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Publication numberUS3670627 A
Publication typeGrant
Publication dateJun 20, 1972
Filing dateOct 13, 1969
Priority dateOct 15, 1968
Also published asDE1952046A1
Publication numberUS 3670627 A, US 3670627A, US-A-3670627, US3670627 A, US3670627A
InventorsValantin Alfred
Original AssigneeCharbonnages De France
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Device for driving a shaft in rotation
US 3670627 A
Abstract
A device for driving a shaft in rotation, of the kind comprising at least one set of two identical rotary jacks mounted on a common shaft, the annular space comprised between the cylindrical casing of each jack and the shaft coaxial with this latter being divided into two fluid-tight chambers of variable volume, separated on the one hand by a longitudinal abutment provided on the internal face of the said cylindrical casing, and on the other hand by a radial blade fixed longitudinally in the said shaft, the cylindrical casing of each jack being provided with a device for locking it with respect to a housing by which said casing is enclosed.
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Description  (OCR text may contain errors)

United States Patent Valantin 51\ June 20, 1972 DEVICE FOR DRIVING A SHAFT IN ROTATION Inventor: Alfred Valantin, Clermont, France Assignee: Charbonnages De France, Paris, France Filed: Oct. 13, 1969 Appl. No.: 865,918

Foreign Application Priority Data Oct. 15, 1968 France ..68170022 US. Cl ..91/167, 92/121, 92/52 Int. Cl. ..FlSb 11/18, FOlb 7/20, FOlc 9/00 Field ofSearch ..91/167, 167 A; 92/121 References Cited UNITED STATES PATENTS Floer ..9l/167 Primary Examiner-Martin P. Schwadron Assistant Examiner-Clemens Schimikowski Att0rney Karl W. Flocks [57] ABSTRACT A device for driving a shaft in rotation, of the kind comprising at least one set of two identical rotary jacks mounted on a common shaft, the annular space comprised between the cylindrical casing of each jack and the shaft coaxial with this latter being divided into two fluid-tight chambers of variable volume, separated on the one hand by a longitudinal abutment provided on the internal face of the said cylindrical casing, and on the other hand by a radial blade fixed longitudinally in the said shaft, the cylindrical casing of each jack being provided with a device for locking it with respect to a housing by which said casing is enclosed.

It comprises: a hydraulic circuit composed of two portions connected to a common tank; a first portion supplied by a main pump and a second portion supplied by a topping-up pump; the locking device of the cylindrical casing of one jack being constituted by a cylindrical housing enclosing the jack casing and comprising a fluid-tight annular chamber, in which the wall in contact with the outer surface of this same casing is a thin wall, the said annular chamber being connected by means of a three-way distributor with two positions, either to the said main pump or the the common tank.

6 Claims, 16 Drawing Figures 'PATENTEDJuu20 m2 3.670.627

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INVENTOR ALFRED VALANTIN ATTORNEY PATENTEOJuu2o m2 3,670,627

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FIG. 6C

FIG. 6e

DEVICE FOR DRIVING A SHAFT IN ROTATION The present invention relates to a device for driving rotary jacks in continuous or almost continuous rotation for the production of high torques, especially applicable to the production of motors intended to supply a high power with an overall size which is as small as possible.

Rotary jacks are already known from which there is obtained a movement of rotation at high torque, these generally comprising a hollow cylindrical casing known as the stator, and being provided with a longitudinal internal abutment mounted on a shaft having the same axis in which is fixed a blade de-limiting two fluid-tight chambers comprised between a lateral face of the blade and a lateral face of the abutment, each chamber being alternatively put under pressure and under depression in order to obtain alternately the rotation of the shaft and rotation of the cylinder, the above cylindrical casing being alternately locked and released with respect to a casing which encloses it.

Jacks of this kind do not however provide the possibility of obtaining a large angle of rotation of the shaft at each cycle, the value of this angle being always less than one revolution, and the utilization of these jacks involves a substantial proportion of dead time.

The present invention avoids these drawbacks by providing a device giving the possibility of obtaining rotation of a shaft through a much greater angle and even continuous rotation, thereby practically eliminating the dead times inherent in conventional rotary jacks.

The device according to the invention, of the kind comprising at least one group of two identical rotary jacks mounted on a common shaft, the annular space comprised between the cylindrical casing of each jack and the shaft coaxial with this latter being divided into two fluid-tight chambers of variable volume, separated on the one hand by a longitudinal abutment arranged on the internal face of the said cylindrical casing, and on the other hand by a radial blade fixed longitudinally in the shaft, the cylindrical casing of each jack being provided with a device for locking it with respect to the housing, is characterized in that it comprises a hydraulic circuit composed of two parts coupled to a common tank, a first portion supplied by a main pump co-operating on the one hand with the first chamberof the first jack and the first chamber of the second jack, and further co-operating with the locking devices of the cylindrical casings of the jacks, and a second portion supplied by a topping-up pump cooperating with the second chamber of the first jack and the second chamber of the second jack, these two chambers being coupled in parallel to the said topping-up pump and members for reversing the direction of circulation of the fluid between the corresponding chambers of the two jacks, cooperating through the intermediary of a control distributor with the elements of the hydraulic circuit, the locking device of the cylindrical casing of one jack being constituted by a cylindrical housing enclosing the said casing and comprising a fluid tight annular chamber, in which the wall in contact with the outer surface of this same casing is a thin wall, the said annular chamber being connected by means of a three-way distributor with two positions, either to the main pump or to the common tank.

In accordance with other characteristic features:

in each jack, the longitudinal abutment of the cylindrical casing is provided on one side with a control contact of a four-way distributor with two positions, the said contact cooperating with the corresponding blade and the said distributor co-operating with two conduits connected in parallel to the topping-up pump;

--The first portion of the hydraulic circuit comprises two valves for reversing the direction of circulation of the fluid in two conduits connected in parallel to the main pump and coupling this latter to the locking devices of the jacks and coupling said jacks to the common tank, these two three-way distributors with two positions being always simultaneously in positions contrary to each other, the control devices of the said distributors co-operating respectively with the fluid circulating in two conduits connected in parallel to the topping-up pump;

The first portion of the hydraulic circuit comprises a distributor for reversing the direction of circulation of the fluid between the first two chambers of the two jacks, the said distributor having four ways and two positions, its control members co-operating respectively with the fluid circulating in the conduits connected in parallel between the main pump and the locking devices of the jack.

According to an alternative form:

--A differential coaxial with each of the two jacks is interposed between them, the cylindrical casing of each of them being rigidly fixed to one of the two crown wheels of the said differential, its satellite pinions being fixed radially and uniformly spaced apart on the common shaft, and engaging with the said crown wheels;

The corresponding chambers of the two jacks are coupled in parallel to circuits which are themselves in parallel on the main pump, while the circuit of the topping-up pump comprises only two branches in parallel connected to the controls of the distributors for reversing the circulation of the fluid in the conduits connecting the main pump to the locking devices.

Other characteristic features and advantages of the invention will be more clearly brought out in the description which follows below, given by way of non-limitative example, reference being made to the accompanying drawings, in which:

FIG. la represents a longitudinal cross-section of a pair of jacks according to the invention;

FIGS. lb and 1c show respectively the transverse sections of the said jacks taken along the lines YY and Z--Z of FIG. la;

FIG. 2 shows the diagram of the hydraulic control circuits of the above pair of jacks:

FIGS. 3a, 3b, 3c, 3d and 32 show diagrammatically the successive stages of the operation of the pair of jacks;

FIG. 4 shows a longitudinal cross-section of another form of construction of a pair of jacks according to the invention;

FIG. 5 represents the diagram of the hydraulic control circuits of the pair of jacks in the form of construction shown in FIG. 4;

FIGS. 60, 6b, 6c, 6d and 6e show diagrammatically the successive stages of the operation of the pair of jacks in the form of construction shown in FIG. 4.

Referring now to FIGS. la, 1b and 1c, the device according to the invention comprises a set of jacks A and B mounted on a common shaft 1, comprising two cylinders 2a and 2b coaxial with the shaft 1 and forming a fluid-tight annular chamber between their internal longitudinal and transverse walls and the outer wall of the said shaft. Each of the cylinders 2a and 2b comprises a longitudinal abutment 3a (and 3b), directed parallel to a generator line arranged from one transverse wall to the other, the internal face of which is in fluid-tight contact with the shaft 1. In each of the parts of this shaft corresponding to the interior of the above cylinders, there are fixed radial blades such as 4a and 4b, the end faces of which are in moving and fluid-tight contact with the corresponding longitudinal inner faces of the cylinders 2a and 2b, and the transverse faces are also in moving and fluid-tight contact with the inner transverse faces of the said cylinders.

The annular space located between the shaft 1 and each of the cylinders 2a and 2b is thus divided by the abutment and the corresponding radial blade into two fluid-tight chambers such as C and C in the cylinder 2a and C and C in the cylinder 2b, and the volume of which varies when the abutment and the blade are in relative movement with respect to each other, the total volume of the two corresponding cham bers remaining constant.

The assembly formed by the cylinders 2a and 2b is enclosed by a common housing 5 comprising, facing each of the said cylinders, a closed annular space or chamber C or C separated from the outer face of the corresponding cylinder by a thin wall 5a or 5b; when one of these chambers is filled with a fluid under pressure, the thin wall produces a bindinghoop efiect on the corresponding cylinder and immobilizes it. Referring now to FIG. 2, the hydraulic circuit for driving the shaft 1 in rotation comprises a first portion, shown in thick lines, which comprises a main high-pressure pump PP coupled by the conduit to the chamber C of the jack A and by the conduit 11 to the chamber C of the jack B, and is coupled to the chambers C and C respectively by the conduits l2 and 13, the conduits l4 and permitting the coupling to the tank B of the chambers C and C through the intermediary of hydraulic distributors HV and HV respectively, each of the type with three ways and two positions, these latter being shown symbolically by the rectangles a and b respectively, the rectangle a of the distributor HV putting the pump PP in communication with the chamber C and its rectangle b putting this same chamber into communication with the tank B, while the rectangle a of the distributor HV establishes the connection between the pump PP and the chamber C and its rectangle b the connection between this same chamber and the tank D.

A distributor l-IV of the type with four ways and two positions 0 and b and the movement of which is controlled by appropriate devices known per se, actuated by the fluid pressure supplied to the said devices by the conduits l6 and 17, respectively branched on the conduits 12 and 13, is arranged on the pair of conduits 10 and 11 so as to permit reversal of the direction of circulation of the fluid between the chambers C and C.

This first conduit is completed by a pressure-limiting device 18, calibrated to a pressure P, mounted between the outlet of the pump PP and the tank, and by a pressure-limiting device 19 calibrated to a value p less than P, mounted between the return circuit of the said pump and the tank D.

The second part of the hydraulic circuit, shown in lines of normal thickness, comprises a topping-up pump PG connected on the one hand to the tank D and on the other hand coupled by the conduits 20 and 21, branched on the common conduit 22, respectively, to the chambers C of the jack A and C of the jack B. The conduit 22 may be connected to the control device of the distributor HV by means of the conduit 23, or to the control device of the distributor HV by means of the conduit 29, through the intermediary of the distributor l-[V of the type with four ways and two positions a and b, the position b enabling the topping-up pump to be put into communication with the control of the distributor HV through the intermediary of the conduits 22 and 23, and permits the control of the distributor I-iV to be put into communication with the tank D through the intermediary of the conduits 24 and 25, the position a permitting the topping-up pump to be put into communication with the control of the distributor HV through the intermediary of the conduits 22 and 24 and also the control of the distributor l-IV to be put into communication with the tank through the intermediary of the conduits 23 and 25.

The distributors HV and HV are identical and are displaced into position a by the effect of the pressure applied by the fluid on their control, and are returned to position b by a spring R when the effect of this pressure ceases. The distributor HV is of the latching type with mechanical control; its movement from position a to position b is obtained by means of the hydraulic end-of-travel contact FC,, placed on each of the abutments 3a and 3b, actuated by one or the other of the blades 4a and 4b arriving at the end of its travel against the corresponding abutment. This second part of the hydraulic circuit is completed by a pressure-limiting device 26 interposed between the tank and the outlet of the topping-up pump in order to protect this latter, and is calibrated to a pressure P,. In addition, a non-retum valve 27, calibrated to a pressure A p is interposed between the return of the main pump PP and the topping-up pump PG.

in the FIG. 2 there has been shown the position of the whole of the device when the distributor HV occupies the position b. Under these conditions, the distributor HV the control of which is under pressure, permits the passage of the fluid under pressure sent by the pump PP into the conduits l2 and 16, which has the effect of maintaining the chamber C under pressure and immobilizing the cylinder 2a, and of pushing or maintaining the distributor HV in the position a while the distributor HV is in the position b, its control being under depression, which has the effect of putting the conduit 13 and therefore the chamber C under depression, together with the conduit 17.

The passage of the distributor HV to the position a has the effect of putting the conduit 24 under pressure and in consequence to cause the distributor HV to pass to the position a and to put under depression the conduit 23 and in consequence to cause the distributor HV to pass into the position b. The conduits 12 and 16 are then under depression while the conduits 13 and 17 are under pressure for this reason, the cylinder 2b is immobilized while the cylinder 2a is freed and the distributor l-lV is pushed from the position a to the position b.

Under these conditions, and referring to FIGS. 2, 3a, 3b, 3c, 3d and 3e, the operation of the whole of the device is as follows: the jacks A and B being assumed to be simultaneously and respectively found in the conditions shown in FIGS. 3a and 3b, for which the end-of-travel contact PC, has just been actuated by the blade 4b of the jack B and occupies the position b, the main pump PP and the topping-up pump PG being also assumed to be in operation, the distributor l-lV operated by the contact PC, into the position a drives in its turn the distributor I-IV into the position a. The fluid contained in the chamber c of the jack A being then put under pressure, the thin wall 5a is deformed and holds the cylinder 2a immobilized, while the chamber C is supplied with fluid under pressure. Under the effect of the thrust applied to the blade 4a, the shaft 1 common to the two jacks A and B is then driven in rotation about its axis X-X. The speed of rotation to of the said shaft and the torque which is applied to it depend on the dimensions of the blade, on the pressure and on the flow-rate Q of the fluid injected by the pump PP.

The blade 4b of the jack B is then driven by the shaft 1 at a speed of rotation which, with respect to a fixed reference point, has also the value or while the cylinder 2b is in turn driven in rotation about the axis XX at a speed m at least equal to 2W with respect to the same fixed reference point. In fact, the fluid stored in the chamber C is delivered into the chamber C as and when the volume of the chamber C,,, increases, the delivery flow-rate having in consequence at each instant, the same value Q as the flow-rate of supply of the fluid under pressure to the chamber C,,,, while the topping-up pump PG supplies a supplementary quantity of fluid with a flow-rate q to the chamber C The pressure of the fluid in the chamber C equal to p1, is greater by A p than the pressure p of the fluid in the chamber C. For this reason, the abutment 3b and in consequence the cylinder 2b is driven in rotation about X-X' with respect to the blade 4b at a speed at least equal to a); as the said blade is itself driven in rotation with respect to the fixed reference point at a speed 01, the speed of the cylinder 2b with respect to the fixed reference point, that is to say its absolute speed, is actually equal to at least 20).

As the abutment 3b of the cylinder 2b of the jack B rotates faster than the blade 4b, it comes up with the latter before the blade 4a of the jack A has completed its travel (see FIG. 30), and then moves at the same speed as the blade 4b until the blade 4a has completed its course, thus being located in the same relative positions as at the outset. When the blade 4a completes its travel (see FIG. 3d) it actuates the end-of-travel contact PC on the abutment 3a, which has the effect of placing the corresponding distributor in the position a and in consequence of causing the release of the cylinder 2a by putting the chamber C into communication with the tank through the intermediary of the distributor HV, passed into the position b, of causing the locking of the cylinder 2b of the jack B, due to the fact that the fluid is under pressure in the chamber C put into communication with the main pump PP, through the intermediary of the distributor HV which has passed into the position a. The jack B is then in the condition in which the jack A was placed at the beginning of the cycle and vice versa. The cycle then continues, the jack B carrying out the same function as the jack A in the previous stage and conversely, and ensuring the rotation of the common shaft until the whole assembly is in the same condition as at the beginning of the cycle, after which a fresh cycle is started.

It is clear that instead of arranging a set of two rotary jacks on the same shaft, it is possible to provide more, three or four for example, and thereby to increase the value of the torque available on the shaft.

Furthermore, in order to obtain rotation of the common shaft in both directions, it is only necessary to complete the hydraulic circuit described above by two distributors of the same type as the distributors l-IV and HV which have the purpose of changing-over the functions of the set of chambers C and C with the functions of the set of chambers C and C by a distributor of the same type as l-IV which ensures the switching over of the movements of fluid between the chambers C and C and by a distributor ensuring the change over of the functions of the chambers C and C In accordance with another form of embodiment, the rotary jack according to the invention differs from that previously described by the addition of a differential interposed between the two elementary jacks A and B. Referring now to FIG. 4, a jack of this kind is constituted by the same elements as the jack shown in FIGS. la, lb and 10, but further comprises two conical toothed crown-wheels 6a and 6b respectively fixed to the cylinders 2a and 2b and arranged face to face as shown in FIG. 4, and also the conical pinions 7 engaging simultaneously with the toothed crown-wheels 6a and 6b, and the axes of which are located in the same plane, perpendicular to the axis X-X' and intersecting on this latter at the point 0, the axes of the said pinions being uniformly spaced apart from the other. These bevel pinions, the number of which is suitably chosen and may be for example from one to six, pivot in the shaft 1 when it is given a movement of rotation.

The hydraulic control circuit of a jack of this kind, shown in FIG. 5, is similar to that of the previous jack, but comprises a few simplifications with respect to this latter. In fact, the chambers C and C on the one hand and C and C on the other are respectively connected in parallel on the main pump PP, in such manner that when the chambers C and C are simultaneously under pressure, the chambers C and C are simultaneously under depression and vice versa, the changing over of the functions being effected by means of the distributor HV,. In this way, the non-return valve can be eliminated, since the over-pressure Ap necessary in the previous case for the driving in rotation of that of the two cylinders 2a which is mobile, is no longer necessary. In consequence, the pressurelimiting device 26 can also be dispensed with.

Under these conditions, the operation of the jack, illustrated by the diagrams of FIGS. 6a, 6b, 6c, 6d and 6e is as follows:

As the distributor l-IV actuated by the end-of-travel contact FC has just taken-up the position b (see FIG. 5), the distributor I-IV actuated by I-IV is placed in its turn in the position a, which has the effect of putting the distributor l-IV into the position a, and in consequence of causing the jack A to drive, since the chamber C is supplied with fluid under pressure through the intermediary of the portion a of the distributor HV and since the fluid has been put under pressure in the chamber C through the intermediary of the position a of the distributor l-IV the cylinder 2a being thereby locked.

The thrust which is applied on the blade 3a imparts to the shaft 1 a speed of rotation W with respect to a fixed reference point, and also a torque, the value of this speed and this torque being, as previously, a function of the dimensions of the blade, of the pressure and of the flow-rate of the fluid utilized. The blade 3b is then driven in rotation by the common shaft 1 at the same speed W as the blade 3a with respect to the same fixed reference as above, but the crown-wheel 6a of the differential, coupled to the locked cylinder 2a has zero speed, and the pinions 7 driven by the shaft 1 in a movement of rotational drive about the axis X-X at the speed W impart to the crown-wheel 6b, coupled to the cylinder 2b, a speed of rotation about the same axis X-X having a value of 2W with respect to the fixed reference point.

During the course of this movement, the increase of the volume of the chamber C has the same value as that of the chamber C these two chambers being simultaneously supplied with fluid under high pressure, at the same pressure and with the same flow-rate. For this reason, a thrust is produced which, being supported on the blade 3b, is applied on the cylinder 2b through the intermediary of the abutment 4b and produces there a torque of the same value as that which is applied to the blade 4a of the jack A. This torque is transmitted through the intermediary of the crown-wheel 6b, to the pinions 7 which transmit it to the shaft 1 by their arbors.

In this way, perfect synchronization is obtained of the relative movements of the cylinders 2a and 2b, respectively relative to the blades 4a and 4b, and there is transmitted to the common shaft 1 the sum of the torques developed by each of the jacks A and B.

When the blade 40 has just completed its travel (see FIG. 6c) and actuates the end-of-travel contact PC the corresponding distributor passes from the position b to the position a, thus causing the change-over of the distributor I'IV; from the position b to the position a and in consequence that of the distributor HV, from the position a to the position b, which has the effect, on the one hand, of locking the cylinder 2a, the fluid under pressure being admitted to the chamber C of releasing the cylinder 2b, the chamber C being put to the tank, and of supplying fluid under pressure to the chambers C and C and in consequence of interchanging the functions of the jacks A and B, the cycle continuing as shown in the diagrams of FIGS. 6d and 6a until the whole assembly is again returned to the initial condition shown in the diagram of FIG. 6a.

This second form of embodiment has the further advantage of slightly simplifying the hydraulic circuit, and also that of permitting the continuous utilization of the torque supplied by the two jacks A and B. In addition, as this hydraulic circuit is perfectly symmetrical with respect to the two jacks, in order to obtain the possibility of rotating the shaft I in both directions, it is only necessary to provide in this circuit two distributors which interchange the functions of the chambers C and C and which respectively couple the chamber C to the position b of the distributor I-IV and the chamber C to the position a of this same distributor.

I claim:

1. A shaft driving arrangement comprising in combination: a shaft having at least one set of two identical rotary driving members mounted thereon, said driving members being in the form of a first and a second cylindrical casing in coaxial relationship around such shaft and being separated therefrom by an annular space, each of said cylindrical casings having a longitudinal abutment on its inner face, said shaft having a radial blade extending longitudinally thereof and cooperating with said longitudinal abutment to form first and second fluid-tight variable volume chambers in said annular space, said chambers being separated on one hand by said longitudinalabutment and on the other hand by said radial blade; a cylindrical housing enclosing each of said casings and including a pair of annular fluid-tight chambers each of which has a thin wall portion in contact with the outer surface of one of said casings, said annular chambers being selectively filled with fluid to lock said housing and one of said casings together so that as the volume of the variable volume chamber is varied the shaft is driven; an hydraulic circuit for reversing the direction of circulation of fluid between corresponding chambers of the two driving members, said circuit comprising a first portion and a second portion, a common tank for said two portions of the hydraulic circuit, a main pump adapted to supply said first portion of the circuit, a topping-up pump adapted to supply said second portion of the circuit, and a three-way distributor device with two positions to alternatively connect one of said annular chambers either to said main pump or to said common tank.

2. A driving device as claimed in claim 7, and further characterized by:

two conduits connected in parallel on said topping-up -a four-way distributor device with two positions, adapted to co-operate with said two conduits,

a control contact mounted on said longitudinal abutment and ensuring the control of said distributor device with four ways and two positions, said contact co-operating with the corresponding said blade.

3. A driving device as claimed in claim 2, further characterized by:

two conduits connected in parallel on said main pump and connecting said pump to said locking devices and connecting said devices to said common tank,

two distributors with three ways and two positions for reversing the direction of circulation of the fluid in said two conduits connected in parallel on said main pump, said two distributors being always simultaneously in contrary positions with respect to each other,

control devices for said reversing distributors, co-operating with the fluid circulating in said two conduits connected in parallel on said topping-up pump,

two further conduits connected in parallel on said main pump and connecting said pump to said first chamber of said first casing and to said first chamber of said second casing,

a four-way distributor with two positions for reversing the direction of circulation of the fluid, mounted on said two other conduits,

control devices for said reversing distributor co-operating with the fluid circulating in said conduits connected in parallel between said main pump and said locking means,

a conduit in parallel on said topping-up pump coupling said latter pump with said second chamber of said first casing and with said second chamber of said second casing.

4. A driving device as claimed in claim 7, and further,

characterized by:

-a differential gear interposed between said two driving members comprising: two toothed crown-wheels each rigidly fixed to said cylindrical casing of one of said driving members,

--satellite pinions fixed radially and uniformly spaced apart on said shaft and adapted to engage with said toothed crown-wheels.

5. A driving device as claimed in claim 4, and further characterized by:

two conduits connected in parallel on said topping-up --a four-way distributor device with two positions cooperating with said two conduits,

a control contact mounted on said longitudinal abutment and ensuring the control of said four-way distributor device with two positions, said contact co-operating with said corresponding blade,

two conduits connected in parallel on said main pump and coupling said latter pump with said locking devices and coupling said devices to said common tank,

two distributors with three ways and two positions for reversing the direction of circulation of the fluid in said two conduits connected in parallel on said main pump, these two distributors being always simultaneously in contrary positions with respect to each other,

-control devices for said reversing distributors co-operating with the fluid circulating in said two conduits connected in parallel on said topping-up pump,

two other conduits connected in parallel on said main pump and coupling in parallel said corresponding chambers of said two driving members, a four-way distributor with two positions for reversing the direction of circulation of the fluid mounted on said two other conduits,

control devices for said reversing distributor adapted to co-operate with the fluid circulating in said conduits connected in parallel between said main pump and said locking devices.

6. A driving device as claimed in claim 7, and further characterized by:

a first calibrated pressure-limiting device mounted between said main pump and said tank,

a second pressure-limiting device, calibrated to a value higher than that of said first pressure-limiting device and mounted between said topping-up pump and said tank,

-a non-retum valve mounted between said first and second pressure-limiting devices.

Patent Citations
Cited PatentFiling datePublication dateApplicantTitle
US3279329 *Sep 28, 1964Oct 18, 1966Bergens Mek VerkstedCranes
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US4759186 *Dec 26, 1985Jul 26, 1988Sundstrand CorporationSelf-powered rotary actuator utilizing rotation-generated centrifugal head
US5809955 *Apr 10, 1997Sep 22, 1998Mitsubishi Jidosha Kogyo Kabushiki KaishaHydraulic actuator and variable valve driving mechanism making use of the same
US20130092482 *Apr 15, 2011Apr 18, 2013Messier-Bugatti-DowtyHydraulically regulated electromagnetic actuator, and landing gear fitted with such an actuator for controlling same
Classifications
U.S. Classification91/167.00A, 92/52, 92/121
International ClassificationF15B15/12, F15B15/00
Cooperative ClassificationF15B15/12
European ClassificationF15B15/12