EP0520943B1 - Pompe à déplacement positif - Google Patents

Pompe à déplacement positif Download PDF

Info

Publication number
EP0520943B1
EP0520943B1 EP19920810442 EP92810442A EP0520943B1 EP 0520943 B1 EP0520943 B1 EP 0520943B1 EP 19920810442 EP19920810442 EP 19920810442 EP 92810442 A EP92810442 A EP 92810442A EP 0520943 B1 EP0520943 B1 EP 0520943B1
Authority
EP
European Patent Office
Prior art keywords
disc
spiral
delivery
displacement pump
outlet
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
EP19920810442
Other languages
German (de)
English (en)
Other versions
EP0520943A1 (fr
Inventor
Heinrich Güttinger
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.)
Aginfor AG
Original Assignee
Aginfor AG fuer industrielle Forschung
Aginfor 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 Aginfor AG fuer industrielle Forschung, Aginfor AG filed Critical Aginfor AG fuer industrielle Forschung
Publication of EP0520943A1 publication Critical patent/EP0520943A1/fr
Application granted granted Critical
Publication of EP0520943B1 publication Critical patent/EP0520943B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • 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
    • F04C2/025—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 the moving and the stationary member having co-operating elements in spiral form
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid

Definitions

  • the invention relates to a positive displacement pump for incompressible media, with at least one conveying space delimited by spiral peripheral walls extending perpendicularly from a side wall of a fixed housing, which leads from an inlet lying outside the spiral to an outlet lying inside the spiral, and with one in the Conveying space protruding, spiral-shaped displacement body, which encompasses a wrap angle of 360 ° and which is mounted in relation to the delivery space to perform a circular, torsion-free movement and the center of which is eccentrically offset from the center of the peripheral walls in such a way that the displacement body is always both external and also almost touches the inner circumferential wall of the delivery chamber on at least one advancing sealing line,
  • Such a machine is suitable for conveying liquids.
  • along the conveying space between the displacer and the two peripheral walls of the conveying space Includes crescent-shaped work spaces that move from the inlet through the delivery chamber to the outlet.
  • Such spiral machines with a wrap angle of 360 ° convey only because they work without internal compression.
  • the pressure in the outlet is independent of the suction pressure in the inlet and is specified by the consumer. With increasing pressure in the outlet, the power requirement naturally also increases.
  • the displacement pump is therefore designed and dimensioned according to the most extreme conditions.
  • the adaptation must be carried out with a blow-off valve as a countermeasure.
  • a blow-off valve as a countermeasure.
  • the unnecessarily expended energy is then not only used unused due to the necessary blowing off, but is also directly misused by heating the recirculating oil.
  • blowing off the oil via a pressure relief valve leads to foam formation, which significantly affects the lubricating properties.
  • the invention aims to prevent all of the disadvantages mentioned in connection with displacement pumps for liquids. It is therefore based on the task of designing a positive displacement pump of the type mentioned at the beginning as a pressure-constant, self-regulating pump.
  • this is achieved in that the orbiting disk with the displacement body is connected axially displaceably to a drive shaft which penetrates the housing and is mounted therein and that spring means which act directly on the back of the disk and which are supported in the depressurized interior of the housing, the disk with the The displacer presses and seals against the side wall, and that the spring means are designed so that when a predetermined working fluid pressure in the outlet is reached, the disk with the displacing body disengages from its sealing position to such an extent that the working fluid pressure remains constant, regardless of the number of circular movements over time and independently of the funding volume.
  • the pump shown in FIGS. 1 and 2 is equipped with two nested conveying spaces 6 and displacement bodies 5 lying therein. It goes without saying that an entire system of spirals arranged in this way can be provided in the same plane. All of these spirals can convey more advantageously from their own inlet 2 into a common outlet 3.
  • the disk-shaped rotor is designated as a whole by 1.
  • the spiral-shaped displacement bodies 5 are arranged on one side of the disk 4. Their spirals extend over a wrap angle of 360 °. They engage in a delivery chamber 6 of the fixed housing 7. They are dimensioned in their axial extent so that with their narrow end faces, they stand at the bottom of the delivery chamber, both at standstill and during operation, i.e. almost touch the disc side 20.
  • the delivery chamber 6 is incorporated into the housing 7 in the manner of a spiral slot. It runs from an inlet 2 arranged on the outer circumference of the spiral in the housing to an outlet 3 arranged in the interior of the housing ° include.
  • the displacement body 5 is guided between these circumferential walls 8, 9.
  • the spiral shape of the delivery chamber and displacement body is made up of two semicircular arches. Of course, other spiral shapes are also possible.
  • the eccentric drive of the disk-shaped rotor 1 carrying the displacement bodies 5 results in a circular movement of each of the points of the displacement bodies, this circular movement being limited by the peripheral walls of the delivery spaces.
  • alternating crescent-shaped working spaces enclosing the working medium result on the inner and outer sides of the displacement bodies.
  • FIG. 1 two end positions of the displacement bodies 5 are shown.
  • the outside diameter of the disc 4, which cannot be seen in this section, is shown in dashed lines.
  • the spiral 5b rests with its inside against the inner peripheral wall 8 of the delivery chamber 6 both at its entry-side end and at its exit-side end. On the one hand, it thus encloses the crescent-shaped work space 12 with its inside.
  • the spiral is open on its outside against both inlet 2 and outlet 3, i.e. at the same time, it sucks in and discharges there, as indicated by the corresponding arrows.
  • the spiral 5a is in the second end position. It encloses the working space 12 with its outside and is opened with its inside against the inlet 2 and the outlet 3.
  • the system of the displacer 5 is rotated by 90 ° in relation to the representation in FIG. 1 in the longitudinal section in FIG. This in order to be able to better show the eccentricity e between the drive and the rotor as well as between the displacement body and the delivery spaces in the section plane.
  • the external feed of the two inlets 2, which can be done in any manner, is not shown.
  • the two housing halves 7 and 7 ' are connected to one another via screw connections 29, which are only indicated in FIG.
  • the drive shaft 14, which penetrates the housing 7 ′, is arranged coaxially with the delivery spaces 6.
  • the centers of the delivery spaces in turn run in the middle of the circular housing part 7.
  • the shaft bearing 18 is located within a housing half 7 ' Integrated bushing 24.
  • a blind bore 26, offset by the eccentricity e, is provided within a shaft collar, via which the connection to the axially displaceable rotor 1 takes place.
  • This connection takes place in the form of a pin 15 protruding from the disk 4.
  • This pin engages in the blind hole 26 via the pin bearing 17.
  • the journal bearing 17 and the shaft bearing 18 are lubricated by means of the working medium conveyed by the spirals.
  • the disc 4 and the pin 15 are provided with a longitudinal bore 16 which communicates with the outlet 3.
  • the lubricant under pressure is supplied to the respective bearing points via transverse bores 19 in the journal and 21 in the shaft collar.
  • the lubricant emerging from the bearing points is passed through a transverse bore 22 in the shaft collar and through a bore 23 in the housing bushing 24 into the interior of the housing half 7 'connected to the inlets 2.
  • the spring means 13 are also located in this interior, which ensure that the pressure in the outlet 3 does not exceed a predetermined level.
  • it is a helical spring which surrounds the bush 24. At one end, this spring is supported on the inner wall of the housing half 7 '. With its other end, it acts directly on the rear side of the disc 4, which is not provided with displacement bodies. Since this disc orbits during operation, the adjacent spring requires a guide.
  • the disc is therefore provided with an annular extension 25 on the corresponding diameter. On the free end face there is a groove in which the tongue lies.
  • the spring means are now designed with a certain strength and according to a certain characteristic. In such a way that when a predetermined pressure in the outlet 3 is exceeded, the pressure on the inner circular surface of the disk 4 and on the adjacent one against the outlet force is sufficient to open the sickle surfaces of the delivery spaces to lift the disc with the displacement body out of its normal sealing position.
  • the pin 15 moves a little deeper into the blind bore 26.
  • the axial movement of the rotor 1 is minimal. Due to the resulting leaks on the end faces of the displacement bodies and the end walls of the delivery spaces, pressurized working fluid flows from the inside working spaces into the outside working spaces and vice versa, depending on the position of the displacement bodies. This reduces the pressure in the outlet until the spring force is sufficient to press the rotor against the housing in the sealing position.
  • the pump only delivers the volume that is required by the consumer.
  • the supply line to the consumer be closed for any reason, i.e. the delivery rate would be zero, so that due to the pressure build-up in outlet 3, the rotor would immediately lift out of the sealing position to such an extent that all of the fluid conveyed from a work space flows over the end faces of the spirals into the radially opposite work space.
  • the pump therefore runs empty, it does not deliver and the power requirement drops.
  • this self-regulating pump differs significantly from the conventional bypass methods, whereby it is also characterized in that the lubricant cannot foam due to the internal pump recirculation.
  • the displacement pump according to FIGS. 3 and 4 differs in terms of the conveying parts in that three displacement bodies 5, which are distributed uniformly over the circumference, are arranged on the disk 4.
  • the corresponding associated three promotion rooms 6 are from a common inlet 2 fed. So even though the spirals convey from the outside in, the supply of the spirals with work equipment takes place in the most direct way from the center of the housing. From the three outlets 3, the working fluid reaches a common annular chamber 27, from where it is fed to a consumer (not shown).
  • the spring means 13 used here are a number of helical springs arranged uniformly over the circumference. At one end, these springs are supported by ball joints 28 in corresponding pans on the inner wall of the housing half 7 '. With their other end they also act via ball joints directly on the rear side of the disc 4, which is not provided with displacement bodies and which is also equipped with ball sockets on the corresponding diameter for this purpose.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Claims (5)

  1. Pompe à déplacement positif pour des fluides incompressibles, avec au moins une chambre de transport (6) limitée par des flancs en forme de spirale (8, 9) s'étendant perpendiculairement à partir d'une paroi latérale (20) d'une enceinte fixe (7, 7'), qui conduit d'une entrée (2) située à l'extérieur de la spirale jusqu'à une sortie (3) située à l'intérieur de la spirale, et avec un corps de déplacement (5) en forme de spirale engagé dans la chambre de transport (6), disposé sur un disque (4), et qui couvre un angle de 360° et qui est supporté par rapport à la chambre de transport pour décrire un mouvement de translation circulaire et dont le centre (10) est excentriquement décalé par rapport au centre (11) des flancs (8, 9) de telle façon que le corps de déplacement (5) soit en permanence pratiquement en contact aussi bien avec le flanc extérieur qu'avec le flanc intérieur (9 respectivement 8) de la chambre de transport (6) suivant au moins une ligne d'étanchéité qui avance, caractérisée en ce que le disque en mouvement orbital (4) avec le corps de déplacement (5) est relié de façon axialement coulissante avec un arbre d'entraînement (14) traversant l'enceinte (7') et supporté dans celle-ci, en ce que des moyens élastiques (13) agissant directement sur le dos du disque (4), qui prennent appui dans l'intérieur sans pression de l'enceinte (7'), poussent et appliquent hermétiquement le disque (4) avec le corps de déplacement (5) contre la paroi latérale (20), et en ce que les moyens élastiques (13) sont conçus de telle manière que lorsque l'on atteint une pression prédéterminée du fluide de travail dans la sortie (3), le disque (4) avec le corps de déplacement (5) s'écarte de sa position d'étanchéité à un point tel que la pression du fluide de travail reste constante, indépendamment du nombre de mouvements circulaires par unité de temps et indépendamment du volume transporté.
  2. Pompe à déplacement positif suivant la revendication 1, caractérisée en ce que la liaison du disque (4) avec l'arbre d'entraînement (14) est réalisée par l'intermédiaire d'un tourillon (15), qui est appuyé excentriquement dans un trou borgne (26) de l'arbre (14).
  3. Pompe à déplacement positif suivant la revendication 2, caractérisée en ce que, dans la région de la sortie (3), le disque (4) et le tourillon (15) de l'arbre d'entraînement sont pourvus d'un trou (16), par lequel le fluide transporté par les spirales peut être envoyé à l'appui du tourillon (17) et à l'appui de l'arbre (18).
  4. Pompe à déplacement positif suivant la revendication 1, caractérisée en ce que deux corps de déplacement (5), décalés l'un par rapport à l'autre de 180°, sont disposés sur le disque (4) en étant emboîtés l'un dans l'autre, et en ce que les deux chambres de transport (6) associées, emboîtées l'une dans l'autre de manière correspondante, débouchent dans une sortie commune (3).
  5. Pompe à déplacement positif suivant la revendication 1, caractérisée en ce qu'au moins trois corps de déplacement (5) sont disposés sur le disque (4) en étant répartis de manière uniforme sur la périphérie, et en ce que les au moins trois chambres de transport (6) associées, disposées de manière correspondante, débouchent dans une entrée commune (2).
EP19920810442 1991-06-22 1992-06-10 Pompe à déplacement positif Expired - Lifetime EP0520943B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1851/91A CH683552A5 (de) 1991-06-22 1991-06-22 Verdrängungspumpe.
CH1851/91 1991-06-22

Publications (2)

Publication Number Publication Date
EP0520943A1 EP0520943A1 (fr) 1992-12-30
EP0520943B1 true EP0520943B1 (fr) 1995-08-23

Family

ID=4220091

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19920810442 Expired - Lifetime EP0520943B1 (fr) 1991-06-22 1992-06-10 Pompe à déplacement positif

Country Status (3)

Country Link
EP (1) EP0520943B1 (fr)
CH (1) CH683552A5 (fr)
DE (1) DE59203356D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022003188A1 (de) 2022-09-01 2024-03-07 Peter Groppenbächer Vorrichtung zur Förderung von Fördergut

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1423584A1 (fr) * 2001-09-05 2004-06-02 RAPP, Manfred Max Machine a piston a rotation parallele pourvue de parois laterales
DE102007043324A1 (de) * 2007-09-12 2009-03-19 Fischer, Francesco Peter, Dipl.-Ing. Verfahren zum Pumpen eines Mediums und dessen Vorrichtung
FR3043148B1 (fr) * 2015-11-03 2020-10-02 Ea Technique Compresseur a spirales

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR825643A (fr) * 1936-11-26 1938-03-09 Perfectionnements au capsulisme à excentrique
US2475247A (en) * 1944-05-22 1949-07-05 Mikulasek John Planetary piston fluid displacement mechanism
US4362479A (en) * 1981-03-25 1982-12-07 Eaton Corporation Rotary fluid pressure device and lubrication circuit therefor
KR890000628B1 (ko) * 1984-05-29 1989-03-22 미쓰비시전기 주식회사 스크롤 유체기계
EP0214164B1 (fr) * 1985-02-27 1990-05-23 Gutag Innovations Ag Machine a deplacement positif, notamment pompe
JPH0830470B2 (ja) * 1985-03-28 1996-03-27 松下電器産業株式会社 スクロ−ル圧縮機
JPH066947B2 (ja) * 1988-04-11 1994-01-26 新明和工業株式会社 スクロール形流体機械

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022003188A1 (de) 2022-09-01 2024-03-07 Peter Groppenbächer Vorrichtung zur Förderung von Fördergut

Also Published As

Publication number Publication date
DE59203356D1 (de) 1995-09-28
CH683552A5 (de) 1994-03-31
EP0520943A1 (fr) 1992-12-30

Similar Documents

Publication Publication Date Title
DE10240409B4 (de) Variable Verdrängungspumpe
DE3015628A1 (de) Drucklager/kopplungseinrichtung und damit ausgeruestete schneckenmaschine
DE3014520A1 (de) Drehkolbenmaschine
DE1944942A1 (de) Schraubenverdichter und Verfahren zu seiner Verwendung
DE3627579A1 (de) Spiralkompressor
DE19746897C2 (de) Schraubenverdichter mit Öleinspritzung
DE102007043595B4 (de) Verdrängermaschine nach dem Spiralprinzip
EP1828611A1 (fr) Pompe a palettes coulissantes
DE2825616C2 (de) Lager- und Dichtungsanordnung an den Wellen einer Zahnradpumpe
EP0692073A1 (fr) Pompe a engrenages pour le refoulement d'un liquide
EP0955466B1 (fr) Etanchéité de jeu annulaire
DE1294205B (de) Rotierende Verdraengerpumpe
DE3839889A1 (de) Stroemungsmittelverdichter
DE3319776C2 (de) Spiralkompressor
EP0520943B1 (fr) Pompe à déplacement positif
DE1428244C3 (de) Schraubenverdichter mit einem Schrau benrippenrotor und einem Schraubennutenrotor
DE1264958B (de) Zahnradpumpe oder -motor
EP1088153A1 (fr) Machine de refoulement construite selon le principe de la spirale
EP2137412B1 (fr) Machine de refoulement construite selon le principe de la spirale
EP2249039A2 (fr) Pompe à engranage externe dotée d'une lubrification de palier améliorée
DE10205121A1 (de) Spiralkompressor
DE69831023T2 (de) Spiralverdichter
DE1553205A1 (de) Pump- und Abmessgeraet
DE102008042233A1 (de) Exzenterschneckenpumpe sowie mechanisches Koppelelement für die Exzenterschnecke einer Exzenterschneckenpumpe
DE1040376B (de) Ausgleichseinrichtung an motorisch angetriebenen Foerderpumpen fuer stroemende Medien

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): CH DE FR GB IT LI SE

17P Request for examination filed

Effective date: 19930226

17Q First examination report despatched

Effective date: 19940316

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH DE FR GB IT LI SE

REF Corresponds to:

Ref document number: 59203356

Country of ref document: DE

Date of ref document: 19950928

ITF It: translation for a ep patent filed

Owner name: DE DOMINICIS & MAYER S.R.L.

ET Fr: translation filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19951102

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19990511

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19990512

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 19990514

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19990525

Year of fee payment: 8

Ref country code: DE

Payment date: 19990525

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000610

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000611

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000630

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000630

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20000610

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

EUG Se: european patent has lapsed

Ref document number: 92810442.1

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20010228

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20010403

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050610