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EP0225834B1 - Rotierende Trommelkolbenpumpe mit festem zentralscharnierpunkt - Google Patents

Rotierende Trommelkolbenpumpe mit festem zentralscharnierpunkt Download PDF

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Publication number
EP0225834B1
EP0225834B1 EP86420172A EP86420172A EP0225834B1 EP 0225834 B1 EP0225834 B1 EP 0225834B1 EP 86420172 A EP86420172 A EP 86420172A EP 86420172 A EP86420172 A EP 86420172A EP 0225834 B1 EP0225834 B1 EP 0225834B1
Authority
EP
European Patent Office
Prior art keywords
barrel
rotary machine
machine according
housing
shaft
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
Application number
EP86420172A
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English (en)
French (fr)
Other versions
EP0225834A1 (de
Inventor
Michel Drevet
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0225834A1 publication Critical patent/EP0225834A1/de
Application granted granted Critical
Publication of EP0225834B1 publication Critical patent/EP0225834B1/de
Expired legal-status Critical Current

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Classifications

    • 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
    • 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
    • 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
    • F04B1/26—Control
    • F04B1/28—Control of machines or pumps with stationary cylinders
    • F04B1/29—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B1/295—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash 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
    • Y10T74/16—Alternating-motion driven device with means during operation to adjust stroke
    • Y10T74/1625—Stroke adjustable to zero and/or reversible in phasing
    • Y10T74/1683—Cam and follower drive
    • Y10T74/1692—Axial-type cam [e.g., wabbler type]
    • 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 machine of the barrel type, more particularly intended for delivering high-pressure fluids, and in particular charged liquids.
  • pumps of this type are commonly used in the mining industry or in the petroleum industry, for pumping loaded liquids, such as petroleum, liquid sludge, fracturing fluids or the like. Pumps of this type are commonly of large dimensions and designed to discharge the liquid with a high flow rate, under high pressures, commonly greater than 200 bars.
  • FR A 2 572 774 published on 9.5.1986, made known an embodiment avoiding certain drawbacks, by making a rotary machine with barrel and rotary inclined plate, the linkage of which makes it possible to increase the discharge pressure of the liquid, while reducing the overall weight of the device.
  • a barrel pump comprising a fixed barrel in the cylindrical bores from which slide delivery pistons, each of which is connected by a connecting rod to an inclined plate with a rotary swiveling movement, the rear face of which is fitted with a central journal.
  • a drive oriented along an axis perpendicular to the front thrust face of the plate and comprises, at its center, a spherical bearing whose circular meridian section corresponds to an angle at the center greater than 180 ° while inside this spherical bearing is arranged a fixed spherical ball joint secured to an arm axially anchored in the center of the barrel, so that the thrust of the plate during operation is transmitted directly to the barrel via the spherical bearing working at tearing, and this without involving the resistance of the walls of the casing, in particular in its rear part.
  • FR-A 2 211 090 has made known a barrel mechanism comprising, inside a casing, a motor shaft driven in rotation about its axis, journalling in two bearings supported respectively by two perpendicular casing bottoms to the axis, and on which is fixed an oblique plate with respect to the axis, a barrel resting on the oblique plate and centered, around an axis intersecting the journal axis, on a cylindrical inclined bearing provided on the shaft, perpendicular to the plate, and a means for blocking the rotation of the barrel, characterized in that the two bases of the casing are connected by a tie rod extending along the axis of the journal, in an axial bore of the motor shaft.
  • the new arrangement according to the invention eliminates the cantilevered position of the central ball joint, which prevents the rupture of the support shaft of this ball joint, a rupture which can be caused by the influence of fatigue due to high rotating loads. .
  • 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 integral with a first half-shaft anchored directly in the central part of the barrel, while the latter is connected to a rigid peripheral casing which covers the rear of the crankshaft behind which it closes, is characterized in that the central ball joint is also integral with a second rigid half-shaft situated opposite the first with which it is aligned on the axis, this second half-shaft being, by its opposite end , rigidly anchored on the rear part of the machine housing.
  • the invention applies in particular to compressors, pumps or hydraulic motors with axial pistons for charged fluids.
  • the casing 30 of the pump is divided into two parts provided one with a flange 58, the other 59 with a counter flange 60 to connect them to each other, these two flanges being circular and centered on the axis 7 of the machine, which makes it possible to shift their relative angular positioning by notches. We can thus choose at will the angular position of the drive shaft around the geometric axis 7 of the machine.
  • a rotary machine for example a pump, comprising a fixed barrel 61, in which are arranged bores 62 parallel to each other, and distributed around the geometric axis 7 of the assembly.
  • a piston 64 slides, the rod 65 of which bears, by a pad 66, on an oscillating inclined plate 67.
  • This plate carries, in its center, a spherical bearing 68, 69 and is engaged around the sphere a fixed ball joint 70.
  • the fixed ball 70 is integral with a first half-shaft 71 and a second half-shaft 72 between which it is located.
  • the two half-shafts 71 and 72 are aligned with each other, on either side of the ball joint 70, both centered on the longitudinal axis 7 of the machine.
  • the two half-shafts 71 and 72 can sometimes form only one rigid, one-piece shaft.
  • the first half-shaft 71 is embedded in the central part of the barrel 61.
  • the second half-shaft 72 is integral with the rear part 59 of the fixed casing 30 of the machine.
  • the second half-shaft 72 is extended towards the rear, by a threaded rod 74, which freely passes through a central orifice 76 of the rear cover 75.
  • a nut 77 screwed onto the threaded rod 74 outside the cover 75 used to fix the second half-shaft 72 in order to stiffen the casing 30.
  • first half-shaft 71 there is provided on the first half-shaft 71, near the ball joint 70, a shoulder 78 which bears on the inner face of the barrel 61 while at the front of this same barrel, the half-shaft 71 is extended by a threaded rod 79, on which one can more or less screw a nut 80.
  • a threaded rod 79 on which one can more or less screw a nut 80.
  • the periphery of this nut bearing on the front face of the barrel 61 it is understood that by acting on the nut 80, one can resume on the front face of the barrel the tensile forces to which the first half-shaft 71 will also be subjected.
  • the central part of the half-shaft 71 is arranged in a central bore 81 of the barrel 61, where it can freely slide in the longitudinal direction.
  • the thrust front face of the plate 67 is perpendicular to a geometric axis 82 which forms with the geometric axis 7, an acute angle 83. These two geometric axes 7 and 82 converge towards the center 90 of the spherical ball joint 70.
  • the plate 67 rotates around the geometric axis 82 and, for this, its rear face is supported by a tapered roller stop 84 on a motion transmitter 85. The latter in turn is supported by a roller stop 86 on the rear cover 75 of the casing 30.
  • This rear cover 75 of the casing 30 is screwed onto the casing 30 with the interposition of a block of annular thickness 87, the thickness of which 88 can be chosen at will, as a function of the desired preloads.
  • the movement transmitter 85 is traversed, in its central part, by a longitudinal bore 89, inside which the second half-shaft 72 can freely move.
  • the movement transmitter 85 On its periphery, the movement transmitter 85 is equipped with a toothed pinion 90, centered on the geometric axis 7.
  • This pinion 90 meshes with a control pinion 91, of smaller diameter, which is located laterally in the casing 30 , secured to a rotating output shaft 92, arranged outside.
  • the geometric axis 93 of this output shaft 92 is parallel to the geometric axis 7.
  • a balancing weight 94 is fixed to the pinion 90 by screws 95.
  • a lateral link 96 is articulated by one of its ends 97 (fig. 1) in a bearing 98, integral with the plate 67 which is thus immobilized in rotation.
  • the linkage thus represented, and in particular the structure of the motion transmitter 85 have the advantage of allowing the axial thrust of the roller thrust bearings 84 and 86, thanks to the shim 87 which is compressed by the rear cover 75, itself fixed to the bottom of the casing 30, by screws 99 and by the nut 77.
  • the thickness 88 of the shim 87 is carefully studied, with a view to applying a preload on the stops 84 and 86 which will be collected by the part of the half-bearings 68 and 69 situated to the left of the theoretical transverse diametral plane 100 defined by the spherical ball joint 70.
  • This preload will therefore relieve the other part of the half-bearings 68 and 69, which is located to the right of the theoretical plane 100 and receives thrust forces exerted by the pistons 64.
  • everything is guaranteed around the spherical cap of the half-bearings 68 and 69 a good distribution of the specific pressures which appear during the operation of the machine.
  • a judicious choice will be for example to calculate the thickness 88 of the wedge 87 so that the stresses to the right and to the left of the transverse plane 100 induce equal pressures on the spherical cap of the central bearing 68, 69. If this condition is fulfilled we say that the machine has in its center a "floating stop" since at this position to balance the spherical stop (bearing 68, 69 on the ball 70) is under zero axial load.
  • the axial compression preload of the stops 84, 86 is carried out, no longer via the shim 87 and the cap 75 (fig. 1) but using a retaining cap 101, which comes fix on the casing 30 by the screws 99 but inside which an annular hydraulic piston 102 can slide.
  • the latter is provided with two annular seals, namely a sliding interior seal 103 and an exterior seal 104, also sliding .
  • the engine space 105 which remains located between the annular piston 102 and the bottom of the cap 101 receives, via a supply opening 106, a hydraulic fluid under pressure shown diagrammatically by the arrow 107.
  • the assembly is calculated so that the minimum stroke of the jack 102, 105 corresponds to a minimum permanent mechanical tightening point on the ball of the stop 86.
  • the motion transmitter 85 of FIG. 1 is produced in the form of two half-transmitters 108 and 109, each with a corner profile.
  • the plane bearing face 110 along which they are in contact with each other is perpendicular to a theoretical axis 111 passing through the geometric center 112 of the ball 70, this axis 111 forming with the axis geometric 7, an angle 113 equal to half the angle 23, and which corresponds to the axis 22.
  • Screws 114 regularly distributed in a circle around the axis 111, make it possible to assemble the two half-transmitters 108 and 109.
  • a continuous control device is used, with external control of the position of the two half-movement transmitters 108 and 109.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Rotational Drive Of Disk (AREA)
  • Soil Working Implements (AREA)

Claims (10)

1. Rotierende Trommelkolbenpumpe mit einem feststehenden Kalottenlager und mit einer Trommel (61) und einer Scheibe (67), die relativ zu der mit der geometrischen Trommelachse zusammenfallenden geometrischen Drehachse (7) geneigt ist, wobei ferner der zentrale Teil der geneigten Scheibe (67) ein Pendellager (68, 69) aufweist und sich um einen mit einer wellenförmigen Stütze (71), die direkt in dem zentralen Teil der Trommel (61) verankert ist, verbundenen Kalottenlager (70) frei dreht, während die Trommel (61) mit einem steifen, peripherischen Gehäuse (30) verbunden ist, das den Stangensatz überdeckt und umschließt, dadurch gekennzeichnet, daß das Kalottenlager (70) ausserdem mit einem zweiten, starren, der Stütze (71) gegenüber angeordneten Achsstück (72) verbunden ist, dessen Achse mit der Drehachse (7) fluchtet, wobei dieses zweite Achsstück (72) mit seinem zweiten, anderen Ende an einem rückwärtigen Teil (75) an dem Gehäuse (30) der Maschine starr befestigt ist.
2. Trommelkolbenpumpe nach Anspruch 1, dadurch gekennzeichnet, daß Mittel zum Vorspannen (87, 99, 102) für das Pendellager (68, 69) zwischen dem rückwärtigen Teil (75) des Gehäuses (30) und Rollenlagern (86, 84) angeordnet sind, die sich auf einem Antriebs- und Lagerelement (85) abstützen.
3. Trommelkolbenpumpe nach einem der Ansprüche 1 und 2, dadurch gekennzeichnet, daß die Stütze (71) und das Achsstück (72) jeweils mit Muttern (80 u. 77) zum Auffangen von Zugkräften auf der vorderen Fläche der Trommel (61) versehen sind und dadurch zur einwandfreien Starrheit des Gehäuses (30) während des Betriebes beitragen.
4. Trommelkolbenpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Mittel zum Vorbelasten des Pendellagers durch Verwendung einer Beilegscheibe (87), deren Stärke (88) entsprechend gewählt ist, zwischen einem abnehmbaren Deckel (75) und der hinteren Fläche des Gehäuses (30) gegeben sind, um auf das Rollenlager (86) eine vorbestimmte Druckkraft auszuüben.
5. Trommelkolbenpumpe nach einem der Ansprüche 1-3, dadurch gekennzeichnet, daß die Mittel zum Vorbelasten des Pendellagers durch Zwischenlegen eines koaxialen, ringförmigen, hydraulischen Zylinders (102, 105) zwischen dem festen Boden am Ende des Gehäuses (30) und das Rollenlager (86), auf dem sich die hintere, geneigte Scheibe (67) abstützt, gegeben sind.
6. Trommelkolbenpumpe nach Anspruch 5, dadurch gekennzeichnet, daß die Versorgung des zum Vorspannen dienenden Zylinders (102, 105) mit Druckflüssigkeit über einen Kanal (106) erfolgt, der mit Druck aus einem Teil der Maschine beaufschlagt ist, wobei dies eine Pumpe bzw. ein Kompressor ist.
7. Trommelkolbenpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß sich die geneigte Scheibe (67) auf einem Antriebselement (85) abstützt, das aus zwei aneinander anliegenden, zusammengefügten Übertragungshälften (108, 109) besteht, die jede für sich ein Eckprofil aufweist, wobei ferner entsprechende Mittel (114) zur lösbaren Befestigung der zwei Übertra- .gungshälften (108, 109) vorgesehen sind und wobei deren relative Winkelorientierung je nach dem für die Kolben (64) der Trommelmaschine gewünschten Weg gewählt sind und wobei die Einstellung zwischen einem maximalen Weg (Abbildung 2) und einem Nullweg (Abbildung 3) liegen kann.
8. Trommelkolbenpumpe nach einem der vorgenannten Ansprüche, dadurch gekennzeichnet, daß der Träger für die Kalotte bzw. die Stütze (71) eine Längsbohrung (81) der Trommel (61) frei durchgreift und sich auf deren vorderen Fläche über einen Bund (78) abstützt, wobei ihr vorderes Ende als Gewindestange (79) ausgebildet ist, auf die eine Mutter (80) zum Abstützen auf der vorderen Fläche der Trommel (61) sowie zur Einstellung der Zugbelastung der Stütze (71) aufschraubbar ist.
9. Trommelkolbenpumpe gemäß einem der vorgenannten Ansprüche, dadurch gekennzeichnet, daß die Stütze (71) und das Achsstück (72) getrennt hergestellt und dann zusammengefügt sind.
10. Trommelkolbenpumpe gemäß einem der Ansprüche 1-8, dadurch gekennzeichnet, daß die Stütze (71) und das Achsstück (72) aus einem Stück hergestellt sind.
EP86420172A 1985-10-14 1986-06-26 Rotierende Trommelkolbenpumpe mit festem zentralscharnierpunkt Expired EP0225834B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8515604A FR2588617B1 (fr) 1985-10-14 1985-10-14 Machine rotative a pistons et a barillet avec rotule de centrage fixe.
FR8515604 1985-10-14

Publications (2)

Publication Number Publication Date
EP0225834A1 EP0225834A1 (de) 1987-06-16
EP0225834B1 true EP0225834B1 (de) 1989-09-27

Family

ID=9324045

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86420172A Expired EP0225834B1 (de) 1985-10-14 1986-06-26 Rotierende Trommelkolbenpumpe mit festem zentralscharnierpunkt

Country Status (8)

Country Link
US (1) US4815327A (de)
EP (1) EP0225834B1 (de)
CA (1) CA1307163C (de)
DE (1) DE3665905D1 (de)
DK (1) DK165063C (de)
FR (1) FR2588617B1 (de)
NO (1) NO165508C (de)
SU (1) SU1514246A3 (de)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2619166B2 (fr) * 1985-10-14 1990-02-02 Drevet Michel Machine rotative a pistons et a barillet avec rotule de centrage fixe
DE3861077D1 (de) * 1987-08-06 1990-12-20 Michel Drevet Rotierende trommelkolbenmaschine mit festem, zentrierendem kebelgelenk.
US4885980A (en) * 1988-03-10 1989-12-12 Stirling Thermal Motors, Inc. Hydrodynamic bearing
US4994004A (en) * 1988-11-30 1991-02-19 Stirling Thermal Motors, Inc. Electric actuator for swashplate
US5114261A (en) * 1989-07-31 1992-05-19 Honda Giken Kogyo Kabushiki Kaisha Swashplate type hydraulic device having a ball joint connection
ZA935640B (en) * 1992-08-06 1995-08-08 Hydrowatt Syst Axial piston machine, in particular axial piston pump or axial piston motor
US5493862A (en) * 1994-11-03 1996-02-27 Martin Marietta Corporation Continuously variable hydrostatic transmission
US5535589A (en) * 1995-01-30 1996-07-16 Martin Marietta Corporation Ratio controller for continuously variable hydrostatic transmission
JP4035193B2 (ja) * 1997-02-26 2008-01-16 株式会社日立製作所 アキシャルピストン機械
US6109034A (en) * 1997-04-25 2000-08-29 General Dynamics Land Systems, Inc. Continuously variable hydrostatic transmission ratio controller capable of generating amplified stroking forces
EP0991849A1 (de) 1997-05-14 2000-04-12 Ahto Anttila Axialkolbenmaschine
FR2935735B1 (fr) * 2008-09-08 2010-09-10 Michel Drevet Machine rotative a pistons et barillet
MD309Y (ro) * 2010-02-23 2010-12-31 Артур НИКИШОВ Maşină cu piston axial

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FR2572774B1 (fr) * 1984-11-06 1989-05-19 Drevet Michel Pompe a pistons a barillet, notamment pour des fluides a haute pression

Also Published As

Publication number Publication date
FR2588617A1 (fr) 1987-04-17
SU1514246A3 (ru) 1989-10-07
DE3665905D1 (en) 1989-11-02
FR2588617B1 (fr) 1989-11-24
NO864069L (no) 1987-04-15
NO165508B (no) 1990-11-12
DK486286D0 (da) 1986-10-10
DK165063B (da) 1992-10-05
CA1307163C (fr) 1992-09-08
NO864069D0 (no) 1986-10-13
NO165508C (no) 1991-02-20
DK165063C (da) 1993-02-15
DK486286A (da) 1987-04-15
EP0225834A1 (de) 1987-06-16
US4815327A (en) 1989-03-28

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