EP0462924A1 - Machine de déplacement de fluide du type à spirales - Google Patents

Machine de déplacement de fluide du type à spirales Download PDF

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Publication number
EP0462924A1
EP0462924A1 EP91810344A EP91810344A EP0462924A1 EP 0462924 A1 EP0462924 A1 EP 0462924A1 EP 91810344 A EP91810344 A EP 91810344A EP 91810344 A EP91810344 A EP 91810344A EP 0462924 A1 EP0462924 A1 EP 0462924A1
Authority
EP
European Patent Office
Prior art keywords
displacement
spiral
bodies
disc
cooperating
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.)
Granted
Application number
EP91810344A
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German (de)
English (en)
Other versions
EP0462924B1 (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 EP0462924A1 publication Critical patent/EP0462924A1/fr
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Publication of EP0462924B1 publication Critical patent/EP0462924B1/fr
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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
    • F01C1/023—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 where both members are moving
    • F01C1/0238—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 where both members are moving with symmetrical double wraps

Definitions

  • the invention relates to a displacer for compressible media, in which a plurality of interlocking, spiral-like displacers are arranged in a fixed manner in a fixed housing, the displacers being held in each case on an eccentrically drivable disk such that during operation each point of a displacer delimits one from the cooperating displacer Performs circular movement, and wherein the curvature of the two spiral displacement bodies is dimensioned such that they almost touch the opposite circumferential walls of the other displacement body on at least one sealing line continuously progressing during operation, and the displacement bodies with their free end faces seal against the opposite disk.
  • the invention is therefore based on the object of providing a displacement machine of the type mentioned at the outset, which combines the advantages of the two machine types discussed and which, moreover, has a smaller overall volume with the same delivery rate.
  • each disc carries at least on one of its two sides two symmetrically arranged displacement bodies which are offset by 180 ° relative to one another, the cooperating spiral displacement bodies of both discs having a different wrap angle, in such a way that that displacement body, which acts as the delivery chamber acts, both the radially outermost and the radially innermost spiral section in the system and thus has the larger wrap angle.
  • FIG. 2 It can be seen from FIG. 2 and in particular from FIG. 3 that the example shown is a machine with two parallel floods.
  • This has the advantage that a disk common to both floods is provided with the working elements of the left as well as the right flood (according to FIG. 3). With this configuration, not only one disc but also support bearings can be saved, as will be explained later.
  • the "middle" rotor of the machine resulting due to the double flow design is designated as a whole.
  • the spirals themselves are composed of a plurality of adjoining ones according to FIG Arcs are formed and loop around an angle of 360 °. These are the spiral strips which are shown in black in FIG. 1 and which are arranged on the only partially recognizable middle pane 2. Only partially recognizable because, for better clarity and better understanding because of FIG.
  • a double eccentric system is provided for driving and guiding rotor 1.
  • a first hub is designated with which the disc 2 is mounted on a rolling bearing, not shown. This bearing sits on an eccentric 9, which in turn is part of a first double eccentric shaft 10.
  • a second hub is designated with which the disc 2 is mounted on a rolling bearing, not shown. This bearing sits on an eccentric 12, which in turn is part of a second double eccentric shaft 13.
  • the two hubs 8 and 11 are arranged on the periphery of the disk 2, specifically in those zones which are not occupied by the spirals.
  • the respective disks 6 and 7 are provided on the two “lateral" runners 4 and 5 on only one of their sides with two spiral bodies displaced by 180 ° to one another. These consist of strips 14a, 14b, which are held vertically on the disks 6 and 7.
  • the spirals themselves are likewise formed from a plurality of circular arcs connected to one another (shown by hatching); Of course, they must have the same geometry as the strips 3a and 3b in order to be able to cooperate with them.
  • the condition must of course also be met here that the displacement of the two spirals and their arrangement on the disk is such that the connecting axis of the centers of the spirals coincides with the connecting axis of the centers of the associated drive or.
  • Leading eccentric in the focus of the respective disc 6 or Cross 7. Due to the distance chosen in the example of the spirals 14a and 14b offset by 180 °, they touch each other over their circumference for a certain distance, specifically at that geometrical point in which the center of gravity of the disk 6 and 6, respectively. 7 lies.
  • the spirals 14a and 14b loop around an angle of 720 °. From a purely static perspective, it can thus be seen in FIG. 1 that the hatched spiral 14 actually forms a conveying space for the black spiral 3. For this reason, the spiral 14 must represent the radially outermost part at the entry of the spiral system and, accordingly, also represent the radially innermost part at the exit of the spiral system. Only in this way can the spiral 14 completely encompass the inner spiral 3 on the occasion of the orbital movement, which explains the different wrap angles . Both the adjoining inner parts of the two spirals 14a and 14b and their adjoining outer parts thus have an S shape. This arrangement prevents vibrations of the air column when entering the spirals.
  • any oil is thrown off the orbiting displacers.
  • the two double eccentric shafts 10 and 13 are supported in a conventional manner, not shown, in the two side housing halves 19a and 19b.
  • the two lateral housing halves are connected to one another at their periphery by a housing jacket 20 via fastening means, not shown.
  • this jacket Since this jacket is not exposed to any significant stress due to its bilateral (inside and outside) exposure to only atmospheric pressure, it must be dimensioned as a bare outer skin.
  • the drive and the guide of the rotor 1, 4 and 5 accordingly provide the two spaced eccentric arrangements 9, 10, 16 and. 12, 13, 18.
  • the two shafts 10 and 13 penetrate one of the side housing halves; they are each provided with a toothed belt pulley 21, 22 at their projecting ends.
  • the two toothed belt pulleys are in the same vertical plane. It goes without saying that only one of the two shafts has to be connected to a drive, not shown.
  • the two eccentric arrangements are synchronized with precise angles so that the runners can be clearly guided on the occasion of the orbital movement in the dead center positions. This is done here by merging the actual drive with a toothed belt 23.
  • the toothed belt drive can also be designed as a belt tensioner.
  • the two "conveying spaces”, each offset by 180 °, can be designated in FIG. 1 by 24a and 24b. They each run from an inlet 25a, 25b formed on the outer circumference of the spiral 14a, 14b to an outlet 26a, 26b provided in the spiral interior.
  • the displacement bodies 3a, 3b engage in these conveying spaces, the curvature of which is dimensioned such that the strips almost touch the inner and outer boundary walls of the respective conveying space at a plurality, for example at two points each.
  • the double eccentric drive ensures that all points of the runners and thus all points of the slats perform a circular displacement movement.
  • the double eccentric drive ensures that all points of the runners and thus all points of the slats perform a circular displacement movement.
  • a breakthrough 27 is provided in each of the two inner spiral ends in the middle disk 2 so that the medium can get from one disk side to the other, ie in the case shown from the right tide to the left tide, in a central outflow 28 arranged only on one side (Fig.3) to be subtracted.
  • the disk 6 of the left runner must of course also be provided with a central opening 29. This opening 29, however, requires sealing measures of the disk 6 against the adjacent lateral one Housing part 19a in order to avoid that the spiral outlet is short-circuited with the spiral inlet.
  • the sealing problem is of paramount importance in this type of machine. It goes without saying that not only the radial sealing of the strips 3a, 3b against the strips 14a, 14b, i.e. the closure of the conveying spaces 24a, 24b in the circumferential direction is important.
  • the axial tightness of the delivery rooms is also important.
  • the ledges of one runner must lie with their end faces against the disks of the opposite, cooperating runner. Sealing takes place on the basis of actual sliding layers 30 (FIGS. 2 + 3) made of, for example, PTFE, which are applied at the required points on the pane sides and only there by suitable means. Since the increasing pressure against the interior of the spiral tends to push the cooperating runners apart, countermeasures must be taken.
  • the lateral rotor 5 is sealed against the housing half 19b by means of a fixed sliding seal 31.
  • This seal designed as a ring, is inserted into a corresponding groove in the housing half 19b and is therefore not subject to the translatory movement.
  • the space 32 within the ring is acted upon by the pressure of the working medium at the outlet, which reaches the rear via a bore 33 in the disk 7. Outside the ring acts on the back of the disc 7 that pressure that prevails in the inlet, ie the atmospheric pressure.
  • This provision can be, for example, a spring-supported sliding ring 34, which is additionally configured such that it seals the outlet side against the inlet side.
  • the spring provides the necessary contact pressure to hold the lateral rotor 4 against the middle rotor 1, the latter against the lateral rotor 5 and the latter against the housing half 19b.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP91810344A 1990-06-20 1991-05-06 Machine de déplacement de fluide du type à spirales Expired - Lifetime EP0462924B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH2047/90 1990-06-20
CH204790 1990-06-20

Publications (2)

Publication Number Publication Date
EP0462924A1 true EP0462924A1 (fr) 1991-12-27
EP0462924B1 EP0462924B1 (fr) 1993-07-21

Family

ID=4224698

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91810344A Expired - Lifetime EP0462924B1 (fr) 1990-06-20 1991-05-06 Machine de déplacement de fluide du type à spirales

Country Status (4)

Country Link
US (1) US5154591A (fr)
EP (1) EP0462924B1 (fr)
JP (1) JPH05126077A (fr)
DE (1) DE59100205D1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE174074C (fr) *
GB868187A (en) * 1958-09-12 1961-05-17 Alsacienne Constr Meca Improvements in or relating to rotary machines, such as rotary engines and pumps
DE2603462C2 (de) * 1975-02-07 1982-03-04 Aginfor AG für industrielle Forschung, Baden Rotationskolbenmaschine für kompressible Medien
DE3141525A1 (de) * 1981-10-20 1983-05-11 Volkswagenwerk Ag, 3180 Wolfsburg Verdraengermaschine fuer kompressible medien

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US801182A (en) * 1905-06-26 1905-10-03 Leon Creux Rotary engine.
CH555476A (de) * 1972-08-31 1974-10-31 Aginfor Ag Verdraengermaschine.
JPS5776202A (en) * 1980-10-30 1982-05-13 Ebara Corp Scroll type machine
JPH0646032B2 (ja) * 1985-02-25 1994-06-15 株式会社日立製作所 容積形オイルフリ−式ガス圧送ポンプ
JPH02115587A (ja) * 1988-10-25 1990-04-27 Sanden Corp うず巻き体流体装置におけるクリアランス調整方法

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE174074C (fr) *
GB868187A (en) * 1958-09-12 1961-05-17 Alsacienne Constr Meca Improvements in or relating to rotary machines, such as rotary engines and pumps
DE2603462C2 (de) * 1975-02-07 1982-03-04 Aginfor AG für industrielle Forschung, Baden Rotationskolbenmaschine für kompressible Medien
DE3141525A1 (de) * 1981-10-20 1983-05-11 Volkswagenwerk Ag, 3180 Wolfsburg Verdraengermaschine fuer kompressible medien

Also Published As

Publication number Publication date
JPH05126077A (ja) 1993-05-21
EP0462924B1 (fr) 1993-07-21
US5154591A (en) 1992-10-13
DE59100205D1 (de) 1993-08-26

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