EP1151196B1 - Machine hydraulique differentielle a mouvement alternatif, en particulier moteur hydraulique differentiel - Google Patents

Machine hydraulique differentielle a mouvement alternatif, en particulier moteur hydraulique differentiel Download PDF

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Publication number
EP1151196B1
EP1151196B1 EP00900619A EP00900619A EP1151196B1 EP 1151196 B1 EP1151196 B1 EP 1151196B1 EP 00900619 A EP00900619 A EP 00900619A EP 00900619 A EP00900619 A EP 00900619A EP 1151196 B1 EP1151196 B1 EP 1151196B1
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EP
European Patent Office
Prior art keywords
piston
lantern ring
machine according
push
rod
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Expired - Lifetime
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EP00900619A
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German (de)
English (en)
French (fr)
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EP1151196A1 (fr
Inventor
Stéphane URRUTIA
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Dosatron International SAS
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Dosatron International SAS
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B13/00—Pumps specially modified to deliver fixed or variable measured quantities
    • F04B13/02—Pumps specially modified to deliver fixed or variable measured quantities of two or more fluids at the same time
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/103—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber
    • F04B9/107—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber rectilinear movement of the pumping member in the working direction being obtained by a single-acting liquid motor, e.g. actuated in the other direction by gravity or a spring

Definitions

  • a differential hydraulic motor of this type is known, for example from EP-B-0255791, or from US-A-5505224, and can be used for an injection device an additive in a main fluid.
  • Ways elastic consist of springs of small size relative to the pieces making up the entire mechanism. These springs act transversely to the direction of piston displacement and require rod type return means, rotatably mounted around axes of rotation which are generally orthogonal, or at least intersecting, to the lines of action of efforts developed by the springs.
  • EP-A-0 161 614 shows a hydraulic motor differential in which the trigger means include connecting rods subjected to the action of means elastic arranged transversely. The change of position of the valves, and the inversion of the movement, impact with one pin against another room. These shocks are a source of noise and detrimental to engine longevity.
  • US-A-5,513,963 shows a hydraulic motor differential in which the locking system is passive, i.e. not ordered. The switching is caused only by the direct action of the springs on the sealing elements which eventually balance the holding forces from locking and effects Hydraulic. Such a design does not allow to accumulate an energy greater than that capable of upset the balance.
  • the object of the invention is, above all, to provide a hydraulic machine, in particular a hydraulic motor differential, which is of simple construction, while having elastic means exerting a following force the geometric axis of displacement of the piston, and which reduce friction caused by spring load and guide surfaces.
  • the invention also aims to increase the lifespan of devices by reducing wear on parts. Yield and speed of the machine are also to be improved.
  • the design of the machine must allow sequential switching, guaranteeing repeatability and reliability, and allow to accumulate energy greater than that capable of breaking the balance, so to have a high operating margin.
  • the elastic means include a coaxial lantern spring and surrounding it.
  • the spring is a spring of helical compression.
  • This spring can thus have a large diameter and a large section of wire, which makes it possible to obtain great operating flexibility.
  • the strong section spring wire gives it good resistance to corrosion wear.
  • the lantern is guided in its lower part by a cylindrical zone of the piston differential.
  • At least one pusher is provided at each end axial of the lantern, the push button (s) of a end being independent of the push button (s) the other end of the lantern, these pushers being in support against the elastic means and being retained axially by stops provided on the lantern, which guides the pushers in translation.
  • the lower pusher may have a crosspiece diametral fitted with a rod coaxial with the piston, in projection on the side opposite to the elastic means.
  • the rod tightly crosses a transverse wall of the piston and comes into abutment, at the low end of travel, against a transverse bar which bears against a part of the envelope.
  • the bar can be mounted sliding in a support linked to the piston.
  • the diametrical cross member can be secured to a ring resting against the lower edge of the lantern, this ring surrounding the side wall of the lantern which has two longitudinal openings of guide through which the crosspiece passes.
  • Two diametrically opposite upper lifters are provided and are guided by the lantern, in particularly by said longitudinal openings.
  • the lantern may have an upper tray inwardly provided with two diametrically notches opposite in which are engaged and slide the upper lifters.
  • the upper tray can be snapped together.
  • the switching means include advantageously valves.
  • the whole lantern, elastic means and pushers has an axial symmetry of achievement guaranteeing the balance of different efforts involved, and making it possible to reduce the risks of jamming.
  • a device of the type three-axis knee brace including a link and a trigger.
  • the link is hinged at one end to the top shelf of the lantern and its other end on the trigger; the trigger is itself articulated on a part linked to the piston.
  • the trigger has two extensions diametrically opposed proper to come into abutment against a stop linked to the piston, respectively above and below this stop following a rotation of approximately 180 °, each extension of the trigger being specific to cooperate with a projection provided respectively on a upper pusher and a lower pusher for trigger the trigger when the elastic means are under sufficient load.
  • the invention consists, apart from the provisions outlined above, in a number other provisions which will be more explicitly question below in a detailed description examples of construction, with reference to the drawings attached, but which are in no way limiting.
  • Figure 1 of these drawings is an axial section vertical of a differential hydraulic motor according to the invention.
  • Figure 2 is a view from the left with respect to Figure 1, of engine components located inside the casing, the differential piston not being represented.
  • Figure 3 is a section along the line III-III of Fig. 2.
  • Figure 4 is a partial axial section, similar to Figure 1, showing the hydraulic motor in another configuration.
  • Figure 5 is a section through the lantern, pushers and elastic means according to line V-V of Figure 6.
  • FIG 6 is a top view with respect to Figure 2, the valves being removed.
  • Figure 7 is an exploded perspective view of engine components, the differential piston not being represented.
  • Figure 8 is a perspective view of the lantern alone.
  • Figure 9 is a perspective view of all the elements arranged inside the engine casing, the differential piston being shown outside.
  • Figure 10 illustrates in perspective a particular realization of rod for the device knee pad.
  • Figure 11 is a partial section, similar to Fig. 4, illustrating a toggle device equipped with the link of Fig. 10.
  • a hydraulic machine M consisting of a differential hydraulic motor 1.
  • This motor has a casing 2, or machine body, consisting of upper part 2a and lower part 2b tightly assembled.
  • the general form of the envelope 2 is cylindrical of revolution around a vertical axis A-A.
  • the upper part 2a is closed, at its upper end, by a dome having an opening control unit 3 which, when the engine is running, is closed by a shutter 3a.
  • the lower part 2b has a wall inner cylinder 4 of smaller diameter determining an annular chamber 5 around it, at inside 2b.
  • This wall 4 further defines a cylindrical inner chamber 6 of smaller diameter that the chamber 7 determined in the upper part by 2a.
  • Part 2b has at its lower end a rim 10 surrounding an opening 11.
  • the rim 10 serves as a support for a sleeve 12 axially traversed by a rod 13, partially shown, for driving a mechanism, for example a pump.
  • Wall cylindrical of the sleeve 12 has openings 14 for the passage of the liquid.
  • a differential piston 15 is able to slide in reciprocating vertical motion in body 2 of engine.
  • the piston 15 has a large section at level of chamber 7 and a smaller section at bedroom level 6.
  • the differential piston 15 comprises a part upper 15a and lower part 15b assembled to each other in a sealed manner.
  • the upper portion 15a has an upper flange provided with a lip sealing 16 forming a skirt whose concavity is turned towards the side of chamber 5.
  • the lip 16 slides from tight against the inner cylindrical surface from part 2a.
  • the flange carrying the lip 16 is connected by a frustoconical part 17, of section decreasing downwards, to a cylindrical part 18 of diameter smaller than that of chamber 6.
  • Part 18 ends with a transverse bottom 19 perpendicular to axis A-A.
  • the lower part 15b of the piston 15 is essentially cylindrical open downwards, and closed at the top by a transverse wall 20 coming to be applied tightly against the bottom 19 to which it is fixed by screws not shown.
  • the wall 20 is provided at its periphery with a flange 21 which comes to cap the lower end of the part 15a.
  • the lower end of the part 15b is provided, externally, of a lip 22, facing the chamber 7, sliding tightly against the surface inside the wall 4.
  • Hydraulic switching means C (see in Fig.2 and Fig.9) for the supply of liquid and the evacuation of chambers 5, 6 and 7 are provided. These switching means C can take two stable states.
  • the switching means C include advantageously two valves 23 diametrically opposed (Fig. 2) suitable for cooperating with a seat 24 (Fig. 9) provided on the large section of the piston 15.
  • Two other valves 25 diametrically opposed, but angularly offset by compared to the valves 23, are provided to cooperate with seats provided in the small walls 19 and 20 piston section 15.
  • valves 23 and 25 close in reverse.
  • the valves 23 close in being lifted against their seat, while the flaps 25 close by being lowered against their seat.
  • of the compression springs R1, R2 are provided to ensure the application of the respective valves 23.25 against their seat and to compensate for manufacturing tolerances.
  • valves 23, 25 are the solution preferred ensuring very good watertightness, the means switching C could be made up of one or drawers.
  • valves 23, 25 are located in front and in back of the plan of Figure 1.
  • the switching means C are carried by a lantern 26, or open cylindrical housing, clearly visible on Fig. 7 and Fig. 8.
  • the lantern 26 comprises a body with side wall 27 cylindrical, coaxial with the piston, provided at its lower part of a projecting flange 28 radial.
  • Two diametrically opposed notches 29 are provided in the lower part, to which correspond, towards inside, two substantially semi-cylindrical projections 30 (FIG. 8), diametrically opposite.
  • Openings rectangular 31 are provided in the projections 30 for allow a snap-fitting of the valves 25 provided, at their upper end, elastic hooks 32.
  • the attachment of the valves 25 to the lantern 26 is provided for so as to leave a certain freedom of sliding vertical valve to allow R2 valve spring previously mentioned to properly apply the valve against his seat.
  • the cylindrical wall 27 of the body has two longitudinal openings 33, diametrically opposite, at vertical parallel edges.
  • the openings 33 are offset by a right angle relative to the notches 29, open upwards but are closed at the bottom above the flange 28.
  • the wall or body 27 further includes notches 34 open towards the high, diametrically opposite, in the same position angular as the notches 29 but separated from them by a sector 35 of matter.
  • the body 27 has hooks at the top 36, for example four in number, regularly distributed, with a certain flexibility.
  • a tray 37 open in its central part and having two diametrically opposed notches 38 clean to come in line with the openings 33, is planned.
  • This tray 37 has a number of openings rectangular 37a equal to the number of hooks 36 for snap hooks into these openings.
  • the front end edge of wall 27 forms a surface abutment 39 against which the face comes to bear bottom of the tray 37 while the hooks 36 are snapped in, as shown in Fig. 8.
  • the upper valves 23 are provided with hooks elastic bands 40 (Fig. 7) suitable for snapping into rectangular openings 41, diametrically opposite, provided on a crosspiece 42 comprising, in its part central, crown 43.
  • the tray 37 has two columns 44 perpendicular to the plate, diametrically opposite and provided with an axial hole. On these columns 44 come slidingly engage two diametrically opposite housings 45 provided on the cross 42, in the vicinity of the crown 43.
  • a spring R1 is placed around each column 44 between the plate 37 and crosspiece 42. According to the representation of Fig. 2, the springs R1 tend to raise the cross 42 and with it the valves 23 for them apply against their seat.
  • a means of restraint (not shown) may be provided at the upper end of columns 44 to prevent the crosspiece 42 from escaping. It should be noted that before assembling the valves 23 to the cross 42 and lantern 26, the latter is first installed in the piston 15, being guided by the cylindrical part 18 of this piston. The valves 23 are placed on the side of the lip 16 of the piston opposite the cross 42 and their rods provided with the hook 40 are engaged through the seat provided on the piston, then are attached to the crosspiece 42.
  • valves 25 on the other hand are hooked to the lantern 26 before its installation in the piston 15, the valve seats 25 located on the wall 19, 20.
  • the lantern 26 is driven by the piston 15 and can take two stable positions relative to this piston.
  • a first high position (Fig. 1) relatively the piston corresponds to the support of the valves 23 against their seat, while the lower valves 25 are open.
  • the second position, or low position of the lantern (Fig. 4) relative to the piston corresponds to the closure of the valves 25 and at the opening of the valves 23.
  • Maintaining in either position lantern 26 stable relative to piston 15 can be insured by any appropriate means.
  • a support 47 is disposed inside the lantern 26 and is fixed, for example by screws, on the transverse walls 19, 20 of the differential piston 15.
  • the support 47 consists of two parallel plates vertical 47a, 47b (Fig. 7) spaced from each other having a substantially trapezoid-shaped outline rectangle; a large vertical side is adjacent to the inner surface of the lantern 26, the edge opposite to this large vertical side is tilted.
  • the two plates 47a, 47b are interconnected in their upper part by a horizontal transverse bar 48.
  • a trigger or rocker 49 is disposed between the plates 47a, 47b and is articulated on a shaft 50 with geometric axis X1.
  • This tree 50 is carried by two bearings provided in plates 47a, 47b.
  • the X1 axis is located in a vertical diametral plane of the lantern 26.
  • the shaft 50 is located substantially at the height of the bar 48.
  • the trigger 49 has two extensions radial 49a, 49b whose thickness is less than that of the trigger, and which are offset from each other the other in the direction of the tree 50.
  • a link 51 (Figs. 3, 5 and 7) made of a material with a certain elasticity, for example in plastic material, establishes an articulated connection between the trigger 49 and plate 37 of lantern 26.
  • the link 51 as clearly visible in Fig. 7, a substantially the shape of an inverted U, both of which branches 51a, 51b, in the form of a plate, surround the rocker 49. These two branches are connected to their upper end by a lower bar 52 width than the branches.
  • Each branch has in its upper part, in the vicinity of bar 52, a hole circular 53 suitable for receiving an anti-friction ring 54 itself crossed by a tree 55 engaged, of outside, in a bearing 56 provided on the plate 37.
  • Two diametrically opposed bearings 56 and two shafts 55 are provided to cooperate with the two holes diametrically opposed 53.
  • Each shaft 55 projects radially inward to engage the ring 54 and the corresponding hole 53.
  • the radial end outside of shaft 55 is provided with a head rectangular 57 coming to hang in a housing correspondent of the stage 37.
  • the stages 56 admit X2 as a geometric axis, parallel to the shaft 50.
  • the axis X2 is located in the same vertical diametral plane as the axis geometric X1.
  • the two branches of the link 51 comprise in addition, towards their lower end, a hole circular 58 to serve as a bearing for a shaft 58a which crosses freely in rotation a circular hole in the rocker 49.
  • a ring 58b is provided at each end from shaft 58a into the corresponding hole 58.
  • X3 is the geometric axis of the tree 58a.
  • Two stable positions of the trigger 49 are determined by the coming into abutment of a part of extension 49a with the upper face of the bar 48 (Fig. 3), and on the other hand of extension 49b with the face lower of the bar 48 (Fig. 5). We go from one position to the other by a rotation of the release 49 about 180 ° relative to support 47, around X1.
  • the rocker 49 To cross the angular position for which the three axes X1, X2, X3 are in the same plane, the rocker 49 must cause slight deformation elastic of the link 51.
  • X3 passed to the side of X1 opposite to X2.
  • the traces of the three axes X1, X2 and X3 still form a flattened triangle, the X3 axis being slightly on the left of the plane passing through X2-X1.
  • the valves upper 23 are open while the valves 25 are closed.
  • Control means are provided to ensure a sudden change from the position of Fig. 3 to that of Fig. 5 and vice versa.
  • These control means include elastic means E exerting a force along the axis geometric A-A of displacement of the piston.
  • the elastic means E are arranged at the exterior of the cylindrical wall of the lantern 26 and are internally guided by the wall of the body 27 of the lantern 26.
  • the elastic means E are constituted by a single coil spring 59 coaxial with the lantern 26, and suitable for working essentially in compression.
  • the large diameter spring 59 allows to obtain a great flexibility of operation and contributes to a simple construction achievement.
  • the section of the coils of the spring is relatively important, which improves its resistance to wear and corrosion.
  • Triggering means D are provided for release, at the end of stroke of the piston 15, the energy accumulated by the spring 59 and to cause the sudden change in position of lantern 26 and switching means C relative to the piston 15.
  • the triggering means D include, in upper part, two upper pushers 60a, 60b diametrically opposed connected to their base by a ring circular 61, and a lower pusher 62 in part low.
  • the upper pushers 60a, 60b are constituted by vertical branches engaged and guided in the indentations 38 of the tray 37 of the lantern 26.
  • the ring 61 passes around the cylindrical wall of the body 27 of the lantern which also serves to guide the whole.
  • the pushers 60a, 60b have projections 63a, 63b radially inward which engage in the longitudinal openings 33 of the lantern, contributing also for guidance.
  • the projection 63a provided in the lower part of the pusher 60a extends radially inward from a distance sufficient to cooperate, at the top end of the piston 15, with extension 49b of trigger 49 (Fig. 3) and bring the trigger 49 to the position of Fig.5.
  • the thicknesses are offset so that 63a cannot cooperate with 49a.
  • the spring 59 bears against the ring 61 itself pressing against the underside of the plate 37.
  • the lower pusher 62 has a crosspiece diametral 64 passing through the openings 33 which provide the sliding guide of the pusher 62.
  • the crosspiece 64 is integral with a ring 65 surrounding the part lower of the body 27 of the lantern 26, and taking axial support against the flange 28. Openings substantially semicircular (Fig. 7) exist between the diametrical walls of the cross member 64 and the contour inside of ring 65, allowing passage of plates 47a, 47b of the support 47.
  • the crosspiece 64 is provided with a rod 66, coaxial to the piston 15, projecting from the side opposite the spring 59.
  • the rod 66 crosses tightly, thanks to a seal toric, a central opening of the walls 19, 20.
  • the bar 67 is slidably mounted in a retaining piece 69 fixed to the piston 15 under the wall 20.
  • the bar 67 has, on each of its long sides, a rib 70 parallel to the axis A-A, capable of sliding in a groove (not shown) provided in the part 69.
  • Maintaining and guiding the cross member 42 relative to the differential piston 15 is advantageously provided by two cylindrical columns 15d (Fig. 9) diametrically opposed, forming part integral with piston 15, projecting vertically above of the large piston section.
  • the crosspiece 42 comprises, towards each of its ends, a cylindrical ring 42d suitable for engaging with reduced play around the corresponding column 15d.
  • the two 42d rings like visible in Fig. 9, are located on either side of the cross 42.
  • Elastic means J (Fig. 5) are provided for recall the link 51 of the toggle mechanism in a locking position for which the axes X1, X2, X3 are not coplanar. According to the representation of Fig. 5 the link 51 is submitted, by the means return elastics J schematically shown, at a couple tending to rotate it clockwise clock around the tree 55.
  • the elastic means J may consist of a means of traction or compression arranged between a point of attachment on the link 51 and a hooking point fixed to the plate 37 lantern, or by a bending spring such as a substantially straight pin extending diametrically and leaning on one side against two pawns diametrically opposite, integral with the plate 37 and, the other side, in its middle part against a pawn in protruding upwards on the link 51.
  • the crosspiece 64 of the lower pusher comprises on one side a projection 64a upwards suitable for cooperating with the extension 49a of the rocker 49 during the descent of the piston 15.
  • the thicknesses are offset so that 64a cannot cooperate with 49b. Thickness offsets as well as the offsets of the cutting planes explain why 64a appears in Fig. 5 but not in Fig. 3.
  • the pressurized liquid arriving through the chamber 5 pushes the piston 15 upwards according to its large annular section, while the liquid from chamber 7 is discharged to the chamber 6 and the exhaust 9.
  • the pushers 60a, 60b are retained by the plate 37 against the action of the spring 59, while the lower pusher 62 is retained by the flange 28 of the lantern 26.
  • the upper end of the pushers 60a, 60b Towards the end of the upward stroke of the piston 15, the upper end of the pushers 60a, 60b abuts against the internal surface 3b of the dome of the envelope. The pushers 60a, 60b are stopped in their course ascending but the piston 15 continues to rise. The spring 59 is then compressed by the pushers 60a, 60b, against the lower pusher 62. The upper plate 37 lantern continues to rise and moves away from the base upper lifters.
  • Extension 49b is stopped, but piston 15 continues a little further upward driving the articulation shaft 50 of the rocker 49.
  • the latter goes so turn clockwise, depending on the representation of Fig. 1, around the tree 50 in causing a slight deformation of the link 51 for cross the position where the three axes X1, X2, X3 are in the same plane (their traces on the drawings are then aligned).
  • spring 59 can relax by causing rotation about 180 ° in the clockwise direction of rocker 49 which is supported by its extension 49b under the bar 48 in the position of Fig. 5.
  • the lantern 26 and the switching means C have moved into the second stable position, namely the low position, relative to the differential piston 15.
  • the ring 61 is again pressed against the plate 37.
  • the valves 23 are open while the valves 25 are closed.
  • the piston 15 is inverted since the pressurized liquid is admitted into the chamber 7 which is isolated from chamber 6.
  • the piston 15 is moves down in the configuration of Fig. 4.
  • extension 49a of rocker abuts against the projection 64a (Fig. 5) ce which causes a rotation of about 180 ° in the direction counter clock of the rocker 49 around the shaft 50. This change of position takes place suddenly under the action of the spring 59 which relaxes.
  • the piston 15 starts again for an upward stroke.
  • the invention allows the use of a spring compression 59 of large diameter which provides a large flexibility of operation and simple implementation of construction. Engine performance is improved and shocks during switching are reduced resulting in a quieter operation.
  • Figures 10 and 11 illustrate a variant of realization of a link 151 for the system with knee switch with three axes X1, X2, X3.
  • the link 151 is made in one piece made of an elastic material specified later.
  • This connecting rod 151 has a central portion substantially U-shaped with the lower transverse branch horizontal 151a is planned to constitute the tree of articulation of the rocker 49.
  • this horizontal branch 151a is connected to a kind of arch 151b, 151c substantially in an arc located in a plane orthogonal to branch 151a.
  • the hoops 151b, 151c are parallel. Their arched shape allows them to deform bending and these arches can then exert substantially tensile and compressive forces vertical, to allow passage from the position where the traces of the three axes X1, X2, X3 are aligned.
  • the hoops 151b, 151c extend at their upper end, by horizontal segments 151d, 151e bent outward and parallel to the branch 151a. These segments 151d, 151e have a certain elasticity in torsion around their axis geometric X2 so as to exercise a reminder on the branches 151b and 151e (and on branch 151a) in rotation around the X2 axis in a non-position coplanar with the axes X1, X2, X3 corresponding to a locking position.
  • the segments 151d, 151e are extend by other segments 151f, 151g curved to right angle on the side opposite to the poles, parallel between them, and orthogonal to branch 151a. The ends of these segments 151f, 151g can be embedded in a part K integral with the lantern 26, this part K possibly for example the plate 37.
  • an auxiliary opening 153 communicating with the previous one to pass the different rod elbows 151 through rocker 49 and to finally bring branch 151a into the opening 152.
  • the link 151 performs both the function of the link 51 and the function of the elastic means J of Figs. 1 to 9.
  • the link 151 is advantageously made with high strength longitudinal fibers mechanical, for example juxtaposed glass fibers, parallel to each other and embedded in a matrix made of plastic. Longitudinal fibers provide an elasticity in tension and compression in the direction vertical, at arches 151b, 151c. In the segments 151d, 151e, torsional elasticity is ensured by the plastic matrix.
  • the link 151 in Fig. 10 simplifies the toggle type locking system shown in Fig. 11.
  • the advantages of the realization of Figs. 1 to 9 are kept in the device of FIG. 11.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)
  • Retarders (AREA)
  • Motor Power Transmission Devices (AREA)
  • Actuator (AREA)
  • Fluid-Pressure Circuits (AREA)
EP00900619A 1999-02-09 2000-01-20 Machine hydraulique differentielle a mouvement alternatif, en particulier moteur hydraulique differentiel Expired - Lifetime EP1151196B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9901482A FR2789445B1 (fr) 1999-02-09 1999-02-09 Machine hydraulique differentielle a mouvement alternatif, en particulier moteur hydraulique differentiel
FR9901482 1999-02-09
PCT/FR2000/000116 WO2000047895A1 (fr) 1999-02-09 2000-01-20 Machine hydraulique differentielle a mouvement alternatif, en particulier moteur hydraulique differentiel

Publications (2)

Publication Number Publication Date
EP1151196A1 EP1151196A1 (fr) 2001-11-07
EP1151196B1 true EP1151196B1 (fr) 2003-07-30

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EP00900619A Expired - Lifetime EP1151196B1 (fr) 1999-02-09 2000-01-20 Machine hydraulique differentielle a mouvement alternatif, en particulier moteur hydraulique differentiel

Country Status (10)

Country Link
US (1) US6684753B1 (da)
EP (1) EP1151196B1 (da)
JP (1) JP2002536592A (da)
AT (1) ATE246314T1 (da)
DE (1) DE60004168T2 (da)
DK (1) DK1151196T3 (da)
ES (1) ES2202036T3 (da)
FR (1) FR2789445B1 (da)
PT (1) PT1151196E (da)
WO (1) WO2000047895A1 (da)

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WO2007080249A1 (fr) * 2006-01-13 2007-07-19 Dosatron International Machine hydraulique, en particulier moteur hydraulique, a mouvement alternatif
WO2007080250A1 (fr) * 2006-01-13 2007-07-19 Dosatron International Machine hydraulique, en particulier moteur hydraulique, et doseur comportant un tel moteur.
WO2007080251A1 (fr) * 2006-01-13 2007-07-19 Dosatron International Machine hydraulique, en particulier moteur hydraulique, a mouvement alternatif, et piston differentiel pour une telle machine
WO2017064197A1 (fr) * 2015-10-13 2017-04-20 Dosatron International Machine hydraulique et pompe doseuse reversible equipee d'une telle machine
US10197071B2 (en) 2013-01-17 2019-02-05 Dosatron International Controllable constriction device for the throat of a venturi channel for introducing a liquid additive into a stream of main liquid

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FR2844310B1 (fr) 2002-09-06 2005-12-30 Dosatron International Dispositif de dosage de liquide permettant une injection de plusieurs liquides differents
FR2847950B1 (fr) 2002-11-28 2005-01-07 Dosatron International Machine hydraulique, en particulier moteur, a mouvement alternatif, et doseur comportant un tel moteur
US6910405B2 (en) * 2003-07-08 2005-06-28 Dosmatic Usa, Inc. On/off switch for liquid additive injection pump
FR2873172B1 (fr) * 2004-07-15 2007-11-02 Dosatron Internat Sa Dispositif de dosage pour introduire un additif dans un courant de liquide
WO2008005996A2 (en) * 2006-07-05 2008-01-10 Stryker Corporation Medical/surgical lavage system capable of selectively and sequentially discharging either a base solution or a solution which includes a therapeutic agent
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US9079142B2 (en) 2013-03-11 2015-07-14 Oms Investments, Inc. Hydraulic mixing device for sprayer system
FR3120402B1 (fr) 2021-03-02 2023-04-14 Dosatron International Procede et pompe de dosage proportionnel a faible debit

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WO2007080249A1 (fr) * 2006-01-13 2007-07-19 Dosatron International Machine hydraulique, en particulier moteur hydraulique, a mouvement alternatif
WO2007080250A1 (fr) * 2006-01-13 2007-07-19 Dosatron International Machine hydraulique, en particulier moteur hydraulique, et doseur comportant un tel moteur.
WO2007080251A1 (fr) * 2006-01-13 2007-07-19 Dosatron International Machine hydraulique, en particulier moteur hydraulique, a mouvement alternatif, et piston differentiel pour une telle machine
FR2896279A1 (fr) * 2006-01-13 2007-07-20 Dosatron International Machine hydraulique, en particulier moteur hydraulique, et doseur comportant un tel moteur.
FR2896281A1 (fr) * 2006-01-13 2007-07-20 Dosatron International Machine hydraulique, en particulier moteur hydraulique, a mouvement alternatif.
FR2896280A1 (fr) * 2006-01-13 2007-07-20 Dosatron International Machine hydraulique, en particulier moteur hydraulique, a mouvement alternatif, et piston differentiel pour une telle machine.
EA013486B1 (ru) * 2006-01-13 2010-04-30 Дозатрон Энтернасьональ Гидравлическая машина, в частности гидравлический двигатель, и дозатор, содержащий такой двигатель
EA013712B1 (ru) * 2006-01-13 2010-06-30 Дозатрон Энтернасьональ Гидравлическая машина, в частности гидравлический двигатель с чередующимся движением
CN101371040B (zh) * 2006-01-13 2012-11-28 多沙特隆国际公司 可往复移动的液压机械尤其是液压马达
US10197071B2 (en) 2013-01-17 2019-02-05 Dosatron International Controllable constriction device for the throat of a venturi channel for introducing a liquid additive into a stream of main liquid
WO2017064197A1 (fr) * 2015-10-13 2017-04-20 Dosatron International Machine hydraulique et pompe doseuse reversible equipee d'une telle machine
EA034841B1 (ru) * 2015-10-13 2020-03-27 Дозатрон Энтернасьональ Гидравлическая машина и реверсивный дозирующий насос, оснащенный такой машиной

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DK1151196T3 (da) 2003-10-27
FR2789445B1 (fr) 2001-03-23
FR2789445A1 (fr) 2000-08-11
ATE246314T1 (de) 2003-08-15
PT1151196E (pt) 2003-11-28
DE60004168T2 (de) 2004-04-15
EP1151196A1 (fr) 2001-11-07
JP2002536592A (ja) 2002-10-29
US6684753B1 (en) 2004-02-03
WO2000047895A1 (fr) 2000-08-17
ES2202036T3 (es) 2004-04-01
DE60004168D1 (de) 2003-09-04

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