EP0031002B1 - Machine rotative avec deux axes non parallèles l'un par rapport à l'autre - Google Patents

Machine rotative avec deux axes non parallèles l'un par rapport à l'autre Download PDF

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Publication number
EP0031002B1
EP0031002B1 EP80105799A EP80105799A EP0031002B1 EP 0031002 B1 EP0031002 B1 EP 0031002B1 EP 80105799 A EP80105799 A EP 80105799A EP 80105799 A EP80105799 A EP 80105799A EP 0031002 B1 EP0031002 B1 EP 0031002B1
Authority
EP
European Patent Office
Prior art keywords
disc rotor
rotor
housing
working space
groove
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
Application number
EP80105799A
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German (de)
English (en)
Other versions
EP0031002A1 (fr
Inventor
Wolfhart Dipl.-Phys. Willimczik
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.)
Willimczik Wolfhart Dipl-Phys
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to AT80105799T priority Critical patent/ATE24346T1/de
Publication of EP0031002A1 publication Critical patent/EP0031002A1/fr
Application granted granted Critical
Publication of EP0031002B1 publication Critical patent/EP0031002B1/fr
Expired legal-status Critical Current

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    • 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
    • F01C3/00—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members
    • F01C3/06—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees

Definitions

  • the invention relates to an angular-axis rotary piston machine with an axially vane rotor rotor arranged rotatably in a housing and a disk rotor having radial slots, the axes of rotation of which enclose an acute angle, the vanes reaching through the slots of the disk rotor and on the walls of the working space, from the Disc rotor is covered, run along, the outer diameter of the disc rotor is larger than the outer diameter of the vane rotor. It can be used as a pump, compressor, compressed air or hot gas engine, flow meter, hydrostatic coupling or retarder.
  • the object of the invention is to eliminate these disadvantages.
  • the aim is to simplify the rotary piston machine mentioned at the beginning and to solve the sealing problem so well that it is not only superior to all other rotary piston machines, but can even compete with the reciprocating piston system in terms of tightness.
  • the sealing problem can only be completely solved on one side of the disc rotor, the work area above the disc rotor is initially dispensed with.
  • the sealing lines on the disc rotor can be placed from its center plane in its end face, which at the same time forms a contact surface with the groove edges.
  • all sealing lines then lie in the plane of contact between the disc rotor and the obliquely cut groove edges.
  • the cross-section of the slits is V-shaped in such a way that the narrowest point lies in the plane of contact or surface so that the sealing lines on the groove edge, the wings and the slits converge exactly at one point.
  • Angular-axis rotary piston machines with vane rotor and disk rotor with only one-sided working space are known per se from DE-C-8 263 381 and GB-A-967 636.
  • the walls of the slots are slightly more inclined than the two axes of rotation to each other.
  • the wings also incline in the slots, which is why they are longer than the wings in the radial direction are wide.
  • a two-stage displacement machine can easily be implemented without increasing the number of moving parts by accommodating several or two coaxial axial ring grooves in the side of the housing.
  • the blades rotate here on different sized concentric circles.
  • the advantage here is that the cross-sectional shape, but above all the size of the two work rooms can be made different independently of one another.
  • Cylindrical walls can now be used as easy-to-produce walls due to the lack of radial blow holes.
  • (Claim 3) On the other hand, a simple automatic adjustment option with even sliding sealing for the wings relative to the walls of the work area is obtained if the cross-section of the annular groove tapers towards the floor, e.g. the lateral walls are conical surfaces or the annular groove is toroidal. If you press the axially displaceable vane rotor against the groove base, for example by an axially working spring (the delivery pressure itself could also generate pressure), the vanes have a very good sealing effect and wear is automatically compensated. (Claim 8) This pressure can, if you want, even during the operation of the machine, be set to the desired level (including zero pressure) and remains independent of the speed and the delivery pressure!
  • the bottom of the ring groove can, because its cross-sectional shape is also freely selectable, e.g. be frustoconical. If the oblique angle of this cone coincides with the angle between the two axes of rotation and if the cone tip of the completed cone lies at the intersection of the two axes of rotation in the inclined plane, the surface of the bottom of the annular groove merges with the oblique plane of the housing at a circumferential point, So where the ring groove is interrupted, that is, the fixed separation point between the suction and pressure chamber. In this case there is no dead volume.
  • the sloping groove edges can in any case be milled to such an extent that in a more or less long circumferential area (this length is basically also arbitrary) the cross section of the ring groove disappears completely. Since the disc rotor only has a sealing function in the circumferential direction at this circumferential point, where there is no ring groove at all, it is clear that its shape can also be selected independently of the shape of the ring groove.
  • the surface of the disc rotor located on the housing wall can e.g.
  • the number of wings is basically arbitrary and can be adapted to the respective problem. For good tightness in the slots, however, it must be taken into account that even fixed angles between the vanes in the oblique disc rotor plane constantly change somewhat depending on the angle of rotation. (For an observer in the disk rotor plane, the penetration points of rigid wings through the disk rotor move back and forth somewhat.) To solve this problem, only movable seals or elastic wings have been proposed so far, which makes this machine unsuitable for many applications. The simplest and best solution is of course the one in which these shifts do not occur. This is exactly the case with a wing spacing of 180 °, because this is the only angle (except 0 °) that remains invariant when projected onto an inclined plane, i.e. it does not change. (A straight line remains a straight line for any projection onto another plane). So if you only use two diametrically positioned wings, the problem is completely solved and the seal in the slots is good. (Claim 7)
  • This principle has a very high variability and can meet all conditions for the applications already mentioned.
  • Figs. 1 and 2 shows e.g. a simple pump.
  • the power unit is the vane rotor 4, which is rigidly connected to the shaft 3. It consists of a disk-shaped base body 4a, to which four vanes 13 are rigidly fastened on a concentric circle, which completely fill the cross section of the annular or working space 11.
  • the disc rotor 7 has only a sealing function; it lies on the inclined plane 6 with its flat end face 7d and seals the working space 11 towards the open side at least on the pressure or suction side and is carried along by the wings 13 which penetrate it through the radial slots 14.
  • the working space is worked into the housing part 1 in the form of an annular groove 11 with cylindrical wall parts 11b, 11c and a cone-shaped groove bottom 11a and is delimited at the top by the inclined plane 6, which is just inclined so that the inclined plane 6 in at a circumferential point 11e the surface of the groove base 11a merges where a linear or areal seal is created between the suction and pressure chamber.
  • the axes of rotation and symmetry 9, 10 of the disk rotor 7 and vane rotor 4 intersect at the intersection S in the inclined plane 6 and form an acute angle a.
  • the disc rotor 7 is held on the surface 6 by a retaining screw 8. In operation, it is already pressed on the suction side onto surface 6 by the pressure prevailing in space 5, which is sufficient for sealing.
  • the slots 14 of the planar disk rotor 7 are cross-sectioned in a V-shape in order to intercept the angle of rotation of the blades 13, which is dependent on the angle of rotation, and to prevent blowholes from being created.
  • FIG. 2 shows a plan view of the division of the annular space or the annular groove 11 or the working space.
  • the actual conveying area is 13 90 ° long with four blades 13. This is followed on both sides by large-area inlet and outlet channels 12a, b, which extend as far as the separation point 11e.
  • FIG. 3 shows the longitudinal section of a pump similar to the first, only that the surface 6 of the housing part 1 is formed by an obliquely lying cone and the end face 7d of the disk rotor 7 is correspondingly conical.
  • the bottom 11 of the annular space 11 is flat and touches a surface line of the conical disk rotor 7 at a circumferential point. If one wishes to dispense with elastic slot edges, the other two rigid vanes 13b must be compared with the first rigid diametrical pair of vanes 13a via circumferentially elastic arms 13 Connect 'b to the remaining vane rotor 4 or shaft 3.
  • the two wings 13b can then follow the displacements of the slots 14.
  • the seal 15 of Fig.5-7 consists of two plates 15a, b, which form the slot edges in a recess of the disc rotor 7 in the slot 14, are elastically connected by two arcuate parts 15c and otherwise have so much play together in the circumferential direction that they can follow the displacements of the slots 14.
  • the seal 15 'of Figures 8 and 9 is housed in a circular recess in the disc rotor 7.
  • Two half disks 15'a and 15'b are stretched around the wings 13 by a circular wave spring 15'c and at the same time are supported against the wall 7a of the recess.
  • 11 e.g. shows a two-stage compressor for oil-free compressed air.
  • the disc rotor 7 runs here without contact because it is also supported by a shaft 18 which leads to the outside. (The disc rotor 7, however, requires only a very small drive power to overcome the bearing friction, since it is not a power part).
  • the vane rotor 4 consists of the base body 4a, on each of which a diametrical pair of vanes 13b, 13c for an annular space 11 or 11 'is arranged along a diameter.
  • Two wings 13 and 13c reach through a common slot 14a.
  • the outlet 12b of the first stage lies next to the annular groove and is only connected to the annular groove 11 after a certain internal compression by the groove 17a in the disk rotor 7.
  • the gas passes through the inlet 12'a into the inner second stage, the annular or working space 11 'and finally through the control groove 17 to the outlet 12'b in the indicated direction of rotation 16.
  • the seal 15 in the slot 14a is not absolutely necessary, since with this arrangement of the wings there are no displacements between the wings and the slots.
  • FIG. 12 shows a machine running with contact between the moving parts, for example a compressor.
  • the four wings 13 of the wing rotor 4 are tapered by the spring 19 on the shaft 3 into the bottom Ring groove 11 pressed.
  • the disc rotor 7 is guided in the radial groove 20.
  • the housing part 2 is enlarged by the cylindrical piece 2a, which has been turned out obliquely and receives the oblique groove 20.
  • An annularly offset part of the disc rotor 7 also runs in a flat axial annular groove, whereby the flat pin la of the housing part 1 is also formed.
  • the slot edges of a slot 14 are not parallel because the cross-section of the wing 13 is not rectangular here, but trapezoidal. The wearing parts automatically adjust themselves here.
  • the inlet and outlet channels 12a and 12b lie behind or in front of the fixed separation point between the suction and pressure space, where the cross-section of the annular groove disappears.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Treatment Of Fiber Materials (AREA)
  • Preliminary Treatment Of Fibers (AREA)
  • Press Drives And Press Lines (AREA)
  • Reciprocating Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (8)

1. Machine à pistons rotatifs et à axe anguleux, comprenant un rotor à palettes (4) monté de façon tournante dans un carter et comportant des palettes axiales (13) ainsi qu'un rotor à disque (7) comportant des fentes radiales (14), les axes de rotation des rotors faisant entre eux un angle aigu, les palettes (13) étant engagées dans les fentes du rotor à disque (7) et étant guidées soit avec du jeu soit avec glissement étanche, sur la paroi du volume de travail qui est recouvert par le rotor à disque et en outre le diamètre extérieur du rotor à disque (7) étant supérieur au diamètre extérieur du rotor à palettes (4), caractérisée en ce que:
a) le volume de travail est réalisé d'un côté sous la forme d'une rainure annulaire axiale (11, 11') ménagée dans la paroi du carter;
b) les fentes radiales (14) du rotor à disque (7) sont réalisées avec une section droite en forme de V de telle sorte que leurs parois en oblique soient inclinées par rapport au plan médian au moins suffisamment fortement pour que les deux axes de rotors soient inclinés l'un par rapport à l'autre et que les zones les plus étroites des fentes soient situées sur la surface de contact (6) entre le rotor à disque (7) et le carter (1);
c) le point d'intersection (S) des deux axes de rotation est situé sur la surface de contact (6) entre le rotor à disque (7) et le carter (1) (Fig. 1, 2, 3, 12, 13).
2. Machine à pistons rotatifs et à axe anguleux, comprenant un rotor à palettes (4) monté de façon tournante dans un carter et comportant des palettes axiales (13) ainsi qu'un rotor à disque (7) comportant des fentes radiales (14), les axes de rotation des rotors faisant entre eux un angle aigu, les palettes (13) étant engagées dans les fentes du rotor à disque (7) et étant guidées soit avec du jeu soit avec glissement étanche, sur les parois des volumes de travail qui sont recouverts par le rotor à disque et en outre le diamètre extérieur du rotor à disque (7) étant supérieur au diamètre extérieur du rotor à palettes (4), caractérisée en ce que:
a) les volumes de travail sont réalisés d'un côte sous la forme de rainures annulaires axiales (11, 11') ménagées dans la paroi du carter;
b) les fentes radiales (14) du rotor à disque (7) sont réalisées avec une section droite en forme de V de telle sorte que leurs parois en oblique soient inclinées par rapport au plan médian au moins suffisamment fortement pour que les deux axes de rotors soient inclinés l'un par rapport à l'autre et que les zones les plus étroites des fentes soient situées sur la surface de contact (6) entre le rotor à disque (7) et le carter (1);
c) le point d'intersection (S) des deux axes de rotation est situé sur la surface de contact (6) entre le rotor à disque (7) et le carter (1);
d) les palettes (13) sont disposées sur le corps de base (4a) du rotor à palettes (4) selon des cercles concentriques et elles pénètrent dans les rainures disposées en correspondance (11, 11') (fig. 10 et 11).
3. Machine à pistons rotatifs et à axe anguleux selon la revendication 1 ou 2, caractérisée en ce que les rainures de forme annulaire (11, 11') sont délimitées chacune par une paroi cylindrique radialement intérieure et une paroi cylindrique radialement extérieure (11b, 11c) (Fig.1, 2, 3, 10 et 11).
4. Machine à pistons rotatifs et à axe anguleux selon la revendication 1, caractérisée en ce que la rainure de forme annulaire (11) diminue de largeur en direction de son fond (11a) (fig. 12).
5. Machine à pistons rotatifs et à axe anguleux selon une des revendications 1 à 4, caractérisée en ce que le fond (11a) de la rainure est réalisé avec une forme tronconique de telle sorte que le sommet du cône correspondant soit situé au point d'intersection S des deux axes de rotation (9) et (10) (Fig. 1, 2, 10, 11, 12 et 13).
6. Machine à pistons rotatifs et à axe anguleux selon la revendication 1, caractérisée en ce que le fond (11a) de la rainure de forme annulaire est plan et la surface du rotor à disque (7) qui est située sur la paroi de carter est pourvue d'un profil conique tandis que la paroi de carter comportant la rainure est pourvue d'un profil conique correspondant (Fig. 3).
7. Machine à pistons rotatifs et à axe anguleux selon la revendication 1 ou 2, caractérisée en ce qu'il est prévu deux palettes diamétralement opposées (13) dans une rainure (fig. 10 et 11).
8. Machine à pistons rotatifs et à axe anguleux selon la revendication 4, caractérisée en ce qu'il est prévu un ressort (19) poussant le rotor à palettes (4) contre le fond de rainure (Fig. 12).
EP80105799A 1979-11-16 1980-09-25 Machine rotative avec deux axes non parallèles l'un par rapport à l'autre Expired EP0031002B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT80105799T ATE24346T1 (de) 1979-11-16 1980-09-25 Winkelachsige rotationskolbenmaschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2946304A DE2946304C2 (de) 1979-11-16 1979-11-16 Drehkolbenartige Rotationskolbenmaschine
DE2946304 1979-11-16

Publications (2)

Publication Number Publication Date
EP0031002A1 EP0031002A1 (fr) 1981-07-01
EP0031002B1 true EP0031002B1 (fr) 1986-12-17

Family

ID=6086163

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80105799A Expired EP0031002B1 (fr) 1979-11-16 1980-09-25 Machine rotative avec deux axes non parallèles l'un par rapport à l'autre

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US (1) US4548559A (fr)
EP (1) EP0031002B1 (fr)
AT (1) ATE24346T1 (fr)
DE (2) DE2946304C2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4884957A (en) * 1986-07-11 1989-12-05 Wolfhart Wilimczik Displacement machine having displacement body and sealing members rotating on non-parallel axes
US8834140B2 (en) 2004-05-25 2014-09-16 Cor Pumps + Compressors Ag Leakage loss flow control and associated media flow delivery assembly
DE102004026048A1 (de) * 2004-05-25 2005-12-29 Cor Pumps + Compressors Ag Spaltverluststromsteuerung

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US173030A (en) * 1876-02-01 Improvement in rotary engines and water-wheels
US167146A (en) * 1875-08-24 Improvement in disk steam-engines
US764551A (en) * 1904-05-13 1904-07-12 William Hero Bot Jr Rotary engine.
GB267509A (en) * 1926-03-11 1928-04-19 Farid Riz Camel Improvements in rotary pumps
US2101051A (en) * 1935-07-20 1937-12-07 Cunward Inc Rotary fluid displacement device
US2242058A (en) * 1937-11-05 1941-05-13 Ernest A Cuny Rotary fluid displacement device
US2232599A (en) * 1939-09-16 1941-02-18 Frank P Fehn Rotary fluid power device
DE826331C (de) * 1950-04-22 1951-12-27 Rudolf Bock Geblaese, bestehend aus zwei in einem Gehaeuse angeordneten, aufeinander abrollenden Drehkoerpern und radialen Scheidewaenden
US2828695A (en) * 1954-02-04 1958-04-01 Marshall John Wilmott Rotary machine
US3034445A (en) * 1958-01-14 1962-05-15 Standard Res Consultants Inc Pump
GB967636A (en) * 1960-03-11 1964-08-26 Pietro Mongitore Rotary fluid engines and pumps
DE1553106A1 (de) * 1966-04-25 1970-07-16 Lusztig Dipl Ing Gavril Drehkolbenpumpe
FR1503746A (fr) * 1966-10-12 1967-12-01 Pompe double corps à palettes
DE1628123A1 (de) * 1967-10-23 1971-09-16 Rudolf Jacob Zweikreis-Hydrostatmotor
US3487787A (en) * 1967-12-06 1970-01-06 Thompson Wendell L Vane type rotary fluid displacement device
US3528242A (en) * 1968-03-21 1970-09-15 Michael D Hartmann Rotary positive displacement machines
US3622255A (en) * 1969-08-07 1971-11-23 Gavril T Lusztig Pump
GB1423673A (en) * 1973-11-19 1976-02-04 Simpson J N Rotary fluid pump

Also Published As

Publication number Publication date
US4548559A (en) 1985-10-22
DE2946304C2 (de) 1983-02-03
DE3071865D1 (en) 1987-01-29
ATE24346T1 (de) 1987-01-15
DE2946304A1 (de) 1981-05-21
EP0031002A1 (fr) 1981-07-01

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