EP0526333B1 - Druckflüssigkeitsvorrichtung mit Ausgleichsräumen - Google Patents

Druckflüssigkeitsvorrichtung mit Ausgleichsräumen Download PDF

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Publication number
EP0526333B1
EP0526333B1 EP92402189A EP92402189A EP0526333B1 EP 0526333 B1 EP0526333 B1 EP 0526333B1 EP 92402189 A EP92402189 A EP 92402189A EP 92402189 A EP92402189 A EP 92402189A EP 0526333 B1 EP0526333 B1 EP 0526333B1
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EP
European Patent Office
Prior art keywords
conduits
enclosures
distribution
face
fluid
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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
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EP92402189A
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English (en)
French (fr)
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EP0526333A1 (de
Inventor
Bernard R. Allard
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Poclain Hydraulics France SA
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Poclain Hydraulics France SA
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Publication of EP0526333A1 publication Critical patent/EP0526333A1/de
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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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves
    • F04B1/0465—Distribution members, e.g. valves plate-like
    • 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
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0447—Controlling
    • F03C1/045—Controlling by using a valve in a system with several pump or motor chambers, wherein the flow path through the chambers can be changed, e.g. series-parallel

Definitions

  • the invention has its origin in the design of a new hydraulic motor, but more generally of a new pressurized fluid mechanism, such as a hydraulic motor or pump, comprising: a reaction cam; a cylinder block mounted for rotation relative to said reaction cam about an axis of rotation and provided with a planar communication face, perpendicular to said axis of rotation; a plurality of cylinders formed in the cylinder block; a plurality of pistons mounted sliding in said cylinders, at least by a cylinder delimiting inside the cylinder a working chamber of the fluid, which communicates with said communication face by a cylinder duct; at least two main fluid enclosures capable of containing a fluid for supplying the working chambers and an exhaust fluid outside said working chambers; an internal fluid distributor stationary with respect to rotation about said axis of rotation relative to said reaction cam and comprising a distribution face, which is planar, perpendicular to said axis of rotation, and capable of being supported substantially sealed on said communication face, and into which there are distribution conduits capable of being connected
  • the invention was originally intended to design a mechanism which could furthermore have two corresponding distinct operating modes, one for the periodic supply of pressurized fluid to all the working chambers. in fluid and the other operating mode, when supplying only the fluid working chambers belonging to a first group of working chambers, the other fluid working chambers no longer being supplied with fluid under pressure: it it was therefore a mechanism having at least two separate displacement.
  • it was necessary to provide at least three, and sometimes four separate main enclosures, and it was necessary to balance the pressure forces tending to separate the distribution face of the internal fluid distributor d 'with the communication face of the cylinder block, enclosure by enclosure.
  • enclosures at least three in number, succeeded one another axially at the periphery of the internal distributor of fluid, separated from each other by a seal, so that the axial length of the internal fluid distributor had a relatively large value, which it was considered desirable to reduce.
  • One proposed solution has consisted in replacing at least one, sometimes two main enclosures by one or two secondary enclosures placed not at the periphery, but inside the internal fluid distributor, which, for a mechanism comprising four enclosures, corresponds an axial size corresponding to the axial succession of only two main speakers.
  • the invention which therefore had the primary aim of solving this problem of balancing the pressure forces of the fluid contained in the internal secondary enclosure (s) of such a mechanism comprising two separate operating displacements, has however a greater scope and is not limited to the production only of such multi-displacement operating mechanisms.
  • This invention is indeed also interesting in the case of a mechanism with a single displacement.
  • the axial length of the internal distributor can be significantly reduced, which improves the mobility of this internal distributor which is less constrained by the various radial bearing surfaces delimiting the main speakers , and which essentially improves the tightness of the contact between the dispensing face and the communication face of this mechanism, it has also been designed from a structure integral with the cam identical to that of the mechanism at least two operating displacements, to provide a mechanism having only one operating displacement.
  • this structure integral with the cam is an important and expensive part of the mechanism, and it is obviously advantageous that it can be common to the mechanisms of a production range comprising both mechanisms with several operating displacements and mechanisms with a single operating displacement.
  • the pressure forces have been balanced both with regard to the multi-displacement operating mechanisms, as with regard to the mechanisms having only one displacement Operating.
  • the internal fluid distributor is delimited by an extreme transverse face which is arranged opposite a reaction face belonging to the one of the two parts constituted by the cylinder block and by a structure integral with the reaction cam, while at least one of said balancing chambers is constituted by a chamber formed in the internal fluid distributor and opening into its so-called extreme transverse face and by a sealing device, which is partially received inside this chamber and which takes reaction support on said reaction face.
  • the main advantages of the invention reside, on the one hand, in the production of pressurized fluid mechanisms having at least two separate operating displacements and comprising an internal fluid distributor axially less bulky than the known prior mechanisms, and consequently better likely to allow the achievement of a good seal between the distribution face and the communication face of the cylinder block, and therefore better able to reduce the leakage of fluid between these two faces in mutual contact, on the other hand, in the possibility of carrying out a production range comprising both mechanisms having several operating displacements and mechanisms having only one operating cubic capacity, by adopting a single model of the most bulky and ultimately the most expensive part , which remains unchanged for these two types of mechanisms.
  • the constitution of the engine represented in FIGS. 1 to 9 corresponds, for example, to the fixing of the casing 1A-1B-1C on a vehicle chassis, and to the rotation of the cylinder block 7 and of the motor shaft 3, which is integral in rotation and which is coupled to a movement member of said vehicle for the purpose of driving the latter.
  • the rotary member is constituted by the casing (and by the cam which is integral therewith in rotation), the fixed member then being the cylinder block.
  • the end transverse face 21A of the internal distributor 21 is arranged opposite a transverse face, with which the cylinder block is provided, and which is similar to the face 67 of the engine which has just been described.
  • the face 67 of the casing like said face of the cylinder block constitute a reaction face allowing the support of the segments 66 and 70.
  • conduits 27 and 28 Note the connection of conduits 27 and 28 to the main fluid distributor 74; the connection of the duct 51 to the secondary fluid distributor 76; and, the connection of the conduit 19 to the reservoir 72.
  • the motor of FIGS. 10 to 15 can be integrated into the circuit of FIG. 9, without any change concerning this circuit.
  • the hydraulic motor of Figures 16 to 18 is a motor having only one operating displacement.
  • This engine resembles the engine shown with reference to FIGS. 1 to 9, except as regards the following characteristics: the internal fluid distributor 121 has been modified and replaces the distributor 21, so as to remove the drawer 38, the conduits 36, 37 and 50, and of course the housing 43 and the indexing pin 44.
  • the distribution conduits 31-136, 32-137 correspond, by pair of distribution conduits 31-32, 136-137, to the undulations of the reaction cam 16; communicate permanently, the conduits 31 and 136 with the main enclosure 25, and, the conduits 32 and 137 with the main enclosure 26; and open into a distribution face 123, which comprises the internal fluid distributor 121, planar and perpendicular to the geometric axis 4, so, during the relative rotation of the cylinder block 7 with respect to the casing 1A-1B- 1C, and consequently with respect to the internal fluid distributor 121 made integral with respect to said rotation of the part 1C of the casing by means of a device of notches and associated lugs 124, to be communicated periodically with the cylinder ducts 13.
  • the conduits 31, 32 communicate with the main enclosures 25, 26, the shapes of which, as previously, have been chosen to hydrostatically balance the thrust due to the pressure of the fluid contained in the conduits 31, 32 and acting on the distributor. fluid 121.
  • conduits 136, 137 which are placed at the locations of the conduits 36, 37 of the embodiment of FIGS. 1 to 9, and which, numerically, correspond to these conduits 36, 37, generate a hydrostatic thrust, due to the effect of the pressure of the fluids they contain, no more balanced than that generated by the fluids contained in the conduits 36, 37 of the engine of FIGS. 1 to 9, and therefore a thrust not balanced by the chosen shapes of the enclosures 25, 26
  • grooves 161, 162 similar to grooves 61, 62 have been provided and provide the same function with respect to conduits 136, 137 as that of grooves 61, 62 with respect to conduits 36 , 37.
  • grooves 161, 162 are formed in the internal fluid distributor 121, open in its rear face 121A, flat, perpendicular to the geometric axis 4, opposite the internal face 67 of the part 1C of the casing.
  • a spring 158 interposed between the internal fluid distributor 121 and the part 1C of the casing, tends to put the distribution face 123 in substantially sealed abutment on the communication face 9 of the cylinder block 7.
  • a plug 87 is screwed into the tapping 88 for connection of the conduit 51 of the embodiment of FIGS. 1 to 9, tapping 88 formed in the part 1C of the casing.
  • FIGS. 16 to 18 is identical to that of FIGS. 1 to 9, in particular as regards the casing 1A-1B-1C, the cylinder block 7, the motor shaft 3, the reaction cam 16, the geometric axis 4, already defined by the description of the motor in FIGS. 1 to 9.
  • the engine shown in Figures 1 to 9 is an engine with two separate displacements, with "symmetrical" distribution.
  • the spring 56 acts alone on the slide 38, which it places in the first configuration shown with reference to FIGS. 1 to 5 and 9.
  • the main fluid distributor 74 placed in its first position, there is the supply of pressurized fluid, by the main pump 73, of the conduits 80, 27, 29, of the groove 25, and of the conduits 31, 33, of the groove 39, and conduits 36.
  • the conduits 32 and 37 (conduits 37 connected to the conduits 32 by the groove 40 and the conduits 34) are connected to the fluid reservoir 72 by the groove 26 and the conduits 30, 28 and 82.
  • the chambers working fluid 12 are each supplied with pressurized fluid, when the rollers 14 are supported on each corrugation of the reaction cam 16.
  • the displacement which corresponds to all of the working chambers 12, constitutes the large engine displacement.
  • the shapes of the main speakers 25, 26 are sufficient to balance the thrust due to the pressure of the fluids contained in the conduits 31, 32, directly connected to said grooves, these main speakers 25, 26 therefore also having the function of balancing with respect to the fluids contained in the distribution conduits 31, 32.
  • the thrust due to the pressure of the fluids contained in the conduits 36, 37, not directly connected to the main speakers 25, 26, is not balanced by the shape of these main speakers.
  • the fluid cylinders constituted by the segments 66, 70, associated with the seals 63, 71, mounted to slide in the grooves 61, 62, which are supplied with fluids contained in the conduits 37, 36 by the conduits 65, 69 , respectively, make it possible to obtain this balancing of the thrust due to the pressure of the fluids contained in the conduits 37, 36, the chambers 64, 68 constituting then balancing chambers with respect to the fluids contained in the distribution conduits 36, 37.
  • conduits 36 are no longer connected to the main enclosure 25 by the groove 39 and the conduit (s) 33. Only the working chambers of the fluid 12 corresponding to the rollers 14 bearing on the corrugations corresponding to the conduits 31 are supplied with pressurized fluid. The displacement obtained constitutes the small displacement of the engine.
  • the conduits 36 and 37 isolated from the conduits 33, 34, and connected to the groove 40 by the blind conduits 41 and 42, which keep their constant angular orientation thanks to the indexing obtained by the combined action of the pin 44 and its housing 43, are placed in communication with the chamber 49 via the conduit 50.
  • the pressure of the fluid contained in the chamber 49 is usually of the order of 5 to 10 bars, while the pressure of the pumped fluid by the main pump 73 is usually of the order of 400 bars. Consequently, not only the working chambers 12 corresponding to said conduits 36, 37 have their supply short-circuited, but also are placed in communication with a fluid under low pressure.
  • the engine shown in FIGS. 10 to 15 is an engine with two separate displacements, with so-called "asymmetric" distribution.
  • the spring 256 acts alone on the slide 238, which it places in the first configuration shown with reference to FIGS. 10 to 12.
  • the main fluid distributor 74 placed in its first position, there is the supply of pressurized fluid, by the main pump 73, of the conduits 80, 27, 29, of the groove 25, and conduits 31 and 236.
  • the conduits 32 and 237 are connected to the fluid reservoir 72 by the groove 26 and the conduits 30, 28 and 82, the groove 240 and the conduits 34 communicating the conduits 237 with the conduits 32.
  • the working chambers of the fluid 12 are each supplied with pressurized fluid when the rollers 14 are supported on each undulation of the reaction cam 16.
  • the displacement which corresponds to all of the working chambers 12, constitutes the large displacement of the engine.
  • the shapes of the main enclosures 25, 26 are sufficient to balance the thrust due to the pressure of the fluids contained in the conduits 31 and 236, on the one hand, 32, on the other hand, respectively, respectively, directly connected to said grooves.
  • the main chambers 25, 26 also have a balancing function with respect to the fluids contained in the distribution conduits 31 and 236, and, 32.
  • the thrust due to the pressure of the fluids contained in the distribution conduits 237, not directly connected to the main speakers 25, 26, is not balanced by the shape of these main speakers.
  • All of these distribution conduits 237 constitute a secondary enclosure.
  • the fluid cylinder constituted by the segment 266 associated with the seal 263, mounted sliding in the groove 261, which is supplied with fluids contained in the conduits 237 by the conduits 265 allows this balancing of the thrust due to the pressure of the fluids contained in the conduits 237.
  • the chamber 264 then constitutes a balancing chamber with respect to the fluids contained in the distribution conduits 237.
  • conduits 237 are no longer connected to the main enclosure 26. Only the working chambers of the fluid 12 corresponding to the rollers 14 bearing on the corrugations corresponds to the conduits 31, 32 are periodically supplied with fluid under pressure and put in communication with the reservoir 72. The displacement obtained constitutes the small displacement of the engine.
  • conduits 237 connected to the groove 240 by the blind conduits 242, which retain their constant angular orientation thanks to the indexing obtained by the combined action of the pin 244 and its housing 243, are placed in communication with the main enclosure 25 via the conduits 33 and 31, as the conduits 236 already are.
  • the conduits 237 and 236 are therefore in communication with the same main enclosure 25.
  • the mechanisms according to the invention make it possible in all cases to obtain balanced operations of the internal fluid distributor, without, in a manufacturing range, there being place to modify the important parts, the most expensive of these mechanisms.
  • the mechanism has several operating displacements, but only two main enclosures 25, 26, which allows excellent axial compactness, balancing remains possible thanks to the small auxiliary cylinders 71-70-62, 63-66-61; 263-266-261; 171-170-162, 163-166-161.
  • the chambers 64, 68, or 264, or 164, 168 are blind chambers, which are connected in derivation, by conduits 65, 69, or 265 , or 165, 169, to conduits 37, 36, or 237, or 137, 136, respectively, and which are therefore not crossed by the flow conveyed by said conduits.
  • these flows are significant: if said chambers had to be crossed by these flows, their sections would necessarily have been large. This is not the case with the embodiments described and shown in which said chambers can have small dimensions while, of course, ensuring the balancing function of the internal fluid distributor, in which they participate.

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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)
  • Fluid-Pressure Circuits (AREA)

Claims (9)

  1. Druckfluidvorrichtung, beispielsweise ein Motor oder eine hydraulische Pumpe mit:
    einer Reaktionskurvenbahn (16);
    einem Zylinderblock (7), der bezüglich der Reaktionskurvenbahn um eine Rotationsachse (4) drehbar montiert und mit einer flachen Kommunikationsfläche (9) rechtwinklig zur Rotationsachse versehen ist;
    einer Mehrzahl von Zylindern (10), die im Zylinderblock angebracht sind;
    einer Mehrzahl von Kolben (11), die gleitend in den Zylindern angebracht sind, wobei mindestens einer pro Zylinder im Inneren des Zylinders eine Fluidarbeitskammer (12) begrenzt, die mit der Kommunikationsfläche (9) durch eine Zylinderleitung (13) in Verbindung steht;
    mindestens zwei Hauptfluidräumen (25, 26), die geeignet sind, ein Zufuhrfluid zu den Arbeitskammern (12) und ein Abführfluid aus den Arbeitskammern zu beinhalten;
    einem inneren Fluidverteiler (21; 221; 121), der gegenüber der Rotation um die genannte Rotationsachse bezüglich der Reaktionskurvenbahn unbeweglich ist (24; 224; 124) und eine Verteilungsfläche (23; 223; 123) aufweist, die flach und rechtwinklig zur Rotationsachse (4) und geeignet ist, im wesentlichen dicht auf der Kommunikationsfläche (9) gehalten zu werden, und in die Verteilungsleitungen (31, 32, 36, 37; 31, 32, 236, 237; 31, 32, 136, 137) münden, die geeignet sind, die einen mit dem einen der Haupträume, die anderen mit dem anderen Hauptraum verbunden zu werden; und
    Ausgleichsräumen (25, 26, 64, 68; 25, 26, 264; 25, 26, 164, 168) des inneren Fluidverteilers, wobei jeder mit bestimmten (31, 32, 36, 37; 31, 32, 237; 31, 32, 136, 137) Verteilungsleitungen in Verbindung steht,
    dadurch gekennzeichnet, daß an der der Verteilungsfläche (23; 223; 123) abgewandten Seite der innere Fluidverteiler von einer äußeren Querfläche (21A; 221A; 121A) begrenzt wird, die gegenüber einer Reaktionsfläche (67) angeordnet ist, die zu einem der beiden Teile gehört, die durch den Zylinderblock und durch eine mit der Reaktionskurvenbahn (16) formschlüssigen Strukur (1C) gebildet werden, während mindestens der eine (64, 68; 264; 164, 168) der Ausgleichsräume durch eine Kammer (64, 68; 264; 164, 168), die im inneren Fluidverteiler (21; 221; 121) vorgesehen ist und in der äußeren Querfläche (21A; 221A, 121A) mündet, und durch eine Dichtvorrichtung (63-66, 71-70; 263-266; 163-166, 171-170) gebildet wird, die teilweise im Inneren dieser Kammer aufgenommen wird und die sich in Reaktion auf die Reaktionsfläche (67) stützt.
  2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß der Ausgleichsraum eine ringförmige Nut (64, 68; 264; 164, 168) mit zylindrischen Wänden mit Achsen parallel zu der Rotationsachse (4) aufweist.
  3. Vorrichtung nach einem der Ansprüche 1 und 2, dadurch gekennzeichnet, daß die Kammer des Ausgleichsraums blind ist und parallel mit bestimmten Verteilungsleitungen verbunden ist, wobei sie nur mit diesen in Verbindung steht, ohne vom Fluiddurchfluß durchquert zu werden, der von den Verteilungsleitungen transportierbar ist.
  4. Vorrichtung nach einem der Ansprüche 1 und 3, dadurch gekennzeichnet, daß die Reaktionsfläche (67) eben und rechtwinklig zur Rotationsachse ist.
  5. Vorrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Teil der äußeren Querfläche (21A; 221A; 121A), in den der Ausgleichsraum mündet, eben und rechtwinklig zur Rotationsachse (4) ist.
  6. Vorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß sie beinhaltet:
    Verteilungsleitungen, die in dem inneren Fluidverteiler (21; 221; 121) vorgesehen sind, die in eine erste (31, 32) und eine zweite (36, 37; 236, 237; 136, 137) Paargruppe von Verteilungsleitungen aufgeteilt sind, wobei jedes Paar eine erste und eine zweite Verteilungsleitung aufweist, während die Formen der Wände, die die Haupträume (25, 26) begrenzen, außerdem den Ausgleich der Druckkräfte der Fluide realisieren, die jeweils in den ersten (31) und zweiten (32) Verteilungsleitungen der ersten Paargruppe (31-32) der Verteilungsleitungen beinhaltet sind, wobei die beiden Haupträume (25, 26) auch zwei erste Ausgleichsräume bilden; und
    mindestens einen zweiten Ausgleichsraum (68, 64; 264; 168, 164), der von einer der Kammern gebildet wird, die in dem inneren Fluidverteiler (21; 221; 121) vorgesehen sind und in seiner äußeren Querfläche (21A; 221A; 121A) münden, und von einer der Dichtungsvorrichtungen (71-70, 63-66; 263-266; 171-170, 163-166) gebildet wird, die teilweise in der Kammer aufgenommen wird, und der durch mindestens eine in dem inneren Fluidverteiler vorgesehene Leitung (69, 65; 265; 169, 165) mit der einen (36, 37; 237; 136, 137) der beiden Gruppen von Verteilungsleitungen verbunden ist, wobei eine erste Gruppe die ersten Verteilungsleitungen (36; 236; 136) der zweiten Paargruppe (36-37; 236-237; 136-137) der Verteilungsleitungen und eine zweite Gruppe die zweiten Verteilungsleitungen (37; 237; 137) der zweiten Paargruppe der Verteilungsleitungen, beinhalten.
  7. Vorrichtung nach Anspruch 6, dadurch gekennzeichnet, daß diese Vorrichtung (Figuren 1 bis 9) zum Typ gehört, der mindestens einen großen und mindestens einen kleinen Funktionshubraum aufweist und aufweist:
    die beiden Haupträume (25, 26), wobei der eine das Zufuhrfluid, der andere das Abführfluid enthalten kann, wenn die Vorrichtung mit jedem der beiden Funktionshubräume arbeitet, wobei die Formen der die Haupträume begrenzenden Wände außerdem den Ausgleich der Druckkräfte des Fluids realisieren, das in den Verteilungsleitungen (31, 32) beinhaltet ist, die ständig mit den Haupträumen in Verbindung stehen; und zwei sekundäre Räume (36, 37), von denen, wenn die Vorrichtung mit dem großen Funktionshubraum (Figuren 1 bis 5) arbeitet, der eine das Zufuhrfluid, der andere das Abführfluid beinhaltet, und welche sekundären Räume, wenn die Vorrichtung mit dem kleinen Funktionshubraum arbeitet (Figuren 6 bis 8), miteinander in Verbindung stehen; und,
    daß die beiden sekundären Räume (36, 37) jeweils mit zwei sogenannten zweiten Ausgleichsräumen (68, 64) verbunden sind, wobei jeder durch mindestens eine innere Leitung (69, 65), die in dem inneren Fluidverteiler angeordnet ist, mit einem der sekundären Räume (36, 37) verbunden ist.
  8. Vorrichtung nach Anspruch 6, dadurch gekennzeichnet, daß diese Vorrichtung (Figuren 10 bis 15) zum Typ gehört, der mindestens einen großen und mindestens einen kleinen Funktionshubraum umfaßt und aufweist:
    die beiden Haupträume (25, 26), von denen der eine das Zufuhrfluid, der andere das Abführfluid beinhalten können, wenn die Vorrichtung mit jeder der beiden Funktionshubräume arbeitet, wobei die Formen der die Haupträume begrenzenden Wände außerdem einen Ausgleich der Druckkräfte realisieren, die in Verteilungsleitungen (31-236, 32) beinhaltet sind, die ständig mit den Haupträumen in Verbindung stehen; und einen sekundären einzigen Raum (237), der, wenn die Vorrichtung mit dem großen Funktionshubraum (Figuren 10 bis 12) arbeitet, eines der Zufuhr- und Abführfluide beinhaltet und, wenn die Vorrichtung mit dem kleinen Funktionshubraum (Figuren 13 bis 15) arbeitet, das andere der Fluide enthält; und daß der sekundäre einzige Raum (237) mit einem sogenannten zweiten einzigen Ausgleichsraum (264) verbunden ist, der durch mindestens eine in dem inneren Fluidverteiler vorgesehenen innere Leitung (265) mit dem zweiten einzigen Raum (237) verbunden ist.
  9. Vorrichtung nach Anspruch 6, dadurch gekennzeichnet, daß sie zum Typ mit einem einzigen Funktionshubraum (Figuren 16 bis 18) gehört und aufweist: die zwei Haupträume (25, 26), wobei der eine das Zufuhrfluid, der andere das Abführfluid beinhalten kann; und
    zwei sogenannte zweite Ausgleichsräume (168, 164), die durch die inneren Leitungen (169, 165), die in dem inneren Fluidraum vorgesehen sind, verbunden sind, wobei der eine (168) der zweiten Ausgleichsräume mit den ersten Verteilungsleitungen (136) der zweiten Paargruppe (136-137) der Verteilungsleitungen verbunden ist, der andere (164) der beiden zweiten Ausgleichsräume mit den zweiten Verteilungsleitungen (137) der zweiten Paargruppe (136-137) der Verteilungsleitungen verbunden ist.
EP92402189A 1991-08-01 1992-07-30 Druckflüssigkeitsvorrichtung mit Ausgleichsräumen Expired - Lifetime EP0526333B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9109817 1991-08-01
FR9109817A FR2679963B1 (fr) 1991-08-01 1991-08-01 Mecanisme a fluide sous pression muni d'enceintes d'equilibrage particulieres.

Publications (2)

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EP0526333A1 EP0526333A1 (de) 1993-02-03
EP0526333B1 true EP0526333B1 (de) 1995-05-10

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EP92402189A Expired - Lifetime EP0526333B1 (de) 1991-08-01 1992-07-30 Druckflüssigkeitsvorrichtung mit Ausgleichsräumen

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US (1) US5261318A (de)
EP (1) EP0526333B1 (de)
DE (1) DE69202418T2 (de)
FR (1) FR2679963B1 (de)

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FR2764947B1 (fr) * 1997-06-23 1999-10-01 Poclain Hydraulics Sa Moteur hydraulique
FI110446B (fi) * 1997-11-11 2003-01-31 Valmet Hydraulics Oy Radiaalimäntähydraulimoottori
FR2794496B1 (fr) * 1999-06-04 2001-08-24 Poclain Hydraulics Ind Selecteur de cylindree pour un moteur hydraulique evitant un freinage brutal lors du passage de petite cylindree en grande cylindree
JP2003006020A (ja) * 2001-06-26 2003-01-10 Hitachi Ltd 複製データベースアクセス装置とそのアクセス方法
FR2834011B1 (fr) * 2001-12-24 2004-03-19 Poclain Hydraulics Ind Moteur hydraulique a pistons radiaux
FR3011045B1 (fr) * 2013-09-25 2015-10-30 Vianney Rabhi Bague d'etancheite pour distributeur de pompe hydraulique
US10632829B2 (en) * 2015-02-20 2020-04-28 Vianney Rabhi Distributer phase shifter for a hydraulic pump motor

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1401395A1 (de) * 1960-03-07 1969-04-03 Karl Eickmann Hochdruckfaehige Steuerungen fuer Drehkolbenmaschinen und Drehfluegelmaschinen
FR2587761B1 (fr) * 1985-09-20 1988-01-15 Poclain Hydraulics Sa Mecanisme hydraulique comportant des glace et contre-glace de distribution du fluide
EP0263218B1 (de) * 1986-10-08 1990-01-03 POCLAIN HYDRAULICS Société Anonyme de droit français Flüssigkeitsmechanismus mit Fluidverteilscheibe und Gegenscheibe
FR2588616B1 (fr) * 1985-10-16 1988-01-08 Poclain Hydraulics Sa Mecanisme, moteur a pompe, a au moins deux cylindrees actives distinctes.
DE3706460A1 (de) * 1986-10-31 1988-09-08 Rexroth Mannesmann Gmbh Kolbenmaschine mit umschaltbarem hubraum

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EP0526333A1 (de) 1993-02-03
US5261318A (en) 1993-11-16
FR2679963B1 (fr) 1993-11-12
DE69202418D1 (de) 1995-06-14
FR2679963A1 (fr) 1993-02-05
DE69202418T2 (de) 1996-02-01

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