FR2510670A1 - HYDRAULIC MOTOR WITH BARREL - Google Patents

Abstract

THIS HYDRAULIC BARREL MOTOR, DESIGNED TO PROVIDE A HIGH ROTATION TORQUE AT REDUCED SPEED, FEATURES BETWEEN THE OUTPUT SHAFT 8 AND THE INCLINED DISC 6 WHICH IS ANIMATED WITH A NUTATION MOVEMENT, DRIVE MEANS SERVING AT THE SAME TIME OF REDUCER 13, 14 WHICH TRANSFORMS THE FREQUENCY OF THIS NUTATION MOVEMENT INTO A SLOWER ROTATION SPEED OF THE OUTPUT SHAFT 8. THIS SPEED REDUCER CONSISTS OF A STRAIGHT TEETH 13 ON THE FACE OF THE INCLINED DISC 6 TURNED TOWARDS THE OUTPUT SHAFT 8 AND, ON THE END OF THIS SHAFT TURNED TOWARDS THE INCLINED DISC 6, A COUNTER-TEETH 14 HAVING A DIFFERENT NUMBER OF TEETH FROM THAT OF THE RIGHT TEETH 13 OF THE INCLINED DISC.

Description

The present invention relates to a hydraulic motor comprising a)

  pistons arranged in a txe barrel

  being distributed around a central axis of it

  Ci, these pistons being able to be moved while being sol-

  licit by a cyclically controlled pressurized fluid, b) an inclined disc supported by sound

  center and attacked by the free ends of the pis-

  tones to generate a mutation movement, c) an output shaft located in the extension of the axis of the barrel and coupled, by means of drive means, to the inclined disc, so

  that the mutation movement of this disc is trans-

  forms a rotational movement of the output shaft

  tie, and d) a speed reduction mechanism.

  The problem to which the invention has provided a solution

  tion consisted in creating a hydraulic motor with axial piston slowly rotating, which is space-saving, of simple structure and which, with a good coefficient of

  efficiency, ensures high torque.

  In hydraulic axial piston motors

  of the kind described above, the means of training

  between the inclined disc and the output shaft are

  designed so that the latter rotates quickly

  which corresponds to the frequency of the movement of nuta-

tion of the tilted disc.

  Since the power of the hydraulic motor ultimately depends on the flow of pressurized fluid which

  cross, one cannot, with a motor of small encumbrance-

  ment, obtain a high power only if the frequency

  of nutaticn of the inclined disc is itself high.

  In other words, the output shaft must rotate quickly.

  and can only provide a low torque

  tion, When the output shaft of such a hydrau-

  lique must be running at slow speed, so it must be ac-

  couple with a speed reducer It is therefore known to associate with a hydraulic motor with axial piston having an output shaft rotating at high speed a speed reducer forming a separate device, for

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  transform such a motor into a slow speed motor with a high rotational angle

  a separate complementary speed reducer

complicates a complication.

  There are also known hydraulic gear motors, slow speed, the volume swallowed is high In these motors, the output shaft can

  turn slowly without the interposition of a reduction gear.

  However, with this type of motor, the maximum admissible fluid pressure can, by construction, only be low, hence necessarily a maximum torque

  Furthermore, these motors have a coefficient of

dement relatively weak.

  I The problem to which the invention has provided a solution

  tion therefore consisted in making a hydraulic motor with axial piston d * enre described in the preamble of such

  so that it is able to provide a couple of rota-

  tion high although this engine is compact and

simple structure.

  The solution to this problem is characterized by the fact that the drive means are designed as a speed reducer which transforms the frequency of the nutation movement of the inclined disc into a lower speed of rotation of the output shaft and which consists of a straight toothing on the face of the inclined disc facing the output shaft, a disc which is supported so as to be able to tilt on all sides and by a counter-toothing with a different number of teeth provided at the end of the output shaft located on the side

  inclined disc, this counter-toothing being in bare engagement

  aunt with the said toothing of the inclined disc Thus, in the hydraulic barrel motor according to the invention,

  the speed reducer is an integral part of the mo-

  The drive means between the inclined disc

  and the output shaft are themselves designed to constitute

  kill this reducer, so that a separate reducer from-

  just superfluous The motor can run at a frequency

  of high nutation of its inclined disc, with a large

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  of driving power and therefore also a small footprint, and yet it provides the output shaft, rotating slowly depending on the reduction ratio chosen, a high torque made possible by a much higher operating pressure than that of gear motors At the same time a good efficiency is obtained and, due to the high nutation frequency, the shaft

  output rotates regularly, practically without pul-

sations.

  It is advantageous that between the inclined disc and the barrel operate support means which transform the frequency of the nutation movement of the inclined disc into slower, or even zero, rotation of this disc.

  in the barrel By choosing the name appropriately-

  number of teeth # analogously to the calculation of the number of teeth on the planetary gears, we can obtain a reduction by the desired value The inclined disc may not turn in the barrel, or turn in the barrel at a speed different from the frequency nutation and in a direction depending on the ratio

many teeth.

  The support means may consist of a toothing on the inclined disc with which a toothing

  supporting the barrel is in nutante grip.

  In this arrangement, the toothing of the inclined disc which forms part of the support means is itself

  time the right teeth which form part of the reduction

  ibeur tor Such means of support are of

  ception simple and easy to perform.

  To vary the rotation speed at the exit

  tie we can ensure that the counter-toothing is

  formed on an interchangeable piece integral in rotation

  tion of the output shaft but which can be detached from the latter It then suffices to provide several interchangeable parts of this kind having different numbers of teeth. It is also possible to transform the hydraulic motor according to the invention into a motor with fast output speed, equal to the nutation frequency, this -4- by means of an interchangeable piece integral with the output shaft and applied by a surface against the inclined disc Thus, by simple exchange of a

  single piece, the field of use of the hydraulic motor

  The invention can be greatly expanded. According to a particularly simple arrangement for transforming the motor according to the invention into a high-speed device, an interchangeable part is provided, which has an inclined entrainment surface which is applied against the front edges of

  the right toothing of the incling disc.

  When the hydraulic motor according to the invention comprises a central control shaft which is provided with

  distributors of fluid under pressure to the pistons

  engine tones and which rotates in the barrel at the

  quence nutation of the inclined disc with which this shaft is engaged, it is possible to associate with this

  clentral commarid tree a secondary output tree.

  Thanks to the latter, a single motor can provide a high torque at low speed and, on the other hand, a low torque at low speed.

high speed.

  An exemplary embodiment of the invention is described below by referring to the appended drawing I on the latter, FIG. 1 is a view in longitudinal section of a hydraulic barrel motor according to the invention, the FIG. 2 illustrates a detail of the control shaft of the hydraulic motor according to FIG. 1 i, in an angular position different from that in FIG. i, and FIGS. 3 and 4 are sectional views of the control shaft according to the fig 2, along the cutting lines

  III-III and IV-IV respectively, trace 6 es in fig 2.

  The hydraulic motor shown in the drawing includes

  a barrel 1 to which 6 is tightly fixed a neck

  around the longitudinal geometrical axis A of the barrel are distributed cylindrical chambers 2 parallel to this axis and at equal angular distance

each other.

  _ 5 _ The drawing shows dux 5 in practice, at least three, preferably five or more, are arranged in the barrel, an odd number being advantageous In each of these cyclic chambers 2 a piston 3 can slide and slightly tilt Each piston 3

  is supported by its rear end against a res-

  compression spell 4 symbolized by dashed lines The other end of each piston is engaged in a hemispherical support housing 5 formed in a

  inclined disc 6 This disc is available O in a recess

  ment 7 of the barrel forming an acute angle with the axis

  geometric A This recess 7 is closed towards the outside

laughing through the lid.

  In the cover the is rotatably mounted, coa-

  1 _ xial to the geometric axis A, an output shaft 8

  str needle bearings 9 One piece interchan-

  geable 10 which, at its end facing the disc

  inlin 6 6, forms a head l Oa consisting of a glue-

  rette, is removably attached to the output shaft

  tie 8 and so as to rotate with it On the head 10 a is provided, on the face of this head facing the inclined disc 6, a rounded support nipple lo O b which enters a rounded support recess It formed in the inclined disc 6 and thanks to which the latter is supported with the possibility of tilting, Between the face of the head l Oa turned towards the output shaft 8 and the cover of the barrel is interposed

a goal 6 e axial 12.

  On the side of the inclined disc 6 facing backward

  output bre 8, a straight toothing 13 is formed,

  the cuneiform teeth widen towards the former.

  With this toothing 13 cooperates a counter

  corresponding cuneiform toothing 14 on the face d: ex -

  end of the tto O 10 turned towards the worn disc 6

  surrounding the rounded nipple lob.

  On the inner surface of the barrel cover 1a, therefore integral with the latter, a support dnture 15 is formed which cooperates with the part of the straight toothing 6 - 13 which extends radially outwards beyond

counter teeth 14.

  To bring the pressurized fluid, notably hydraulic oil, to the hydraulic motor, and to evacuate it, connections 16 and 17 are provided in the barrel. A control shaft 18 is rotatably mounted in the barrel 1, in the geometric axis A As can be seen in particular in FIGS. 2 to 4, this shaft 18 is provided with control channels and grooves by which, in connection with the grooves and channels formed in the barrel, the pressurized fluid is cyclically brought to the chambers cylindrical 2 and evacuated from them At its end facing the inclined disc 6 the control shaft 18 disc carrier

  drive 19 which, by a corresponding inclined face

  at the inclination of the inclined disc 6, is in friction contact with the face of this disc facing the control shaft 18 The drive disc 19 rests, by its rear face, on an axial stop

  20 mounted at the bottom of the recess 7 of the barrel.

  The hydraulic barrel motor described above operates as follows, Via the control shaft 18, pressurized fluid is cyclically sent into the

  cylindrical chambers 2 and evacuated therefrom, conti-

  nuellement Therefore the pistons 3 are, at the rate of the arrival of the fluid, pushed out of these chambers by forcing the inclined disc 6 to describe a rocking movement around the central support nipple lob Since this rocking movement occurs cyclically,

  the inclined disc 6 therefore describes a nutation in the evi-

7 of the barrel.

  When the number of teeth of the back teeth is equal to that of the teeth of the right teeth 13, the meshing between the teeth 13 and 15 means that any rotation of the inclined disc 6 in the barrel 1 is excluded This is desired to obtain: n as low a rotation speed as possible at the outlet; this is

2510670

  why the number of teeth in 13 is the same as that

  at 15 in the preferred embodiment I 1 is always

  However, it is possible to design different numbers of teeth when you want the inclined disc to rotate in the barrel 1 In this case, however, the pistons 3 should attack the inclined disc 6

by sliding pads.

  The pistons 3 can follow the nutation movement because, as can be seen in FIG, they are held with a certain possibility of tilting and penetrate by domed heads in the support housings 5 The compression springs 4 guarantee permanent contact between the pistons 3 and the housings 5 The pistons 3 are traversed by a bore, so that their support on the inclined disc 6 is hydraulically relieved in a

great measure.

  The nutation movement of the inclined disc 6 is,

  via the drive disc 19 in con-

  tact with its rear face, transformed into a rotational movement of the control shaft 18 which corresponds to the frequency of the fine fluid pressure cycle, so that the arrival and evacuation of this

  fluid is thus controlled in the desired manner.

  The straight toothing 13 of the imined disc 6 is, in its radially inner part, in nutante engagement with the counter-toothing 14 of the interchangeable part The speed of rotation of the output shaft 8 depends on the relative number of teeth of these two toothing 3 and of the ratio between the number of teeth of the toothing 13 and that of the toothing 15 With an equal number of teeth the transmission ratio is s Member of teeth of the counter-tooth 14

  Number of teeth of the straight teeth 3 ire of the teeth

  toothing, 4 If for example the straight toothing 13 has 22

  teeth while the counter teeth 14 have 21, the demul-

  multiplication is equal to 21, 1 We can therefore, in nchoi-

  sissant a small difference between the numbers of teeth, 7 - to obtain a strong reduction and thus a low speed of rotation with the output shaft, from where a couple

high rotation 6.

  The teeth 13 and 14 thus form a speed reducer integrated into the hydraulic motor which allows, at high nutation frequency of the inclined disc 6 and therefore at high fluid flow, to rotate the output shaft 8 at low speed without separate reducer and to provide this shaft with a high torque,

  all this with a small footprint.

  By providing interchangeable parts 10 having different numbers of teeth in the counter teeth 14

  it is possible to provide 4 different demul-

  multiplication In any case, account must be taken of the g 4 o-

  m 6 sorting of the teeth When the right teeth 13 has da-

  vantage of teeth than the counter-teeth 14, there is an inversion of the direction of rotation One can also provide an * interchangeable part O 10 in which the straight teeth 14 is replaced by

  an inclined face, similar to that of the drive disc "-

  19, which rests by its surface on the fron edges.

  tales of straight teeth 13 or on a Misque de nuta-

  non & ntde In this case, the inclined disc 6 drives

  do the output shaft at the frequency of its nutation movement, so that this results in direct control. To the control shaft 18 can be connected a secondary sort of shaft 21 emerging from the barrel 2 on the side opposite to the primary output shaft 8 Thus it is possible to have, on the same hydraulic motor,

  on one side with a low speed of rotation with a

  ple of high rotation, on the other side of a rotation speed which corresponds to the frequency of nutatim of the inclined disc 6, with a weak rotational necka The secondary PTO can be used for example for the rapid speed of a machine, while the primary power take-off makes it work under normal conditions. It is also possible to install a tachometer on the secondary output shaft 21, and / or a brake. This 8 - -9 _ shaft could also drive an auxiliary pump, etc.

  The invention is not limited to the example of an example

  cution described above In particular, the system

  support plate which, in barrel 1, locks the

  inclined disc 6 in rotation, can be designed differently

  remment It would be possible for example to use

  for this a mobile restraint provision The den-

  support structure 15 could also be provided on the inner wall of the recess 7 and cooperate with

  a straight toothing of the inclined disc 6 A

  tion on the inner axial face of the recess 7 is also conceivable 5 in this case, it would be necessary to provide a corresponding counter-toothing on the back of the inclined disc These last two arrangements have the advantage that the diameter of the counter-toothing 14 on the interchangeable part 10 could be provided larger, thus allowing the transmission of forces

  larger between teeth 13 and 14.

  The compression springs 4 can be omitted and the cylindrical chambers 2 provided shorter as much if one makes sure that the pistons 3 are by their heads engaged in the support housings 5? prisoners movably on the inclined disc 6, for example by means of annular retaining washers arranged at the back of their heads This would allow

  to further shorten the hydraulic motor.

  It is obvious that the output shaft 8 and the interchangeable part 10 could be in one piece, provided that the possibility of being able to change

counter teeth 14.

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Claims (6)

  1 Hydraulic motor comprising a) pistons arranged in a fixed barrel while being distributed around a central axis thereof, these pistons being able to be displaced by being acted upon by a pressurized fluid cyclically controlled, b) an inclined disc bearing in its center and attacked by the free ends   pistons to generate a nuta- movement   tion, c) an output shaft located in the extension   axis of the barrel and coupled, by the   drive means, disc   tilted, so that the movement of nuta-   tion of this disc turns into a movement   of the output shaft, and d) a mechanism   gear reducer, this hydraulic motor   being remarkable in that the means of   are designed as a speed reducer   tesse (13,14) which transforms the frequency of the   nutation of the inclined disc (6) in one   lower speed of the output shaft   tie (8) and which consists of a straight toothing (13) on the face of the inclined disc (6) facing the output shaft (8), which disc is supported so that it can tilt from   all 8 sides, and by a counter-toothing (14) with nom-   different bre of teeth provided at the end of the output shaft (8) located c 8 inclined disc tee, this counter-toothing being in nutante engagement with   said toothing (13) of the inclined disc (6).   2 hydraulic motor according to claim 1, remarkable in that between the inclined disc (6) and the barrel (1) operate support means   (13,15) which transform the frequency of the movement   nutation of the inclined disc (6) in a rotation   tion of this slower disc in the barrel (1), may be zero. -11 -   3 Hydraulic motor according to the claim   tion 2, remarkable in that the support means (13,15) consist of a toothing (13)   on the inclined disc (6) with which a den-   support structure (15) integral with the barrel (1) is in nutante grip.   4 Hydraulic motor according to any one   that of the preceding claims, remarkable   in that the toothing (13) of the inclined disc (6) which forms part of the support means (13,15)   is at the same time the toothing (13) which forms a part   tie of the speed reducer (13,14).   Hydraulic motor according to any one   that of the preceding claims, remarkable   in that the counter-toothing (14) is formed on   an interchangeable part (10) integral in rotation   tion of the output shaft (8) but which can be detached from the latter, and in that several   interchangeable parts of this kind having names   different teeth are planned.   6 hydraulic motor according to claim, remarkable in that it is provided with a part   interchangeable which includes a surface   inclination applied against the front edges   straight teeth (13) of the inclined disc (6)   7 Hydraulic motor according to any one   as in the preceding claims, in which   is arranged a central control shaft which is   fitted with fluid dispensing parts under press.   the pistons of the engine and which turns in the   barrel at the nutation frequency of the inclined disc   born with which this tree is engaged, this engine being remarkable in that at the control shaft   (18) is connected to a secondary output shaft (21).