EP0294399B1 - Pompe a tiroirs oscillants - Google Patents

Pompe a tiroirs oscillants Download PDF

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Publication number
EP0294399B1
EP0294399B1 EP87906386A EP87906386A EP0294399B1 EP 0294399 B1 EP0294399 B1 EP 0294399B1 EP 87906386 A EP87906386 A EP 87906386A EP 87906386 A EP87906386 A EP 87906386A EP 0294399 B1 EP0294399 B1 EP 0294399B1
Authority
EP
European Patent Office
Prior art keywords
rotor
swivelling
vane
pump
cage
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
EP87906386A
Other languages
German (de)
English (en)
Other versions
EP0294399A1 (fr
Inventor
Gerhard Winiger
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.)
NOTRON Engineering AG
Original Assignee
NOTRON Engineering AG
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 NOTRON Engineering AG filed Critical NOTRON Engineering AG
Priority to AT87906386T priority Critical patent/ATE59438T1/de
Publication of EP0294399A1 publication Critical patent/EP0294399A1/fr
Application granted granted Critical
Publication of EP0294399B1 publication Critical patent/EP0294399B1/fr
Anticipated expiration legal-status Critical
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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • 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
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/32—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members
    • F04C2/332—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member
    • F04C2/336—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member and hinged to the inner member

Definitions

  • the invention relates to a rotary vane pump for conveying liquid or gaseous media according to the preamble of the first claim.
  • a large number of different pumps for liquid or gaseous media are known, which require the broad field of application.
  • Positive displacement pumps are used for tasks that require an almost constant flow rate that is almost independent of back pressure.
  • a volume part of the pumped medium enclosed in the pump chamber is transported from the inlet to the outlet by means of pistons, slides, membranes or by shaping the parts.
  • the delivery area must not be reduced compared to the inlet after it has been shut off; for compressible media (e.g. gases) this may be desirable to increase the pressure.
  • a pump known only from the literature according to the German patent DE-C-942314 has the following structure.
  • the inner cylinder jacket of a cylinder revolving in a housing has semi-cylindrical bearings for receiving wings with two arms.
  • a loosely rotating rotary piston rotates on a bolt that is eccentric to the cylinder, in which the second arms of the wings engage by means of sliding jaws that have recesses.
  • the double-armed design of the wings has the disadvantage that the number of sealing edges doubles. In addition, they make it impossible to completely empty the work area, so that the suction capacity of the pump is reduced.
  • the rectangular design of the wings engaging in the sliding jaws means that the sliding jaws must each consist of two parts, which therefore jam during operation.
  • Another pump known only from the patent literature according to British patent GB-A-109186 provides for a rotatable driver provided with side plates to be arranged between the housing and the rotor. Wings are articulated to the rotatable driver, which act in the rotor through articulated, slotted tips.
  • the synchronous rotation of the rotor with the rotatable drivers and the side plates is brought about by the pins arranged on the plates and engaging in bores in the rotor.
  • the rotatable driver is connected by one of the plates and rotates with it, so that the rotor rotates about an eccentrically arranged bearing which can be adapted to the shaft by rotation.
  • Such a pump in turn has the disadvantage of a double number of sealing edges, resulting from the articulation in the driver, which in turn has to be sealed off from the housing. It is also unfavorable that this articulation of the wings is exposed to the medium and thus exposed to wear.
  • the proposed rotation of the rotor by means of pins engaging in the provided bores leads to high friction and wear of the touching parts.
  • the slotted tips are also only possible in two parts, which also causes jamming.
  • the radial adjustment of the rotor bearing inevitably changes the control times, so that continuous flow control is impossible. Its construction is complicated, prone to failure and difficult to assemble.
  • the invention seeks to remedy this.
  • the invention as characterized in the claims, solves the problem of making available a low-wear, structurally simple, universally usable pump for a wide pressure range with particularly quiet running and variable flow rate at constant speed.
  • the particularly simple construction of the invention provides for one-armed slides rotatably mounted on rotor cage bolts, which seal directly on the housing. This eliminates the sealing edges in the driver, which has a positive effect on internal leakage and wear.
  • the slide sensor are formed in one piece to prevent jamming. This is achieved according to the invention in such a way that the slide guided by the driver has a rectangular crenellated edge which engages in the corresponding recess of the driver, which earlier similar pump designers apparently had not recognized and therefore this type of slide guide could not be implemented in practice.
  • the radial, stepless adjustment of the rotor core is solved by sitting on a hollow secondary shaft which is mounted on one side and outside of the pump chamber and is designed to be continuously and radially displaceable is.
  • the drive shaft is located inside this secondary shaft, at a sufficient distance for the radial displacement thereof.
  • the drive shaft is connected to the rotor cage on one side and thus drives the rotor core, which is firmly connected to the secondary shaft, via the rotor cage bolts and the slide.
  • the pump is now also suitable for pumping non-lubricating media, which may also have abrasive additives, without bearing wear occurring at higher pressures.
  • the proposed solution of the infinitely variable delivery rate control via the radial displacement of the secondary shaft has the decisive advantage that the eccentricity can be varied with a simple construction practically independent of the pressure in the pump.
  • a particularly expedient embodiment of the invention provides for the cage bolts to be dimensioned such that the compressive force acts centrally on the cage bolt in the area of the maximum eccentricity of the rotor core and thus the sliding friction in the slide sensor is minimized. It is also provided that, depending on the intended use and size, between three and twelve slides are evenly distributed between the rotor core and cage; but preferably five to nine slides if high pressures are to be achieved (space reasons due to the massive design of the bolts, slides and transducers).
  • the aspirator. Pressure channels should preferably be designed to extend radially in the housing over almost the entire width of the valve, whereby the most tangential feed and discharge must be ensured so that favorable inflow and outflow conditions prevail.
  • the proposed invention is characterized in that the design enables a speed-independent, infinitely variable flow rate change with high forces and that the design of the pivoting slide results in minimal wear due to sliding friction and that the cleaning of the pump or the replacement of wearing parts can be carried out quickly and easily .
  • the pump is therefore simple, veil-sided and low-wear.
  • FIGS. 1 to 6 of the swivel vane pump according to the invention stands on a rectangular base plate 1, which serves as additional stiffening against rotation.
  • the front 2 and rear 3 supports are on this.
  • the horizontally displaceable slide rings 5, 6 and the intermediate bearing carrier 4 are inserted in a form-fitting manner.
  • the pump housing 19 is fixed on the front side of the carrier 2 by means of screws.
  • the pump housing 19 is closed with the bearing cover 18, which contains the slide bearing 26 of the primary shaft 12.
  • the bearing flange 10 is screwed, which contains the rear bearing by means of plain bearings 26 of the primary shaft 12 and thus represents part of the rear wall.
  • a pump channel e with inlet a, the sealing area f and the outlet b with outlet space g are formed in the pump housing 19.
  • a hollow cylindrical rotor 13 runs in it, which has axial bores which are offset at equal intervals on the circumference and which break through the outer cylinder jacket. These holes contain the one-piece Slider sensor 16, which in turn receive the one-armed slider 15.
  • the one-armed slides 15 are rotatably supported at the upper end on cage bolts 14 and, with their round upper side, seal the rotor cage h against the pump housing 19 with a minimal gap in the sealing area f.
  • the rotor cage h consisting of the rotor wall 17 and the circumferentially equally spaced five cage bolts 14 fixed on one side, sits on the primary shaft 12 and is driven by it.
  • This secondary shaft 7 can now be shifted in the horizontal plane, so that the eccentricity of the rotor 13, which is seated on this shaft, can be varied.
  • the adjustment mechanism which consists of four support bolts with support pieces 31 pushed over them, the holder 32, the adjustment shaft 33 and the adjustment wheel 34.
  • the bearing bracket 4 is now displaced in the horizontal plane, together with the sliding rings 5, 6 which are positively attached on both sides.
  • This, displaceably guided secondary shaft bearing 4, 5, 6, 8, 9 arranged between the carriers 2, 3 is set with six clamping screws 25 in play.
  • the seal to the rotor 13 is provided by a mechanical seal 23 mounted on the secondary shaft 7, which comes to rest in a sufficiently large bore for the horizontal displacement in the carrier 2.
  • the bearing 9 is sealed by the shaft sealing ring 28, the rear of the pump with the shaft sealing ring 24.
  • the intermediate ring 20 and the guide pin 22 serve to axially guide the primary shaft 12.
  • the cover 21 seals the pump from the outside.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Jet Pumps And Other Pumps (AREA)
  • Check Valves (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (9)

1. Pompe à tiroirs oscillants avec carter (19), entrée (a), sortie (b), canal de la pompe avec chambre d'aspiration (e), zone étanche (f) et chambre de refoulement (g) et un rotor radialement déplaçable à cavités équipées de porte-coulisse caractérisés par le fait que le rotor (13) prend appui sur une axe secondaire creux radialement déplaçable (7) entourant l'axe primaire (12) et logé dans une cage à rotor (h) avec des chevilles de cage rigides (14) servant de supports immobiles transversant les coulisses ajourées (15), et par le fait que les coulisses (15) ainsi montées de manière à pourvoir pivoter s'engagent dans les porte-coulisse monobloc équipés d'ouverture de telles manière que ces porte-coulisse (16) puissent effectuer un mouvement de balancement limité par les arêtes des orifices du rotor et ainsi, pendant la rotation de la cage du rotor (h) ou du rotor (13), compenser l'excentricité variable de l'axe (d) grâce à un mouvement de balancement et de coulisse et assurer ainsi l'étanchéité du carter de la pompe (19) dans la zone d'étanchéité (f), les paliers (8, 9) de l'axe secondaire (7) se trouvant en-dehors de l'espace de la pompe, protégés du médium pompe (23).
2. Pompe à tiroirs oscillants selon la revendication 1, caractérisée par le fait que le flux pompé sortant de l'axe primaire (12) circule vers le carter du rotor (h) en passant par le tiroir (15).
3. Pompe à tiroirs oscillants selon la revendication 1, caractérisée par le fait que la disposition et le positionnement concentriques périphériques des chevilles de cage (14) dans la paroi postérieure du rotor (35) et/ou la paroi du rotor (17) soit choisi de telle manière que la zone étanche (f) n'exerce qu'un couple minimum sur les tiroirs en position extérieure (15).
4. Pompe à tiroirs oscillants correspondant à la revendication 1, caractérisée par le fait que les tiroirs sont dotés d'un crénelage rectangulaire (15) pénétrant dans le porte-tiroir usiné de manière complémentaire (16) selon le principe de la serrure et de la clé, de manière que les porte-tiroir (16) ne soient que d'une pièce.
5. Pompe à tiroirs oscillants selon la revendication 1, caractérisée par le fait que le support (4) des paliers de l'axe secondaire (7) entre les deux supports (2, 3) peut être déplacé de manière continue de manière radiale et dans le plan horizontal au moyen des anneaux de glissement (5, 6) et du mécanisme d'ajustage (30, 31, 32, 33, 34), ce qui permet de modifier directement l'excentricité du rotor (d).
6. Pompe à tiroirs oscillants selon la revendication 1, caractérisée par le fait que, de par sa construction, il est possible de disposer deux ou plusieurs éléments de pompe (13, 17', 41', 15', 16', 35) sur un même axe, selon une symétrie d'image miroir, séparés par des paliers (8) et des parois (2, 3) de séparation intermédiaires.
7. Pompe à tiroirs oscillants selon la revendication 1, caractérisée par le fait que les chevilles de cage (14) de la cage du rotor (h) ne sont fixées que d'un côté de telle manière que le changement des tiroirs (15) ne nécessite que la dépose du couvercle de palier (18) et de la paroi du rotor (17).
8. Pompe à tiroirs oscillants selon la revendication 1, caractérisée par le fait que l'axe primaire entraîné (12) tourne à l'intérieur d'un axe secondaire creux (7) présentant une excentricité au moins égale à la distance d'excentricité maximale (d) et monté (7) de manière à pouvoir pivoter (8, 9) sur le support de palier (4) extérieur au carter de la pompe (19).
9. Pompe à tiroirs oscillants selon la revendication 1, caractérisée par le fait que l'élément de pompe compact composé de l'agrégat (13, 17', 41, 15', 16', 35) puisse être retiré axialement après la dépose du couvercle du palier (18'), le desserrage de la vis de serrage (39) et le retrait de la douille de serrage (38) des axes primaire (12) et secondaire (7).
EP87906386A 1986-10-27 1987-10-13 Pompe a tiroirs oscillants Expired - Lifetime EP0294399B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87906386T ATE59438T1 (de) 1986-10-27 1987-10-13 Schwenkschieberpumpe.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH4252/86 1986-10-27
CH4252/86A CH673509A5 (fr) 1986-10-27 1986-10-27

Publications (2)

Publication Number Publication Date
EP0294399A1 EP0294399A1 (fr) 1988-12-14
EP0294399B1 true EP0294399B1 (fr) 1990-12-27

Family

ID=4272646

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87906386A Expired - Lifetime EP0294399B1 (fr) 1986-10-27 1987-10-13 Pompe a tiroirs oscillants

Country Status (8)

Country Link
US (1) US4958992A (fr)
EP (1) EP0294399B1 (fr)
JP (1) JP2587665B2 (fr)
AT (1) ATE59438T1 (fr)
CH (1) CH673509A5 (fr)
DE (1) DE3767154D1 (fr)
RU (1) RU1809864C (fr)
WO (1) WO1988003229A2 (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5235821A (en) * 1992-12-31 1993-08-17 Micropump Corporation Method and apparatus for refrigerant recovery
AU683012B2 (en) * 1993-03-01 1997-10-30 Japan I.D. Tech. Inc. Forced compression type pump
EP0695870B1 (fr) * 1993-03-01 1999-12-15 Japan I.D. Tech. Inc. Pompe du type compresseur renforcee
AU1018899A (en) 1997-11-19 1999-06-15 Notron Engineering A.G. Swivelling vane pump
US6203302B1 (en) * 1998-10-15 2001-03-20 Hypro Corporation Rubber impeller pump
US7128540B2 (en) * 2001-09-27 2006-10-31 Sanyo Electric Co., Ltd. Refrigeration system having a rotary compressor
ITRM20040623A1 (it) * 2004-12-20 2005-03-20 Marzia Murri Camera mobile.
US8177536B2 (en) * 2007-09-26 2012-05-15 Kemp Gregory T Rotary compressor having gate axially movable with respect to rotor
US7955063B2 (en) * 2008-05-19 2011-06-07 Stackpole Limited Vane pump
US8177483B2 (en) * 2009-05-22 2012-05-15 General Electric Company Active casing alignment control system and method
US20100296912A1 (en) * 2009-05-22 2010-11-25 General Electric Company Active Rotor Alignment Control System And Method
WO2015065228A1 (fr) * 2013-10-31 2015-05-07 Владимир Григорьевич МАКАРЕНКО Procédé d'évaporation de produits en écoulement et dispositif d'évaporation pour sa mise en œuvre
EP3350447B1 (fr) 2015-09-14 2020-03-25 Torad Engineering, LLC Dispositif d'hélice à aubes multiples
US12085045B1 (en) * 2023-08-02 2024-09-10 Stoneridge Control Devices, Inc. Low stiction vane pump for evaporative emissions system

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Publication number Priority date Publication date Assignee Title
DE543535C (de) * 1932-02-06 Gottlieb Soehngen Fluessigkeitswechselgetriebe mit exzentrisch einstellbaren Fluegelkolben
GB109186A (en) * 1916-12-22 1917-09-06 Herbert Augustus Bullard Improvements in or relating to Rotary Engines and Pumps.
US1961592A (en) * 1929-01-18 1934-06-05 Muller Wolfgang Carl Variable capacity pump or motor
US2029554A (en) * 1932-08-24 1936-02-04 Berggren Charles William Pump and compressor
US2233269A (en) * 1938-08-12 1941-02-25 Napolitano Attilio Vane pump
US2336476A (en) * 1940-05-20 1943-12-14 Fulcher Frank Christian Rotary vane pump
US2336344A (en) * 1941-05-03 1943-12-07 Merrill August Rotary pump
US2368789A (en) * 1941-10-21 1945-02-06 Hydraulic Dev Corp Inc Balanced vane pump
FR988476A (fr) * 1948-03-27 1951-08-28 Hivag Machine rotative pour l'acheminement de fluides liquides, vaporeux ou gazeux et pouvant également travailler comme moteur
GB646407A (en) * 1948-06-24 1950-11-22 Hugh Cochrane Halket Orr Improvements relating to rotary pumps and engines
GB743088A (en) * 1952-08-25 1956-01-11 Raymond John Francis Moore Improvements relating to rotary pumps and motors
DE942314C (de) * 1952-10-01 1956-05-03 Otto Pfrengle Drehkolbenpumpe mit einem in einem Zylinder exzentrisch umlaufenden Drehkolben
US2764941A (en) * 1953-08-21 1956-10-02 Racine Hydraulics And Machiner Multiple pump
US2859911A (en) * 1953-09-08 1958-11-11 Reitter Teodoro Rotary compressor
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JPS5716290A (en) * 1980-06-30 1982-01-27 Matsushita Electric Works Ltd Vane type driving apparatus
US4563131A (en) * 1984-04-30 1986-01-07 Mechanical Technology Incorporated Variable displacement blower

Also Published As

Publication number Publication date
US4958992A (en) 1990-09-25
WO1988003229A3 (fr) 1988-06-30
AU8074787A (en) 1988-05-25
ATE59438T1 (de) 1991-01-15
DE3767154D1 (de) 1991-02-07
WO1988003229A2 (fr) 1988-05-05
RU1809864C (ru) 1993-04-15
CH673509A5 (fr) 1990-03-15
EP0294399A1 (fr) 1988-12-14
JPH01501082A (ja) 1989-04-13
AU625256B2 (en) 1992-07-02
JP2587665B2 (ja) 1997-03-05

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