EP1216358B1 - Spiralverdichter - Google Patents

Spiralverdichter Download PDF

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Publication number
EP1216358B1
EP1216358B1 EP00966206A EP00966206A EP1216358B1 EP 1216358 B1 EP1216358 B1 EP 1216358B1 EP 00966206 A EP00966206 A EP 00966206A EP 00966206 A EP00966206 A EP 00966206A EP 1216358 B1 EP1216358 B1 EP 1216358B1
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EP
European Patent Office
Prior art keywords
rotor
internal combustion
combustion according
same
radius
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
EP00966206A
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English (en)
French (fr)
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EP1216358A1 (de
Inventor
Bernard Helliot
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Blackmer
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Blackmer
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Publication date
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Publication of EP1216358A1 publication Critical patent/EP1216358A1/de
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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
    • 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
    • F04C18/04—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 of internal-axis type

Definitions

  • the present invention relates to a new type of capsulism for a rotating machine conveying a gaseous fluid which can function as a compressor or vacuum pump.
  • the invention relates more precisely to a new family of compressors or vacuum pumps "Dry", including a family of air compressors or particularly compact, light, one, two gases or three stages, capable of delivering at low pressure, medium or high (for example 3, 8 or 20 bars, respectively).
  • medium pressure compressors they are designed with low pressure cells, delivering to an air or gas cooler, and medium pressure, sucking in the same refrigerant, this which improves the compression efficiency and avoids profile temperatures and deformations due to heat released by compressed air, prohibitive.
  • the invention is as described in claim 1.
  • the radius of curvature of the line median increases from each end, up to a maximum radius for the middle area of capsulism.
  • compression ratio will be understood in the sense of this patent the ratio between the volume of the compression chamber when closing the compression orifice, and the volume of this chamber compression when opening the orifice of discharge.
  • the essential technical characteristic of capsulism according to the invention relates to the angle formed between the extreme rays, which is greater than 360 °. This characteristic is contrary to what could to be observed in known capsulisms.
  • French patent FR825643 describes a device comprising closed chambers with a total angle less than 360 °.
  • the patent US1967957 also describes a device having a traditional capsulism, not allowing to realize a compressor within the meaning of this patent, nor a pump empty.
  • the cell of base which includes two compression cells.
  • the rotor as in scroll compressors, is driven by two parallel shafts by means of two eccentrics with the same eccentricity E. Each point of the rotor therefore describes, in its movement, a circle, or an "orbit", of radius E.
  • a rotor 1 being assumed to have zero eccentricity, compared to a stator fixed 2, will be said "in medium position" - that never occupies in practice its eccentricity being always equal to E -. Its dawn is shaped like a vs.
  • the fixed stator is the envelope of the circles of radius E centered on the rotor in the middle position.
  • Curve C can consist of two spirals in opposite directions, one in direction -, going from As aspiration towards B, and one of sense +, going from repression Re towards B.
  • Curve C should form, at the discharge Re, a loop all the more closed as one wishes a higher discharge pressure. It will suffice stops horizontally, or roughly, on suction As.
  • the center line of the rotor (1) has two ends (110, 111).
  • the normals respectively (100) and (101) at the ends (110, 111) form between they a total angle exceeding 360 °, in the example described in figure 3, this total angle approaches 500 °.
  • the radius of curvature of the midline of the rotor gradually increases from each of ends, up to an intermediate zone.
  • the progression of the radius of curvature is not symmetrical with respect to this middle zone.
  • this shows the successive phases of compression in a basic cell.
  • the shaded areas show the alveoli communicating with the suction, up to the closing of this one, and those hatched the alveoli expelling compressed air into the discharge port. Suction and discharge are uninterrupted, and there results that the compression principle itself decreases pulsations of air and noise at the upstream ports and downstream.
  • the dials show the common angle of rotation of the two eccentric drives.
  • the theoretical cubic capacity of the cell is equal to the sum of the areas SA and SB multiplied by the length of the compression chamber, or of the rotor, parallel to the axes of the drive shafts.
  • the scroll compressor consists of casings successive of the same basic spiral, generated by circles ⁇ 1, ⁇ 2, ⁇ 3 ... of the same radius E, located on the same normal N to the base spiral, in Re, of which the centers describe, by turning, the rotor (supposed thickness) in the middle position, and whose intersections with N describe the stator.
  • the basic cell of the compressor C-shaped has its stator defined directly by the envelope of the circles sliding on the serving rotor generator.
  • the rotor curve can be, in the framework of the invention, described by several arcs of successive circles.
  • the maximum air speed in the cell is indeed ⁇ .R, and the orbital speed of any point of the rotor is ⁇ .E, which allows to multiply the speed in the R / E ratio, and therefore to obtain a high throughput in a small footprint, the R / E ratio can exceed 10.
  • this shows a compression chamber in which the drive shafts do not pass through the rotor, which is cantilevered.
  • this represents the diagram of a medium pressure compressor: the two large cells discharge into a cooler Rf1 the compressed air then until the final pressure in the two small cells.
  • a final refrigerant Rf2 completes this achievement.
  • the alveoli are grouped head to tail, to reduce reactions bearings.
  • the trees listed there subject to same efforts on average, for reasons of symmetry, can be identical as well as their seals, bearings and counterweight.
  • figure 12 shows a compressor with three floors with through trees.
  • the rotors must be radially balanced, especially if the rotation is high, but this is easy to achieve, because said rotors have a low mass due to their compact and hollowed out shape, and a low eccentricity with regard to their displacement.
  • this shows possible sealing at speed medium, where one of two identical trees shown is notched to make all or part of balancing.
  • the shaft 3 drives the rotor 4 by via needle bearings 5, attached to seals 6, retaining the oil, the circulation under low pressure is indicated by arrows.
  • this shows another design, for compressors rotating at high speed, where the bearing 7 is force-fitted in rotor 8.
  • Oil leakage tightness is ensured by an air barrier, taken from the discharge (in the rotor), at both ends of the crankpin offset 9 from one of the two drive shafts identical.
  • the compressed air action is completed by two threads in opposite directions bringing back the oil toward the center of the crankpin.
  • Lubricating oil circulating according to the arrows, arrives at the center of the crankpin and is recovered from either side of the central pad.
  • the crankpin is of a diameter slightly lower in parts with threads and grooves, so that the pad does not rub not in these parts little or not lubricated.
  • FIG 17 shows an overview of a low pressure compressor, in which the eccentrics, in the center of the rotor, are at the end of trees.
  • the tree 10 shown rotates in the stator 11 by means of bearings 12 and 13.
  • the eccentric drives the rotor 22 by means of the bearing 14.
  • Seals 15, 16 and 17 isolate the compression chamber of the lubricating oil.
  • the oil inlet, in stator 11, is located between the bearing 12 and the seal 17.
  • the pinion 18 meshes with the wheel 19 which also drives the other shaft.
  • Counterweights 20 and 21 balance the rotor in the radial direction.
  • the axial stops are not shown on the figures of this application, so as not to overcomplicate these.
  • the capsulism according to the invention has designed in particular (but not exclusively) to allow the production of more compressors lower flow rates than screw compressors.
  • the border of a given family of compressors when the dimensions decrease, comes from the increase relative clearances, bounded by tolerances achievable, the arrows of the parts, the settlements of bearing, relative expansions of organs neighbors, all values that cannot be reduced beyond certain limits.
  • the family of air capsulisms or gas "dry” according to the invention will also have its own lower flow limit. This could be greatly reduced (in a ratio of 10 or more) in using liquid injection (oil - water - fluid refrigerant), before or during compression, or with lubrication of the compression chamber, this technique using the classic together: tank with filter-separator, refrigerant, and regulation, obviously falls within the scope of the invention.
  • the total angle formed between the normal of a first end of the median curved line of the rotor, and the normal at the opposite end is greater than 360 °.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Peptides Or Proteins (AREA)
  • Reciprocating Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Claims (15)

  1. Exzenterschnecke für drehende Maschinen, welche eine gashaltige Flüssigkeit befördern und als Kompressor oder als Vakuumpumpe funktionieren können, wobei die bewegliche Rotorenschaufel (1) einer Grundzelle aus zwei in entgegengesetzt gerichteten Spiralen besteht, wobei die erste mit der Ansaugung As und die zweite mit der Verdrängung Re verbunden ist, dadurch gekennzeichnet, dass diese beiden Spiralen dem Rotor die allgemeine Form eines « C » mit einem gesamten Winkel AT von über 360° verleiht, oder AT den gesamten durch die Senkrechte des ersten Endes der mittleren Kurvenlinie des Rotors und die Senkrechte am entgegengesetzten Ende gebildeten Winkel bezeichnet, und dadurch, dass die Kurve C bei der Verdrängung eine Schleife bildet, die geschlossener als bei der Ansaugung ist.
  2. Exzenterschnecke nach Anspruch 1, dadurch gekennzeichnet, dass die Kurve C durch die beiden Spiralen bestimmt ist, oder durch jegliche andere Arten von mathematischen Kurven, welche vorzugsweise gemeinsame Tangenten an ihren Anschlussstellen (B, B1, B2, B3 ...) aufweisen.
  3. Exzenterschnecke nach Anspruch 1, dadurch gekennzeichnet, dass die Kurve C bei der Verdrängung Re eine Schleife bildet, welche um so geschlossener ist, wie der Kompressionssatz hoch ist (oder das Verhältnis der absoluten Drucke Verdrängung über Ansaugung), und welche ungefähr in der Waagerechten, auf der Ansaugseite As endet.
  4. Exzenterschnecke nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass der Rotor durch eine orbitale Bewegung animiert wird, wobei jede seiner Spitzen einen gleichen außenmittigen Kreis E schlägt und einen gleichen Winkel zu demselben Augenblick mit ihrem Ausgangspunkt hat, wobei der besagte Rotor durch zwei identische Wellen mit parallelen Achsen, in der Drehung synchronisiert mittel Exzenterscheiben eines selben Radius E angetrieben wird.
  5. Exzenterschnecke nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die Hülse des feststehenden Stators (2) die Hülle der aufeinanderfolgenden Stellungen des Rotors (1) in seiner Bewegung ist, d.h. die Hülle der Kreise mit Radien, welche der Außenmittigkeit E gleichen, erhöht durch die Hälfte der Dicke der Rotorschaufeln, deren Zentren auf der Mittelachse dieser Schaufel gleiten.
  6. Exzenterschnecke nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass die beiden Spiralen des Rotors (1) aus Kreisbögen (C0, C1, C2, C3, ...) bestehen können, um die Abmessungsberechnungen und die Fertigungsprüfungen zu vereinfachen und wobei das Innere der Hülse des Stators (2) dabei durch Kreisbögen (C'0, C'1, C'2, C'3, ... und C"0, C"1, C"2, C"3, ...) bestimmt wird, welche zu denen des Rotors konzentrisch sind, wobei alle diese Kreise vorzugsweise gemeinsame Tangenten an ihren Anschlussstellen haben.
  7. Exzenterschnecke nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass mehrere einfache oder auf ein, zwei oder drei Drucketagen übereinanderliegende Grundzellen in einer einzigen Druckkammer (Kompressoren mit niedrigem, mittlerem oder hohem Druck) oder einer Vakuumkammer zusammengeordnet sind, wobei Zwischenkühler die verschiedenen Etagen der Kompressoren so trennen, dass übermäßige Temperaturen und hitzebedingte Verformungen vermieden werden.
  8. Exzenterschnecke nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die Hülsen entgegengesetzt angeordnet werden können, um die Reaktionen auf den Stufen zu vermindern.
  9. Exzenterschnecke nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass das Verhältnis zwischen dem Radius R der am weitesten vom Zentrum Ω entferntesten Wand des Stators zur Außenmittigkeit dem Verhältnis der Höchstgeschwindigkeit der Luft in der Hülse zur orbitalen Geschwindigkeit jeglicher Rotorenspitzen gleicht, und 10 überschreiten kann.
  10. Exzenterschnecke nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass die Antriebswellen die Druckkammer ganz oder teilweise durchqueren.
  11. Exzenterschnecke nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, dass zwei Rotoren eines selben seitlichen Profils Rücken an Rücken oder von einander entfernt gegenübergestellt werden, um jeglichen, axialen Stoß zu vermeiden.
  12. Exzenterschnecke nach einem der Ansprüche 1 bis 11, dadurch gekennzeichnet, dass die Rotoren radial durch außerhalb der Druckkammer angeordnete Gegengewichte ausgeglichen werden.
  13. Exzenterschnecke nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, dass die Kompressoren oder Vakuumpumpen nur Luft oder trockene Gase komprimieren.
  14. Exzenterschnecke nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, dass die Kompressoren oder Vakuumpumpen mit Einspritzen einer Flüssigkeit vor oder während der Kompression oder mit der Schmierung der Kompressionskammer funktionieren.
  15. Exzenterschnecke nach einem der Ansprüche 1 bis 14, dadurch gekennzeichnet, dass der Kurvenradius der Mittellinie des Rotors allmählich von jedem Ende aus zunimmt, bis zu einem Zwischenbereich.
EP00966206A 1999-09-29 2000-09-27 Spiralverdichter Expired - Lifetime EP1216358B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9912143A FR2798967B1 (fr) 1999-09-29 1999-09-29 Capsulisme pour machine tournante vehiculant un fluide gazeux et pouvant fonctionner en compresseur ou en pompe a vide
FR9912143 1999-09-29
PCT/FR2000/002669 WO2001023761A1 (fr) 1999-09-29 2000-09-27 Compresseur ou en pompe a vide a spirales

Publications (2)

Publication Number Publication Date
EP1216358A1 EP1216358A1 (de) 2002-06-26
EP1216358B1 true EP1216358B1 (de) 2004-03-10

Family

ID=9550370

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Application Number Title Priority Date Filing Date
EP00966206A Expired - Lifetime EP1216358B1 (de) 1999-09-29 2000-09-27 Spiralverdichter

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EP (1) EP1216358B1 (de)
AT (1) ATE261547T1 (de)
AU (1) AU7667700A (de)
DE (1) DE60008896D1 (de)
FR (1) FR2798967B1 (de)
WO (1) WO2001023761A1 (de)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2674515A1 (de) 2012-06-11 2013-12-18 Siemens Aktiengesellschaft Temperaturregelung eines Hochtemperatur-Elektrolyseurs
WO2013185994A1 (de) 2012-06-11 2013-12-19 Siemens Aktiengesellschaft Temperaturregelsystem für eine hochtemperatur-batterie bzw. einen hochtemperatur-elektrolyseur

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1378065A (en) * 1920-08-31 1921-05-17 Varley Cromwell Hanford Rotary engine or pump
US1967957A (en) * 1933-05-01 1934-07-24 Nat Electrical Supply Company Vacuum pump
FR825643A (fr) * 1936-11-26 1938-03-09 Perfectionnements au capsulisme à excentrique
JPS5990789A (ja) * 1982-11-16 1984-05-25 Nippon Soken Inc スクロ−ル型ポンプ
US4606711A (en) * 1983-01-10 1986-08-19 Nippon Soken, Inc. Fluid pump with eccentrically driven C-shaped pumping member
JPS59141786A (ja) * 1983-02-02 1984-08-14 Nippon Soken Inc リング型ポンプ
JPH0235159B2 (ja) * 1983-02-09 1990-08-08 Nippon Jidosha Buhin Sogo Kenkyusho Kk Ringugatahonpu
DE4215038A1 (de) * 1992-05-07 1993-11-11 Bitzer Kuehlmaschinenbau Gmbh Spiralverdichter für kompressible Medien
US5318424A (en) * 1992-12-07 1994-06-07 Carrier Corporation Minimum diameter scroll component
JPH06323277A (ja) * 1993-05-12 1994-11-22 Mitsubishi Heavy Ind Ltd スクロール流体機械
JPH07317667A (ja) * 1994-05-26 1995-12-05 Sanden Corp スクロール型コンプレッサ
DE29603280U1 (de) * 1996-02-23 1996-04-11 Walter, Jürgen, 07318 Saalfeld Maschine zur Aufladung von Verbrennungsmotoren
DE19614477A1 (de) * 1996-04-12 1997-10-16 Juergen Walter Drehkolbenmaschine

Also Published As

Publication number Publication date
DE60008896D1 (de) 2004-04-15
FR2798967B1 (fr) 2001-11-23
AU7667700A (en) 2001-04-30
FR2798967A1 (fr) 2001-03-30
ATE261547T1 (de) 2004-03-15
EP1216358A1 (de) 2002-06-26
WO2001023761A1 (fr) 2001-04-05

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