EP0362133B1 - Machine pour fluide non compressible - Google Patents

Machine pour fluide non compressible Download PDF

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Publication number
EP0362133B1
EP0362133B1 EP89810698A EP89810698A EP0362133B1 EP 0362133 B1 EP0362133 B1 EP 0362133B1 EP 89810698 A EP89810698 A EP 89810698A EP 89810698 A EP89810698 A EP 89810698A EP 0362133 B1 EP0362133 B1 EP 0362133B1
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EP
European Patent Office
Prior art keywords
inlet
displacer
outlet
pumping space
displacement machine
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
EP89810698A
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German (de)
English (en)
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EP0362133A1 (fr
Inventor
Kurt GÜTTINGER
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Cessione vdo Adolf Schindling AG
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Gutag Innovations AG
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Publication of EP0362133A1 publication Critical patent/EP0362133A1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/04—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents of internal-axis type
    • F01C1/045—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents of internal-axis type having a C-shaped piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/02—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C2/04—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents of internal axis type
    • F04C2/045—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents of internal axis type having a C-shaped piston

Definitions

  • the invention relates to a displacement machine for incompressible media with a conveying space arranged in a fixed housing, designed in the manner of a circular slot, and with a displacer body, which is also circular and is assigned to the conveying space and is held on a disk-shaped rotor which can be driven eccentrically relative to the housing.
  • each of its points executes a circular movement delimited by the circumferential walls of the delivery chamber, and its curvature relative to that of the delivery chamber is dimensioned such that it touches the inner and outer circumferential walls of the delivery chamber on at least one sealing line that continuously progresses during operation and thus the delivery chamber divided into inner and outer work spaces through which the medium is conveyed from an inlet to an outlet, the inlet and outlet being preferably radially in the conveying space m extending web are separated from each other, which is why the displacer is interrupted in the region of the web, and a cross-disk clutch is provided for guiding the rotor relative to the housing, and a wobble rod is connected to a driving crank drive for circular drive of the displacer.
  • Displacement machines for liquids with a circular displacement body have been known from DE-C-177654 since 1905.
  • the annular piston protruding into the delivery chamber is arranged in a swinging manner, for which purpose it is guided on the web that separates the inlet from the outlet. It is driven by a crank on which it is supported by means of a hub.
  • This machine should be characterized by an uninterrupted and even conveying.
  • a displacement machine but not with a circular displacement body but with a heart-shaped displacement body, is known from WO 86/05241.
  • 4 displacement vanes are simultaneously set in a cyclical relative movement to their associated chambers by means of a crank mechanism.
  • a radially adjustable member generates a driving force with a radial and tangential component, which acts on the carrier of the displacement wing, so that they always remain in sealing contact with their chambers.
  • the adjustable link can be resilient, wedge-like or otherwise non-positive, but not positive.
  • the carrier having the displacer wings is always tilt-free in a certain position due to the mutual contact points of the wings arranged in a ring.
  • displacement machines with a wobble drive are known, for example from DE-C-2603462 and US-A-3560119.
  • similar displacement machines with a cross disc clutch are also known, for example from EP 10930 B1, US-A-4,437,820 and DE-A-2735664. All of these facilities are so-called displacement machines for compressible media. They consist, on the one hand, of a conveying space which is delimited by spiral-like circumferential walls which extend perpendicularly from a side wall and which leads from an inlet lying outside the spiral to an outlet lying inside the spiral. Secondly, they point you in the displacement space protruding, also spiral-like displacement body. This is mounted in relation to the conveying space to perform a circular, rotation-free movement.
  • the wobble drive is in each case the means for converting the rotating movement of the drive machine into the translatory movement of the displacer.
  • the drive solution in DE-C-2603462 provides an eccentric body which is seated in a rotationally fixed manner with a counterweight and on which a drive disk is mounted by means of a ball bearing.
  • This is equipped with four evenly distributed ball joint pans, in each of which sits the ball end of a wobble rod.
  • the balls only have line contact in their associated pan.
  • the drive-side pin of the wobble rod is rotatably and pivotably mounted in an eccentric position by means of a self-aligning ball bearing.
  • the second and third spherical sections are each with profile rings, for example Provide teeth, which in correspondingly profiled counterparts in the displacer or. intervene in the fixed housing part and are pivotally mounted therein.
  • the wobble shaft is axially secured via a lock washer located in the fixed housing part.
  • the cross-disk clutch forms the rotation-inhibiting means for the displacer. Its radial displacement is limited by the contact of the spiral ribs with the walls of the delivery chambers. The limit theoretically corresponds to a circle, in this case the translation circle.
  • the displacer which is free of rotation with respect to the delivery chamber, must now be guided by means of the cross disc coupling in such a way that the parallel guide allows a larger diameter than the diameter of the translation circle.
  • the reason for this is that the radial displacement of the displacer should be limited by the combination of rib / chamber wall and not by the leading cross-plate coupling. Using this rule, the dimensions for the cross plate coupling can be easily determined.
  • cross-type couplings of this type are unsuitable for the transmission of high torques and for high speeds because of the bending stress and the losses due to friction.
  • the strips consist of right-angled blocks that engage in appropriately configured grooves.
  • the concerns about the use of the cross disc clutch are understandable insofar as the lateral play in the grooves for the purpose of proper guidance is minimal have to be. However, this inevitably leads to friction surfaces that wear out. In addition, if dirt enters the guide, its parts can jam against each other, which impairs the functionality of the coupling.
  • the invention is therefore based on the object of designing a rotary piston positive displacement pump with very low pulsations in such a way that it remains free of play even with increasing material removal as a result of wear.
  • the advantage of the invention is that the new configuration creates a self-priming, low-pulsation, self-adjusting and almost maintenance-free pump during operation.
  • the wobble rod is seated at its crank-side end with a ball section in an articulated socket of the crank, if it is mounted at its other end with a ball section in a hemispherical socket of the fixed housing part, and if it is between its two ends has a spherical section which is rotatably and tumble mounted in a hemispherical socket in the displacer, spring medium ensure that the spherical sections fit snugly in the socket.
  • This type of drive contains very small friction paths and therefore friction losses.
  • the cross-plate coupling has a freely movable intermediate ring, which carries on its flat sides two convex strips at 90 ° to each other, which engage in correspondingly concave grooves of the parts to be coupled, the intermediate ring together with the strips being a one-piece, Prestressed workpiece made of spring steel.
  • this very inexpensive element also generates the contact pressure for the displacement body against the bottom of the delivery chamber.
  • the pump according to FIGS. 1 and 2 essentially consists of two housing halves 1, 2, which are connected to one another in a suitable manner, and the displacer lying therein, together with the drive and guide.
  • An annular delivery chamber 4 is incorporated into the left housing half 1. It has parallel circumferential walls which are at a constant distance from one another and which comprise an angular range of approximately 360 °, even if this is not evident in FIG. 2. It is subdivided by means of a web 5 which extends over the entire chamber depth.
  • the inlet 6 and the outlet 7 for the working medium to be conveyed are arranged on both sides of the web in the rear wall of the housing half 1.
  • the displacement body 8 engages in the delivery chamber 4 between the peripheral walls.
  • This displacement body which accordingly represents the ring piston, is a rib which is held perpendicularly on the rotor disk 8.
  • the displacer 8 is on that Point, which is opposite the web 5, slotted, ie interrupted in its entire depth.
  • the rotor 3 performs an orbital movement together with the displacer body 8, hereinafter simply referred to as the displacer.
  • the ring piston constantly touches both the inner and the outer peripheral wall of the delivery chamber. This results in crescent-shaped working spaces 27, 28 enclosing the working medium on both sides of the displacer body, which are displaced from the inlet 6 in the direction of the outlet 7 during the drive of the rotor through the delivery chamber.
  • a drive by means of a wobble rod 12 is provided for the orbital circulation of the displacer.
  • a crank mechanism 13, not shown, is equipped on the crank side with a joint socket 14 in which the wobble rod 12 is rotatably seated with a first ball section 15. It is understood that the invention is not limited to this drive variant.
  • the only decisive factor is a construction in which the wobble rod does not perform a rotary movement, but a wobble movement, the movement axis 30 being located on a conical jacket.
  • the wobble rod 12 has a second ball section 16. Coaxially with the main axis 31 of the crank mechanism 13, this second ball section is rotatably mounted in the left fixed housing part 1 and is capable of tumbling.
  • the wobble rod 12 is provided with a third ball section 17, the ball radius of which advantageously corresponds to that of the second ball section.
  • This third ball section is rotatably supported in the hub of rotor 3 and is capable of tumbling.
  • bearing points are therefore designed as hemispherical joint sockets 18, 19. Hemispherical because, on the one hand, this reduces the required individual parts to a minimum, and on the other hand, assembly is very easy.
  • FIG. 3 A first solution to this is shown in Fig. 3.
  • the second ball section 16 ' is provided with a central bore and loosely attached to the wobble rod 12', so that it is displaceable on the wobble rod.
  • the opposing surfaces of the ball sections 16 'and 17' are flattened and each form a stop for a compression spring 20 '. In the assembled state, this spring 20 'pushes the ball sections apart.
  • the socket 18 ' is provided in the left housing half 1 with a recess 21.
  • the solution shown in Fig. 4 is based on a sliding block 22 which is axially displaceable in the left housing part 1.
  • the joint socket 18 is incorporated in the sliding block.
  • the ball section 16 lies in this. So that the ball section at any time has a defined spherical support, the base of the pan is also provided with a recess 21 here, so that the head end of the spherical section has no ground contact in any case.
  • the axial force is applied here via the helical spring 20, which acts on the sliding block 22 from the housing part 1.
  • the angle of the movement axis 30 located on a conical surface also changes. This also applies to the distance between the ball sections 16 and. 17 and 15.
  • the eccentricity e (Fig. 4) must be maintained on the displacer.
  • the plane of the second spherical section is decisive for the translation circle and is therefore the reference plane. Therefore, the first ball section 15 must also be designed to be displaceable. Namely, it must be displaceable on the one hand in the longitudinal direction of the wobble rod, as is indicated in FIG. 4; secondly, it must also be displaceable in the direction perpendicular to the plane of the drawing because of the possible change in angle mentioned.
  • This first ball section 15 is therefore preferably also embedded in a bearing bushing equipped with a joint socket 14.
  • This joint socket 14, which is shown only schematically in FIGS. 3 and 4, is in turn provided with a sliding surface 26 which can be displaced on all sides on a corresponding counter surface of the crank mechanism 13.
  • the sliding surface 26 and counter surface are in a plane parallel to the axis of the 31 crank mechanism.
  • FIG. 5 An example of the drive of the wobble rod 12, 12 'is shown in Fig. 5.
  • the drive shaft 33 is provided with a collar 34 at its end facing the machine. This is recessed on the end face such that a driver offset 35 is formed below the main axis 31. This has the above-mentioned counter surface running parallel to the main axis for interaction with the sliding surface 26. This is the actual crank mechanism 13.
  • the bearing bush 32 with the embedded joint socket 14 for receiving the ball section 15 is dimensioned somewhat narrower in its axial extension than the driver offset. This allows the bush to be displaced in the axial direction via the sliding surface 26, as shown by arrows. The bushing can also be displaced perpendicular to the axial direction in the indicated arrow directions over the same sliding surface. Changes in the angle of the movement axis 30 can hereby be compensated for.
  • the size of the eccentricity E between the main axis 31 and the end point of the movement axis 30 is a function of the displacer eccentricity e and the translation ratio between the three bearing points of the wobble rod 12, 12 '.
  • a cross-plate coupling is provided for torsion-free guidance of the displacer. It consists essentially of an intermediate ring 9, which is provided on its plan sides with strips 10, 10 '.
  • the strips 10 facing the runner 3 can be displaced in relation to the displacer on a common vertical axis. They engage in appropriately configured, vertically running grooves 11 in the rotor 3.
  • the strips 10 ' which must be arranged perpendicular to the strips 10 - in the present case, therefore, horizontally and therefore not in the longitudinal section according to FIG. 1 shown - are facing the fixed right housing half 2 and can be moved in relation to this on a common horizontal axis. They slide in appropriately configured, horizontally machined grooves 11 'in the front of the housing half 2'.
  • FIG. 6 The principle can be seen in Fig. 6, in which the hubs of the components to be coupled are shown as simple rings. 1, the reference number 2 for the fixed housing part and the reference numbers 3 and 8 for the rotating rotor together with the annular displacement body 8.
  • FIG. 7 The actual geometry of the parts sliding on one another is shown in FIG. 7.
  • the convex friction surface 23 of the strip must of course match the concave curvature of the groove wall 24.
  • a circular shape with the radius R was chosen for both.
  • the right half of FIG. 7 shows a run-in clutch, where the groove wall extends over the entire available surface wearing.
  • the left half of Fig. 7 shows the clutch before retracting. Due to manufacturing inaccuracies or because of deliberately different radius selection of "ball and pan", the bar is not fully inserted. Nevertheless, it is already worn over a not inconsiderable section at the upper edge of the groove. It can also be seen that jamming is not possible due to irregular material removal. Finally, the coupling is absolutely free of play, regardless of the mutual position of the bar and groove.
  • the bottom of the groove 25 is set back in such a way that contact with the bottom of the groove is avoided even when the strip is completely in the groove.
  • the recessed groove base in any case avoids that in the event of deformation of the intermediate ring together with the strips, the load-bearing zone is located in the head of the strips, ie in the groove base. In this case, there could be a lateral play between the wall and the strips at the groove edges, as tests have shown.
  • the prevailing forces are, on the one hand, the contact pressure F S , which acts vertically according to FIG. 7, ie in the axial direction of the clutch. This force usually corresponds to a spring force; it is reasonably constant due to the minimal spring travel.
  • a horizontal force F t acts on the vertical strips 10, which is variable in size and direction. Both are dependent on the position and size of the frictional forces between the annular displacement body 8 and the walls of the delivery chamber 4.
  • the normal force acting on the bearing wall 24 of the grooves is the result of the two forces F S and F t . It can thus be seen that the load along the load-bearing zone is not uniform. If F t is greater than F S , the load in the upper segment of the groove is greater than in the lower. On the other hand, it can happen that when the force relationships are reversed, the mean vector of the reaction force slowly turns downwards. It is now important to avoid the force vector migrating into the bottom of the groove. The recessed groove bottom provides a remedy.
  • the intermediate ring and the strips are in one piece. It can be a deep-drawn workpiece, which has a very favorable effect on the manufacturing costs.
  • the one-piece workpiece consists of corrosion-resistant spring steel. As shown in Fig. 8, the intermediate ring is to be pretensioned so that a play-free contact in the grooves is guaranteed in all operating states. In addition, the element also exerts that axial force on the displacer 3 that is necessary for the sealing effect between the end faces of the displacer 8 and the delivery chamber 4 is maintained.
  • each work area must be separated from one another by at least one sealing line. Furthermore, each work area must currently have two sealing lines that are directly adjacent to the inlet and outlet if a seal over a full 360 ° is to be guaranteed.
  • the curves of the displacer body and the conveying space must form a common tangent at their respective points of contact, the tangents at the inner and outer points of contact having to run parallel to one another as a result of the same direction of movement.
  • the distance between the inner and outer tangents corresponds to a first dimension of the piston cross section.
  • the other dimension is given by the depth of the displacement ribs projecting into the delivery chamber; it is constant over the entire course of the production area. This means that for an absolutely uniform, ie pulsation-free conveyance, the tangent distance would have to be constant over the entire 360 °.
  • gap L This means that all the conditions are in place to determine the maximum dimension of the distance between the ends of the displacement body, hereinafter referred to as gap L. This situation is outlined in FIG. 9.
  • the hatched displacement body 8 is in its upper position, i.e. its ends touch the outer peripheral walls of the delivery chamber; the outer, crescent-shaped delivery chamber 28 is therefore closed with two sealing lines. It is not shown that the lower part of the body lies against the inner wall of the delivery chamber. Compared to the illustration in FIG. 2, in which the inner working space 27 is closed, the displacer body is thus rotated further by 180 °.
  • the dashed and dotted displacer body is located on the left stop, ie its right end has its minimum distance s from the web 5. When choosing this minimum distance s, care must be taken to ensure that the displacer should not abut web 5, even when material is removed due to continued operation.
  • R VI denotes the inner radius of the displacer 8. With this radius the body is formed on its predominant circumference.
  • B is the width of the delivery space, which is composed of the diameter of the translation circle, ie twice the eccentricity e and the thickness of the displacement body.
  • R UI is the inside radius of the delivery chamber.
  • R VIe and R UIe are the corresponding inner radii at the inlet (6) and outlet (7) ends of the elements. These radii of curvature are smaller, as is still to be done.
  • the maximum dimension of the stated distance is determined, i.e. the width of the gap L from the sum of the thickness C of the web 5 + twice the minimum dimension s + twice the eccentricity e.
  • the curve must not have any straight sections since the medium would be squeezed out in such a section.
  • the curve must not have any turning points, ie all centers of the sections of curvature to be strung together must lie within the resulting curve. Otherwise they would Do not move contact lines continuously, but they would skip sections.
  • R denotes a symbolic radius, which stands both for the displacement body and for the peripheral walls of the delivery chamber. It is the radius that is predominant in each case.
  • R e denotes the radius of curvature at the ends of the corresponding elements, which prevails over the wrap angle ⁇ .
  • T The distance between the tangents, the course of which on the occasion of a revolution of the displacement body is decisive for the pulsation of the medium being conveyed, is designated by T.
  • the gap L should have a width of 1 / 2R.
  • the width of the gap L is also important for another reason. Space must be created with a sufficiently large cross section for the arrangement of the inlet 6 and the outlet 7.
  • FIG. 9 Let us consider FIG. 9 again here.
  • both the inner and the outer peripheral wall of the delivery space are interrupted in the same plane with the hatched displacement body. This interruption forms the radial inlet 6 or outlet 7, depending on the direction of rotation of the displacer 8.
  • This arrangement therefore does not impair the desired sealing over the full 360 °, but shows that there is only a limited space available for the inlet and outlet.
  • the inflow of the medium can thus take place radially from above and from below. Even if the displacer has its minimum distance s in this case, there is no problem filling or filling the inner and outer working spaces 27, 28. to empty.
  • the inlet and outlet are each located in the fixed housing part. However, it can also happen that one of the two openings 6 or 7 is located in the displacer itself.
  • an appropriately designed recess must be provided on the face of the rotor in the inlet or outlet area. This too must have a width which is greater than the thickness of the displacement body, so that the outer and the inner working chamber communicate with one another.
  • the recess is arranged below the displacer rib, ie the rib has no contact with the end face of the rotor at this point.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (10)

1. Machine volumétrique pour des fluides incompressibles, avec une chambre de transport (4) du genre d'une fente de forme circulaire disposée dans une enceinte fixe (1, 2), et avec un corps de déplacement (8) également de forme circulaire associé à la chambre de transport, qui est fixé sur un rotor (3) en forme de disque actionnable excentriquement par rapport à l'enceinte de telle sorte que, pendant le fonctionnement, chacun de ses points décrit un mouvement circulaire limité par les flancs de la chambre de transport, et dont la courbure est dimensionnée, par rapport à celle de la chambre de transport, de telle sorte qu'il touche les flancs intérieurs et extérieurs de la chambre de transport en au moins une ligne d'étanchéité progressant de manière continue pendant le fonctionnement et subdivise ainsi la chambre de transport en des chambres de travail intérieure et extérieure (27, 28) à travers lesquelles le fluide est transporté depuis une entrée (6) jusqu'à une sortie (7), dans laquelle l'entrée et la sortie sont séparées l'une de l'autre par une ailette (5) disposée de préférence radialement dans la chambre de transport (4), le corps de déplacement (8) étant dès lors interrompu dans la région de l'ailette, et dans laquelle il est prévu un joint Oldham (9, 10) pour le guidage du rotor par rapport à l'enceinte et une tige oscillante (12, 12′) avec une commande à manivelle (13) pour l'entraînement circulaire du corps de déplacement, caractérisée en ce que
― dans la zone de l'ailette (5), les chambres de travail intérieure et extérieure (27, 28) communiquent l'une avec l'autre à l'entrée (6) et à la sortie (7),
― le corps de déplacement (8) et la chambre de transport (4) présentent une forme au moins à peu près circulaire dans la majeure partie de leur périmètre,
― le corps de déplacement (8) est étanche sur au moins 360°,
― et qu'à cet effet les extrémités du corps de déplacement et de la chambre de transport, du côté de l'entrée et de la sortie, présentent dans une zone angulaire (α) de 30° maximum des rayons de courbure nettement plus petits que ceux de la majeure partie de leur périmètre.
2. Machine volumétrique suivant la revendication 1, caractérisée en ce que l'entrée (6) et la sortie (7) sont disposées directement dans l'ailette (5) et débouchent radialement dans la chambre de transport (4) et en ce que le fond de la chambre de transport (4) est pourvu d'un évidement (29) au milieu du canal, dans la région de l'entrée (6) et de la sortie (7).
3. Machine volumétrique suivant la revendication 1, caractérisée en ce que l'entrée (6) et la sortie (7) sont disposées directement dans l'ailette (5) et débouchent radialement dans la chambre de transport (4) et en ce que la face frontale du rotor (3) est pourvue d'un évidement sous le corps de déplacement, dans la région de l'entrée (6) et de la sortie (7).
4. Machine volumétrique suivant la revendication 1, caractérisée en ce que la tige oscillante (12, 12′) repose par un premier tronçon à rotule (15) à son extrémité proche de la manivelle dans une cuvette d'articulation (14) de la manivelle, en ce qu'elle est supportée à son autre extrémité par un deuxième tronçon à rotule (16, 16′) dans une cuvette d'articulation hémisphérique (18, 18′) de la partie fixe (1) de l'enceinte, et en ce qu'elle présente entre ses deux extrémités un troisième tronçon à rotule (17, 17′) rotatif et oscillant qui repose dans une cuvette d'articulation hémisphérique (19) du corps de déplacement (3), des moyens formant ressort (20, 20′) veillant à assurer un joint à plat des tronçons à rotule dans les cuvettes d'articulation.
5. Machine volumétrique suivant la revendication 4, caractérisée en ce que le deuxième tronçon à rotule (16′) est engagé librement sur la tige oscillante (12′), et en ce qu'un ressort hélicoïdal (20′) est disposé entre le deuxième et le troisième tronçons à rotule (16′, respectivement 17′).
6. Machine volumétrique suivant la revendication 4, caractérisée en ce que la cuvette d'articulation (19) destinée à recevoir le troisième tronçon à rotule (17) est prévue dans un coulisseau (22) qui coulisse dans la partie fixe (1) de l'enceinte sous l'action d'un ressort (20).
7. Machine volumétrique suivant la revendication 4, caractérisée en ce que la cuvette d'articulation (14) destinée à recevoir le premier tronçon à rotule (15) est mobile dans un plan parallèle à l'axe de la manivelle.
8. Machine volumétrique suivant la revendication 1, caractérisée en ce que le joint Oldham présente une bague intermédiaire (9) librement mobile, qui porte sur ses deux faces plates des nervures galbées (10, 10′) convexes disposées à 90° l'une par rapport à l'autre, qui s'engagent dans des rainures correspondantes (11, 11′) des pièces à coupler, dans laquelle les nervures (10, 10′) sont ont une courbure convexe à leurs faces de frottement (23) et où les parois portantes (24) des rainures (11, 11′) ont une courbure concave pour accueillir les nervures, et en ce que le fond (25) des rainures est déporté pour assurer l'absence de contact avec la nervure (10, 10′).
9. Machine volumétrique suivant la revendication 8, caractérisée en ce que les surfaces de frottement des nervures et les surfaces portantes des rainures présentent une section transversale de forme circulaire.
10. Joint Oldham suivant la revendication 8, caractérisé en ce que la bague intermédiaire (9) forme avec les nervures (10, 10′) une pièce unique, précontrainte, en acier à ressort.
EP89810698A 1988-09-20 1989-09-14 Machine pour fluide non compressible Expired - Lifetime EP0362133B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH3493/88 1988-09-20
CH349388 1988-09-20

Publications (2)

Publication Number Publication Date
EP0362133A1 EP0362133A1 (fr) 1990-04-04
EP0362133B1 true EP0362133B1 (fr) 1991-11-27

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ID=4257184

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89810698A Expired - Lifetime EP0362133B1 (fr) 1988-09-20 1989-09-14 Machine pour fluide non compressible

Country Status (4)

Country Link
US (1) US5011386A (fr)
EP (1) EP0362133B1 (fr)
JP (1) JP2776911B2 (fr)
DE (1) DE58900498D1 (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2063888C (fr) * 1991-04-26 2001-08-07 Hubert Richardson Jr. Compresseur rotatif volumetrique orbital
JP2676174B2 (ja) * 1991-10-31 1997-11-12 旭精密工業株式会社 流体ポンプ
JP4732572B2 (ja) * 2000-10-02 2011-07-27 株式会社日立産機システム 給油ポンプ
WO2005103496A1 (fr) * 2004-04-23 2005-11-03 Daikin Industries, Ltd. Machine rotative à fluide
JP3778203B2 (ja) * 2004-05-11 2006-05-24 ダイキン工業株式会社 回転式圧縮機
JP3724495B1 (ja) * 2004-07-09 2005-12-07 ダイキン工業株式会社 回転式流体機械
US8137754B2 (en) * 2004-08-06 2012-03-20 Lubrizol Advanced Materials, Inc. Hydroxyl-terminated thiocarbonate containing compounds, polymers, and copolymers, and polyurethanes and urethane acrylics made therefrom
KR100590496B1 (ko) * 2004-12-14 2006-06-19 엘지전자 주식회사 선회베인 압축기의 용량 가변장치
KR100590494B1 (ko) * 2004-12-14 2006-06-19 엘지전자 주식회사 선회베인 압축기의 압축장치
JP5035570B2 (ja) * 2009-11-25 2012-09-26 株式会社リッチストーン スクロール流体機械
DE112013007633T5 (de) * 2013-11-25 2016-08-04 Halliburton Energy Services, Inc. Nutierender fluidmechanischer Energiewandler
CA2934615C (fr) 2014-01-30 2019-10-22 Halliburton Energy Services, Inc. Convertisseur d'energie mecanique fluide a nutation pour fournir de l'energie de forage de puits de forage
TWI726764B (zh) 2020-07-07 2021-05-01 楊進煌 迴轉式流體傳送裝置

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4606711A (en) * 1983-01-10 1986-08-19 Nippon Soken, Inc. Fluid pump with eccentrically driven C-shaped pumping member

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3125032A (en) * 1964-03-17 Rotary pump
US460711A (en) * 1891-10-06 Sliding gate
DE177654C (fr) *
FR467050A (fr) * 1914-01-06 1914-06-02 Claude Nicolas Bonnet Perfectionnements aux pompes à piston annulaire
US3195470A (en) * 1962-01-24 1965-07-20 Fluid Dynamics Corp Rotary pump
FR1481188A (fr) * 1966-04-05 1967-05-19 Commissariat Energie Atomique Machine étanche de transfert
GB1255799A (en) * 1967-12-18 1971-12-01 Krauss Maffei Ag Rotary positive fluid displacement apparatus
US3782865A (en) * 1971-03-05 1974-01-01 A Braun Sealing sleeve
CH586348A5 (fr) * 1975-02-07 1977-03-31 Aginfor Ag
US4121438A (en) * 1976-09-13 1978-10-24 Arthur D. Little, Inc. Coupling member for orbiting machinery
EP0010930B1 (fr) * 1978-10-30 1983-09-21 Sanden Corporation Compresseurs du type spiroidal
JPS578385A (en) * 1980-06-16 1982-01-16 Tokuji Kariya Ring swinging-type liquid ejection pump
CA1222986A (fr) * 1980-09-30 1987-06-16 Kiyoshi Terauchi Compresseur centrifuge
JPS59128991A (ja) * 1983-01-10 1984-07-25 Nippon Soken Inc リング型ポンプ
JPS6087385U (ja) * 1983-11-22 1985-06-15 三菱重工業株式会社 リング揺動型流体機械
JPS6090584U (ja) * 1983-11-29 1985-06-21 三菱重工業株式会社 リング揺動型流体機械
EP0214164B1 (fr) * 1985-02-27 1990-05-23 Gutag Innovations Ag Machine a deplacement positif, notamment pompe

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4606711A (en) * 1983-01-10 1986-08-19 Nippon Soken, Inc. Fluid pump with eccentrically driven C-shaped pumping member

Also Published As

Publication number Publication date
JPH02191883A (ja) 1990-07-27
EP0362133A1 (fr) 1990-04-04
JP2776911B2 (ja) 1998-07-16
DE58900498D1 (de) 1992-01-09
US5011386A (en) 1991-04-30

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