EP0524104B1 - Hydaulikmotor mit hin- und hergehendem Differentialkolben - Google Patents

Hydaulikmotor mit hin- und hergehendem Differentialkolben Download PDF

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Publication number
EP0524104B1
EP0524104B1 EP92402066A EP92402066A EP0524104B1 EP 0524104 B1 EP0524104 B1 EP 0524104B1 EP 92402066 A EP92402066 A EP 92402066A EP 92402066 A EP92402066 A EP 92402066A EP 0524104 B1 EP0524104 B1 EP 0524104B1
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EP
European Patent Office
Prior art keywords
flap
chamber
fluid
moving assembly
exhaust
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
EP92402066A
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English (en)
French (fr)
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EP0524104A1 (de
Inventor
Philippe Cloup
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.)
Civile De Recherche S A M Ste
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Civile De Recherche S A M Ste
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Anticipated expiration legal-status Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L21/00—Use of working pistons or pistons-rods as fluid-distributing valves or as valve-supporting elements, e.g. in free-piston machines
    • F01L21/04—Valves arranged in or on piston or piston-rod
    • 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
    • F03C1/007—Reciprocating-piston liquid engines with single cylinder, double-acting piston
    • F03C1/0073—Reciprocating-piston liquid engines with single cylinder, double-acting piston one side of the double-acting piston being always under the influence of the liquid under pressure
    • F03C1/0076—Reciprocating-piston liquid engines with single cylinder, double-acting piston one side of the double-acting piston being always under the influence of the liquid under pressure the liquid under pressure being continuously delivered to one cylinder chamber through a valve in the piston for actuating the return stroke
    • 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

Definitions

  • the present invention relates to reciprocating hydraulic motors with differential piston which use the energy of the main fluid to generate their movement.
  • the basic principle of these engines is to transfer the inlet fluid, at pressure P1, into an intermediate chamber of variable volume, which, after closing the inlet valves and opening the exhaust valves, empties at the outlet in a fluid of the same flow rate but of pressure P2 lower than the pressure P1.
  • the overall energy used by these hydraulic motors is a function of the flow rate of the fluid and the difference between the pressures P1 and P2.
  • One of the very important constituent elements in this type of device is the assembly constituted by the inlet and exhaust valves and their control system.
  • the object of the present invention is to provide a simplified alternative hydraulic motor.
  • the alternative hydraulic motor proposed comprises a single valve which makes it possible to manage, by itself, the filling and emptying of the volumes concerned.
  • Said motor makes it possible to automatically transfer at each operating cycle a volume of fluid from said inlet duct to said intermediate chamber, then to transfer the same volume of fluid from said intermediate chamber to the exhaust duct under the action of the difference pressure P1-P2, and said control means.
  • the motor is characterized in that said control means comprise a single valve disposed in said cavity and mounted to pivot about a pivot axis located in the general plane of said valve and substantially perpendicular to the general plane of said conduits, and means for actuating said valve carried by said mobile assembly and actuating said valve so that the latter can take two positions in each operating cycle: a first position in which said inlet chamber communicates with said intermediate chamber, the exhaust chamber being isolated, a second position in which the intermediate chamber communicates with the exhaust chamber, the inlet chamber being isolated.
  • the valve mounted on the mobile assembly thus behaves like a two-position valve of a three-way valve.
  • said valve is in support, in each of said positions, on two wall portions of said movable assembly, said two wall portions being located on either side of the general plane of said valve.
  • One of said wall portions is arranged, relative to the general plane of said valve, on the side of the fluid at pressure P1, and the other of said wall portions is disposed on the side of the fluid at pressure P2.
  • the wall portion located on the side of the fluid at the pressure P2 is farther from the pivot axis than the other wall portion so that the fluid pressures exerted on the two faces of the valve create a torque of positive closure.
  • the means for actuating said valve comprise: a trigger rod slidingly mounted on said movable element parallel to the directions of movement of said pistons, said trigger rod being capable of being displaced relative to the movable element when it abuts on the walls of said stepped cylinder, a link secured to the pivot axis of said valve and, a spring interposed between said link and said trigger rod and, intended to tilt the valve during movement of the trigger rod.
  • said link is pivotally mounted on said pivot axis, so that the torque exerted by the spring after tilting of the link is greater than the positive closing torque exerted by fluid pressures.
  • the cavity of said movable element has two walls parallel to each other and perpendicular to the pivot axis, the wall portions cooperating with the valve are substantially parallel to the pivot axis.
  • the reciprocating hydraulic motor 1 shown in the drawing comprises a stepped cylinder 2 consisting of two concentric sleeves 3 and 4 delimiting between them an annular space 5 into which an inlet conduit 6 opens with a fluid at a pressure P1.
  • the outer sleeve 4 is extended by a cylindrical bell 7 fixed to the outer sleeve 4 by a ring 8.
  • the bell 7 has an inner diameter greater than the inner diameter of the inner sleeve 3.
  • the inner sleeve 3 and the bell 7 constitute the inner wall of the stepped cylinder 2.
  • a movable assembly 9 having two pistons 10 and 11 of different diameter connected together by a body 12.
  • the smaller diameter piston 10 is mounted sliding and sealed in the sleeve internal 3 with interposition of a seal 13.
  • the larger diameter piston 11 is slidably and sealed in the bell 7 with interposition of a seal 14a.
  • the exhaust pipe 14 of the fluid at pressure P2 opens, through the end wall 15 of the inner sleeve 3 which is opposite the bell 7, into an exhaust chamber 16 of variable volume located between the piston of smaller section 10 and the end face 15.
  • the annular space 5 is in permanent communication with an inlet chamber 17 of variable volume located in the stepped cylinder 2 between the pistons 10 and 11.
  • An intermediate chamber 18 of variable volume is delimited by the end wall 19 of the bell 7 and the larger diameter piston 11.
  • a cavity 20 is formed in the body 12 of the movable assembly 8. This cavity 20 communicates with the inlet chamber 17 by a first conduit 21. It also communicates with the exhaust chamber 16 by a second conduit 22 passing through the piston 10, and with the intermediate chamber 18 by a third conduit 23 passing through the piston 11.
  • a valve 25 In the cavity 20 is pivotally mounted around a pivot axis 24 a valve 25.
  • the pivot axis 24 is located in the general plane of the valve 25 and is substantially perpendicular to the general plane defined by the three conduits 21, 22 and 23.
  • the valve 25 can take two extreme positions: on the one hand, a first position, shown in FIG. 1, in which the inlet chamber 17 is in communication with the intermediate chamber 18 via the conduits 21 and 23 and in which the exhaust chamber 16 is isolated, and, on the other hand, a second position shown in FIG. 2, in which the inlet chamber 17 is isolated and in which the exhaust chamber 16 is in communication with the intermediate chamber 18 via the conduits 22 and 23.
  • valve 25 In the first position, shown in FIG. 1, the valve 25 is supported on two wall portions 26 and 27 to isolate the exhaust chamber 16.
  • the wall portions 26 and 27 are located on either side of the pivot axis 24 and on either side of the general plane of the valve 25.
  • the wall portion 26 is located relative to the valve 25 on the side of the face subjected to the pressure P1; the wall portion 27 is located on the contrary on the side of the face of valve subject to pressure P2 which is less than P1.
  • the distance separating the wall portion 27 from the pivot axis 24 is greater than the distance separating the wall portion 26 from the pivot axis 24.
  • the pressures P1 and P2 being exerted on the two faces of the valve 25 , therefore generate on the valve a resulting torque, represented by arrow 28, which tends to positively hold the valve 25 in the first position.
  • valve 25 In the second position, shown in Figure 2, the valve 25 is also supported on two wall portions 29 and 30 arranged on either side of the pivot axis 24 and on either side of the general plane of the valve 25.
  • One of the faces of the valve 25 is also subjected to the pressure P1 and the other face to the pressure P2.
  • the wall portion 29 located on the side of the pressure P2 is further from the pivot axis 24 than the wall portion 30 on which the face of the valve 25 subjected to the pressure P1 is supported.
  • the valve 25 is also in this case subjected to a torque resulting from positive closure, represented by the arrow 31.
  • the cavity 20 has two walls 20a and 20b perpendicular to the pivot axis 24, and the wall portions 26, 27, 29 and 30 are straight and parallel to the pivot axis 24.
  • the valve 25 then has a substantially rectangular shape and has on its edges seals cooperating with the walls 20a and 20b.
  • the valve 25 is produced in a conventional manner by elastic membranes interposed between stiffening plates.
  • the valve 25 is carried by the pivot axis 24 which passes through at least one of the walls, 20a for example, of the body 12 of the mobile assembly 9.
  • the valve 25 is actuated by actuating means which comprise a trigger rod 32, a link 33 secured to the pivot axis 24 and a spring 34 interposed between the trigger rod 32 and the free end of the link 33 .
  • the trigger rod 32 is slidably mounted on the mobile assembly 9 and is parallel to the directions of movement of the mobile assembly 9 in the stepped cylinder 2.
  • the trigger rod 32 is moved relative to the mobile assembly 9 when one of its ends abuts on the walls of the stepped cylinder 2, the end walls 15 and 19 for example. This movement causes the spring 34 to pivot about the free end of the link 33, and creates an opposing torque which causes the valve 25 to tilt when it is greater than one of the couples 28 or 31 described above.
  • the link 33 is pivotally mounted on the pivot axis 24.
  • the pivot axis 24 comprises two opposite lugs 35 accommodating in two openings 36 in the form of sectors, so as to allow free movement of the rod 33 relative to the pivot axis 24, when the spring 34 pivots as a result of the displacement of the trigger rod 32.
  • the valve 25 is in the first position, shown in Figure 1; the mobile assembly 9 is in the low position, and the trigger rod 32 is in the high position relative to the mobile assembly 9.
  • the inlet chamber 17 and the intermediate chamber 18 are at pressure P1.
  • the exhaust chamber 16 is at pressure P2. Due to the difference in the cross sections of the pistons 10 and 11, the movable assembly 9 moves upward in the direction of arrow 37. A volume of fluid is transferred from the inlet duct 6 to the intermediate chamber 18. A same volume of fluid is expelled from the exhaust chamber 16 to the exhaust duct 14.
  • the force used to move the movable assembly is the product of the section of the piston 10 by the difference in pressures (P1-P2).
  • the rod 33 finally pivots around the pivot axis 24, which causes a shock of the lugs 35 against the side walls of the openings 36 and a frank tilting of the valve 25 from the first position to the second position, shown in FIG. 2
  • the trigger rod 32 is now in the low position on the mobile assembly 9.
  • the exhaust chamber 16 and the intermediate chamber 18 now contain a fluid at pressure P2.
  • the inlet chamber 17 contains a fluid at pressure P1.
  • the movable assembly 9 moves downward in the direction of arrow 38. The force used in this movement to move the engine is equal to the product of the difference in the cross sections of the pistons 10 and 11 by the difference in pressures P1- P2. A volume of fluid is transferred from the intermediate chamber 18 to the exhaust chamber 16.
  • the mobile assembly 9 can be equipped with a rod 40 sealingly passing through the end wall 19 and making it possible to actuate a member external to the engine, a metering device for example.
  • valve actuation means in particular the rod 33 and the spring 34 are located outside the body 12 connecting the pistons 10 and 11, so as to make them directly accessible for repair after removal of the bell 7 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Hydraulic Motors (AREA)

Claims (6)

  1. Hydraulikmotor mit hin- und hergehendem Differentialkolben zwischen einer Eintrittsleitung (6) für Fluid mit einem Druck P1 und einer Austrittsleitung (14) für Fluid unter einem Druck P2, der kleiner als P1 ist, mit
    einem Stufenzylinder (2),
    einer beweglichen Baugruppe (9) mit zwei Kolben (10, 11) von unterschiedlichem Querschnitt, die miteinander verbunden und gleitend sowie dichtend in den Stufenzylinder (2) eingebaut sind, wobei die bewegliche Baugruppe (9) mit der Innenwand des Stufenzylinders (2) drei Kammern veränderlichen Volumens begrenzt: eine zwischen den beiden Kolben (10, 11) angeordnete Eintrittskammer (17), in welche die Eintrittsleitung (6) mündet, eine bezüglich der Eintrittskammer (17) auf der anderen Seite des Kolbens (10) von geringerem Querschnitt angeordnete Austrittskammer (16), in welche die Austrittsleitung (14) mündet, und eine bezüglich der Eintrittskammer (17) auf der anderen Seite des Kolbens (11) von größerem Querschnitt angeordnete Zwischenkammer (18),
    einem ersten Durchlaß, durch den die Eintrittskammer (17) und die Zwischenkammer (18) zeitweise miteinander verbindbar sind,
    einem zweiten Durchlaß, durch den die Zwischenkammer (18) und die Austrittskammer (16) zeitweise miteinander verbindbar sind, und
    einer Steuereinrichtung, um während jedes Betriebszyklus den ersten und den zweiten Durchlaß wechselnd zu öffnen und zu schließen,
    wobei der erste Durchlaß und der zweite Durchlaß von einem in die bewegliche Baugruppe (9) eingearbeiteten Hohlraum (20) und drei Leitungen (21, 22, 23) gebildet sind, welche den Hohlraum (20) mit der Eintrittskammer (17) bzw. der Austrittskammer (16) bzw. der Zwischenkammer (18) verbinden,
    dadurch gekennzeichnet, daß die Steuereinrichtung aufweist:
    eine einzige Ventilklappe (25), die in dem Hohlraum (20) angeordnet und um eine Schwenkachse (24) schwenkbar gelagert ist, welche in der allgemeinen Ebene der Ventilklappe (25) und im wesentlichen rechtwinklig zur allgemeinen Ebene der Leitungen (21, 22, 23) angeordnet ist,
    und Betätigungsmittel (32, 33, 34) für die Ventilklappe (25), welche von der beweglichen Baugruppe (9) getragen werden und die Ventilklappe (25) betätigen, damit diese bei jedem Betriebszyklus zwei Stellungen einnehmen kann:
    eine erste Stellung, in welcher die Eintrittskammer (17) mit der Zwischenkammer (18) verbunden und die Austrittskammer (16) abgetrennt ist, und
    eine zweite Stellung, in welcher die Zwischenkammer (18) mit der Austrittskammer (16) verbunden und die Eintrittskammer (17) abgetrennt ist.
  2. Motor nach Anspruch 1, dadurch gekennzeichnet, daß die Ventilklappe (25) sich in jeder der genannten Stellungen an zwei zur beweglichen Baugruppe (9) gehörigen Wandabschnitten (26, 27; 29, 30) abstützt, welche auf je einer seite der allgemeinen Ebene der Ventilklappe (25) angeordnet sind, wobei einer der Wandabschnitte (26, 30) bezüglich der allgemeinen Ebene der Dichtungsklappe (25) auf der Seite des Fluids mit dem Druck P1 angeordnet ist und der andere Wandabschnitt (27, 29) auf der Seite des Fluids mit dem Druck P2 angeordnet ist, und
       daß der auf der Seite des Fluids mit dem Druck P2 angeordnete Wandabschnitt (27, 29) von der Schwenkachse (24) weiter entfernt ist als der andere Wandabschnitt (26, 30), derart, daß die auf die beiden Flächen der Ventilklappe (25) einwirkenden Fluiddrucke ein positives Schließdrehmoment erzeugen.
  3. Motor nach Anspruch 1, dadurch gekennzeichnet, daß die Betätigungsmittel für die Ventilklappe (25) aufweisen:
    eine Auslösestange (32), die an der bewegten Baugruppe (9) parallel zu den Bewegungsrichtungen der Kolben (10, 11) gleitend geführt und in bezug auf die bewegliche Baugruppe (9) verschiebbar ist, wenn sie gegen die Wände des Stufenzylinders (2) stößt,
    einen Schwingarm (33), der an der Schwenkachse (24) der Ventilklappe (25) befestigt ist, und
    eine Feder (34), die zwischen dem Schwingarm (33) und der Auslösestange (32) angeordnet und dazu bestimmt ist, bei der Bewegung der Auslösestange (32) die Ventilklappe (25) hin- und herzuschwenken.
  4. Motor nach Anspruch 3, dadurch gekennzeichnet, daß der Schwingarm (33) auf der Schwenkachse (24) derart schwenkbar gelagert ist, daß das von der Feder (34) nach der Schwenkung des Schwingarms (33) ausgeübte Drehmoment größer ist als das von den Fluiddrucken ausgeübte positive Schließdrehmoment.
  5. Motor nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Hohlraum (20) der beweglichen Baugruppe (9) zwei zueinander parallele und zur Schwenkachse (24) rechtwinklige Wände (20a, 20b) aufweist, und daß die mit der Ventilklappe (25) zusammenwirkenden Wandabschnitte (26, 27; 29, 30) zur Schwenkachse (24) im wesentlichen parallel sind.
  6. Motor nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß die Betätigungsmittel für die Ventilklappe (25), insbesondere der Schwingarm (33) und die Feder (34), außerhalb des die beiden Kolben (10 und 11) miteinander verbindenden Körpers (12) derart angeordnet sind, daß sie nach Abnehmen einer Glocke (7) unmittelbar zur wartung und Reparatur zugänglich sind.
EP92402066A 1991-07-18 1992-07-17 Hydaulikmotor mit hin- und hergehendem Differentialkolben Expired - Lifetime EP0524104B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9109105A FR2679298B1 (fr) 1991-07-18 1991-07-18 Moteur hydraulique alternatif a piston differentiel.
FR9109105 1991-07-18

Publications (2)

Publication Number Publication Date
EP0524104A1 EP0524104A1 (de) 1993-01-20
EP0524104B1 true EP0524104B1 (de) 1996-03-20

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP92402066A Expired - Lifetime EP0524104B1 (de) 1991-07-18 1992-07-17 Hydaulikmotor mit hin- und hergehendem Differentialkolben

Country Status (4)

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US (1) US5261311A (de)
EP (1) EP0524104B1 (de)
DE (1) DE69209176T2 (de)
FR (1) FR2679298B1 (de)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6626079B1 (en) * 2002-03-28 2003-09-30 Rehco, Llc Pneumatic motor
TWI684705B (zh) * 2016-12-21 2020-02-11 黃進添 低能源高汽壓、油壓、汽動引擎

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US245310A (en) * 1881-08-09 Water-meter
US437097A (en) * 1890-09-23 Peter t
US119076A (en) * 1871-09-19 Improvement in liquid-meters
US2987051A (en) * 1958-10-22 1961-06-06 Lodding Engineering Corp Water-operated oscillator
FR2205361A1 (en) * 1972-11-09 1974-05-31 Cloup Philippe Automatic injection of an additive into a liquid - using a differential piston assembly, the displacement of piston being controlled by liq. under pressure
US4031812A (en) * 1974-03-08 1977-06-28 Nikolai Vasilievich Koshelev Hydraulic vibrator for actuator drive
FR2602282B1 (fr) * 1986-07-31 1988-09-23 Cloup Jean Perfectionnement aux dispositifs d'injection d'un produit additif dose dans un fluide principal
US5137435A (en) * 1991-03-25 1992-08-11 Frank And Robyn Walton 1990 Family Trust Compression spring fluid motor

Also Published As

Publication number Publication date
DE69209176D1 (de) 1996-04-25
FR2679298B1 (fr) 1993-11-26
DE69209176T2 (de) 1996-11-07
EP0524104A1 (de) 1993-01-20
FR2679298A1 (fr) 1993-01-22
US5261311A (en) 1993-11-16

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