EP0302786A1 - Rotating machine with pistons and barrel with a fixed centering toggle type joint - Google Patents

Rotating machine with pistons and barrel with a fixed centering toggle type joint Download PDF

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Publication number
EP0302786A1
EP0302786A1 EP88402009A EP88402009A EP0302786A1 EP 0302786 A1 EP0302786 A1 EP 0302786A1 EP 88402009 A EP88402009 A EP 88402009A EP 88402009 A EP88402009 A EP 88402009A EP 0302786 A1 EP0302786 A1 EP 0302786A1
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EP
European Patent Office
Prior art keywords
barrel
plate
machine according
ball joint
bearing
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.)
Granted
Application number
EP88402009A
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German (de)
French (fr)
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EP0302786B1 (en
Inventor
Michel Drevet
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Individual
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Individual
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Publication date
Priority claimed from FR8711193A external-priority patent/FR2619166B2/en
Application filed by Individual filed Critical Individual
Priority to AT88402009T priority Critical patent/ATE58416T1/en
Publication of EP0302786A1 publication Critical patent/EP0302786A1/en
Application granted granted Critical
Publication of EP0302786B1 publication Critical patent/EP0302786B1/en
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Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/146—Swash plates; Actuating elements
    • F04B1/148—Bearings therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/02—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis with wobble-plate
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18296—Cam and slide
    • Y10T74/18336—Wabbler type

Definitions

  • the present invention relates to a rotary piston and barrel machine for pumps, hydraulic motors or compressors.
  • the invention relates to a machine of the type which is the subject of French patent application No. 85 15604 filed by the Applicant in which the rotary piston and barrel machine comprises a thrust plate inclined relative to its geometric axis of rotation. which coincides with the geometric axis of the barrel, the central part of the inclined plate comprising a spherical bearing which rotates freely around a fixed central ball joint, integral with a half-shaft anchored directly in the central part of the barrel, while that -this is connected by a rigid peripheral casing which covers the rear of the crankshaft behind which it closes, and in this machine the central spherical ball joint is secured to a second rigid half-shaft, located opposite the first with which it is aligned, this second half-shaft being, by its opposite end, rigidly anchored on the rear part of the casing of the machine.
  • the invention aims first of all to transfer the various forces and constraints to which the ball joint is subjected to the barrel of the machine because it has been found that the barrel constitutes an extremely rigid assembly unlike the casing in which the thrust plate is housed and the motion transmitter.
  • the invention also makes it possible to automatically compensate for the differential expansions which may occur during the operation of the machine.
  • the invention makes it possible, by subjecting the thrust plate to a prestress, to compensate for the forces exerted on it during operation.
  • the rotary piston and barrel machine comprising a thrust plate inclined with respect to its geometric axis of rotation which coincides with the geometric axis of the barrel, the central part of the inclined plate comprising a spherical bearing which rotates freely around a fixed central ball joint anchored to the central part of the barrel while the latter is connected to a rigid peripheral casing, the central ball joint being integral with a rigid half-shaft connected to the rear part of the casing is characterized by at least one rod rigidly connected to the ball joint as well as to a piston arranged in a bore of the barrel and subjected to the action of a fluid under pressure, so that at least part of the axial stresses applied to the ball joint is transmitted to the barrel without being applied to the casing.
  • the machine shown according to the embodiment of FIG. 1 comprises a casing 1 connected to the periphery of a barrel 2 to which are fixed tie rods 3 forming at the same time spacers and used for fixing and supporting a body 4 delimiting cylinders 6 in which pistons slide.
  • the body 4 constitutes either a pump body or a motor body depending on whether the cylinders 6 are used for the delivery of a fluid or for the admission of a fluid intended to drive the pistons 7.
  • the body 4 is well known, as is the arrangement of the pistons 7 in the cylinders 6 and, therefore, this part of the machine is not described further.
  • the barrel 2 delimits sheaths 8, only one of which is visible, and in each of which can be moved a slide 9 connected by a rod 10 to one of the pistons 7.
  • the slide 9 contains bearings 11 for a cylindrical head 12 of connecting rods, the foot 13 of which is also cylindrical, is articulated in one of several bearings 14 which contains an oscillating thrust plate 15.
  • the thrust plate 15 is carried by a ball joint 16 to which it is connected by hemispherical rings 17 forming bearings.
  • the thrust plate 15 is prevented from turning freely by a reaction rod 18 articulated by its spherical head 19 in a clamp 20 rigidly connected by a frame 21 which is itself connected both to the casing 1 and to the barrel 2 by gussets 22.
  • the frame 21 forms a bearing support 23 for a motor shaft 24 provided with a pinion 25.
  • the motor shaft 24 is further carried in a bearing 26 connected to the rear part 1 a of the casing 1.
  • the rear part 1 a above is itself reinforced by a plate 27 which can form a thrust plate and which cooperates with said rear part 1 a for maintaining a thrust bearing 28 of a motion transmitter 29 constituted in the form of a beveled disc comprising a toothed crown 30 meshing with the pinion 25.
  • the motion transmitter 29 carries a bearing stop 31 which connects it to the oscillating thrust plate 15.
  • the motion transmitter 29 is carried by bearings 32, the inner cage of which is threaded on a half-shaft constituted by a tubular tail 33 rigidly connected to the ball joint 16, said tubular tail possibly being formed in one piece with said ball joint.
  • the tubular tail 33 is coaxial with the geometric axis of the barrel 2 and it is engaged in an opening 34 of the plate 27.
  • a stop ring 35 is preferably mounted in an adjustable manner on the end of the tubular tail 33 to bear, preferably by an elastic member 36, for example a conical elastic washer, against the plate 27.
  • a preload block 27 a is interposed between the plate 27 and the rear plate 1 a of the casing.
  • the part of the ball joint 16 facing the barrel 2 is fixed to the latter by means of a key 37.
  • the ball joint 16 is also carried by the threaded part of a rod 38 concentric with the tubular tail 33.
  • the rod 38 forms a part of larger diameter 38 a guided in a bore 39 of the barrel 2 to which it is tightly connected by seals 40.
  • the rod 38 forms a part of smaller diameter 38 b which extends to the inside the tubular tail 33, defining therewith an annular chamber 41.
  • the part of smaller diameter 38 b is tightly connected to the tubular tail 33 by a seal 42 and it is also mechanically connected to said tubular tail 33 by a stop lock nut 43 which bears on the free end of said tubular tail 33.
  • the lock nut 43 thus makes it possible to block the position of the rod 38 in the ball joint 16 so as to leave a clearance 16 a in the housing on the barrel 2 of the cylindrical front part of the ball joint 16.
  • a channel 44 makes it possible to connect the annular chamber 41 described above to a source of pressurized fluid, in particular oil, so that this oil is brought by said annular chamber to distribution channels 45 provided in the ball joint 16 and making it possible to lead the oil to the hemispherical rings 17 forming a ball bearing.
  • the large diameter portion 38a of the rod 38 is rigidly connected to a piston 46 disposed in a cylinder 47 of the barrel 2.
  • the rear face of the piston 46 defines with the cylinder 47 a chamber 48 for the admission of a fluid pressure regulation including oil from an adjustable source 49.
  • the source 49 can be constituted by a compressor or a regulator applying in the chamber 48 a setting pressure which can for example depend on the working pressure prevailing in the body 4.
  • the barrel assembly 2, pulling 3, body 4 constitutes an extremely rigid unit so that the pressure developed in the chamber 48 can be a pressure high enough to balance at least part of the opposing forces applied to the ball joint 16 by the oscillating thrust plate 15 during operation of the machine.
  • the pressure in the chamber 48 exerted on the piston 46 is transmitted by the different parts of the rod 38 to the ball joint and to the stop nut 43 which bears against the tubular shank 33, and the stop ring 35 can apply part of the forces on the plate 27 holding the bearing 28 without these forces being applied to the housing 1.
  • the clearance 16 is provided in the housing on the barrel 2 on the front cylindrical portion of the ball 16 is made for controlling the stroke of the piston 46 whose role is to shoot the ball 16 apply part of the forces to it during pumping in order to relieve the thrust bearings 28 and 31.
  • FIG. 2 illustrates a simplified variant according to which the same reference numbers designate the same members known in FIG. 1.
  • the ball joint 16 is directly fixed to the threaded part of a rod 381 itself connected to a piston 461 delimiting with a cylinder 471 of the barrel 2 a chamber 481 to develop a compensation pressure.
  • a hydraulic cylinder 50 is provided in the plate 27 reinforcing the rear part 1 a of the casing 1, said hydraulic cylinder 50 acting on the bearing 28 against which abuts the movement of transmitter 29.
  • the hydraulic cylinder may be formed as shown schematically by a simple annular seal.
  • the above arrangement allows, as is apparent from consideration of the drawing and the preceding explanations, to distribute the hydraulic pressures intended to balance the axial stresses, on the one hand, on the barrel 2 and, on the other hand, on the plate 27.
  • the pressure that can be exerted by the hydraulic cylinder 50 is applied to the motion transmitter 29 and by the thrust bearing 31 to the oscillating thrust plate 15, which makes it possible to reduce and practically cancel under certain operating conditions the axial forces between the ball joint 16 and the hemispherical rings 17 of the oscillating thrust plate 15.
  • Fig. 2 shows that the hydraulic cylinder 50 is connected by a conduit 51 to a pressure regulator 52 which can be controlled by any suitable member, for example a computer making it possible to vary the compensation pressures exerted both by the hydraulic cylinder 50 only by the piston 461 depending on the cyclic pressure variations exerted by the thrust plate 15 on the ball joint 16.
  • a pressure regulator 52 which can be controlled by any suitable member, for example a computer making it possible to vary the compensation pressures exerted both by the hydraulic cylinder 50 only by the piston 461 depending on the cyclic pressure variations exerted by the thrust plate 15 on the ball joint 16.
  • the use of the shim 27 a in the embodiment of FIG. 2 means that it provides additional security in the event of failure of the hydraulic compensation.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Medicines Containing Antibodies Or Antigens For Use As Internal Diagnostic Agents (AREA)
  • A Measuring Device Byusing Mechanical Method (AREA)
  • Treatment Of Fiber Materials (AREA)
  • Actuator (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)

Abstract

Rotating machine with pistons (7) and barrel (2) comprising a thrust plate (15) inclined in relation to its geometric axis of rotation which coincides with the geometric axis of the barrel, the central part of the inclined plate (15) comprising a spherical bearing (17) which turns freely about a fixed central trunnion (16) anchored to the central section of the barrel (2) whilst the latter is connected to a rigid peripheral housing (1), the central trunnion being firmly attached to a rigid half-shaft (33) linked to the rear section of the housing (1), characterised by at least one rod (38) rigidly connected to the trunnion (16) and to a piston (46) arranged in a bore (47) in the barrel (2) and subjected to the action of a pressurised liquid in such a way that at least some of the axial stresses applied to the trunnion (16) are transmitted to the barrel (2) without being applied to the housing (1). <IMAGE>

Description

La présente invention est relative à une machine rotative à pistons et à barillet pour pompes, moteurs hydrauliques ou compresseurs.The present invention relates to a rotary piston and barrel machine for pumps, hydraulic motors or compressors.

L'invention concerne une machine du type faisant l'objet de la demande de brevet français N° 85 15604 déposée par le Demandeur dans laquelle la machine rotative à pistons et à barillet comprend un plateau de poussée incliné par rapport à son axe géométrique de rotation qui coïncide avec l'axe géométrique du barillet, la partie centrale du plateau incliné comportant un palier sphérique qui tourne librement autour d'une rotule centrale fixe, solidaire d'un demi-arbre ancré directement dans la partie centrale du barillet, alors que celui-ci est relié par un carter périphérique rigide qui coiffe l'arrière de l'embiellage derrière lequel il se referme, et dans cette machine la rotule sphérique centrale est solidaire d'un second demi-arbre rigide, situé à l'opposé du premier avec lequel il est aligné, ce second demi-arbre étant, par son extrémité opposée, rigidement ancré sur la partie arrière du carter de la machine.The invention relates to a machine of the type which is the subject of French patent application No. 85 15604 filed by the Applicant in which the rotary piston and barrel machine comprises a thrust plate inclined relative to its geometric axis of rotation. which coincides with the geometric axis of the barrel, the central part of the inclined plate comprising a spherical bearing which rotates freely around a fixed central ball joint, integral with a half-shaft anchored directly in the central part of the barrel, while that -this is connected by a rigid peripheral casing which covers the rear of the crankshaft behind which it closes, and in this machine the central spherical ball joint is secured to a second rigid half-shaft, located opposite the first with which it is aligned, this second half-shaft being, by its opposite end, rigidly anchored on the rear part of the casing of the machine.

L'invention vise tout d'abord à reporter les efforts et contraintes divers auxquels la rotule est soumise sur le barillet de la machine car il a été constaté que le barillet constitue un ensemble extrêmement rigide con­trairement au carter dans lequel est logé le plateau de poussée et le transmetteur de mouvement.The invention aims first of all to transfer the various forces and constraints to which the ball joint is subjected to the barrel of the machine because it has been found that the barrel constitutes an extremely rigid assembly unlike the casing in which the thrust plate is housed and the motion transmitter.

Selon l'invention, on crée une nouvelle disposition dans laquelle le carter n'est plus soumis qu'à des contraintes faibles, ce qui rend possible de le constituer d'une manière plus légère que jusqu'à présent.According to the invention, a new arrangement is created in which the casing is only subjected to stresses weak, which makes it possible to constitute it in a lighter way than hitherto.

Par ailleurs, l'invention permet également de compenser de façon automatique les dilatations différentielles qui peuvent se produire au cours du fonctionnement de la machine.Furthermore, the invention also makes it possible to automatically compensate for the differential expansions which may occur during the operation of the machine.

Supplémentairement encore, l'invention rend possible, en soumettant le plateau de poussée à une précontrainte, de compenser les efforts qui s'exercent sur lui pendant le fonctionnement.Additionally, the invention makes it possible, by subjecting the thrust plate to a prestress, to compensate for the forces exerted on it during operation.

La compensation des efforts pour rendre le plateau de poussée pratiquement flottant par rapport à la rotule qui le porte peut n'être exercée que pendant le fonctionne­ment de la machine de sorte que les pièces de celle-ci ne sont pas soumises à des efforts statiques importants lorsqu'elle n'est pas en fonctionnement.The compensation of the forces to make the thrust plate practically floating with respect to the ball joint which carries it can only be exerted during the operation of the machine so that the parts thereof are not subjected to significant static forces when it is not in operation.

Conformément à l'invention, la machine rotative à pistons et à barillet comprenant un plateau de poussée incliné par rapport à son axe géométrique de rotation qui coïn­cide avec l'axe géométrique du barillet, la partie centrale du plateau incliné comportant un palier sphéri­que qui tourne librement autour d'une rotule centrale fixe ancrée à la partie centrale du barillet alors que celui-ci est relié à un carter périphérique rigide, la rotule centrale étant solidaire d'un demi-arbre rigide relié à la partie arrière du carter est caractérisée par au moins une tige reliée rigidement à la rotule ainsi qu'à un piston disposé dans un alésage du barillet et soumis à l'action d'un fluide sous pression, de sorte qu'une partie au moins des contraintes axiales appliquées à la rotule est transmise au barillet sans être appliquée au carter.According to the invention, the rotary piston and barrel machine comprising a thrust plate inclined with respect to its geometric axis of rotation which coincides with the geometric axis of the barrel, the central part of the inclined plate comprising a spherical bearing which rotates freely around a fixed central ball joint anchored to the central part of the barrel while the latter is connected to a rigid peripheral casing, the central ball joint being integral with a rigid half-shaft connected to the rear part of the casing is characterized by at least one rod rigidly connected to the ball joint as well as to a piston arranged in a bore of the barrel and subjected to the action of a fluid under pressure, so that at least part of the axial stresses applied to the ball joint is transmitted to the barrel without being applied to the casing.

Diverses autres caractéristiques de l'invention ressor­tent d'ailleurs de la description détaillée qui suit.Various other characteristics of the invention will also emerge from the detailed description which follows.

Des formes de réalisation de l'objet de l'invention sont représentées, à titre d'exemples non limitatifs, aux dessins annexés.

  • La fig. 1 est une coupe élévation de la machine suivant l'invention.
  • La fig. 2 est une coupe élévation analogue à la fig.1 d'une variante.
Embodiments of the object of the invention are shown, by way of nonlimiting examples, in the accompanying drawings.
  • Fig. 1 is a sectional elevation of the machine according to the invention.
  • Fig. 2 is a sectional elevation similar to fig.1 of a variant.

La machine représentée suivant la réalisation de la fig. 1 comporte un carter 1 relié à la périphérie d'un barillet 2 auquel sont fixés des tirants 3 formant en même temps entretoises et servant à la fixation et support d'un corps 4 délimitant des cylindres 6 dans lesquels coulissent des pistons 7. Le corps 4 constitue soit un corps de pompe soit un corps de moteur suivant que les cylindres 6 servent au refoulement d'un fluide ou à l'admission d'un fluide destiné à entraîner les pis­tons 7.The machine shown according to the embodiment of FIG. 1 comprises a casing 1 connected to the periphery of a barrel 2 to which are fixed tie rods 3 forming at the same time spacers and used for fixing and supporting a body 4 delimiting cylinders 6 in which pistons slide. The body 4 constitutes either a pump body or a motor body depending on whether the cylinders 6 are used for the delivery of a fluid or for the admission of a fluid intended to drive the pistons 7.

Dans le type de machine auquel se réfère l'invention, le corps 4 est bien connu, de même que l'agencement des pistons 7 dans les cylindres 6 et, par conséquent, cette partie de la machine n'est pas décrite davantage.In the type of machine to which the invention refers, the body 4 is well known, as is the arrangement of the pistons 7 in the cylinders 6 and, therefore, this part of the machine is not described further.

Le barillet 2 délimite des fourreaux 8, dont un seul est apparent, et dans chacun desquels peut être déplacé un coulisseau 9 relié par une tige 10 à l'un des pistons 7.The barrel 2 delimits sheaths 8, only one of which is visible, and in each of which can be moved a slide 9 connected by a rod 10 to one of the pistons 7.

Le coulisseau 9 contient des coussinets 11 pour une tête cylindrique 12 de bielles dont le pied 13 également cylindrique est articulé dans l'un de plusieurs coussi­nets 14 que contient un plateau de poussée oscillant 15.The slide 9 contains bearings 11 for a cylindrical head 12 of connecting rods, the foot 13 of which is also cylindrical, is articulated in one of several bearings 14 which contains an oscillating thrust plate 15.

Le plateau de poussée 15 est porté par une rotule 16 à laquelle il est relié par des bagues hémisphériques 17 formant coussinets. Le plateau de poussée 15 est empêché de tourner librement par une bielle de réaction 18 articulée par sa tête sphérique 19 dans une crapaudine 20 reliée rigidement par un bâti 21 qui est lui-même relié tant au carter 1 qu'au barillet 2 par des goussets 22.The thrust plate 15 is carried by a ball joint 16 to which it is connected by hemispherical rings 17 forming bearings. The thrust plate 15 is prevented from turning freely by a reaction rod 18 articulated by its spherical head 19 in a clamp 20 rigidly connected by a frame 21 which is itself connected both to the casing 1 and to the barrel 2 by gussets 22.

Le bâti 21 forme un support de palier 23 pour un arbre moteur 24 muni d'un pignon 25.The frame 21 forms a bearing support 23 for a motor shaft 24 provided with a pinion 25.

L'arbre moteur 24 est en outre porté dans un palier 26 relié à la partie postérieure 1a du carter 1. La partie postérieure 1a ci-dessus est elle-même renforcée par une plaque 27 pouvant former plaque de poussée et qui coopère avec ladite partie postérieure 1a pour le maintien d'un palier de butée 28 d'un transmetteur de mouvement 29 constitué sous la forme d'un disque biseauté comportant une couronne dentée 30 engrènant avec le pignon 25. Le transmetteur de mouvement 29 porte un palier de butée 31 qui le relie au plateau de poussée oscillant 15.The motor shaft 24 is further carried in a bearing 26 connected to the rear part 1 a of the casing 1. The rear part 1 a above is itself reinforced by a plate 27 which can form a thrust plate and which cooperates with said rear part 1 a for maintaining a thrust bearing 28 of a motion transmitter 29 constituted in the form of a beveled disc comprising a toothed crown 30 meshing with the pinion 25. The motion transmitter 29 carries a bearing stop 31 which connects it to the oscillating thrust plate 15.

Le transmetteur de mouvement 29 est porté par des paliers 32 dont la cage intérieure est enfilée sur un demi-arbre constitué par une queue tubulaire 33 reliée rigidement à la rotule 16, ladite queue tubulaire pouvant le cas échéant être formée d'une seule pièce avec ladite rotule.The motion transmitter 29 is carried by bearings 32, the inner cage of which is threaded on a half-shaft constituted by a tubular tail 33 rigidly connected to the ball joint 16, said tubular tail possibly being formed in one piece with said ball joint.

La queue tubulaire 33 est coaxiale à l'axe géométrique du barillet 2 et elle est engagée dans une ouverture 34 de la plaque 27.The tubular tail 33 is coaxial with the geometric axis of the barrel 2 and it is engaged in an opening 34 of the plate 27.

Une bague de butée 35 est montée de préférence de façon réglable, sur l'extrémité de la queue tubulaire 33 pour prendre appui, de préférence par un organe élastique 36, par exemple une rondelle élastique conique, contre la plaque 27.A stop ring 35 is preferably mounted in an adjustable manner on the end of the tubular tail 33 to bear, preferably by an elastic member 36, for example a conical elastic washer, against the plate 27.

Il est avantageux ainsi que le montre le dessin qu'une cale de précharge 27a soit interposée entre la plaque 27 et la plaque postérieure 1a du carter. L'épaisseur de la cale 27a est calculée pour le réglage des valeurs respec­tives des forces de précharge figurées en L₁ et L₂ soit fonction du rapport de répartition désirée. On pourra par exemple choisir que L₁ = L₂ = L/2.It is advantageous as shown in the drawing that a preload block 27 a is interposed between the plate 27 and the rear plate 1 a of the casing. The thickness of the shim 27 a is calculated for the adjustment of the respective values of the preload forces shown in L₁ and L₂ depending on the desired distribution ratio. We could for example choose that L₁ = L₂ = L / 2.

Pour empêcher que la rotule 16 et la queue tubulaire 33 puissent tourner, la partie de la rotule 16 tournée vers le barillet 2 est calée à celui-ci au moyen d'une cla­vette 37.To prevent the ball joint 16 and the tubular shank 33 from rotating, the part of the ball joint 16 facing the barrel 2 is fixed to the latter by means of a key 37.

La rotule 16 est également portée par la partie filetée d'une tige 38 concentrique à la queue tubulaire 33.The ball joint 16 is also carried by the threaded part of a rod 38 concentric with the tubular tail 33.

La tige 38 forme une partie de plus grand diamètre 38a guidée dans un alésage 39 du barillet 2 auquel elle est reliée de façon étanche par des joints 40. La tige 38 forme une partie de plus petit diamètre 38b qui s'étend à l'intérieur de la queue tubulaire 33 en délimitant avec celle-ci une chambre annulaire 41.The rod 38 forms a part of larger diameter 38 a guided in a bore 39 of the barrel 2 to which it is tightly connected by seals 40. The rod 38 forms a part of smaller diameter 38 b which extends to the inside the tubular tail 33, defining therewith an annular chamber 41.

La partie de plus petit diamètre 38b est reliée de façon étanche à la queue tubulaire 33 par un joint d'étanchéité 42 et elle est par ailleurs reliée mécaniquement à ladite queue tubulaire 33 par un contre-écrou de butée 43 qui prend appui sur l'extrémité libre de ladite queue tubu­laire 33. Le contre-écrou 43 permet ainsi de bloquer au réglage désiré la position de la tige 38 dans la rotule 16 de manière à laisser un jeu 16a dans le logement sur le barillet 2 de la partie avant cylindrique de la rotule 16.The part of smaller diameter 38 b is tightly connected to the tubular tail 33 by a seal 42 and it is also mechanically connected to said tubular tail 33 by a stop lock nut 43 which bears on the free end of said tubular tail 33. The lock nut 43 thus makes it possible to block the position of the rod 38 in the ball joint 16 so as to leave a clearance 16 a in the housing on the barrel 2 of the cylindrical front part of the ball joint 16.

Un canal 44 permet de relier la chambre annulaire 41 décrite ci-dessus à une source de fluide sous pression notamment de l'huile pour que cette huile soit amenée par ladite chambre annulaire à des canaux de répartition 45 prévus dans la rotule 16 et permettant de conduire l'huile aux bagues hémisphériques 17 formant un coussinet sphérique.A channel 44 makes it possible to connect the annular chamber 41 described above to a source of pressurized fluid, in particular oil, so that this oil is brought by said annular chamber to distribution channels 45 provided in the ball joint 16 and making it possible to lead the oil to the hemispherical rings 17 forming a ball bearing.

La partie de grand diamètre 38a de la tige 38 est reliée rigidement à un piston 46 disposé dans un cylindre 47 du barillet 2. La face postérieure du piston 46 délimite avec le cylindre 47 une chambre 48 pour l'admission d'un fluide de régulation sous pression notamment de l'huile provenant d'une source réglable 49.The large diameter portion 38a of the rod 38 is rigidly connected to a piston 46 disposed in a cylinder 47 of the barrel 2. The rear face of the piston 46 defines with the cylinder 47 a chamber 48 for the admission of a fluid pressure regulation including oil from an adjustable source 49.

La source 49 peut être constituée par un compresseur ou un régulateur appliquant dans la chambre 48 une pression de tarage pouvant par exemple dépendre de la pression de travail régnant dans le corps 4.The source 49 can be constituted by a compressor or a regulator applying in the chamber 48 a setting pressure which can for example depend on the working pressure prevailing in the body 4.

L'ensemble barillet 2, tirant 3, corps 4 constitue une unité extrêmement rigide de sorte que la pression déve­loppée dans la chambre 48 peut être une pression suffi­samment élevée pour équilibrer au moins une partie des efforts antagonistes appliqués sur la rotule 16 par le plateau de poussée oscillant 15 lors du fonctionnement de la machine.The barrel assembly 2, pulling 3, body 4 constitutes an extremely rigid unit so that the pressure developed in the chamber 48 can be a pressure high enough to balance at least part of the opposing forces applied to the ball joint 16 by the oscillating thrust plate 15 during operation of the machine.

La pression dans la chambre 48 s'exerçant sur le piston 46 est transmise par les différentes parties de la tige 38 à la rotule et à l'écrou de butée 43 qui porte contre la queue tubulaire 33, et la bague de butée 35 peut appliquer une partie des efforts à la plaque 27 mainte­nant le palier 28 sans que ces efforts soient appliqués au carter 1.The pressure in the chamber 48 exerted on the piston 46 is transmitted by the different parts of the rod 38 to the ball joint and to the stop nut 43 which bears against the tubular shank 33, and the stop ring 35 can apply part of the forces on the plate 27 holding the bearing 28 without these forces being applied to the housing 1.

Comme cela ressort de ce qui précède, le jeu 16a prévu dans le logement sur le barillet 2 de la partie avant cylindrique de la rotule 16 est en fait destiné à contrô­ler la course du piston 46 dont le rôle est de tirer la rotule 16 pour lui appliquer une partie des efforts pendant le pompage en vue de soulager les paliers de butée 28 et 31.As apparent from the foregoing, the clearance 16 is provided in the housing on the barrel 2 on the front cylindrical portion of the ball 16 is made for controlling the stroke of the piston 46 whose role is to shoot the ball 16 apply part of the forces to it during pumping in order to relieve the thrust bearings 28 and 31.

En choisissant convenablement la pression dans la chambre 48, on peut, si on le désire, faire en sorte que toutes les contraintes qui s'exercent axialement sur la rotule 16 soient transmises par la queue tubulaire 33 sans être transmises au carter 1 qui peut alors être réalisé de façon particulièrement légère.By suitably choosing the pressure in the chamber 48, it is possible, if desired, to ensure that all the stresses which are exerted axially on the ball joint 16 are transmitted by the tubular tail 33 without being transmitted to the casing 1 which can then be carried out in a particularly light way.

Etant donné que les contraintes axiales sont appliquées au matelas fluide que constitue la chambre 48, celle-ci agit également en tant qu'élément compensateur de dilata­tion différentielle pouvant exister entre la queue tubulaire 33, les différentes parties de la tige 38 et le corps du barillet 2.Since the axial stresses are applied to the fluid mattress that constitutes the chamber 48, it also acts as a compensating element for differential expansion which may exist between the tubular tail 33, the different parts of the rod 38 and the body of the barrel 2.

La fig. 2 illustre une variante simplifiée selon laquelle les mêmes numéros de référence désignent les mêmes organes connus à la fig. 1.Fig. 2 illustrates a simplified variant according to which the same reference numbers designate the same members known in FIG. 1.

Selon la fig. 2, la rotule 16 est directement fixée à la partie filetée d'une tige 38₁ elle-même reliée à un piston 46₁ délimitant avec un cylindre 47₁ du barillet 2 une chambre 48₁ pour développer une pression de compensa­tion.According to fig. 2, the ball joint 16 is directly fixed to the threaded part of a rod 38₁ itself connected to a piston 46₁ delimiting with a cylinder 47₁ of the barrel 2 a chamber 48₁ to develop a compensation pressure.

Par ailleurs, un cylindre hydraulique 50 est prévu dans la plaque 27 renforçant la partie postérieure 1a du carter 1, ledit cylindre hydraulique 50 agissant sur le palier 28 contre lequel bute le transmetteur de mouvement 29. Le cylindre hydraulique peut être constitué comme représenté schématiquement par un simple joint annulaire.Moreover, a hydraulic cylinder 50 is provided in the plate 27 reinforcing the rear part 1 a of the casing 1, said hydraulic cylinder 50 acting on the bearing 28 against which abuts the movement of transmitter 29. The hydraulic cylinder may be formed as shown schematically by a simple annular seal.

La disposition ci-dessus permet, comme cela ressort de la considération du dessin et des explications qui précè­dent, de répartir les pressions hydrauliques destinées à équilibrer les contraintes axiales, d'une part, sur le barillet 2 et, d'autre part, sur la plaque 27. La pres­sion pouvant être exercée par le cylindre hydraulique 50 est appliquée au transmetteur de mouvement 29 et par le palier de butée 31 au plateau de poussée oscillant 15, ce qui permet de réduire et pratiquement d'annuler dans certaines conditions de fonctionnement les efforts axiaux entre la rotule 16 et les bagues hémisphériques 17 du plateau de poussée oscillant 15.The above arrangement allows, as is apparent from consideration of the drawing and the preceding explanations, to distribute the hydraulic pressures intended to balance the axial stresses, on the one hand, on the barrel 2 and, on the other hand, on the plate 27. The pressure that can be exerted by the hydraulic cylinder 50 is applied to the motion transmitter 29 and by the thrust bearing 31 to the oscillating thrust plate 15, which makes it possible to reduce and practically cancel under certain operating conditions the axial forces between the ball joint 16 and the hemispherical rings 17 of the oscillating thrust plate 15.

La fig. 2 montre que le cylindre hydraulique 50 est relié par un conduit 51 à un régulateur de pression 52 qui peut être piloté par tout organe approprié par exemple un ordinateur permettant de faire varier les pressions de compensation exercées tant par le cylindre hydraulique 50 que par le piston 46₁ en dépendance des variations cycliques de pression exercées par le plateau de poussée 15 sur la rotule 16.Fig. 2 shows that the hydraulic cylinder 50 is connected by a conduit 51 to a pressure regulator 52 which can be controlled by any suitable member, for example a computer making it possible to vary the compensation pressures exerted both by the hydraulic cylinder 50 only by the piston 46₁ depending on the cyclic pressure variations exerted by the thrust plate 15 on the ball joint 16.

L'utilisation de la cale 27a dans la réalisation de la fig. 2 fait qu'elle assure une sécurité supplémentaire en cas de panne de la compensation hydraulique.The use of the shim 27 a in the embodiment of FIG. 2 means that it provides additional security in the event of failure of the hydraulic compensation.

L'invention n'est pas limitée aux exemples de réalisation représentés et décrits en détail car diverses modifica­tions peuvent y être apportées sans sortir de son cadre.The invention is not limited to the embodiments shown and described in detail since various modifications can be made thereto without departing from its scope.

Claims (12)

1. Machine rotative à pistons (7) et à barillet (2) comprenant un plateau de poussée (15) incliné par rapport à son axe géométrique de rotation qui coïncide avec l'axe géométrique du barillet, la partie centrale du plateau incliné (15) comportant un palier sphérique (17) qui tourne librement autour d'une rotule centrale fixe (16) ancrée à la partie centrale du barillet (2) alors que celui-ci est relié à un carter périphérique rigide (1), 1a rotule centrale étant solidaire d'un demi-arbre rigide (33) relié à la partie arrière du carter (1), caractéri­sée par au moins une tige (38, 38₁) reliée rigidement à la rotule (16) ainsi qu'à un piston (46, 46₁) disposé dans un alésage (47, 47₁) du barillet (2) et soumis à l'action d'un fluide sous pression de sorte qu'une partie au moins des contraintes axiales appliquées à la rotule (16) est transmise au barillet (2) sans être appliquée au carter (1).1. rotary piston machine (7) and barrel (2) comprising a thrust plate (15) inclined relative to its geometric axis of rotation which coincides with the geometric axis of the barrel, the central part of the inclined plate (15 ) comprising a spherical bearing (17) which rotates freely around a fixed central ball joint (16) anchored to the central part of the barrel (2) while the latter is connected to a rigid peripheral casing (1), the central ball joint being integral with a rigid half-shaft (33) connected to the rear part of the casing (1), characterized by at least one rod (38, 38₁) rigidly connected to the ball joint (16) as well as to a piston (46 , 46₁) arranged in a bore (47, 47₁) of the barrel (2) and subjected to the action of a fluid under pressure so that at least part of the axial stresses applied to the ball joint (16) is transmitted to the barrel (2) without being applied to the casing (1). 2. Machine suivant la revendication 1, caractérisée par un jeu (16a) de réglage de la course du piston (46, 46₁) prévu entre la rotule (16) et le barillet (2).2. Machine according to claim 1, characterized by a game (16 a ) for adjusting the stroke of the piston (46, 46₁) provided between the ball joint (16) and the barrel (2). 3. Machine suivant l'une des revendications 1 et 2, caractérisée en ce que le demi-arbre (33) solidaire de la rotule (16) est opposé à la tige (38, 38₁) et prend appui contre une plaque (27) fixée à la partie arrière du carter (1), ladite plaque formant butée pour un palier (28) d'un transmetteur de mouvement (29) d'actionnement, par un palier de butée (31), d'un plateau de poussée (15).3. Machine according to one of claims 1 and 2, characterized in that the half-shaft (33) integral with the ball joint (16) is opposite the rod (38, 38₁) and bears against a plate (27) fixed to the rear part of the casing (1), said plate forming a stop for a bearing (28) of a motion transmitter (29) for actuation, by a stop bearing (31), of a thrust plate ( 15). 4. Machine suivant l'une des revendications 1 à 3, caractérisée par un cylindre hydraulique (50) interposé entre la plaque (27) contre laquelle s'appliquent le demi-arbre (33) et le palier (28) formant butée pour le transmetteur de mouvement (29) relié au plateau de poussée (15) par le palier de butée (31), ledit cylindre hydraulique (50) étant alimenté en fluide sous pression pour compenser au moins partiellement les contraintes axiales s'exerçant sur le plateau de poussée (7).4. Machine according to one of claims 1 to 3, characterized by a hydraulic cylinder (50) interposed between the plate (27) against which the half-shaft (33) is applied and the bearing (28) forming a stop for the motion transmitter (29) connected to the thrust plate (15) by the stop bearing (31) , said hydraulic cylinder (50) being supplied with pressurized fluid to at least partially compensate for the axial stresses exerted on the thrust plate (7). 5. Machine suivant l'une des revendications 1 à 4, caractérisée en ce que le demi-arbre (33) est constitué par une queue tubulaire formée à partir de la rotule (16), ladite queue étant traversée par une partie (38b) de la tige (38) à laquelle elle est reliée par un écrou de butée (43).5. Machine according to one of claims 1 to 4, characterized in that the half-shaft (33) consists of a tubular tail formed from the ball joint (16), said tail being traversed by a part (38 b ) of the rod (38) to which it is connected by a stop nut (43). 6. Machine suivant l'une des revendications 1 à 5, caractérisée en ce que la queue tubulaire (33) formant le demi-arbre et la partie (38b) délimitent une chambre annulaire (41) pour l'amenée par des canaux (44, 45) d'un fluide de lubrification au coussinet sphérique (17) du plateau de poussée (15).6. Machine according to one of claims 1 to 5, characterized in that the tubular tail (33) forming the half-shaft and the part (38 b ) define an annular chamber (41) for the supply by channels ( 44, 45) of a lubrication fluid to the ball bearing (17) of the thrust plate (15). 7. Machine suivant l'une des revendications 1 à 6, caractérisée en ce que la queue tubulaire (33) prend appui contre la plaque (27) de renforcement de la partie arrière du carter (1) par une bague de butée (35).7. Machine according to one of claims 1 to 6, characterized in that the tubular tail (33) bears against the plate (27) for reinforcing the rear part of the casing (1) by a stop ring (35) . 8. Machine suivant la revendication 7, caractérisée par un organe élastique du genre rondelle conique interposé entre la bague de butée (35) de la queue tubulaire (33) et la plaque de renforcement (27).8. Machine according to claim 7, characterized by an elastic member of the conical washer type interposed between the stop ring (35) of the tubular shank (33) and the reinforcing plate (27). 9. Machine suivant l'une des revendications 1 à 8, caractérisée en ce que la pression exercée sur le piston (46, 46₁) est déterminée en fonction des pressions de travail de pistons (7) de la machine.9. Machine according to one of claims 1 to 8, characterized in that the pressure exerted on the piston (46, 46₁) is determined according to the working pressures of pistons (7) of the machine. 10. Machine suivant l'une des revendications 1 à 9, caractérisée en ce que la pression de compensation exercée par le cylindre hydraulique (50) est déterminée en dépendance de la pression de travail par un régulateur de pression (52).10. Machine according to one of claims 1 to 9, characterized in that the compensation pressure exerted by the hydraulic cylinder (50) is determined in dependence on the working pressure by a pressure regulator (52). 11. Machine suivant l'une des revendications 1 à 10, caractérisée en ce que les pressions de compensation sont déterminées par un ordinateur en dépendance des varia­tions cycliques des pressions de travail.11. Machine according to one of claims 1 to 10, characterized in that the compensation pressures are determined by a computer in dependence on the cyclic variations of the working pressures. 12. Machine suivant l'une des revendications 1 à 11, caractérisée par une cale de précharge (27a) insérée entre la plaque (27) et la plaque postérieure (1a) du carter.12. Machine according to one of claims 1 to 11, characterized by a preload block (27 a ) inserted between the plate (27) and the rear plate (1 a ) of the housing.
EP88402009A 1987-08-06 1988-08-02 Rotating machine with pistons and barrel with a fixed centering toggle type joint Expired - Lifetime EP0302786B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88402009T ATE58416T1 (en) 1987-08-06 1988-08-02 ROTATING DRUM PISTON MACHINE WITH FIXED, CENTERING BELLY JOINT.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8711193 1987-08-06
FR8711193A FR2619166B2 (en) 1985-10-14 1987-08-06 ROTARY PISTON AND BARREL MACHINE WITH FIXED CENTERING BALL

Publications (2)

Publication Number Publication Date
EP0302786A1 true EP0302786A1 (en) 1989-02-08
EP0302786B1 EP0302786B1 (en) 1990-11-14

Family

ID=9353967

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88402009A Expired - Lifetime EP0302786B1 (en) 1987-08-06 1988-08-02 Rotating machine with pistons and barrel with a fixed centering toggle type joint

Country Status (12)

Country Link
US (1) US4911064A (en)
EP (1) EP0302786B1 (en)
JP (1) JP2567921B2 (en)
CN (1) CN1012198B (en)
AT (1) ATE58416T1 (en)
CA (1) CA1304985C (en)
DE (1) DE3861077D1 (en)
ES (1) ES2018627B3 (en)
GR (1) GR3001391T3 (en)
NO (1) NO167824C (en)
SU (1) SU1748659A3 (en)
UA (1) UA9866A (en)

Cited By (1)

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US4978774A (en) * 1989-01-27 1990-12-18 Hoechst Aktiengesellschaft Process for the preparation of D(+)-2-(4-acetylphenoxy)-propionic esters

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JPH07179504A (en) * 1993-12-22 1995-07-18 Fujimori Kogyo Kk Fine particle polymer and its production
JPH09137775A (en) * 1995-09-14 1997-05-27 Calsonic Corp Capacity variable swash plate type compressor
US7118595B2 (en) * 2002-03-18 2006-10-10 Medtronic, Inc. Flexible annuloplasty prosthesis and holder
US6719786B2 (en) * 2002-03-18 2004-04-13 Medtronic, Inc. Flexible annuloplasty prosthesis and holder
US8048152B2 (en) * 2005-09-30 2011-11-01 Medtronic, Inc. Method of implanting an annuloplasty prosthesis
US9011528B2 (en) * 2005-09-30 2015-04-21 Medtronic, Inc. Flexible annuloplasty prosthesis
MD309Y (en) * 2010-02-23 2010-12-31 Артур НИКИШОВ Axial-piston machine
JP6688724B2 (en) * 2016-03-28 2020-04-28 株式会社神戸製鋼所 Hydraulic rotary machine

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FR2211090A5 (en) * 1972-12-14 1974-07-12 Creusot Loire
EP0130912A1 (en) * 1983-07-01 1985-01-09 Framatome Swash plate mechanism, especially for the drive of a pump
FR2588617A1 (en) * 1985-10-14 1987-04-17 Drevet Michel ROTARY PISTON AND BARREL MACHINE WITH FIXED CENTERING.

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FR2211090A5 (en) * 1972-12-14 1974-07-12 Creusot Loire
EP0130912A1 (en) * 1983-07-01 1985-01-09 Framatome Swash plate mechanism, especially for the drive of a pump
FR2588617A1 (en) * 1985-10-14 1987-04-17 Drevet Michel ROTARY PISTON AND BARREL MACHINE WITH FIXED CENTERING.

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4978774A (en) * 1989-01-27 1990-12-18 Hoechst Aktiengesellschaft Process for the preparation of D(+)-2-(4-acetylphenoxy)-propionic esters

Also Published As

Publication number Publication date
CA1304985C (en) 1992-07-14
GR3001391T3 (en) 1992-09-11
ATE58416T1 (en) 1990-11-15
NO883478L (en) 1989-02-07
US4911064A (en) 1990-03-27
NO167824B (en) 1991-09-02
DE3861077D1 (en) 1990-12-20
NO883478D0 (en) 1988-08-04
CN1032222A (en) 1989-04-05
JPS6463663A (en) 1989-03-09
CN1012198B (en) 1991-03-27
EP0302786B1 (en) 1990-11-14
ES2018627B3 (en) 1991-04-16
NO167824C (en) 1991-12-11
UA9866A (en) 1996-09-30
JP2567921B2 (en) 1996-12-25
SU1748659A3 (en) 1992-07-15

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