FR2586281A1 - FLUID-MECHANICAL DRIVE DEVICE - Google Patents

Abstract

THE INVENTION RELATES TO A FLUIDIC-MECHANICAL TRAINING DEVICE. THE DEVICE INCLUDES AN INPUT DRIVE SHAFT 2, AN OUTPUT DRIVE SHAFT 3, A TORQUE TRANSMISSION SYSTEM 4 MECHANICALLY CONNECTING THE INPUT SHAFT 2 WITH THE OUTPUT SHAFT 3 AND AN ASSEMBLY OF FLUIDIC DRIVE 5 CONNECTING THE TORQUE TRANSMISSION SYSTEM 4 WITH THE OUTPUT SHAFT 3; THE FLUID DRIVE ASSEMBLY INCLUDES A HYDRAULIC PUMP 6, A PUMP GEAR 7 CONNECTING THE TORQUE TRANSMISSION SYSTEM TO THE PUMP, A HYDRAULIC MOTOR 9 CONNECTED TO THE PUMP AND A GEAR 10 CONNECTING THE MOTOR 9 TO THE SHAFT EXIT 3. APPLICATION TO TRAINING GROUPS.

Description

The present invention relates to a device which accelere a charqe

  from rest to a predetermined maximum angular velocity. The device can also accelerate a moving load to a predetermined upper angular velocity. U.S. Patent No. 4,049,095 to Montalvo discloses a multi-speed transmission system, and more particularly a transmission system for driving the shaft of a winder or unwinder apparatus to maintain surface speed and tension. of a web of a reel being wound or unrolled at a substantially constant value while the diameter of the reel changes. The present invention relates to a transmission device for transmitting rotational energy,

  or a couple, between an input shaft and an output shaft.

  The entroe tree is driven by a source of energy while

  that the output shaft causes a load.

  The energy transmission device - Start (idle load) in a purely fluidic mode, as a hydraulic mode, in an instantaneous condition, where it progresses to a hydraulic-mechanical condition, coimined, in a progressive manner without steps. and it ends in a pre-determined maximum angular velocity 3 in a completely mechanical manner. The axial angular velocity is a function of design ratios and the speed of entry. The system can operate continuously in any report, to switch from a logical mode to a mechanical node or, at the limits, it can function only in relation to the command type u: -. Iis $ e and with the capacity of the device, the control system can be manual, or at least, and it is then controlled according to the speed, the load or a number of The present invention relates to a mechanical control device comprising an input shaft; an output tree; a torque transmission system mechanically connecting the input shaft with the output shaft; and a fluidic drive assembly providing the linkage of the torque transmission system with the output shaft. When the transmission device

  of energy or drive device according to the invention.

  In the fluidic drive mode, for example the hydraulic drive mode, the input shaft produces the rotational energy to drive the torque transmission system which drives the fluidic drive assembly providing the drive. tree training

Release.

  When the energy transmission device,

  or drive device according to the invention

  In the mechanical drive mode, the input shaft provides the rotational energy to drive the torque transmission system which in turn ensures

  the drive of the output shaft.

  Consequently, when the training device

  initially engages and when the output shaft is stationary, the fluidic drive assembly can

  be requested in order to couple the transmission system

  torque with the output shaft. However, after the driving device has been operating for a time sufficient to bring the output shaft to its desired angular velocity, the torque transmission system can mechanically and directly couple the input shaft with the drive shaft.

  exit. This is due to the fact that the operation of the whole

  fluidic drive has been suspended or stopped pending so that the torque transmission system can bypass the fluidic drive assembly when the rotational movement is transmitted from the input shaft to

the output shaft.

  The torque transmitting system comprises a drive gear which is fixed to the input shaft and a transmission device which connects the input shaft gear to the drive shaft. is provided that, whenever the output shaft is immobilized because an initial stationary load holds the output shaft in a fixed position, the transmission device causes the pump gear to operate there pump hydraulic to engage the hydraulic motor, so that the output shaft begins to rotate driven only by the hydraulic motor; and it is further provided that each time the output shaft has been driven to its maximum rotational speed by the hydraulic motor, the motor forces the pump to immobilize the pump gear so that the the output shaft continues its rotational movement while being driven by the

  transmission device which is itself

  by the gearing leading from the input shaft.

  In accordance with the present invention, there are provided three embodiments of the device which are

  based on three different transmission devices.

  The first embodiment of the transmission device comprises an output shaft drive gear; at least one transmission pinion connecting the input shaft drive gear with the output shaft drive gear; at least one transverse shaft for supporting at least the transmission bevel pinion to produce a rotational movement between the input shaft drive gear and the output shaft drive gear; a circumferential ring gear having the transverse shaft positioned along its inner diameter and fixed to the inner wall of the ring gear, the arrangement of the bevel gear with respect to the gears being such that the circumferential ring gear rotates in the same direction as the shaft leading gear

  input, the said direction being opposed to that of the gear

Leading edge of output shaft.

  The second embodiment of the device

  transmission comprises a circumferential ring gear

  disposed coaxially with the input shaft drive gear, the ring gear having an inside diameter larger than the outside diameter of the input shaft drive gear; at least one planet pinion positioned between the input shaft drive gear and the ring gear, the planet gear being simultaneously engaged with both the driving gear and the ring gear; an output drive disk S mounted in a fixed position on the output shaft; at least one shaft connecting the satellite gear with the output drive disc; and bearings for the planet gear that are mounted between the planet gear and the satellite shaft so that the planet gear can rotate about said shaft and within said circumferential ring gear.

  The third embodiment of the

  transmission shaft comprises an output shaft drive gear fixed to the output shaft; at least one input pinion gear in contact with the input shaft drive gear an input drive disk rotatably mounted on the input drive shaft; at least one output planet pinion in contact with the output shaft drive gear; an output drive disk rotatably mounted on the output drive shaft; at least one satellite shaft interconnecting the input drive disk, the satellite gear

  the satellite output gear and the drive disk.

  exit; the satellite shaft being rotatably connected at one end to the input drive disk and being rotatably connected at its other end to the output drive disk; and the satellite tree being fixed on the satellite gear

  input and being fixed to the output satellite pinion.

  The present invention has the advantage of using a hydraulic acceleration means to produce

  a gradual acceleration of maniare to obtain a training

  which is ultimately purely mechanical. We realize a

  energy saving through the use of mechanical drive

  only in cooperation with hydraulic drive, by

  opposition to a purely hydraulic drive.

  Other features and advantages of the invention will be highlighted later in the

  description, given by way of non-limiting example, in

  reference to the accompanying drawings, in which: FIG. 1 is a perspective view of a first embodiment of the fluidic mechanical drive device according to the present invention; FIG. 2 represents a perspective view of the second

  embodiment of the fluidic drive device-

  FIG. 3 is a perspective view of a third embodiment of the present invention.

  embodiment of the fluidic drive device-

  mechanical according to the present invention.

  Figures 1, 2 and 3 represent respectively

  three embodiments of the present invention.

  Whenever possible, the same numerical references will be used to designate identical features and elements in these three different embodiments. However, in the second embodiment shown in FIG. 2, each of the numerical references corresponding to the identical feature represented on FIG.

  Figure 1 shall be prefixed with "200" for the

  indicated in Figure 2. Similarly in Figure 3,

  the numerical references which relate to the same

  than those shown in Figure 1 will be based on the same numerical references but provided with a

prefix of "300".

  The fluidic drive device

  mechanical device is designated 1 in Figure 1, 201 in Figure 2 and 301 in Figure 3. This device comprises an input shaft 2 in Figure 1, 202 in Figure 2, and 302 in Figure 3 The device further comprises an output shaft 3 in FIG. 1, 203 in FIG. 2, and 303 in FIG. 3. The device also comprises a torque transmission system which mechanically connects the input shaft 2 with the output shaft 3. This torque transmission system is designated as a whole by reference 4 in FIG. 1, 204 in FIG. 2 and 304 in FIG.

Figure 3.

  The device 1 further comprises a fluidic drive assembly generally designated 5 in Figure 1, 205 in Figure 2 and 305 in Figure 3. This fluidic drive assembly provides the linkage of the torque transmission system. 4 of Figure 1

  with the output shaft 3, the link of the transmission system

  torque pair 204 of FIG. 2 with the output drive shaft 203, and the linkage of the transmission system of FIG.

  torque 304 of Figure 3 with the output shaft 303.

  The hydraulic drive unit S comprises a hydraulic pump 6, a gear 7 which connects the torque transmission system 4 with the hydraulic pump 6. The pump gear 7 is connected by a shaft 8 with the hydraulic pump. The fluidic drive assembly further comprises a hydraulic motor 9 which is connected to the hydraulic pump 6. A motor gear 10 is connected by a shaft 11 to the hydraulic motor. The motor gear

  connects the hydraulic motor to the output shaft 3.

  The corresponding features of Figures 2 and 3 are highlighted in the drawings for

  the components of the fluidic drive assembly.

  The hydraulic pump 6 of FIG. 1 further comprises a high pressure outlet 12 and a

  low-pressure intake port 13. The hydraulic motor

  includes a high pressure inlet 14 and a low pressure outlet 15. A high conduit

  pressure, designated by 16 and although not shown complete-

  In the drawings to simplify them, connects the high pressure outlet 12 of the hydraulic pump with the high pressure inlet 14 of the hydraulic motor. A low pressure conduit 17, which is also partially shown to simplify the drawing, is disposed between the low pressure inlet 13 of the hydraulic pump and the low pressure outlet 15 of the hydraulic motor 9. A gear output 18 is fixed on the output shaft 3 and is in contact with the motor gear 10. By the term "contact" is meant that the teeth provided on the outer surface of the output gear are engaged with the teeth provided on the outer surface of the motor gear so that rotational movement produced by one gear in one direction rotates the other gear in the opposite direction. The hydraulic pump 6 further comprises a

  first fluid flow control lever 19.

  The hydraulic motor 9 further comprises a second lever

  of fluid flow control.

  The control lever 19 of the hydraulic pump

  that is represented as being placed on the outer side

  of the pump 6. This lever 19 controls a means placed in the

  the pump to adjust the fluid flow and

  pressure inside the pump. This means placed within the

  The pump has been designated 21 and could be pistons or paddles. An example could be a piston pump of the swash plate type. The second fluid control lever 20 for the hydraulic motor is placed on the outer side of this engine and is connected to a means 22 placed inside the hydraulic motor for adjusting the fluid flow and the pressure to the fluid. inside the hydraulic motor. This means 22 could be constituted by pallets or pistons,

  as in a reciprocating piston pump.

  The torque transmission system 4 comprises an input shaft drive gear 23 which is fixed on the input shaft 2. A transmission device connects the input shaft drive gear 23 with the shaft It is expected that each time the output shaft 3 is immobilized under the effect of an initial stationary load (not shown) maintaining this stationary output shaft 3, the transmission device forces the output shaft 3 to be stationary. pump gear 7 to actuate the hydraulic pump 6 to engage the hydraulic motor 9 so that the output shaft

  3 begins its rotational movement by being driven alone.

by the hydraulic motor 9.

  It is furthermore provided that, each time the output shaft 3 has been driven to its maximum angular speed by the hydraulic motor 9, this motor 9 causes the hydraulic pump 6 to immobilize its pump gear 7 such that the output shaft 3 continues to rotate while being driven by the transmission device which is itself driven only by said gear

leading 23 of the input shaft.

  Until now, the different parties

  The features described and shown for the first embodiment of the invention indicated in FIG. 1 are identical to corresponding features occurring in the second embodiment of FIG. 2 or in the third embodiment of FIG. transmission device corresponding to the first embodiment of the present invention shown in Figure 1 is different from the transmission device corresponding to the second embodiment of the invention shown in Figure 2 and it is also different from the transmission device corresponding to the third embodiment

  of the invention shown in FIG.

  Referring now to FIG. 1, it will be seen that the gear 23 is attached to the input shaft 2 by welding or otherwise such that rotation of the shaft 2 causes the gear 23 to rotate. in the same direction, and without any slippage between the gear

23 and the tree 2.

  The transmission device of Fig. 1 comprises an output shaft drive gear 24. This gear 24 is fixed, for example by welding, on the output shaft 3 in such a way that a rotation of the gear 24 rotates the shaft 3 in the corresponding direction.

  and without any slippage between the gear 24 and the shaft 3.

  There is provided at least one transmission bevel pinion 25 connecting the drive gear 23 of the input shaft with the drive gear 24 of the output shaft. There is at least one transverse shaft 26 for supporting the bevel gear for transmitting a rotational movement between the drive gear 23 of the input shaft and the gear

leading 24 of the output shaft.

  The transmission device of FIG. 1 also comprises a circumferential ring gear 27 in which the transverse shaft 26 is positioned along one of its inner diameters, this transverse shaft 26 being fastened to the inner wall 28 of said circumferential ring gear 27. The arrangement of the bevel gear with respect to the driving gears 23 and 24 is such that the circumferential ring gear 27 rotates in the same direction as the input shaft and the driving gear 23 of this input shaft, said direction being opposed to the direction of rotation of the driving gear 24 of the shaft

Release.

  As shown in FIG. 1, two transmission bevel gears are provided which are mounted on the transverse shaft. The second bevel gear 29 is supported by the transverse shaft 26 in such a way that the four gears are continuously engaged with each other.

  the other, as shown in Figure 1. As a result, the

  23 of the input shaft is simultaneously engaged with the bevel gears 25 and 29, said bevel gears being simultaneously engaged with the driving gear 24 of

the output shaft. -

  Bearings are provided for each of the bevel gears. Thus a bearing 30 is provided for the pinion

  conical 25 while a bearing 31 is provided for the pinion 29.

  Each bearing is mounted between its respective conical pinion and the transverse shaft 26 so that each bevel gear can perform an independent rotational movement about the transverse shaft 26 and within the

  circumferential ring gear 27.

  The circumferential ring gear 27 has, along its outer periphery, teeth 32 which engage the teeth 33 of the pump gear 7. The outer diameter of each of the bevel gears 25 and 29 is smaller than the diameter inside the circumferential ring gear 27, so that the bevel gears do not touch the circumferential ring gear. The only contact between the bevel gears is established through the transverse shaft 26 which is in contact with the inner wall and which is fixed

  on this inner wall 28 of the ring gear circumferentially

  27. Referring now to FIG. 2, the transmission device comprises a circumferential ring gear 40 disposed coaxially with the gearing.

  leading 223 of the input shaft. The ring gear circumferentially

  The differential 40 has an inside diameter greater than the outside diameter of the driving gear 223 of the input shaft. There is at least one satellite pinion 41 disposed between the drive gear 223 of the input shaft and the circumferential ring gear 40. The pinion gear 41 is simultaneously engaged with both the drive gear and the gearbox. circumferential ring gear. Simultaneous engagement means that the teeth 42 provided on the outer surface of the pinion-satellite 41 engage with the teeth 43 provided on the outer surface of the gear 223 and that they are simultaneously engaged with the teeth 44 provided on the inner surface of the ring gear

circumferential 40.

  There is provided a carrier member 45, which is constituted by an output drive disc and which is mounted in a fixed position on the output shaft 203. On this carrier element, or spider, is welded the shaft of

exit 203.

  At least one satellite shaft is provided

  46 ensuring the connection of the pinion-satellite 41 with the cross

  groove, or carrier member, or output drive disc 45. The satellite shaft is attached to the disc

  output drive 45 at one end thereof.

  A bearing 47 for the planet gear 41 is mounted between the planet gear 41 and the planet shaft 46 so that the planet gear 41 can execute

  a rotational movement around the shaft 46 and to the inte-

  of the ring gear 40. Consequently the pinion

  satellite can turn around the tree 46 but this tree of it satellite 46 is unable to execute a movement of

  rotation since it is firmly attached to the drive disk.

exit 45.

  As shown in FIG. 2, the transmission device comprises three planet gears, namely the gears 41, 48 and 49. These three planet gears are arranged between the driving gear 223 of the input shaft and

  the circumferential ring gear 40. The three pinions-

  satellites are spaced equal distances around the input shaft drive gear and inside the circumferential ring gear so that the three planet gears 41, 48 and 49 are arranged in such a way that

  so that the outer surface of each pinion is simul-

  momentarily engaged with the outer surface of the driving gear 223 of the input shaft and simultaneously engaged

  with the inner surface of the ring gear.

40.

  The circumferential ring gear 40 has teeth 50 along its outer periphery which engage with the teeth 233 of the pump gear 207, so that the ring gear 40 constitutes a

  drive gear of the pump.

  The pinion-satellite 48 comprises a corresponding shaft 51 connecting this pinion-satellite 48 with the output drive disc 45. A bearing 52 for the pinion-satellite 48 is mounted between this pinion-satellite 48

  and its corresponding shaft 51 so that the pinion

  satellite can perform a rotational movement around

  its shaft 51 and inside the ring gear circumferentially

  However, the satellite shaft 51 is rigidly fixed to the output shaft 45 and is not capable of

  to execute a rotation movement.

  The pinion-satellite 49 comprises a shaft 53 ensuring the connection of this pinion-satellite 49 with the disk

  output drive 45. A bearing 54 for the pinion

  satellite 49 is mounted between this planet gear and its corresponding shaft 53 so that the planet gear 49 can rotate about the shaft

58628 1

  53 and inside the circumferential ring gear 40. However, one end of the planet shaft 53 is securely fastened to the output drive disc 45 and therefore the shaft 53 is unable to execute a motion dv rot: l ilo.

  In Figure 2, the arrangement of the gears

  satellites 41, 48 and 49 with respect to the driving gear 223

  of the input shaft is such that the ring gear circumscribes

  ferential 40 turns in the opposite direction to the direction

  rotation of the driving gear 223 of the input shaft, each time the output shaft is driven only by the hydraulic motor 209, causing the output shaft 203 to rotate in the same direction. direction than the driving gear 223 of the input shaft. The driving gear of the input shaft rotates in the same direction as

the input shaft 202.

  The arrangement of the planet gears 41, 48 and 49 with respect to the driving gear 223 of the input shaft is such that, each time the pump gear 207 immobilizes the circumferential ring gear 40, the pinions -satellites actuate the output drive disc 45 to rotate it in the same direction as the driving gear 223 of the input shaft, so that the input shaft 202 and the output shaft 203 are running in

the same direction.

  Referring now to FIG. 3, the transmission device comprises an output shaft drive gear 60 which is attached to the output shaft 303, for example by welding, so that the drive shaft gear exit does not turn or slip

  while in contact with the output shaft 303.

  At least one input satellite pinion 61 is provided which is in contact with the driving gear 323 of the input shaft. There is provided an input drive disk 62, or input carrier, or spider, rotatably mounted on the input shaft 302. Bearings 63 are used to rotatably support the disk.

  input drive 62 on the input shaft 302.

  At least one output sprocket 64 is provided in engagement with the drive gear 60 of the output shaft. There is provided an output drive disk 65 rotatably mounted on the output shaft 303.

  Bearings 66 are used to rotatably support

  te the output drive disk 65 on the shaft of

exit 303.

  There is at least one satellite shaft 67 interconnecting the input drive disk 62, the input satellite pinion 61, the output pinion 64 and the output drive disk 65. At least one provided satellite shaft 67 is rotatably connected by one end and by means of a bearing 68 with the input drive disk 62. The satellite shaft 67 is connected

  in a rotating manner at its other end through the intermediary

  re a bearing 69 with the output drive disc 65.

  The satellite shaft 67 is fixed on the satellite gear

  61 and it is simultaneously fixed on the pinion-

  As a result, the satellite shaft rotates and is driven by the input satellite pinion 61 to transmit the torque from the input satellite gear 61 to the output satellite pinion 64. there is no slippage between the satellite shaft 67 and either of the planet gears, namely the input satellite pinion 61 or the satellite exit pinion 64. As shown in Figure 3 , there is actually three gears-satellites input, namely the pinion

  61, as described above, and secondly the second pinion

  input satellite 70-and the third input-satellite gear 75. There are also provided three output gears-satellites, namely the pinion 75, as mentioned above, along with the second gear-satellite of exit 71 and

  the third output planet gear 76. As shown in FIG. 3, three planet shafts are provided. The

  first satellite tree 67 has been described above. The second satellite shaft 72 connects the second input satellite gear 70 with the second output satellite gear 71. The third satellite shaft 77 connects the third input satellite gear 75 with the

  third exit sprocket 76.

  Each of the three planet shafts 67, 72 and 77 are spaced equal distances around the surface of each of the disks formed by the drive disk.

  input 62 and the output drive disk 65.

  The second satellite shaft 72 is rotatably connected at one end and by means of a bearing 73 with the input drive disc 62 and is rotatably connected at its other end and through the bearing.

  74 with the output drive disk 65.

  The third satellite shaft 77 is rotatably connected by one end and by means of the bearing 78 with the input drive disk 62 while it is

  rotatably connected at its other end through the

  79 of the bearing 79 with the output drive disc 65.

  A circumferential ring gear is provided

  80 pump drive, which is arranged coaxially.

  to the output shaft 303 and which has an inside diameter

  larger than the outer diameter of the output shaft 303.

  As a result, the pump drive ring does not come into contact with the output shaft 303. The pump drive circumferential ring gear 80 has teeth 81 distributed along its outer surface and which are

  engaged with the teeth 333 of the pump gear 307.

  There is provided a cylindrical tube 82 for attaching the circumferential ring gear 80 to the pump drive on the output drive disc 65. The first embodiment of the fluo-mechanical drive device 1 of the present invention. invention

  is illustrated in Figure 1 and operates as follows.

  The source of energy, like an electric motor

  that or an internal combustion engine (not shown) is connected directly to the input shaft 2 which is integral with the input drive gear 23. The input drive gear is engaged with the two transfer gears 25 and 29 which are carried by bearings 30 and 31 mounted on a transverse shaft 26 which is integral with the ring gear 27. The ring gear 27 has teeth

  32 which engage with the teeth 33 of the gear

pump stroke 7.

  The transfer gears 25 and 29 are also engaged with the output bevel pinion 24. The conical output gear 24 is integral with the output shaft.

exit 3.

  The output gear 18 is also solidified

  of the output shaft 3, this output gear 18

  being engaged with the gear 10 of the engine.

  Pump 6 and motor 9 are both

variable displacement type.

  The delivery port 12 of the pump 6 is connected to the intake port 14 of the engine 9 while the discharge port 15 of the engine 9 is connected to the intake port 13 of the pump 6. pressure jerk compensation device-is usually used in this

closed loop circuit.

  An examination of the device reveals that the direction of rotation of the output shaft is reversed from the direction of rotation of the input shaft 2. This first embodiment has the advantage that, if the device is correctly mounted,

  it then has an appropriate effect of torque cancellation.

  For the first embodiment of the

  In Figure 1, the initial conditions are the

following: - -

  (a) the power source is in operation; (b) the pump control lever 19 and the motor control lever 20 are each placed in the zero displacement position; and

  (c) the load and the output shaft 3 are stationary.

  To start the movement, the control lever 20 of the motor 9 is first placed in the position of 258628i maximum displacement, establishing the correct direction of rotation. Then the control lever 19 of the pump 6 is placed in the position of maximum displacement, establishing again the correct direction of rotation. As a result, the output shaft 3 begins to rotate. At the very beginning of this rotational movement, the pump 6 drives the motor 9 so that the device 1 is actuated in a completely hydraulic manner. As soon as the rotational movement of the output shaft 3 begins, the device 1

  is then operated partially mechanically and simultaneously

hydraulically.

  From its initial position of rest at the beginning of the movement, the following processes take place in the device. The initially stationary load maintains the stationary and stationary output shaft 3. The power source drives the input shaft 2 and drives the drive or main gear 23, which in turn drives the transfer gears 25 and 29. The transfer gears 25 and 29 are engaged with the output bevel pinion 24, which is stationary at startup because the output shaft 3 is

at rest.

  As shown in FIG. 1, if the input shaft 2 is supposed to turn in a clockwise direction, this condition then causes the transfer gears to rotate as shown in FIG. 1 and move by translation around the conical output gear 24 which is stationary. As a result, the pinions 25 and 29 drive the ring gear 27 through the transverse shaft 26. As a result, the ring gear 27 rotates in a clockwise direction.

watch, looking at the figurative 1.

  The ring gear 27, now rotating, actuates the gear 7 which drives the pump 6. The pump 6 delivers hydraulic fluid into the conduit 16 into the

  the engine 9 to ensure its training, and consequently

  the drive of the motor gear.

  The motor gear 10 is engaged with the output gear 18. When the motor gear 10

  starts to rotate, the output gear 18 also starts

  rotational, which triggers the movement of the output shaft 3, and therefore the coupled load (not shown). Instantly at the beginning of this movement, the system operates in a purely hydraulic mode. To switch to the minimum hydraulic mode and

  purely mechanical, the following operations are carried out.

  The control lever 20 of the engine 9 is

  moved towards the zero displacement position.

  When this is done, the motor 9 increases speed, as does the output shaft. This results from the reduction of the cubic capacity. At the same time, the pump 6 slows down, because of the increase of the resistance in the motor 9. For the zero displacement of the motor 9, the motor operates in "freewheeling" and the pump 6 is blocked, because it does not pass more fluid in the engine 9. The ponpe being

  thus locked, the ring gear 27 is also blocked.

  At this time, the device 1 operates in a purely mechanical mode and the transmission of energy

is done as follows.

  The input shaft 2, which is driven by the energy source so as to turn in a clockwise direction, with reference to FIG. 1, drives the input gear 23 which in turn ensures the transfer gears 25 and 29 are rotated in the direction indicated in FIG. 1. The transfer gears 29 drive the output bevel gear 24, which in turn drives the output shaft 3 of way that it turns counterclockwise as shown in Figure 1, this shaft causing the load

coupled (not shown) .-

  Device 1 now works at the

  maximum speed in a purely mechanical mode (non-

  hydraulic). The second embodiment of the device

  fluidic-mechanical drive 201 of the present invention.

  This is illustrated in Figure 2 and operates as follows.

  The input shaft 202 and the driving gear 1 8 223 are integral with each other and are driven

  directly by the energy source (not shown).

  The planet gears 41, 48 and 49 are engaged with the driving gear 223 and are supported by respective bearings 47, 52 and 54, mounted on respective planet shafts 46, 51 and 53, said shafts being

  integral with the carrier disc 45. (This of course corresponds to

  only one of the different mounting modes of the satellite gears). The ring gear 40 has an internal toothing 44 which is engaged with the planet gears 41,

  48 and 49 thereby forming a complete planetary gear.

  The ring gear 40 is shown with a toothing

external 50.

* The external toothing of the crown 40 ensures

  driving the gear 207 of the pump.

  The carrier disc 45 is also integrally connected to the output shaft 203 which is attached to the output gear 218. The output gear 218 is

  taken with the gear 210 of the engine.

  The discharge port 212 of the pump 206 is connected to the intake port 214 of the engine 209 while the discharge port 215 of the engine 209 is connected to the inlet port 213 of the pump 206. pressure compensation means is usually provided

  in this "closed loop" circuit.

  Both the pump 206 and the motor 209 are of the variable displacement type and are manually controlled (in the drawings) by respective control levers.

  219 and 220. It is possible to use automatic

  according to actual operating conditions.

  For the second embodiment of the

  tif 201, Figure 2, the initial conditions are the following:

  are: (a) the power source is in operation; (b) the pump control lever 219 and the pump control lever 220 are each placed in the zero displacement position; and

  (c) the load and the output shaft 203 are stationary.

  To start the movement, the lever of

  motor control 220 is placed without the cylinder position

  maximum treble, taking into account that the direction of S rotation of the shaft 203 must be the same as that of

the input shaft 202.

  Then the pump control lever 219 is placed in the maximum displacement position, taking

  also counts the direction of rotation of the tree.

  The drive is now in the minimum angular velocity mode with the maximum ratio of the integral hydraulic mode. The load which is coupled to the output shaft 203 is now rotated and the integral hydraulic mode of the torque transmission

is established instantly.

  The transmission of energy from the power source (not shown) to the output shaft

- is carried out as follows.

  The input shaft 202 is driven by the energy source in a clockwise direction

  and the shaft 202 drives the gear 223 to which it is connected.

in one piece.

  At the initial starting point, only the carrier disc 45 is now immobilized by the stationary output shaft 203. The planet shafts 46, 51 and 53, which are integrally connected to the carrier disc 45,

  are also stationary at this time.

  Gear 223 drives the gears

  satellites 41, 48 and 49 and the ring gear 40 to rotate the pump gear 207. The gear

  pump 207 drives the pump 206.

  The pump 206 generates a hydraulic pressure

which is transmitted to the engine 209.

  The motor 209 now starts rotating by driving the gear 210 counterclockwise, causing the output gear 218 to be driven clockwise, and therefore driving the output shaft 203 in a clockwise direction. The training is now carried out at its maximum ratio and with the

slowest output speed.

  To change the ratio of the driving device, and therefore to change the output speed, the motor control lever 209 is moved to the zero displacement position. This produces an increase in engine speed due to a reduction in engine displacement. At the same time the pump 206 starts to slow down because of the increase in the throttling of

  fluid resulting from the displacement reduction of the engine 209.

  The result of this situation is that the engine 209 increases the speed of the output shaft 203 while the pump 206 slows down the speed

the ring gear 40.

  When the engine 206 has reached zero displacement, the control lever 219 being maintained at the angle

  zero, the motor 209 can operate freewheeling.

  The pump 206 is blocked because it

  remains in its maximum displacement mode, which corresponds to

  to a condition of no fluid flow in

the engine 209.

  The device 201 now operates in a completely mechanical mode and the transmission of energy

is as follows.

  The energy source drives the input shaft 202 in a clockwise direction, considering

  FIG. 2, this shaft driving gearing 223. The gearbox

  stroke 223 in turn drives the planet gears 41, 48 and 49. The planet gears, driven by the gear 223,

  have to perform a circular motion on the inner side

of the ring gear 40.

  The movement of the planet gears 41, 48 and 49 rotates the carrier disk 45 via

  respective planet shafts 46, 51 and 53.

  Since the carrier disk 45 and the output shaft 203 are integrally connected, the output shaft 203 is now driven in a purely mechanical mode.

from the energy source.

  As in the embodiment previously

  As described, the device 20 operates without a variable displacement pump but is still engaged in the drive mode. The zero displacement position of the pump 206 establishes a neutral mode (no drive)

for the device.

  To reverse the operation of the device, the motor 209 is placed in the initial position of maximum displacement. This causes a slowing down of the device

  drive up to its minimum angular velocity.

  Then the pump control lever 219 is brought into its

  full reverse position.

  If the two features defined above are to be incorporated in the device 201, then it is

  necessary to have a variable displacement pump.

  The third embodiment of the

  The fluidic mechanical drive 301 of the present invention is shown in FIG.

as following.

  An energy source (not shown) is coupled to the input shaft 302 which is integrally connected to the input drive gear 323. The input shaft

  is supported by a bearing 63 which is mounted in the cross-

  lon, or carrier member 62 provided on the input side.

  The brace includes an input drive disk or flange 62 and an output drive disk or flange 65, as shown. It is possible to have three or more disks in practice, one or more of which are centrally arranged. These discs

  contain bearings that support the satellite shafts

  lites 67, 72 and 77, the input drive shaft 302 and

  the output drive shaft 303.

  The pump gear 81 is integrally attached to the end of the tube 82 which is itself fixed to the drive disc 65 so that a rotation of the

  disc 65 produces a rotation of the gear wheel 80 of

  pump. Gear 80 provides training for

the pump gear 307.

  The input shaft 302 is keyed, welded or

  secured otherwise to the driving gear 323.

  The output drive gear 60 is coupled to the output drive shaft 303, which is itself coupled with the output shaft gear 318 in the same manner. The output shaft gear 318 is engaged with the motor gear 310. The motor gear 310 drives the output shaft gear 318 and the drive shaft.

  output 303 during part of the operating cycle.

  The assembly can be housed in a suitable housing that supports the internal components on bearings placed between the housing and the main shaft and is provided with flange supports for the pump! hydraulic and

the hydraulic motor.

  The engine 309 is a hydraulic motor of the variable displacement type. It can have any suitable structure, for example a structure with pistons. For example the piston type and swash plate is appropriate

to be used.

  The pump 306 is also cubic

  variable. In the description, it can be assumed that the

  pump is set to maximum displacement at start-up

  age and is maintained in this condition.

  The discharge port 312 of the pump 306 is connected to the inlet port 314 of the engine 309. The orifice

  315 of the engine 309 is connected to the intake port

  313 of the pump 306. A device for compensation of

  pressure shots is conventionally used in this circuit

closed loop.

  In the third embodiment of the device 301 of FIG. 3, the initial conditions are as follows: (a) the load and the output shaft 303 are stationary; (b) the pump control lever 319 and the lever of

  motor control 320 are each placed in a position

  zero cubic capacity; and (c) the energy source (ie an electric motor

  or an internal combustion engine) is running.

  To begin, the joystick 320

  the engine 309 is placed in the maximum displacement position

  male in correspondence to the direction of rotation selected. The energy source is running. As shown in Figure 3, the input shaft 302 rotates clockwise. Depending on the direction of rotation selected, the control lever 319 of the pump 306 is moved into the

  maximum displacement position. When this second maneuver

  is made, the movement of the device starts from the

following way.

  The energy source drives the input shaft 302 which rotates in a clockwise direction,

  considering Figure 3, the leading gear 323 input.

  The initial startup condition is that the output shaft

  303 is blocked and is rendered motionless by the stationary

  (not shown). As a result, the input gear 323 rotates the input planet gears 61, 70 and 75 which rotate by transferring their motion through the planet shafts 67, 72 and 77 to the planet. respective output planet gears 64, 71 and 76.

  Because of the initially stationary condition

  the output shaft 303, and therefore the gearbox

  60 output drive, the output satellite gears move around the drive gear of

  exit 60 counterclockwise.

  This causes the drives 62 and 65 to drive, thereby rotating counterclockwise. Since the pump drive gear is integrally mechanically connected to the cylindrical coupling member 82 and the disk 65, this gear

  rotates at the same speed as disk 65.

  The pump drive gear 80 drives

  do the gear 307 of the pump so as to operate

the pump 306.

  Pump 305, which is now in motion,

  In this embodiment, a hydraulic pressure is produced which is transmitted through a conduit 316 to the engine 309 which is not in the full displacement mode and which responds by driving the motor gear 310 counterclockwise. 'a watch. The gear 310 drives the output shaft gear 318 clockwise and the output shaft 303 in the direction of the spindles.

  Clockwise. As a result, the charge is

  maximum speed and minimum speed in this initial mode of energy transmission

  completely hydraulic. At this moment there is no training

  mechanically and we are dealing only with a training

hydraulic.

  To modify the relationship between training

  mechanical and hydraulic drive, the control lever

  320 engine 309 is moved to the displacement position

  minimal. When this is done, several processes begin.

  hundred to occur simultaneously. The engine 309, due to the displacement reduction, begins to accelerate its angular velocity. The throttling increase that is caused by the displacement reduction of the engine 309 begins to slow down the pump 306. The increase in the rotational speed of the engine 309 is transmitted by the motor gear 310 to the shaft gear. output shaft 318 and therefore to the output shaft 303. The motor gear 310 rotates counterclockwise by rotating the gear 318 and the output shaft 303 in the direction of the needles. of a watch, or in the same direction as

the input shaft 302.

  The rotational speed reduction of the pump 306 is transmitted through the pump gear 307 to the pump drive gear 80 which begins to brake, or slow down, the rotational speed.

of the disc 65.

  The final result of this modification is that, when the control lever 320 of the engine 309 has been brought into the zero displacement position, the motor can operate as a freewheel. The engine 309 then leaves no fluid to pass through and accordingly

  it blocks the pump 306 which remains in the cylinder position

  maximum dreaus, and therefore immobilizes the disk

carrier 65.

  When the pump 306 is blocked, as is the disc 65, and when the motor 309 is freewheeling, the resulting path of motion transmission

is the following.

  The energy source rotates the input shaft 302 clockwise and

  therefore provides the drive 323 gear.

  The input gear 323 drives the input satellite gears 61, 70 and 75 in the counterclockwise direction, these gears transmitting this torque through the planet shafts 67; 72 and 77, which are supported in bearings 69, 74, 79 by the disk

now stationary.

  The planet shafts 67, 72 and 77 transmit a counter-clockwise motion to the output planet gears 64, 71 and 76 which in turn transmit a clockwise motion to the planet. the drive gear of

exit 60.

  The output drive gear 60 is

attached to the output shaft 303.

  The output shaft 303 is carried in the disk 65 by a bearing 66 and transmits rotational energy in a clockwise direction to the load.

to which he is coupled. -

  The device operates without a variable displacement pump but is then always engaged in a drive mode. The zero displacement position of the pump 306 establishes a neutral, drive-free mode for the system. To reverse the direction of travel of the device, the engine 309 must be placed in its maximum displacement position, which slows down the drive to the minimum rotational speed. The pump control lever 319 should

  then be brought into the full inversion position.

  If both of these positions are to be used then a variable displacement pump must be used.

  In the description of the invention which

  been made above, the terminology "transmission device"

  mission "refers to a training train which, in

  part, links together the input elements with the ele-

mechanical output.

  A specific example of a hydraulic pump that can be used is the Vickers PVB-5 variable displacement piston and piston pump. However, we

  can use other known pumps with variable displacement.

  A specific example of the hydraulic motor that can be used is the Vickers MVB5 variable displacement piston and swashplate engine. However, it is possible to use other known engines with displacement

variable.

  Whenever possible, the components of the device are made of hard, durable and durable material, such as metals, for example

steel or brass.

  Naturally, the invention is not limited to the embodiments described above and shown, from which we can provide other modes and other embodiments, without departing from the

framework of the invention.

258'628 81

Claims (13)

  1. Fluidic-mechanical drive device   characterized in that it comprises: - an input drive shaft (2; 202; 302); an output drive shaft (3; 203; 303); a torque transmission system (4; 204; 304) mechanically connecting said input drive shaft with said output drive shaft; and - a fluidic drive assembly (5; 205; 305) connecting said torque transmission system to said output drive shaft.   2. Device according to claim 1, characterized   characterized in that said fluidic drive assembly (5) comprises: a hydraulic pump (6)   a pump gear (7) connecting the transmission system   torque supply to said pump - a hydraulic motor (9) connected to said pump (6); and - a motor gear (10) connecting said motor (9) to said   output drive shaft (3).   The apparatus of claim 2, wherein said hydraulic pump further comprises a high pressure outlet port (12) and a low pressure suction port (13) while the hydraulic motor further comprises a high inlet port pressure (14) and a low pressure discharge port (15), and characterized in that said fluidic drive assembly further comprises: - a high pressure conduit (16) positioned between said pump outlet port and said orifice input of said motor - a low pressure conduit (17) placed between said suction port (13) of said pump and said discharge port (15) of said motor (9), and - an output gear (18) fixed on said output shaft   (3) and engaged with the gear (10) of the motor.   4. Device according to claim 3, characterized in that said fluidic drive assembly further comprises: a first fluidic control lever (19) for said hydraulic pump (6), and a second fluidic control lever (20). ) for said hydraulic motor (9).   5. Device according to claim 1, characterized   characterized in that said torque transmission system (4) comprises: a driving gear (23) attached to said input shaft (2); a transmission device connecting said gear   driving shaft (23) with said drive shaft   outflow (3); and in that it is provided that each time said output shaft (3) is stationary because an initial stationary load maintains said output shaft in   a fixed position, said transmission device makes   whereby said pump gear (7) actuates said   hydraulic pump (6) to engage the hydraulic motor-   (9) such that the output drive shaft (3) begins its rotational movement driven only by the hydraulic motor (9); and in that it is furthermore provided that, each time said output shaft (3) has been driven to its maximum rotational speed by said hydraulic motor (9), said motor ensures that said pump (6) immobilizes said pump gear (7) such that said output drive shaft (3) continues its movement   rotation by being driven by the transmission device   mission that is only powered by said gear leading (23) of the input shaft.   6. Device according to claim 1, characterized   characterized in that said transmission device comprises: - a driving gear (24) of the output shaft (3); at least one conical transfer gear (25) connecting said input shaft drive gear with said output shaft drive gear; - a transverse shaft (26) for supporting said at least one bevel gear (25) for transmitting a rotational movement between said input shaft drive gear (23) and said drive gear (24) output shaft; a circumferential ring gear (27) in which said transverse shaft (26) is positioned along an inner diameter and is fixed on the inner wall 10 (28) of said ring gear (27); and - said conical pin (25) is disposed with respect to said driving gears (23, 24) such that said circumferential ring gear (27) rotates in the same direction as said shaft drive gear (23). of entry, this direction being opposed to that of   the drive gear (24) of the output shaft.   7. Device according to claim 6, characterized   characterized in that two conical transfer gears (25, 29) are provided which are supported by said transverse shaft (26), in that a bearing (30, 31) is provided for each of said bevel gears (25). , 29), the bearing being mounted between each bevel gear and said transverse shaft so that each bevel gear can perform independent rotation movement about said transverse shaft (26) and within said circumferential ring gear (27). , and in that said crown   the circumferential tooth (27) has along its periphery   outside the teeth (32) which are engaged with the teeth of the pump gear (7).   8. Device according to claim 7, characterized in that the outer diameter of each of the conical transfer gears (25, 29) is smaller than   the inside diameter of said circumferential ring gear   (27) such that said conical transfer gears (27, 29) are not in contact with said   circumferential ring gear (27).   9. Training device according to the   5, characterized in that said transmission device comprises: - a circumferential ring gear (40) arranged coaxially with said drive gear (223) of the shaft   input gear, said ring gear having an integral diameter   greater than the outside diameter of said input shaft drive gear (223) - at least one planet gear (41) disposed between said input shaft drive gear and said ring gear, said pinion gear being simultaneously taken with both said gear; driving (223) and said ring gear (40); an output drive disc (45) mounted in a fixed position on said output drive shaft   at least one satellite shaft (46) connecting said pinion   satellite (41) with said output drive disk (45); and a bearing (47) for said pinion-satellite (41), mounted between said pinion satellite and said satellite shaft, so that said pinion satellite can rotate about said satellite shaft   and within said circumferential ring gear the (40).   10. Drive device according to the claim   9, characterized in that said transmission device   comprises three planet gears (41, 48, 49) which are disposed between said input shaft drive gear and said ring gear, the three aforementioned planet gears (41, 48, 49) being spaced equally spaced around said drive shaft drive gear, in that said circumferential ring gear (40) has teeth (50) along its outer periphery which engage with the teeth of the pump gear (207) of such so that said circumferential ring gear constitutes a   pump drive gear, in that said pinions   satellites (41, d3, 49) are disposed with respect to said drive gear (223) to the drive shaft so that said circumferential ring gear (40) rotates in the opposite direction to that of the drive gear of drive shaft each time said output drive shaft is driven only by said hydraulic motor, causing said output drive shaft to rotate in the same direction as said drive gear (223) of the input shaft, in that said gears   satellites (41, 48, 49) are arranged in relation to the gear   driving shaft (223) of the input shaft so that, whenever said pump gear (207) immobilizes said circumferential ring gear (40), said planet gears (41, 48, 49) operate said output drive disk to rotate in the same direction as said driving gear (223) of the input shaft, such that said input shaft (202) and   said output shaft (203) rotate in the same direction.   11. Training device according to the   cation 5, characterized in that said transmission device   comprises: - an output shaft drive gear (60) which is fixed on the output shaft (303); at least one input satellite gear (61) meshing with said driving gear (323) of the input shaft; an input drive disk (62) rotatably mounted on said input drive shaft (302); at least one output planet gear (64) meshing with said output gear (60) of the output shaft; an output drive disk (65) rotatably mounted on said output drive shaft (303); - at least one satellite tree (67) connecting together   said input drive disk (62), said pinion   input satellite (61), said output satellite gear (64) and said output drive disk (65)   said satellite shaft (67) being connected in a tour-   terminating with said input drive disk (62) and being rotatably connected at its other end to said output drive disk (65); and   said planet shaft (67) being integral with said pinion   input satellite (61) and being integral with said pinion output satellite (64).   12. Training device according to the   11, characterized in that it comprises: - three input satellite gears (61, 70, 75); - three exit planet gears (64, 71, 76) three satellite trees (67, 72, 77), connecting each   a corresponding input-gear-satellite with its pinion-   respective output satellite; and said planet shafts (67, 72, 77) being spaced at equal distances around the surface of each of the disks formed by the input drive disk.   and the output drive disk (65).   13. Training device according to the   11, characterized in that it further comprises: - a circumferential ring gear (80) for pump drive, which is arranged coaxially with the output shaft (303), said pump drive ring gear comprising an inside diameter greater than the outside diameter of said output shaft (303); said circumferential, pump-driven ring gear (80) having along its outer surface teeth (81) which engage the teeth (333) of said pump gear (307); and - a cylindrical tube (82) for attaching said circumferential toothed gear (80) to said pump drive   output drive disk (65).