EP2195511B1 - Machine de refoulement à spirales - Google Patents

Machine de refoulement à spirales Download PDF

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Publication number
EP2195511B1
EP2195511B1 EP08757301A EP08757301A EP2195511B1 EP 2195511 B1 EP2195511 B1 EP 2195511B1 EP 08757301 A EP08757301 A EP 08757301A EP 08757301 A EP08757301 A EP 08757301A EP 2195511 B1 EP2195511 B1 EP 2195511B1
Authority
EP
European Patent Office
Prior art keywords
spiral
disc
housing
strips
shaped
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.)
Not-in-force
Application number
EP08757301A
Other languages
German (de)
English (en)
Other versions
EP2195511A1 (fr
Inventor
Fritz Spinnler
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.)
Spinnler Engineering
Original Assignee
Spinnler Engineering
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Filing date
Publication date
Application filed by Spinnler Engineering filed Critical Spinnler Engineering
Publication of EP2195511A1 publication Critical patent/EP2195511A1/fr
Application granted granted Critical
Publication of EP2195511B1 publication Critical patent/EP2195511B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids 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
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids 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 both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids 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 both members having co-operating elements in spiral form where only one member is moving
    • F04C18/0223—Rotary-piston pumps specially adapted for elastic fluids 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 both members having co-operating elements in spiral form where only one member is moving with symmetrical double wraps
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids 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
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids 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 both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0269—Details concerning the involute wraps
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/001—Radial sealings for working fluid

Definitions

  • the invention relates to a spiral compressor with double spiral for compressible media according to the introductory part of patent claim 1.
  • Spiral compressors with double spiral for example, by the DE 2603462 A1 known.
  • a built-up according to this principle compressor is characterized by virtually pulsation-free promotion of existing example of air or an air-fuel mixture gaseous working fluid and therefore could be used inter alia for charging purposes of internal combustion engines with advantage.
  • a plurality of approximately crescent-shaped working spaces are trapped along the displacer chamber between the spirally-shaped runner and the two peripheral walls, moving from the inlet through the displacer chamber to the outlet, with their volume constantly reduced and the pressure of the working fluid is increased accordingly.
  • the rotor there called rotary piston, held to its leadership relative to the housing at its inlet end by a rocker whose length is greater than the length of the drive crank.
  • the disc carrying the spiral strips terminates with the outer contour of the non-overlapped strips and the contour of the disc in the overlapped area is formed in the shape of the movement path which defines a housing edge, which by the necessary lowering of the outer cylinder wall of the delivery chamber on a housing half to record the disc has arisen when swinging the rotor in this area.
  • the invention is therefore an object of the invention to provide a machine of the type mentioned in which in particular in the low speed range adjacent conveyor spaces in which different pressures prevail, are completely sealed from each other.
  • the advantages of the invention are to be seen in the fact that they both in a scroll compressor with double spiral with rocker as a guide element for the displacer and with guide shaft for guiding the displacer, as for example from the DE 3107231 A1 is known, can be used. Furthermore, the invention allows a - viewed in the radial direction - outwardly free arrangement of the rocker, if such as a guide element is assumed. The invention is particularly effective when used in machines with internal compression, as in the above-mentioned DE 2603462 A1 are described and in the above-mentioned DE 3107231 A1 are shown graphically.
  • Fig. 1 in the drawing denotes the rotor of the machine as a whole. It consists of a disk 2 and from both sides axially of the disk 2 vertically projecting spiral strips 3.
  • Fig. 1 is the spiral, ie, the bar 3 is formed of a plurality of adjoining circular arcs and has a wrap angle of about 360 °.
  • the outlet-side end of the spiral is equipped with a slight so-called internal compression, as they are known from the above DE 2603462 A1 is known. This is worth mentioning in that the higher pressure in the working space caused by the internal compression has a perfect seal as a condition.
  • a plurality of apertures 6 are provided in the disk 2, so that the medium can pass from one side of the disk to the other, for example, in a central outlet 13 (FIG. Fig. 2 ) to be deducted.
  • 4 with the hub is designated, with which the disc 2 is mounted on a roller bearing 22 on an eccentric disc 23. This is in turn part of a drive shaft 24.
  • "e” means the eccentricity between the axis 9 of the drive shaft 24 and the axis 10 of the eccentric disc 23rd
  • the disk 2 carrying the spiral-shaped strips 3 terminates on the predominant part of its circumference with the outer contour of the strips 3.
  • This area is considered to be the non-overlapped spiral area and is decisive for the keeping of the outside diameter of the machine.
  • the angle dimension "OV" indicates the overlapped area of the spiral. In that area, the disc 2 projects radially beyond the strips 3. With 5 in this area "OV” is a radially outside of the strips 3 arranged eye designated for receiving a guide bearing, not shown, which is mounted on a guide pin 30.
  • the contour of the disc 2 is formed at the location provided for the mutual sealing of the (to be explained later) delivery chambers 11 in the form of the path of movement of the disc. In the example, it is a recess 20 which is elliptical.
  • Fig. 2 the housing half 7b of the assembled from two halves, via fastening eyes 8 for receiving screw connections connected machine housing is shown.
  • 11 denotes the delivery chamber, which incorporated in the manner of a spiral slot in both housing halves is. It runs parallel from an outer circumference of the spiral disposed in the housing inlet 12 to an interior provided for the outlet 13.
  • the delivery chamber 11 has substantially approximately parallel, approximately equally spaced cylinder walls 14, 15, which like the strips 3 a spiral include.
  • an axis 28 is provided for the rotatable mounting of the guide device.
  • the disc 2 Since in the area "OV" the disc 2 protrudes beyond the strips 3, it must penetrate at least one half of the housing. This happens in the present case on the illustrated housing half 7b.
  • the inner web 18 of the housing half 7b relative to the outer web 17 is lowered at an appropriate point of the housing - at one edge of the overlapped region "OV" of the spiral - by the amount of the disc thickness.
  • This measure has, inter alia, the advantage that in the lower half of the housing 7b, a sealing strip (not shown) is to be arranged only at the inner web, which seals the delivery space 11 against the suction space 16 up to the outlet 13. Due to this necessary lowering of the outer cylinder wall on at least one half of the housing, here 7b, for receiving the disc 2 when swinging the rotor in this area creates a housing edge 19th
  • the leadership of the rotor 1 is concerned by the guide means 29.
  • the guide means 29 Depending on whether the guide means 29 from a rocker or from a with the drive shaft synchronously running guide shaft (not shown), perform all points on the strips 3 an elliptical or a circular displacement movement.
  • the guide means 29 consists of a rocker 31, one end of which is rotatably mounted about the axis 28 in the housing ( Fig. 2 ), while the other end engages over the guide pin 30 in the eye 5 of the rotor.
  • the tuning of the essential elements for the correct functioning is now as follows:
  • the housing edge 19, which forms the transition between raised first part 17 and lowered second part 18 of the outer cylinder wall 14 is formed as a bulbous thickening.
  • Their extension "D" in the radial direction should be at the widest point of the thickening at least half as large as the measure of the eccentricity "e”.
  • the thickening is formed as a substantially circular paragraph, wherein extension "D" in this case represents the diameter of the paragraph.
  • the recess 20 of the disc is then formed in the shape of its trajectory, depending on the geometry of the thickening arc similar, here elliptical.
  • Fig. 4 the position of the rotor 1 is registered, in which the crescent-shaped outer working space formed by the strips 3 and the outer cylinder wall 14 is completely enclosed. It can be seen that the sealing line 21 is engaged. From this representation it is also apparent that the diameter "D" of the edge 19, if it is circular, must have a certain minimum size in order for the operative connection to function. The mere rounding off of the housing wall to break off, as they are known from the DE 3407939 C1 is known, does not lead to success.
  • Fig. 5 shows the outermost angular position at which a seal still takes place. The ejection of the working fluid from the outer working space is almost completed. Work equipment is already expelled from the inner workspace. This outermost sealing line is extremely important in order to avoid that compressed working fluid from the spiral end flows back into the suction chamber.
  • Fig. 6 shows the area where a seal is unnecessary, even unwanted.
  • the recess 20 has now lifted off the edge 19; it takes place in this Area no seal instead.
  • working fluid is conveyed out at the end of the spiral from the inner working space towards the outlet 13, and already sucked back into the inner working space from the inlet 12 at the beginning of the spiral.
  • the outer working space is open at the end of the coil against the suction chamber 16 and at the beginning of the spiral against the inlet 12, which facilitates its filling.
  • a backflow of compressed working fluid from the inner working space around the spiral end into the suction chamber 16 is not possible, since at this time in the exit-side region of the spiral, the strip 3 seals against the outer cylinder wall 14.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Filling Or Emptying Of Bunkers, Hoppers, And Tanks (AREA)

Claims (2)

  1. Compresseur à spirale avec double-spirale pour produits compressibles, avec un espace de convoyage (11) en forme de spirale situé dans un boîtier fixe (7a, 7b) entre des parois de cylindre (14, 15), dans lequel est monté un curseur (1), composé principalement d'un disque (2) et de languettes (3) en forme de spirale sur au moins un côté du disque, lesquelles sont maintenues de façon excentrique par rapport au boîtier de telle sorte que pendant l'exploitation, chaque point des languettes (3) effectue un mouvement limité par les parois de l'espace de convoyage, sachant que le disque (2) portant les languettes en forme de spirale est contiguë au contour extérieur des languettes sous forme de zone dite sans chevauchement, et sachant que le contour du disque (2) dépasse par-dessus les languettes (3) de façon radiale sous forme de zone dite de chevauchement (« OV ») où est formée un point faisant office de voie de déplacement prévue pour l'étanchéité réciproque des espaces traversés (11, 16), prévoyant un rebord de boîtier (19), rebord (19) qui de par l'abaissement nécessaire de la paroi de cylindre extérieure (14) de l'espace de convoyage (11) sur au moins une moitié du boîtier (7b) servant à porter le disque lors de l'amorçage du curseur dans cette zone, fait office de transition entre la garniture extérieure supérieure (17) et la garniture intérieure rabaissée (18) de la paroi du cylindre (14), caractérisé en ce que, à l'endroit prévu pour l'étanchéité réciproque des espaces traversés (11, 16), le rebord du boîtier (19) a également la forme d'une voie de déplacement plutôt qu'un épaississement en forme de nodule globalement rond, sachant que l'étirement « D » de l'épaississement dans le sens radial est au moins deux fois moins grand que la masse de l'excentricité « e » au point le plus large, d'un axe (9) d'un arbre de transmission (24) et d'un axe (10) d'un disque excentrique (23), sur lequel est enfilé le disque (2) et que pendant l'exploitation de la machine, durant les périodes pendant lesquelles la pression qui règne dans l'espace de travail extérieur en forme de faucille formée par les languettes (3) et la paroi extérieure de cylindre (14) est supérieure à la pression régnant dans l'espace d'aspiration (16) disposé dans le sens radial en dehors de la paroi de cylindre extérieure (14), l'épaississement en forme de nodule globalement rond (19) coopère avec un évidement (20) globalement rond ou en forme d'ellipse du disque (2) sous forme d'une voie de déplacement afin de former une ligne d'étanchéité (21) s'étirant au-dessus de la hauteur de transition.
  2. Compresseur à spirale avec double spirale selon la revendication 1, caractérisé en ce que l'épaississement en forme de nodule (19) et le contour du disque (20) sont disposés contre l'extrémité de la spirale se trouvant du côté de la sortie.
EP08757301A 2007-08-22 2008-07-10 Machine de refoulement à spirales Not-in-force EP2195511B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH13192007 2007-08-22
PCT/CH2008/000309 WO2009023974A1 (fr) 2007-08-22 2008-07-10 Machine de refoulement hélicoïdale

Publications (2)

Publication Number Publication Date
EP2195511A1 EP2195511A1 (fr) 2010-06-16
EP2195511B1 true EP2195511B1 (fr) 2011-11-16

Family

ID=39916343

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08757301A Not-in-force EP2195511B1 (fr) 2007-08-22 2008-07-10 Machine de refoulement à spirales

Country Status (5)

Country Link
US (1) US8425211B2 (fr)
EP (1) EP2195511B1 (fr)
CN (1) CN101784754B (fr)
AT (1) ATE533920T1 (fr)
WO (1) WO2009023974A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2402611A3 (fr) * 2010-07-02 2013-06-26 Handtmann Systemtechnik GmbH & Co. KG Dispositif de chargement pour l'étanchéification d'air de suralimentation pour un moteur à combustion interne

Family Cites Families (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH586348A5 (fr) 1975-02-07 1977-03-31 Aginfor Ag
DE3107231A1 (de) 1981-02-26 1982-09-02 Volkswagenwerk Ag, 3180 Wolfsburg Verdraengermaschine fuer kompressible medien
DE3231756C2 (de) * 1982-08-26 1985-08-01 Pierburg Gmbh & Co Kg, 4040 Neuss Rotationskolbenmaschine für Fluide
DE3231754C2 (de) * 1982-08-26 1986-01-02 Pierburg Gmbh & Co Kg, 4040 Neuss Rotationskolbenmaschine für kompressible Medien
JPS60132085A (ja) 1983-12-19 1985-07-13 Sanden Corp スクロ−ル型圧縮機
DE3407939C1 (de) 1984-03-03 1985-07-18 Pierburg Gmbh & Co Kg, 4040 Neuss Rotationskolbenmaschine fuer Fluide
CN85101350B (zh) * 1985-04-01 1987-10-07 三菱重工业株式会社 涡旋式流体机械
CH673874A5 (fr) 1987-03-24 1990-04-12 Bbc Brown Boveri & Cie
EP0354342B1 (fr) * 1988-08-03 1994-01-05 AGINFOR AG für industrielle Forschung Machine de déplacement de fluide de type à spirale
US5171140A (en) * 1990-10-19 1992-12-15 Volkswagen Ag Spiral displacement machine with angularly offset spiral vanes
DE59206416D1 (de) * 1991-12-05 1996-07-04 Aginfor Ag Verdrängermaschine nach dem Spiralprinzip
EP0545191B1 (fr) * 1991-12-05 1995-09-13 AGINFOR AG für industrielle Forschung Machine de déplacement de fluide de type à spirale
DE59203379D1 (de) * 1991-12-16 1995-09-28 Aginfor Ag Verdrängermaschine nach dem Spiralprinzip.
DE4207984A1 (de) 1992-03-13 1993-09-16 Asea Brown Boveri Verdraengermaschine nach dem spiralprinzip
DE59400648D1 (de) * 1993-01-19 1996-10-24 Aginfor Ag Verdrängermaschine nach dem Spiralprinzip
ES2164398T3 (es) * 1997-08-26 2002-02-16 Crt Common Rail Tech Ag Maquinas de desplazamiento espiral para medios compresibles.
DE59806600D1 (de) * 1997-08-26 2003-01-23 Crt Common Rail Tech Ag Spiralverdrängermaschine für kompressible Medien
US6089839A (en) * 1997-12-09 2000-07-18 Carrier Corporation Optimized location for scroll compressor economizer injection ports
US6217301B1 (en) * 1998-04-08 2001-04-17 Daikin Industries, Ltd. Scroll fluid machinery
DE19980588C2 (de) 1998-04-29 2002-05-23 Chunkyung Kim Pumpe
JP2000352384A (ja) 1999-06-07 2000-12-19 Mitsubishi Heavy Ind Ltd スクロール型流体機械
US6705848B2 (en) * 2002-01-24 2004-03-16 Copeland Corporation Powder metal scrolls
JP4241862B2 (ja) * 2007-08-06 2009-03-18 ダイキン工業株式会社 圧縮機構及びスクロール圧縮機

Also Published As

Publication number Publication date
US20110027116A1 (en) 2011-02-03
WO2009023974A1 (fr) 2009-02-26
CN101784754B (zh) 2012-07-25
ATE533920T1 (de) 2011-12-15
US8425211B2 (en) 2013-04-23
EP2195511A1 (fr) 2010-06-16
CN101784754A (zh) 2010-07-21

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