishes a linear transmission ratio and increasing in correspondence with the rotational speed of the engine. For a high speed of rotation of the engine, the rotational speed of the driven part remains constant, friction linings providing a controlled braking of the brake connected to the central gear until the speed of rotation of the engine becomes sufficiently large that the brake is released. In this case, a unidirectional coupling locks the central pinion with the planet carrier so that the

  leading part and the led part are interconnected.

  The disadvantage of this known drive device for auxiliary equipment consists in the relatively large bulk resulting from the brake arrangement outside the transmission housing, in the strong

  solicitation and consequently rapid wear corresponding to

  brake linings for the normal running speed and also because of deficiencies - caused by leaks - of the order placed

  in relation to the pumping pressure of the hydraulic fluid

  than. In addition, a wide range of rotational speeds is

  necessary for the switching of the driving device

is lying.

  The object of the invention is therefore to improve

  the drive of the above mentioned type of

  such that the commutation of the transmission is

  Kills automatically in a simpler and faster way.

  To solve this problem, it is planned, in accordance

  In accordance with an essential characteristic of the driving device, an internal control arranged in the transmission to effect the switching of the latter as a function of the speed of rotation. So the

  control system is arranged in the crankcase of the trans-

  mission so that the drive device is of a compact structure and that virtually all

  rotating parts of the transmission may be

  by a casing that does not turn.

  According to other features of the device

  according to the invention - the housing consists of a transmission housing and a

  basic housing that is connected to it.

  - An inner brake body is held between the flange of the base housing and the flange of the transmission housing without being able to rotate or translate axially.

  - The outer body and the inner brake body

  carry recesses in which are guided alter-

natively the brake discs.

  - The toothed annular element is part of the outer body. - The driven shaft is mounted by means of a freewheel in the intermediate shaft and the drive shaft and the driven shaft

  are arranged in alignment in the intermediate shaft.

  - For switching the transmission according to the

  rotational speed, centrifugal weights are

  fuges between a radial collar of the intermediate shaft

  and an actuating member (pressure plate)

  biased by a return spring.

  - The centrifugal weights are arranged in the form of

balls.

  - The collar of the intermediate shaft comprises, in a radially outer portion, a rolling cone

directed to the pressure plate.

  - The return spring for soliciting the tray

  pressure consists of at least two coil springs

  coïdaux. - The coil springs are arranged on guide rods. - Each guide rod is advantageously arranged with

  possibility of axial translation in a recess of-

  pressure plate and without possibility of translation

  axial in a hole in the base case.

  - For the lengthening of the holes provided in the base casing, it is enlarged by means of an appendage in

Sleeve shape.

  - At least one valve pusher is provided for the

  control of the intake and return of oil under pres-

  this push is connected without the possibility of trans-

  the axial pressure with the pressure plate, whereas by tale it is arranged with possibility of translation

264-4866

  axial in the hole of the base housing.

  - The valve pusher is arranged as a rod of

  additional guidance for the pressure plate.

  - The pusher has a circular cross section and a portion of the pusher has a reduced diameter (recess). - The pusher has, at its end opposite the pressure plate, a collar which opens or closes, depending on the speed of rotation, the arrival of oil

  under pressure on an actuating piston.

  - The piston is arranged radially between the appendix in

  Sleeve shape and flange of the base housing.

  - A sheath is provided, spring-loaded and displaceable

  axially by the piston for the solicitation of

brake discs.

  - The sheath has at its two ends zones

with ledges.

  - The brake has a pressure disc (disc of

  mite), which is urged by one of the edges of the sheath.

  - For the elastic biasing of the sleeve, there is provided an annular spring which is supported on one side against the inner body of the brake and on the other side against the

  edge of the sheath that is opposite to the end disk.

  - The inner body of the brake has a step against

  which rests the annular spring. -

  - There are holes in the base housing for pressurized oil inlets and the oil drain channel.

  Thus the flange fixing of the transmission casing

  mission on the base case provides a structure

  compact. Clamping the inner brake body between the flanges of the base case and the transmission case avoids the use of additional fastening means. A simplification of the training device with respect to

  the prior art corresponding to German Patent No. 31 03397 results from

  the particular arrangement of the outer body, which includes not only additional recesses for

  guiding the brake discs, but also the

  dented annular ring against which the satellite gears are leaning. Due to the use of centrifugal weights between a radial collar of the intermediate shaft, which is simultaneously the porteatellites, and an actuator, arranged as a pressure plate and biased by a return spring, a system is obtained

  particularly simple and reliable to move a

  evening in the hydraulic conduit for switching the transmission depending on the speed of rotation in this regard, to reduce friction losses, it is advantageous that the weights are arranged under

  ball shape. Thanks to the arrangement of the outer part

  the collar of the intermediate shaft under the

  shape of a rolling cone directed towards the organ of action-

  In simple terms, a component is

  axial to the radial movement of the centrifugal weights.

  In this respect, it is particularly advantageous, in order to obtain precise commutation of the transmission, to eliminate the influence of the friction between the centrifugal weights and the radial flange or the plateau of

  pressure. This result is obtained in a particular way

  appropriate when, in the control mechanism of the centrifugal force, for example the radial collar

  turns and the pressure plate does not turn and

  then between these two parts balls acting as centrifugal weights and rolling between the two parts

like in a bearing.

  To avoid switching and therefore a

  skating of the mating in a wide range of

  It is advantageous for the centrifugal weights (balls) to be shifted outwardly as the speed increases beyond a predetermined value and to be forced again inwards when the speed drops

  below a second, slightly lower value, the

  valve evening being each time brought directly into one or the other limit position. This result can be obtained by making the differential angle between the flange and the pressure plate in the area

  internal diameters, ie the diameters in-

  rolling bearings, the same or more

  large than in the field of outside diameters, that is

  that is, the outer diameters of the ball bearings and / or by ensuring that the return springs for the pressure plate (such as coil springs or ring springs) exert an elastic force that is as constant as possible or decreasing on the

spring race.

  By using at least two helical springs as return springs for the pressing of the pressure plate, it is possible to adjust exactly the force

recall.

  When using an annular spring, the restoring force can be chosen constant, increasing or decreasing, depending on the angle between the collar

and the pressure disc.

  Helical spring guide on rods

  is intrinsically classic; however, it is particularly

  advantageously for the simplification of the device

  that these guide rods, which are

  without the possibility of axial translation in holes of the base casing and which serve other.part to guide the coil springs, are also used for a guide of the actuating member, which comprises

  with regard to the recesses for the reception of guide rods

  ge. To maintain a safer way. the guide rods, it is advantageous to lengthen the base casing, in this case

  place, by means of an appendage in the form of a sleeve.

  By means of one of the guide rods, it is possible

  Another function may be accomplished by arranging it as a valve pusher for controlling the intake of pressurized oil. In this case the guide rod is connected however without possibility of translation with the actuating member but it is arranged with the possibility of

  translation into the basic housing. As a control organ

  de, the pusher advantageously has a cross section of circular shape and it comprises a portion of reduced diameter, which serves as a connection between two pressurized oil inlet zones, while the end of the pusher which is remote from the actuating member and which has the complete section forms a collar which, depending on the speed of rotation, opens the oil inlet under pressure on a piston actuating the brake or releases the oil return. For a uniform solicitation of the brake discs, it suffices to use a sleeve requested by

  spring axially displaceable by a piston and which

  at both ends of the edges, this sheath now

  in frictional contact with the brake discs by means of an annular spring bearing against a step

of the inner brake body.

  For the pressurized oil supply on the piston that actuates the brake and also for oil evacuation, it is sufficient to form suitable holes in the base housing. Thus complicated tubular links are eliminated.

  Other features and advantages of the

  will be highlighted later in the description of the

  FIG. 1 is a view in axial section of the transmission of the drive device according to the invention,

264'4866

  Figure 2 shows the arrival of oil under pressure on the piston in the condition of loosening the brake discs. The two-stage auxiliary drive device accommodates a base housing 1 against the flange from which is bolted the flange 5a of a transmission housing 5. An axial hole

  1 of the base housing 1 serves to receive an intermediate shaft

  hollow diagonal 7 which is connected at one of its ends to a driving part 6, in particular a camshaft or

  a crankshaft, for example in a fixed manner through

  diary of a toothing; the intermediate shaft 7 can then be simultaneously maintained and centered via

  of this toothing. At its other end, the intermediate shaft

  7 is the outer ring of a bearing forming

  13 and which may comprise for example two rolls

  needle bearings and a free wheel 14 arranged between the bearings 13, bearing in which is mounted rotatably the pin 12a of a driven shaft 12. The driven shaft 12 has in the center a toothed collar which represents the central pinion 11 of a planetary transmission. The associated planet gears 10 are mounted via needle bearings 9 on pins 8 which are fixed on a

  flange 7a - the planet carrier - of the intermediate shaft

  7. The planet gears 10 are engaged with the internal toothing of a corresponding annular element 19a (coredent), which

  part of a hollow outer body 19. This outer body

  19 is mounted, by means of a bearing 20, on an axially inwardly directed sleeve-shaped appendix 5b of the transmission housing 5, which has a radially inward bearing on another bearing 15 for the pin 12b of the driven shaft 12, which is supported by a collar 12c against the inner ring of the bearing 15. The bearing 15 is held axially on one side of its outer ring by a collar 5c against the 5b of transmission case 5 and on the other side by a

2644 866

  stop ring 17 which is engaged in a groove of the

  dice 5b. The pin 12b of the driven shaft 12 is rigidly connected axially to the outside of the bearing 15, with a pulley 16 through which the auxiliary equipment is driven. The outer body 19 has at its end

  free of the recesses 19b for guiding external disks.

  The inner discs 23 are guided in recesses 24b of an inner brake body 24, which is securely held between the flange 1a of the base housing 1 and the flange 5a of the transmission housing.

  5. The brake 21 has, at its end opposite to the

  radial portion of the inner brake body 24, an end disc arranged as a pressure disk 25, which is supported by its radially inner end against a rim 26a, directed radially outward, of a sleeve 26. A its axially opposite end, the sleeve 26 comprises another rim 26b directed radially outwards and against which are supported tongues of an annular spring 27 whose radially outer end rests against in step 24a of the inner body of 24. Under the action of the annular spring 27, the outer discs 22 and the inner discs 23 are

  held in contact with each other by friction

  intermediate of the sleeve 26 and the end disc 25.

  To remove the frictional contact between

  discs 22, 23 of the brake, the sleeve 26 is displaced axially.

  in opposition to the force of the annular spring 27 by an annular-shaped piston 35 which is guided radially in a pressure-tight manner in a recess 1d of the base casing 1. The piston 35 is loaded with

  the pressurized oil from a conduit 2, 33.

  For a modification of the transmission ratio between the driving part and the driving part according to

  the speed of rotation, the flange 7a, directed radially

  outwardly, the intermediate shaft 7 is

  provided with a conical shape at 7b at its radial end

  the outer brake corresponding to the brake 21. On this

  Rette 7a, 7b roll centrifugal weights 28 which may have a shape of balls. These centrifugal weights 28 are held against the flange 7a, 7b by an actuating member 29 arranged as a pressure plate and biased by return springs 30. The return springs 30 are guided on rods 31,

  0lo which are held by one of their ends without

  translational flexibility in holes 1a of the base casing 1 and with possibility of translation into recesses

29a of the pressure plate 29.

  At least one of the guide rods 31 is arranged as a valve pusher 32, which obviously bears in the same way as the other guide rods 31 a return spring 30 but which is nevertheless maintained, unlike the other guide rods. 31, without possibility of translation in the recess 29a of the pressure plate 29, and with possibility of translation in the hole of the base housing 1. The valve pusher 32 has a circular cross section which is adapted to that of the hole the of the base casing but it comprises, at its end opposite the pressure plate 29, a portion of reduced diameter forming a recess 32a, which is closed by a collar

  32b corresponding to the cross section of the push-button

  pe 32 outside the setback 32a. This collar 32b closes, in the switching stage shown in FIG. 1, the passage connecting the duct 2 for admitting oil under pressure with the oil channel 33 or with the cylindrical volume 34 containing the piston. 35, so that pressurized oil in this cylindrical volume 34 can return to a tank, not shown. In the other switching stage shown in FIG. 2, the collar 32b opens, via the recess 32a, the communication passage between the pressurized oil inlet duct 2 and the oil channel 33. for an actuation of the piston 35. As the oil intake pipe 2 or as the oil channel 33, there are provided in the base housing 1 holes which are closed

  outwards by plugs 2a, 33a.

  The drive device operates as follows: As shown in FIG. 1, the centrifugal weights 28 are located, for low rotational speeds of the engine, on an inner diameter of the rolling cone 7b. The valve pusher 32 closes the pressurized oil inlet on the piston 35 in that the collar 32b of the pusher 32 is situated between the pressurized oil inlet duct 2 and the oil channel 33. The discs 22, 23 of the brake are applied against each other by the pressure exerted by the annular spring 27 and consequently the outer body 19 is prevented from rotating. The satellite gears 10 are

  driven in the direction of engine rotation through the

  6. The planet gears 10 are then engaged with the toothing, immobilized by the brake 21, of the annular toothed element 19a and cause

  the central pinion 11 of the driven shaft 12 with a transmission

  speed in the increasing direction, for example in a ratio of 1: 3. The transmission in the increasing direction is a function of the diameter of the planet gears 10 by

  compared to that of the central gear 11.

  In this condition, the driven shaft 12 then turns

  if faster than the driving shaft 6.

  When exceeding the switching speed excessively, the centrifugal weights 28 are displaced radially outwards along the contour of the rolling cone 7b and they then produce a withdrawal towards the left of the pressure plate 29 and also the Valve pusher 32. Thus, the pressurized oil inlet pipe 2 is brought into communication, via the recess 32a of the valve pusher 32, with the oil channel 33 leading to the cylindrical volume 34. effect of the pressurized oil, the piston 35 is pushed, in opposition to the force of the annular spring 27, as far as against the radial portion of the inner brake body 24. Under the effect of this axial movement of the piston 35, also the sleeve 26 is pushed to the right, considering Figure 1, in opposition to the force of the annular spring 27 which eliminates the contact between the brake discs 22, 23. This condition is shown in Figure 2. The outer body 19 is released and can thus rotate in unison with the planet gears 10. The torque transmission is now ensured between

  the driving shaft 6 and the driven shaft 12 by the intermediate shaft

7 and the freewheel 14.

  Because the pressure plate 29 is non-rotatably connected to the base housing 1 via the guide rods 31, and also the valve tappet 32 and the taper 7b are rigidly connected with the intermediate shaft 7 - in this case due to the one-piece construction - provides a precise and hysteresis-free switching when the motor goes from low speeds to high speeds, and vice versa. The centrifugal weights 28, arranged for example in the form of balls, continue to roll during the step and thus ensure a hysteresis-free switching and an exactly defined speed of switching during an acceleration or deceleration of the engine, simply according to of

  the angle of the rolling cone 7b on its radial extent.

  In principle it is possible to switch between

  them the driving shaft 6 and the led shaft 1l2.

Claims (24)

  1. Multi-stage driving device, in particular a two-stage auxiliary supporting device, comprising a housing, a planetary transmission, consisting of at least one central gear, an outer body arranged as a hollow gear and planet gears. mounted on a planet carrier, the central pinion being connected to a shaft, as the driven shaft and the planet carrier being non-rotatably connected to another shaft, as   the driving shaft, for example by means of an intermediate shaft   and in which there is further provided a toothed annular element non-rotatably connected to the outer body and a brake provided with multiple disks which are actuated by means of a hydraulic device,   characterized in that for switching the transmission   depending on the speed of rotation, it is   an interior control (7a + 28 + 29 + 30 + 32) in the transmission   if we. Drive device according to claim 1, characterized in that the housing comprises a transmission housing (5) and a base housing (1) which is connected to it.   Drive device according to Claim 2, characterized in that an inner brake body (24) is held between the flange (1a) of the base housing (1) and the flange (5a) of the transmission housing ( 5) without power   rotate or axial translation.   Drive device according to Claim 3, characterized in that the outer body (19) and the inner brake body (24) have recesses (19b, 24b) in which the discs (22, 23) of the brake (21).   5. Training device according to one of the claims   1 to 4, characterized in that the annular element   toothed (19a) is part of the outer body (19).   6. Drive device according to one of the claims   1 to 5, where the driven shaft (12) is mounted by means of a freewheel (14) in the intermediate shaft (7), characterized in that the drive shaft (6) and the driven shaft (12 are arranged in alignment in the intermediate shaft (7).   7. Drive device according to one of the claims   1 to 6, characterized in that, for switching the transmission as a function of the rotational speed, centrifugal weights (28) are provided between a radial flange (7a) of the intermediate shaft (7). and an actuating member (pressure plate) (29) biased by a return spring (30).   8. Drive device according to claim 7, characterized in that the centrifugal weights are   arranged in the form of balls (28).   9. Drive device according to one of the   7 or 8, characterized in that the flange (7a) of   the intermediate shaft (7) comprises, in a radial portion   outside, a rolling cone (7b) directed towards   the actuating member (pressure plate) (29).   10. Drive device according to one of the claims   7 to 9, characterized in that the return spring (30) for biasing the actuating member (plate   pressure gauge) (29) consists of at least two coiduals (30).   Drive device according to claim 1, characterized in that the coil springs (30)   are arranged on guide rods (31).   12. Drive device according to claim 11, characterized in that each guide rod (31) is advantageously arranged with the possibility of translation.   in a recess of the actuating member (   pressure water) (29) and without the possibility of translation   axial in a hole (1c) of the base case (1).   13. Drive device according to claim 12, characterized in that, for the extension of the holes (1c) provided in the base housing (1) it is enlarged to   using a sleeve-shaped appendage.   14. Drive device according to one of claims 11 to 13, characterized in that at least one valve pusher (32) is provided for the control of the inlet and the return of oil under pressure. push being connected   without the possibility of axial translation with the organ of ac-   tioning (pressure plate)! (29) whereas against it is arranged with possibility of axial translation in the hole (1e) of the base case (1).   15. Drive device according to one of the claims   1 to 14, characterized in that the valve tappet (32) is arranged as an additional guide rod for the pressure plate (29).   16. Drive device according to one of the claims   4 or 15, characterized in that the pusher (32) has a circular cross section and a portion of the pusher has   a reduced diameter (recess) (32a).   17. Drive device according to one of the claims   14 to 16, characterized in that the pusher (32) has, at its end opposite the actuating member (pressure plate) (29), a collar (32b) which opens or closes, depending on the speed of rotation, the arrival   of oil under pressure on an actuating piston (35).   18. Drive device according to the claim   17, characterized in that the piston (35) is arranged radially   between the sleeve-shaped appendix (lc) and the flange (la) of the basic housing (1).   19. Drive device according to one of the   cations 1 to 18, characterized in that a   sleeve (26), spring loaded and axially displaceable   by the piston (35) for the solicitation of the disks brake (22, 23).   20. Drive device according to claim 19, characterized in that the sleeve (26) comprises at its   two ends of the zones with flanges (26a, 26b).   21. Drive device according to one of the   1 to 20, characterized in that the brake (21) comprises a pressure disk (end disk) (25) which   is urged by one of the flanges (26a) of the sleeve (26).   22. Drive device according to one of the   cations 18 to 21, characterized in that for the solicitation   elastically of the sleeve (26), a spring is provided   ring (27) which is supported by a shoulder against the body   brake (21) 3 t on the other side against the rim (26b) of the sleeve (26) which is opposite the disc end (25).   23. Drive device according to claim 22, characterized in that the inner body (24) of the brake (21) comprises a step (24a) against which rests the annular spring (27).   24. Drive device according to one of the claims   cations 1 to 23, characterized in that holes (33) for the oil inlets are provided in the base housing (1).   under pressure (2) and the oil discharge channel (3).