EP0560009A1 - Machine à déplacement positif selon le principe de la spirale - Google Patents

Machine à déplacement positif selon le principe de la spirale Download PDF

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Publication number
EP0560009A1
EP0560009A1 EP93100202A EP93100202A EP0560009A1 EP 0560009 A1 EP0560009 A1 EP 0560009A1 EP 93100202 A EP93100202 A EP 93100202A EP 93100202 A EP93100202 A EP 93100202A EP 0560009 A1 EP0560009 A1 EP 0560009A1
Authority
EP
European Patent Office
Prior art keywords
spiral
inlet
disc
displacement machine
machine according
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.)
Withdrawn
Application number
EP93100202A
Other languages
German (de)
English (en)
Inventor
Roland Kolb
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.)
ABB Asea Brown Boveri Ltd
ABB AB
Original Assignee
ABB Asea Brown Boveri Ltd
Asea Brown Boveri AB
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 ABB Asea Brown Boveri Ltd, Asea Brown Boveri AB filed Critical ABB Asea Brown Boveri Ltd
Publication of EP0560009A1 publication Critical patent/EP0560009A1/fr
Withdrawn legal-status Critical Current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
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines 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
    • F01C1/0207—Rotary-piston machines or engines 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
    • F01C1/0246—Details concerning the involute wraps or their base, e.g. geometry

Definitions

  • Displacement machine for compressible media with a plurality of spiral conveying spaces arranged in a fixed housing, which lead from a radially outer inlet to a radially inner outlet, and with a displacer assigned to the conveying spaces, essentially consisting of a disk with spiral strips arranged vertically on both sides, the eccentrically driven displacement body executes a circular movement delimited by the circumferential walls of the delivery chamber with each of its points during operation.
  • Displacement machines of the spiral type are known for example from DE-C-26 03 462.
  • a compressor constructed according to this principle is characterized by an almost pulsation-free delivery of the gaseous working medium, which consists, for example, of air or an air / fuel mixture and could therefore also be used with advantage for charging purposes of internal combustion engines.
  • the gaseous working medium which consists, for example, of air or an air / fuel mixture and could therefore also be used with advantage for charging purposes of internal combustion engines.
  • a machine of the type mentioned at the outset, in which the spirals span a total wrap angle of approximately 360 °, is known from EP-A-0 321 781.
  • Such a machine has one of the number of nested in the displacer body at the inlet-side ends of the spirals Spirals corresponding number of discontinuities in the radial extension of the center disc. The discontinuity is increased in the axial direction by the spiral strips.
  • the temperature of the working fluid increases due to the increasing compression.
  • the center disk has a higher temperature in its hub section than in its outer area at the inlet-side end of the spirals. If the displacement body is made of a commercially available material with a coefficient of thermal expansion greater than zero, this temperature distribution creates tensile stresses in the outer area of the disk and compressive stresses in the hub area.
  • the geometric discontinuities mentioned and the temperature profile result in a stress concentration in the inlet area of the pane and thus an increased material stress.
  • the displacement body is therefore preferably made of a light metal alloy, for example magnesium.
  • Such alloys have quite good strength values at room temperature; however, these good values drop rapidly at higher temperatures when it comes to commercially available alloys without costly additives.
  • the object of the invention is to constructively modify a displacement machine of the type mentioned at the beginning in such a way that the stress concentration in the inlet area of the displacement disk is considerably reduced becomes.
  • clamping flap is dimensioned thinner than the disk or the immediately adjacent disk extension. This allows a further reduction of the tensile stresses in the outlet of the groin ends, since a thin clamping tab is more elastic than a thick-walled version.
  • the rotor of the machine as a whole is designated by 1 in FIG. 2.
  • Arranged on both sides of the disk 2 are two, displaced, mutually offset by 180 °, spirally extending bodies. These are strips 3a, 3b which are held vertically on the pane 2.
  • the spirals themselves are formed from a plurality of circular arcs adjoining one another. 4 with the hub is designated, via which the disc 2 with a roller bearing 22 is seated on an eccentric disc 23 (FIG. 3). This disk is in turn part of the main shaft 24.
  • the guide eye 5 of the guide eccentric arrangement is connected to the runner via a bow-shaped 21 rib.
  • the eye lies in the tangential extension of the inlet side End of the spiral bar 3a.
  • FIG. 1 shows the housing half 7b shown on the right in FIG. 3 of the machine housing which is composed of two halves 7a, 7b and is connected via fastening eyes 8 (FIG. 3) for receiving screw connections.
  • 11a and 11b denote the two delivery spaces, each offset by 180 °, which are worked into the two housing halves in the manner of a spiral slot. They each run from an inlet 12a, 12b arranged on the outer circumference of the spiral in the housing to an outlet 13 provided in the interior of the housing and common to both delivery spaces. They have essentially parallel cylinder walls 14a, 14b, 15a, 15b arranged at a constant distance from one another. which, like the displacement bodies of the disk 2, comprise a spiral of 360 °.
  • the displacement bodies 3a, 3b engage, the curvature of which is dimensioned such that the strips almost touch the inner and outer cylinder walls of the housing at several, for example at two points each.
  • seals 49 are inserted in corresponding grooves. With them, the working rooms against the side walls of the housing respectively. sealed against the displacement disc.
  • FIG. 1 also shows that the disc 2 - apart from the radially protruding eye 5 - closes radially with the strips 3a, 3b.
  • the disk has to penetrate at least one half of the housing in the radial direction in the area of the inlets 12a, 12b. In the present case, this is done on the housing half 7 shown on the left in FIG.
  • This measure has the advantage that, in this housing half, sealing strips are only to be arranged on the inner webs 46a, 46b, which seal the delivery spaces 11a, 11b against one another via the disk 2 up to the outlet.
  • this transition is now designed as a circular shoulder 47a, 47b with the radius R1.
  • the counter surface on the disk 2 is provided with a corresponding circular arc-shaped recess 48a, 48b, the radius R2 of this recess corresponding to the eccentricity e + radius R1.
  • the discontinuity in the radial extent of the center disk 2 is locally displaced and that is brought forward. This means that the disc in the The area of the inlet 12a, 12b of the spiral strips 3a, 3b is extended beyond the spiral inlet.
  • the dimension A of the extension 2a, 2b corresponds at least to the simple inside width B between two adjacent, nested spirals in the inlet area.
  • the dimension A of the disk extension 2a, 2b is significantly larger than the clear width B between two adjacent, nested spirals - which clear width also corresponds to that of the associated conveying spaces - for the following reason:
  • the spirals span a wrap angle of a total of 360 °, the majority of which are formed with a first curvature and have a significantly smaller radius of curvature on the outlet side over an angular range of approximately 45 °.
  • This shortening of the spiral enables the passage windows 6 ′ to be arranged in the pane 2. These windows are now located approximately in the radial plane of the inlet area of the pane which is at risk from the stress concentration.
  • the minimum dimension by which the pane protrudes beyond the inlet area is not measured from the inlet edge of the spiral, but from the plane which marks the narrowest cross section between the passage window 6 'and discontinuity in the pane transition. In the present case, this is the radial plane C.
  • a minimum dimension A for the extension 2a, 2b which is greater than the clear width B of the associated delivery area.
  • the disk extensions 2a, 2b are provided radially on the outside with a material accumulation, which form clamping tabs 50a, 50b for the mechanical processing of the rotor.
  • These clamping tabs are thinner than the disc 2 (Fig. 4 and 5). As a result, they are not touched by the milling tool, which is usually used on both sides of the wheel. The pore-free cast skin thus remains unprocessed and does not form a starting point for possible crack formation.
  • the spiral strips 3a, 3b run into the pane extension 2a, 2b at their ends on the entry side, the outlet 51a, 51b opening into the clamping tabs 50a, 50b (FIG. 5).
  • This outlet 51a, 51b of the strip ends is dimensioned thinner than the strips 3a, 3b. The fact that the end edges of the strips do not run perpendicular to the pane, but rather at an angle to them, gives the free-standing ends of the strips greater stability.
  • the said slope has a curvature and opens into the clamping tabs 50a, 50b with a very flat transition angle ⁇ .
  • This extension of the foot area of the strips in the circumferential direction thus ends in an unprocessed area. This has a favorable effect on the reduction of the tensile stresses which arise due to the temperature gradient present in the radial direction during operation.
  • the clamping tab 50a is located radially inside the rib 21, which defines the limits of its geometric extension. It has a smaller mass than the opposing clamping tab 50b. This is achieved in that the latter is dimensioned larger in the tangential direction with the same thickness. With this measure you have a simple means in hand to make a mass balance for the rib 21 based on the dimensioning of the flap 50b. This is advantageous for the sake of relieving the guiding intervention provided in eye 5.
  • the drive and the guide of the rotor 1 are provided by the two spaced-apart eccentric arrangements 23, 24 and. 26, 27.
  • the main shaft 24 is supported in a roller bearing 17 and a slide bearing 18. At its end protruding from the housing half 7b, the shaft is provided with a V-belt pulley 19 for the drive.
  • Counterweights 20 are arranged on the shaft in order to compensate for the inertial forces arising when the rotor is eccentrically driven.
  • the guide shaft 27 is inserted in a sliding bearing 28 within the housing half 7b.
  • the two eccentric arrangements are synchronized with precise angles. This is done via a toothed belt drive 16.
  • the double eccentric drive ensures that all points of the rotor disk and thus also all points of the two strips 3a, 3b perform a circular displacement movement.
  • crescent-shaped workrooms enclosing the working medium result on both sides of the strips, which are displaced by the delivery chambers during the drive of the rotor disk in the direction of the outlet. The volumes of these working spaces are reduced and the pressure of the working fluid is increased accordingly.
  • the invention is not limited to the exemplary embodiment shown and described.
  • the new measure can be used just as advantageously for positive-displacement runners whose disc does not end on the outside with the strips, but where the center disc forms a sealing surface projects beyond the strips in diameter, as is the case, for example, in the aforementioned DE-C-26 03 462.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP93100202A 1992-03-13 1993-01-08 Machine à déplacement positif selon le principe de la spirale Withdrawn EP0560009A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19924207984 DE4207984A1 (de) 1992-03-13 1992-03-13 Verdraengermaschine nach dem spiralprinzip
DE4207984 1992-03-13

Publications (1)

Publication Number Publication Date
EP0560009A1 true EP0560009A1 (fr) 1993-09-15

Family

ID=6453948

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93100202A Withdrawn EP0560009A1 (fr) 1992-03-13 1993-01-08 Machine à déplacement positif selon le principe de la spirale

Country Status (3)

Country Link
EP (1) EP0560009A1 (fr)
JP (1) JPH0610860A (fr)
DE (1) DE4207984A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009023974A1 (fr) * 2007-08-22 2009-02-26 Spinnler Engineering Machine de refoulement hélicoïdale
ITRN20090011A1 (it) * 2009-03-06 2010-09-07 Leonardo Battistelli Spirale rotante

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09265623A (ja) * 1996-03-29 1997-10-07 Tdk Corp 磁気記録媒体
US6214448B1 (en) 1998-03-31 2001-04-10 Tdk Corporation Magnetic recording medium
DE102007043674B4 (de) * 2007-09-13 2009-11-12 Handtmann Systemtechnik Gmbh & Co. Kg Spiralverdichter mit Doppelspirale
DE102008026601A1 (de) 2008-06-03 2009-12-10 Schaeffler Kg Spiralverdrängermaschine für ein kompressibles Arbeitsmedium
DE102010025986A1 (de) * 2010-07-02 2012-01-05 Handtmann Systemtechnik Gmbh & Co. Kg Ladevorrichtung zur Verdichtung von Ladeluft

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0321781A1 (fr) * 1987-12-21 1989-06-28 BBC Brown Boveri AG Machine de déplacement de fluide du type à spirale
EP0392975A1 (fr) * 1989-04-08 1990-10-17 AGINFOR AG für industrielle Forschung Suralimentateur rotatif à spirales pour milieux compressibles
EP0545188A1 (fr) * 1991-12-05 1993-06-09 AGINFOR AG für industrielle Forschung Machine de déplacement de fluide de type à spirale

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3535309A1 (de) * 1984-10-12 1986-04-24 Volkswagen AG, 3180 Wolfsburg Verdraengermaschine fuer kompressible medien
DE3800931A1 (de) * 1987-01-24 1988-08-04 Volkswagen Ag Verdraengermaschine fuer kompressible medien
CH673874A5 (fr) * 1987-03-24 1990-04-12 Bbc Brown Boveri & Cie
DE3839252A1 (de) * 1988-11-21 1990-05-23 Asea Brown Boveri Verdraengermaschine nach dem spiralprinzip

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0321781A1 (fr) * 1987-12-21 1989-06-28 BBC Brown Boveri AG Machine de déplacement de fluide du type à spirale
EP0392975A1 (fr) * 1989-04-08 1990-10-17 AGINFOR AG für industrielle Forschung Suralimentateur rotatif à spirales pour milieux compressibles
EP0545188A1 (fr) * 1991-12-05 1993-06-09 AGINFOR AG für industrielle Forschung Machine de déplacement de fluide de type à spirale

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009023974A1 (fr) * 2007-08-22 2009-02-26 Spinnler Engineering Machine de refoulement hélicoïdale
CN101784754B (zh) * 2007-08-22 2012-07-25 斯宾勒工程公司 按照螺旋原理的挤压机
US8425211B2 (en) 2007-08-22 2013-04-23 Spinnler Engineering Positive displacement machine according to the spiral principle
ITRN20090011A1 (it) * 2009-03-06 2010-09-07 Leonardo Battistelli Spirale rotante

Also Published As

Publication number Publication date
DE4207984A1 (de) 1993-09-16
JPH0610860A (ja) 1994-01-21

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