EP1565653B1 - Hydraulische maschine - Google Patents

Hydraulische maschine Download PDF

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Publication number
EP1565653B1
EP1565653B1 EP03767903A EP03767903A EP1565653B1 EP 1565653 B1 EP1565653 B1 EP 1565653B1 EP 03767903 A EP03767903 A EP 03767903A EP 03767903 A EP03767903 A EP 03767903A EP 1565653 B1 EP1565653 B1 EP 1565653B1
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EP
European Patent Office
Prior art keywords
piston
machine
switching means
valve
passage
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP03767903A
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English (en)
French (fr)
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EP1565653A1 (de
Inventor
Gaëtan THIERRY
David Higham
David Vacher
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Dosatron International SAS
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Dosatron International SAS
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Publication of EP1565653A1 publication Critical patent/EP1565653A1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/03—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with movement in two directions being obtained by two single-acting piston liquid engines, each acting in one direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/08—Distributing valve-gear peculiar thereto
    • F03C1/10—Distributing valve-gear peculiar thereto actuated by piston or piston-rod
    • F03C1/12—Distributing valve-gear peculiar thereto actuated by piston or piston-rod mechanically
    • 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
    • F04B9/1035—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 the movement of the pump piston in the two directions being obtained by two single-acting liquid motors each acting in one direction

Definitions

  • the invention relates more particularly, but not exclusively, to hydraulic motors. However, the invention could be applied to other machines, such as hydraulic pumps.
  • a first object of the invention is to provide a hydraulic machine of the kind in question whose size, particularly in the direction of movement of the piston, is lower.
  • Another object is to improve the sealing of the switching means and to avoid an influence of the position of the piston on these switching means.
  • Another object of the invention is to provide a hydraulic machine of simple structure making it possible to clearly define the races of the piston, especially to ensure a precise dosage in the case of a motor coupled to a metering device.
  • Ducts are provided in the body for supplying and discharging liquid from the chambers in connection with the switching means.
  • the body of the machine comprises, inside, an exchangeable cylindrical liner defining the cylindrical housing of the piston.
  • This cylindrical jacket may be of a different material than the body, more resistant to wear.
  • the body of the machine may be cylindrical and admit a first geometric axis, and the cylindrical housing of the piston has a second geometric axis, parallel to the first, but radially offset.
  • the switching means may comprise two valves having seats located in the body, or in a fixed part relative to the body, a valve ensuring the admission of liquid and the other valve ensuring the exit.
  • valves are preferably housed in the part of the body located, relative to the geometric axis of the body, opposite the geometric axis of the piston housing.
  • Each valve may comprise a cylindrical passage opening at each axial end to communicate with one of the chambers delimited by the piston.
  • Each passage is provided with a seat at each of its ends, and an axially movable core in the passage is adapted to close, depending on its position, one of the ends of the passage by bearing against the corresponding seat.
  • the geometric axes of the passages of the two valves are parallel to each other and to the direction of movement of the piston.
  • the passages may be close to each other, separated by a wall.
  • Each core may comprise, towards each end, a bulge, advantageously provided with a seal, able to bear against a corresponding seat, and the zone located substantially at mid-length of the passage communicates with an inlet or outlet duct leading to the outside.
  • This duct may have an orthogonal axis to that of the flap passage and cut this passage.
  • the cores of the valves are coupled to a lantern that can move parallel to the direction of the axes of the valve passages.
  • This lantern can be arranged in a housing of the body located on the side of the valves opposite a closure lid of the body. The lantern can occupy two stable positions.
  • the control means for a sudden change in the position of the switching means, and the lantern are advantageously formed by a rocker device oriented as a whole orthogonal to the direction of movement of the piston.
  • the rocker may comprise an articulated rod, at its end remote from the lantern, on an axis carried by the body of the machine, and a rotary arm articulated on the same axis, this arm being longer than the rod and carrying, at its far end of the axis of articulation, a hammer that can move in a window of the lantern; a leaf spring curve arc is compressed between two integral axes respectively of the rod and the arm.
  • the two stable positions of the rocker correspond to two configurations in which the link is on one side or the other of the arm.
  • a stopper plug is rotatably mounted in the housing of the body below the lantern and allows, in a given angular position, to stop the lantern substantially halfway to ensure a bypass function.
  • a calibrated spring valve is advantageously disposed between the inlet and the outlet so as to open in the event of a rise in pressure drop.
  • the invention also relates to a metering device equipped with a hydraulic motor constituting a machine as defined above, characterized in that it comprises an injection device comprising a cylindrical metering body fixed to the body of the engine, coaxially to the housing of the engine piston, and a plunger hitched to the engine piston and sliding in the metering body.
  • a doser D comprising a hydraulic motor M of generally cylindrical shape, and an injection device I fixed under the engine.
  • the motor M comprises a substantially cylindrical body 1 with a circular section of vertical geometric axis AA.
  • the body 1 is closed at the top by a cover 2 screwed on an external thread of the upper end of the body 1.
  • the cover 2 is provided at its center with a bleed button 3 having a threaded hole in which is screwed the end of a screw 4.
  • the cap 3 is coated with a deformable bellows flexible material.
  • the screw 4 passes through a hole provided in the cover 2 and the screw head is located inside the cover.
  • An O-ring 5 is provided around the screw 4 inside the cover 2 to be sealingly applied by the screw head against the cover.
  • a compression spring 6 is disposed outside the cover 2 between the button 5 and the cover. The spring 6 pushes the button 3 and applies the seal 5 against the lid. Pressing the button 3 makes it possible to drive the screw 4 and create an air purge by passage of air or fluid between the screw and the wall of the hole of the lid.
  • the liner 8 may be of a different material from that of the body 1, more resistant to wear.
  • the body 1 is made of PVC
  • the liner 8 is made of glass or HDPE (high density polyethylene).
  • the liner 8 could be in the same material as the body 1, for example PVC, as the case may be.
  • a piston 9 is adapted to slide reciprocating in the direction of the axis B, in the housing 7.
  • This piston 9 is a simple, non-differential piston which has a closed cross section 10, devoid of any opening.
  • the piston 9 forms a kind of slightly frustoconical disc whose concavity is turned towards the cover 2.
  • the peripheral edge of the piston 9 comprises an annular groove 11 in which is housed a sealing segment 12, shown in detail on Fig.8 .
  • the piston 9 is generally made of plastic, for example polypropylene or polyethylene.
  • the segment 12 comprises an outer ring 12a of a low friction material, for example PTFE (polytetrafluoroethylene), having a concave inner surface in which is housed an inner ring 12b, for example ring, in a softer material especially in elastomeric material, the cross section of which is compressed.
  • the ring 12b exerts a radial outward thrust on the ring 12a to apply it against the wall of the housing 7.
  • the lower end position and the upper end of the piston 9 are respectively determined by abutments e1, e2 which have a fixed position determined relative to the body 1.
  • the abutment e1 can be formed by a shoulder provided directly on the body
  • the high stop e2 may be constituted by a flange projecting downwardly under the cover 2.
  • Two chambers C1, C2 are formed in the body 1 on either side of the piston, respectively below and above the piston 9.
  • the piston 9 comprises at its center a cylindrical sleeve 13 coaxial closed on the side of the lid 2 and open on the opposite side.
  • the upper end of the rod 14 of a plunger 15 is fixed in the sleeve 13, in particular by screwing.
  • the plunger 15 can slide in a tubular element 16 of the injection device I, sealed in the lower part of the body 1, coaxially with the jacket 8.
  • the plunger 15 has an annular groove provided with a plunger seal 17 provided to allow the passage of liquid when the plunger 15 descends, and to prevent any passage of liquid when the plunger 15 rises.
  • the lower end of the tubular element 16 is provided with a splined connection 18, with a valve 19 having a slot 19a in its middle.
  • the valve 19 opens during the rise of the plunger 15 (suction phase) and closes during the descent of the piston 15 (discharge or injection phase).
  • a pipe (not shown) which is immersed in a container containing a liquid additive to be injected into the main liquid.
  • This main liquid is formed for example by water under sufficient pressure, which ensures the actuation of the motor M.
  • Hydraulic switching means G ( Figs.4-6 ) provide the supply and the liquid evacuation of the chambers C1 and C2.
  • the switching means G are arranged in the body 1 radially outside the cylindrical housing 7 and the jacket 8.
  • the means G are housed in a zone of the body 1 located, with respect to the axis A, of the opposite side. to the axis B.
  • the body 1 may comprise, in this area, a bulge 20 forming a cylinder portion whose generatrices are orthogonal to the axis A.
  • the switching means G comprise two valves Va, Vs, respectively for the inlet and the outlet of the liquid, represented by arrows.
  • the seats 21a, 22a and 21s, 22s of the valves Va and Vs are located on the body 1 or on a fixed part relative to the body.
  • Each valve comprises a cylindrical passage 23a, 23s provided in the body 1, with an axis parallel to the axis A of the body and opening, at its upper axial end, in a space K located radially at the outside of the wall 8.
  • the space K communicates, in the upper part, with the chamber C2.
  • each passage 23a, 23s opens into a housing L communicating with the chamber C1.
  • the passages 23a, 23s are separated from each other by a median wall 24 of the body 1.
  • Each valve comprises a core 25a, 25s with two axially spaced bulges respectively provided with O-rings 26a, 26s and 27a, 27s.
  • the seat 21a for the seal 26a is formed by a frustoconical surface tapering downwards and provided directly in the body 1.
  • the seat 22a, provided in the upper part, is formed by a surface frustoconical decreasing in diameter upwards.
  • This seat 22a is located at the lower end of a cylindrical piece 28 having a lower portion of smaller outside diameter than that of the upper part.
  • a shoulder 29 is formed at the transition of the two outer surfaces.
  • the lower part of the piece 28 is received in a bore of the body 1, coaxial with the passage 23a.
  • the shoulder 29 comes into axial abutment against the upper edge of the bore of the body 1.
  • the part 28 is held in a fixed position by pressing the flange e2 of the cap 2 against its upper edge.
  • the seats 21s and 22s are constituted by frustoconical surfaces provided directly on the body 1 and increasing in diameter from the passage respectively downwards and upwards.
  • the lower ends of the cores 25a, 25s are fixed by screws 30a, 30s against the top wall of a lantern 31 formed by a substantially rectangular frame.
  • the lantern 31 comprises a window opening on its two faces parallel to the plane passing through the axes of the cores 25a, 25s.
  • the lantern 31 is disposed in the housing L of the body 1 located below the valves Va, Vs.
  • the lantern 31 is in contact with two opposite zones of the wall of the housing L, which provide sliding guidance of this lantern.
  • the liquid inlet in the engine has an internally threaded hole Ta for mounting a fitting.
  • the hole Ta is extended by a duct Ta1 eccentric radially outward and smaller in diameter than Ta. This duct Ta1 cuts at right angles to the passage 23a with which it communicates.
  • a threaded hole Ts and a duct Ts1 are provided to establish the connection between the passage 23s and the outlet.
  • the conduit Ts1 cuts at a right angle passage 23s.
  • the wall 24 separates the inlet duct Ta1 from the outlet duct Ts1.
  • the duct Ta1 instead of being eccentric, is coaxial with the inlet hole Ta, and of the same diameter. It is the same for the outlet conduit Ts1 and the outlet hole Ts.
  • the molding of the plastic body 1 is facilitated according to this variant.
  • Advantageously Ta, Ta1, Ts, Ts1 are coaxial.
  • a flip-flop device H constitutes a control means for a sudden change in the position of the lantern 31 and the switching means G.
  • the switching means G in a first stable position illustrated on Fig.5 (Corresponding to the high position of the lantern 31), on the one hand ensure the entry of the liquid into the housing L and the chamber C1 and, on the other hand, the connection of the chamber C2 with the outlet.
  • the core 25a is supported by its seal 27a against the seat 22a and closes the communication with the chamber C2.
  • the seal 27s is spaced from the seat 21a and allows communication with the housing L and the chamber C1.
  • the seal 27s is spaced from the seat 22s and allows a communication of the passage 23s with the space K and the chamber C2.
  • the seal 26s bears against the seat 21s and cuts off any communication between the passage 23s and the chamber C1.
  • the fluid inlet is in the chamber C1, while the chamber C2 is connected to the outlet.
  • a second stable position corresponds to the low position of the lantern 31, with the seat 21a closed / the seat 22a open, and the seat 22s closed / 25s seat opening.
  • the housing L and the chamber C1 are connected to the output Ts, while the space K and the chamber C2 are connected to the input Ta.
  • the rocker H makes it possible to pass the lantern 31 suddenly, and the cores 25a, 25s of the valves, from the high position of Fig.5 at the low position of Fig.6 and vice versa.
  • the mean direction of the rocker H is substantially orthogonal to the axis BB of the housing 7, that is to say the direction of displacement BB of the piston 9.
  • the rocker H comprises a rod 32 having two parallel branches 32a, 32b between which the rod 14 of the plunger 15.
  • the end of the rod 32 remote from the lantern 31 is articulated by an axis 33 orthogonal to the plane passing through the axes A and B.
  • the axis 33 is held in a housing of the body 1 by a flange 34 maintained by a Screw 35 inside the body 1.
  • the rod 32 comprises, at each rear end of its branches, a projection 36a, 36b upwards, with a substantially trapezoidal contour.
  • the average direction of link 32 in the stable position of Fig.2 and Fig.5 is slightly inclined, from the axis 33, downwards with respect to a plane orthogonal to the axis B.
  • the rocker H further comprises an arm 37 formed of two branches 37a, 37b located on either side of the branches 32a, 32b of the rod 32.
  • the branches 37a, 37b are articulated on the axis 33.
  • the length of the branches 37a, 37b is greater than that of the rod 32.
  • the branches 37a, 37b are bent towards each other, in an area 38 beyond the free end of the rod 32, so that their spacing decreases.
  • the branches 37a, 37b, at their end remote from the axis 33, are engaged in the lantern 31 and carry an axis 39 on which is mounted a hammer 40 in the form of a circular ring.
  • the hammer 40 may be included in the arm 37 to form a single piece with this arm.
  • a leaf spring 41 shaped curve arc is compressed between an axis 42 carried at the end of the rod 32 facing the lantern, and an axis 43 carried by the branches 37a, 37b of the arm 37 beyond the end of the rod 32.
  • the spring 41 turns its concavity downwards and tends to increase the angle of the compass formed between the rod 32 and the arm 37.
  • the link 32 is thus held in abutment against the bottom of the body 1 while the hammer 40 is held in abutment against the upper face of the opening of the lantern 31.
  • the lower part of the housing L is provided with a plug 44 which comprises, on its inner surface, two protrusions 44a, 44b, diametrically opposite, provided with a helical ramp 45.
  • This plug 44 is designed to occupy two distant angular positions. a quarter of a turn. In the position illustrated on Fig.2 the projections 44a, 44b are located outside the path of the lantern 31 which can freely move.
  • the lantern 31 When the cap 44 is rotated a quarter of a turn relative to the position of Fig.2 or 3 , the lantern 31 is stopped substantially halfway through the projections 44 when it descends from the high position illustrated on Fig.2 . If the lantern 31 is in the low position, the ramps 45, during rotation of the plug 44, raise the lantern 31 in the intermediate position. The lantern 31 then establishes a bypass between the input Ta and the output Ts of the engine in this intermediate position. Indeed none of the seats 21a - 22s is closed.
  • a valve Q ( Fig.9 ) with calibrated spring Qr is advantageously disposed in an opening U of the wall 24, between the input Ta, Ta1, and the output Ts1, Ts of the motor.
  • the valve Q, opening directly connects the inlet and outlet, which preserves the mechanisms, particularly those located inside the body 1, in case of a specific increase in pressure drop.
  • the valve head Q, in the closed position is held in sealing engagement by the spring Qr against a seat on the wall 24 on the outlet side. On the inlet side, the spring Qr is compressed between the wall 24 and a stop provided at the end of a valve stem.
  • valve Q has been shown only in the variant of Fig.9 it is clear that it could also be provided in the embodiments according to the other figures.
  • the liquid pressure is exerted below the piston 9 over its entire section and causes the rise of this piston.
  • the liquid from the chamber C2 is discharged to the outlet.
  • the plunger 15 rises in the tubular element 16 and can suck an additive from a container connected to the connector 18.
  • the plunger 15 raises the rod 32 and causes additional compression of the leaf spring 41.
  • the shaft 42 passes the alignment position with the pins 33 and 43, the leaf spring 41 partially relaxes and causes a sudden change in the configuration of the scale.
  • the arm 37 rotates, according to the representation of Fig.2 in the clockwise direction about the axis 33 and the hammer 40 strikes the lower wall of the lantern 31 which passes abruptly in the lower position, as shown in FIG. Figs. 3 and 6 .
  • the cores 25a, 25s of the valves are in the low position.
  • the chamber C1 is placed in communication with the outlet, while the chamber C2 is placed in communication with the inlet of liquid under pressure.
  • the plunger 15 also descends, which causes the closure of the valve 19 and the injection of the additive sucked up.
  • the passage of liquid is authorized by the seal 17, during the descent of the plunger 15, from the low side to the high side of this plunger.
  • the invention makes it possible to use, in rise and descent, the entire stroke of the piston and its diameter. This results in an optimization of the compactness.
  • the rocker H is simple, reliable and compact.
  • valve seats being provided on the body, there is little or no deformation of the seats.
  • the position of the piston has no influence on the seat / valve core torque.
  • the tightness of the valves is good at any flow.
  • the approach of the inlet / outlet flaps (separated by the single wall 24) promotes compactness and in the by-pass position the liquid does not pass into the engine.
  • the sleeve 8 / segment 12 makes it easy to modify the materials used according to the applications, for example depending on the chemicals constituting the liquid and / or the temperature.
  • the change of liner 8 is carried out quickly by unscrewing the lid 2, extraction by translation of the liner 8, and implementation of a new liner.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)
  • Lubricants (AREA)

Claims (19)

  1. Hydraulische Maschine, insbesondere ein Hydraulikmotor, mit:
    - einem Körper (1);
    - einem Kolben (9), der gleitend in einer zylindrischen Aufnahme (7) des Körpers hin und her bewegbar ist, wobei auf jeder Seite des Kolbens eine Kammer (C1, C2) gebildet ist;
    - hydraulischen Schalteinrichtungen (G) zur Versorgung und Evakuierung der jeweiligen Kammern (C1, C2) wobei die Schalteinrichtungen zwei stabile Positionen einnehmen können;
    - elastische Einrichtungen aufweisenden Steuereinrichtungen (H) für ein abruptes Wechseln der Position der Schalteinrichtungen;
    - Auslöseeinrichtungen (13, 15), die geeignet sind, den Positionswechsel der Schalteinrichtungen (G) am Ende des Kolbenhubs (9) zu bewirken,
    dadurch gekennzeichnet, dass
    - der Kolben (9) ein einfach wirkender, nicht differentialer Kolben mit einem geschlossenen Querschnitt ist;
    - und die hydraulischen Schalteinrichtungen (G) in dem Körper (1) der Maschine radial außerhalb der zylindrischen Aufnahme (7) angeordnet sind, in welcher der Kolben (9) gleitet.
  2. Maschine nach Anspruch 1, dadurch gekennzeichnet, dass der Körper (1) der Maschine im Inneren eine austauschbare zylindrische Buchse (8) aufweist, welche die zylindrische Aufnahme (7) des Kolbens bildet.
  3. Maschine nach Anspruch 2, dadurch gekennzeichnet, dass die zylindrische Buchse (8) aus einem anderen, verschleißfesteren Material besteht als der Körper (1).
  4. Maschine nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass der Körper (1) zylindrisch ist und eine erste geometrische Achse (A-A) aufweist, und die zylindrische Aufnahme (7) des Kolbens eine zweite geometrische Achse (B-B) aufweist, welche zu der ersten (A-A) parallel, jedoch radial versetzt ist.
  5. Maschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Schalteinrichtungen (G) zwei Ventile (Va, Vs) mit Sitzen (21a, 21s; 22a, 22s) aufweisen, welche in dem Körper (1) oder in einem in Bezug auf den Körper feststehenden Teil (28) angeordnet sind, wobei ein Ventil (Va) den Einlass von Flüssigkeit und das andere Ventil (Vs) den Auslass derselben gewährleistet.
  6. Maschine nach der Gesamtheit der Ansprüche 4 und 5, dadurch gekennzeichnet, dass die Ventile (Va, Vs) in dem Teil des Körpers (1) angeordnet sind, der in Bezug auf die geometrische Achse (A-A) des Körpers der geometrischen Achse (B-B) der Aufnahme (7) des Kolbens entgegengesetzt ist.
  7. Maschine nach einem der Ansprüche 5 oder 6, dadurch gekennzeichnet, dass jedes Ventil (Va, Vs) einen zylindrischen Durchlass (23a, 23s) aufweist, welcher zur Verbindung mit einer der durch den Kolben begrenzten Kammern (C1, C2) an jedem axialen Ende offen ist.
  8. Maschine nach Anspruch 7, dadurch gekennzeichnet, dass jeder Durchlass (23a, 23s) an jedem seiner Enden mit einem Sitz (21a, 21s; 22a, 22s) versehen ist, und dass ein in dem Durchlass axial bewegbarer Kern (25a, 25s) in der Lage ist, je nach seiner Position, eines der Enden des Durchlasses durch Anlage an dem entsprechenden Sitz zu schließen.
  9. Maschine nach Anspruch 8, dadurch gekennzeichnet, dass die geometrischen Achsen der Durchlässe (23a, 23s) der beiden Ventile zueinander und zu der Bewegungsrichtung (B-B) des Kolbens parallel sind.
  10. Maschine nach Anspruch 9, dadurch gekennzeichnet, dass die Durchlässe (23a, 23s) einander benachbart sind, wobei sie durch eine Wand (24) voneinander getrennt sind.
  11. Maschine nach einem der Ansprüche 8 bis 10, dadurch gekennzeichnet, dass jeder Kern (25a, 25s) nahe jedem Ende eine mit einer Dichtung (26a, 26s; 27a, 27s) versehene Verdickung aufweist, die geeignet ist, sich an einen entsprechenden Sitz anzulegen, und dass die im Wesentlichen in der Mitte der Länge des Durchlasses befindliche Zone mit einer auf der Außenseite mündenden Einlass- oder Auslassleitung (Ta1; Ts1) steht.
  12. Maschine nach Anspruch 11, dadurch gekennzeichnet, dass die Einlass- oder Auslassleitung (Ta1; Ts1) eine Achse aufweist, die zu derjenigen des Durchlasses (23a, 23s) des Ventils orthogonal ist und den Durchlass schneidet.
  13. Maschine nach einem der Ansprüche 8 bis 12, dadurch gekennzeichnet, dass die Kerne (25a, 25s) der Ventile mit einer Laterne (31) gekoppelt sind, welche parallel zur Richtung der Achsen der Durchlässe der Ventile bewegbar ist.
  14. Maschine nach Anspruch 13, dadurch gekennzeichnet, dass die Laterne (31) in einer Aufnahme (L) des Körpers angeordnet ist, welche sich auf der einem Verschlussdeckel (2) des Körpers gegenüberliegenden Seite der Ventile befindet.
  15. Maschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Steuereinrichtungen (H) für einen abrupten Wechsel der Position der Schalteinrichtungen (G) durch eine Wippenvorrichtung (H) gebildet sind, welche in ihrer Gesamtheit orthogonal zur Bewegungsrichtung (B-B) des Kolbens ausgerichtet ist.
  16. Maschine nach der Gesamtheit des Anspruchs 13 oder 14 und des Anspruchs 15, dadurch gekennzeichnet, dass die Wippe (H) eine Stange (32), das an seinem der Laterne abgewandten Ende an einer von dem Körper der Maschine gestützten Achse (33) angelenkt ist, und einen drehbaren Arm (37) aufweist, welcher an der selben Achse (33) angelenkt ist, wobei der Arm (37) länger als die Stange (32) ist und an seinem der Gelenkachse (33) abgewandten Ende einen Hammer (40) aufweist, welcher sich in einer Ausnehmung der Laterne (31) bewegen kann, wobei eine kurvenbogenförmige Blattfeder (41) zwischen zwei fest mit der Stange (32) beziehungsweise dem Arm (37) verbundenen Achsen (42, 43) zusammengedrückt ist, wobei zwei stabile Positionen der Wippe (H) zwei Konfigurationen entsprechen, in welchen die Stange (32) sich auf der einen oder der anderen Seite des Arms (37) befindet.
  17. Maschine nach Anspruch 14, dadurch gekennzeichnet, dass ein einen Anschlag bildender Verschluss (44) drehbar in der Aufnahme (L) des Körpers unter der Laterne (31) angebracht ist und es in einer vorgegebenen Winkelposition ermöglicht, die Laterne (31) im Wesentlichen in der Mitte des Hubs anzuhalten, um eine Bypass-Funktion zu gewährleisten.
  18. Maschine nach einem der vorhergehenden Ansprüche mit einem Flüssigkeitseinlass (Ta, Ta1) und einem Flüssigkeitsauslass (Ts, Ts1), dadurch gekennzeichnet, dass ein mit einer belasteten Feder (Qr) versehenes Ventil (Q) derart zwischen dem Einlass (Ta, Ta1) und dem Auslass (Ts, Ts1) angeordnet ist, dass es sich im Falle eines ansteigenden Druckverlusts öffnet.
  19. Dosierer, versehen mit einem Hydraulikmotor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass er eine Einspritzvorrichtung (I) aufweist, welche einen koaxial zu der zylindrischen Aufnahme (7) des Kolbens (9) des Motors an dem Körper (1) des Motors befestigten zylindrischen Dosiererkörper (16) und einen mit dem Kolben (9) gekoppelten und in dem Körper (16) des Dosierers gleitenden Stößel (15) aufweist.
EP03767903A 2002-11-28 2003-11-04 Hydraulische maschine Expired - Lifetime EP1565653B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR0214924 2002-11-28
FR0214924A FR2847950B1 (fr) 2002-11-28 2002-11-28 Machine hydraulique, en particulier moteur, a mouvement alternatif, et doseur comportant un tel moteur
PCT/FR2003/003291 WO2004051085A1 (fr) 2002-11-28 2003-11-04 Machine hydraulique

Publications (2)

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EP1565653A1 EP1565653A1 (de) 2005-08-24
EP1565653B1 true EP1565653B1 (de) 2010-07-21

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EP03767903A Expired - Lifetime EP1565653B1 (de) 2002-11-28 2003-11-04 Hydraulische maschine

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US (1) US7207260B2 (de)
EP (1) EP1565653B1 (de)
JP (1) JP2006508295A (de)
CN (1) CN100365275C (de)
AT (1) ATE475015T1 (de)
AU (1) AU2003292336A1 (de)
DE (1) DE60333473D1 (de)
ES (1) ES2349747T3 (de)
FR (1) FR2847950B1 (de)
WO (1) WO2004051085A1 (de)

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US20100015000A1 (en) * 2008-07-17 2010-01-21 Lawrence Pumps, Inc. Apparatus for simultaneous support of pressurized and unpressurized mechanical shaft sealing barrier fluid systems
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FR2965864B1 (fr) 2010-10-08 2012-12-14 Dosatron International Pompe doseuse de liquide, et dispositif detecteur de la variation de pression pour une telle pompe.
US9316216B1 (en) * 2012-03-28 2016-04-19 Pumptec, Inc. Proportioning pump, control systems and applicator apparatus
RU2511925C1 (ru) * 2012-09-10 2014-04-10 Общество с ограниченной ответственностью "Краснодарский Компрессорный Завод" Поршень составной дифференциальный (варианты)
USD786794S1 (en) * 2015-04-15 2017-05-16 Graco Minnesota Inc. Air motor
US10760557B1 (en) 2016-05-06 2020-09-01 Pumptec, Inc. High efficiency, high pressure pump suitable for remote installations and solar power sources
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Also Published As

Publication number Publication date
FR2847950A1 (fr) 2004-06-04
CN100365275C (zh) 2008-01-30
FR2847950B1 (fr) 2005-01-07
DE60333473D1 (de) 2010-09-02
EP1565653A1 (de) 2005-08-24
AU2003292336A1 (en) 2004-06-23
US7207260B2 (en) 2007-04-24
US20060037465A1 (en) 2006-02-23
ATE475015T1 (de) 2010-08-15
JP2006508295A (ja) 2006-03-09
WO2004051085A1 (fr) 2004-06-17
CN1717544A (zh) 2006-01-04
ES2349747T3 (es) 2011-01-11

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