EP0137421B1 - Machine à piston rotatif à axe externe - Google Patents

Machine à piston rotatif à axe externe Download PDF

Info

Publication number
EP0137421B1
EP0137421B1 EP84111533A EP84111533A EP0137421B1 EP 0137421 B1 EP0137421 B1 EP 0137421B1 EP 84111533 A EP84111533 A EP 84111533A EP 84111533 A EP84111533 A EP 84111533A EP 0137421 B1 EP0137421 B1 EP 0137421B1
Authority
EP
European Patent Office
Prior art keywords
piston
rotor
opening
cavity
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.)
Expired
Application number
EP84111533A
Other languages
German (de)
English (en)
Other versions
EP0137421A2 (fr
EP0137421A3 (fr
Inventor
Felix Dr. H. C. Wankel
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.)
Aisin Corp
Original Assignee
Aisin Seiki Co Ltd
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 Aisin Seiki Co Ltd filed Critical Aisin Seiki Co Ltd
Priority to AT84111533T priority Critical patent/ATE35020T1/de
Publication of EP0137421A2 publication Critical patent/EP0137421A2/fr
Publication of EP0137421A3 publication Critical patent/EP0137421A3/xx
Application granted granted Critical
Publication of EP0137421B1 publication Critical patent/EP0137421B1/fr
Expired 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
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/20—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with dissimilar tooth forms

Definitions

  • the invention relates to an external-axis rotary piston machine with the features of the preamble of claim 1.
  • a rotary piston machine of this type is known from EP-A-63 240 by the same applicant. It has a cavity in the shut-off rotor which is considerably larger than is required for the engagement of a piston of the piston rotor. This has the advantage that when the piston enters the cavity there are no squeezing flows or compressions leading to energy losses.
  • the enlarged cavity in the shut-off rotor can result in a small, though small, portion of compressed gas getting through the cavity back to the low-pressure side of the machine during the movement of the piston.
  • the circumferential surface of the piston therefore rolls on a central part of the shut-off rotor in order to form a seal against such overflow.
  • the provision of this middle part leads to a comparatively great design effort, and moreover the movement of the piston against this middle part leads locally, albeit slightly, to squeezing currents or compressions, which contribute to energy losses and noise.
  • the object of the invention is to enable the piston to pass through a cavity of the shut-off rotor to a large extent to avoid loss flows and noise, without this cavity forming a harmful space. H. an undesirable overflow from the high-pressure to the low-pressure side of the machine enables the machine to be highly efficient with low noise. This object is achieved on the basis of the features of the characterizing part of patent claim 1.
  • the invention thus shows for the first time for external-axis rotary piston machines with a piston rotor and a shut-off rotor, how a piston can remain in constant sealing contact with edge regions of the receiving opening of the cavity during its passage through a cavity of the shut-off rotor, so that a harmful space via the gas from the Pressure on the suction side can be almost completely avoided.
  • a radial displacement of an engaging edge from the circular cylindrical circumference of a shut-off rotor inwards is known per se from other types of machines.
  • the edges of the receiving opening are rounded, so that the contact with the side surfaces of the pistons takes place radially inward.
  • the boundary edges of an arcuate, flat recess in the shut-off rotor are beveled in order to enable engagement with a piston designed as a circular body .
  • the housing 1 encloses the piston rotor 2 and the shut-off rotor 3, which are mounted on the two axial ends of the housing in a manner which is not shown, but are usual, and which are in drive connection with one another in a speed ratio of 1: 2 via two gearwheels.
  • the runners 2, 3 rotate in the opposite direction, as indicated by arrows.
  • the gas to be compressed is sucked in by the movement of the pistons 4, 5 along the inner wall 6 of the housing through the housing connector 7.
  • the housing connector 7 is arranged directly adjacent to the housing part 8 sealingly enclosing the shut-off rotor 3 and opens in an approximately tangential direction into the circular-cylindrical working space 9 through which the pistons 4, 5 pass.
  • This working space is delimited on the inside by a hollow shaft 10 of the piston rotor 2. on the circumference of the pistons 4, 5 are attached.
  • the pistons can also be fastened to an outer hollow cylindrical rotor part 11, which firmly encloses an inner hollow shaft 12.
  • the hollow shaft 10 encloses a non-rotating hollow cylindrical control sleeve 13, which has an opening 14 in its wall, which extends over an arc angle. Openings 15, 16 are also respectively provided in the hollow shaft 12 in the direction of rotation in front of the pistons 4, 5. While these openings 15, 16 of the hollow shaft run through the opening 14 by rotating the rotor 2, the gas compressed in the annular space 9 can flow inward into the outflow channel 17 enclosed by the control sleeve 13.
  • the outflow opening 14 in the control sleeve 13, like the intake duct 7, is arranged as close as possible to the shut-off rotor 3 or the sealing area 18 between the two rotors 2, 3, in order to make the pistons 4, 5 one as possible with each revolution to achieve a high compression ratio.
  • the angular position of the outflow opening 14 can be changed to control the performance of the machine.
  • the opening 14 closes as shown in FIG. 3 shortly after the outer peripheral surface 19 of the piston 5 or 4, which moves along the inner wall 6 of the housing, has left the edge 20 of the annular working space 9.
  • the trailing boundary surface 21 of the opening 16 undercuts the piston 5 in the hollow shaft of the piston rotor.
  • the pistons 4, 5 begin to compress some gas into the cavity 22 of the shut-off rotor 3 until the trailing edge region 23 of the receiving opening 24 of the shut-off rotor approaches in a sealing manner or contact with the piston 5.
  • the gas compressed into the cavity 22 of the shut-off rotor during this short rotation angle of the piston runner returns to the suction side of the machine and thus reduces the efficiency of the machine.
  • this angle of rotation is reduced to a minimum, since the trailing edge region 23 of the opening 24 approaches the piston 5 much earlier than is possible according to known construction principles.
  • the drawing shows that the trailing boundary edge 25 of the receiving opening 24 of the shut-off rotor is offset radially inward, while the leading boundary edge 26 of the receiving opening 24 is located on the outer circumference of the shut-off rotor. From this trailing edge 25 of the shut-off rotor, which is offset radially inward, the edge region of the receiving opening 24 runs outward in an arc shape and merges continuously into the peripheral surface of the shut-off rotor.
  • the leading or first edge 26 on the circumference of the shut-off rotor should move along the leading piston surface 28 and the trailing, radially inwardly offset boundary edge 25 of the receiving opening 24 should move along a radially outer part 29 of the trailing piston surface, while the arcuate If the edge region 23 of the receiving opening 24 is to roll on a radially inner part of the trailing piston surface, the cross-sectional shape of the pistons 5, 4 is geometrically determined. The cross section of the pistons 5, 4 is thus approximately S-shaped.
  • the trailing or second edge of the shut-off rotor grazes along the convex surface part 29, as shown in FIGS. 4 and 5, and then, in accordance with the representations of FIGS.
  • the arcuate edge region 23 rolls on the concave surface part of the trailing piston surface.
  • the circumferential width of the pistons 4, 5 determines the size of the receiving opening 24 in the shut-off valve. This width has a certain dimension in order to obtain a sufficient seal between the circumferential surface of the pistons and the inner surface 6 of the housing 1.
  • sealing strips can be attached to the circumference of the pistons, preferably according to the principle known from DE-OS 3 005 694.
  • the gate valve can consist of a thin-walled sleeve.
  • the part of the shut-off rotor adjoining the leading opening edge 26 and the trailing arc-shaped edge region is solid and, for example, as a separately produced strip (31, 32) on the wall of the shut-off rotor attached.
  • This separate production of strips thus delimiting the receiving opening 24 facilitates the precise production of the surface contour of the edges 25 and 26 and of the convexly curved region 23 adjoining the edge 25.
  • the edges 25, 26 can, as shown in FIGS. be relatively sharp, but also be designed with a rounded cross-section.
  • FIGS. 8 and 9 show two exemplary embodiments with measures to avoid, albeit slight, squeezing currents which can occur when the convex edge region 23 rolls according to the exemplary embodiment in FIGS. 1 to 7 up to the peripheral surface 33 of the shaft of the piston rotor.
  • the convexly curved region 34 which rolls against the limiting edge 25 and rolls on the piston 5, is substantially reduced for this purpose by providing a recess 36 between this region 34 and the peripheral surface 35 of the shut-off rotor.
  • a cutout 36 instead of a cutout 36, a plurality of smaller cutouts one behind the other also in the circumferential direction of the shut-off rotor can be provided.
  • the exemplary embodiment according to FIG. 9 shows a recess 37 in the piston region which adjoins the outer convex surface part 29 of the piston 5 and merges into the peripheral surface 33 of the shaft of the piston rotor and which likewise prevents a squeezing flow which leads to losses.
  • this cutout 37 can also be replaced by a plurality of smaller cutouts.
  • the cutouts 36, 37 can also be arranged in large numbers next to one another in the axial direction, so that they are separated from one another by web parts in a manner not shown. These web parts act to weaken the cross section z. B. counter in the root region of the piston 5.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Sealing Devices (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Flexible Shafts (AREA)
  • Toys (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)

Claims (8)

1. Machine à piston rotatif à axe externe comportant un rotor à pistons (2) et un rotor de fermeture (3) qui sont enfermés dans un carter (1) commun, le rotor à pistons (2) présentant un arbre creux (10) qui entoure un fourreau de commande (13) dans lequel est pratiqué un orifice d'écoulement (14), de sorte qu'au moins un orifice (16) prévu dans l'arbre creux recouvre l'orifice de fourreau (14) sur un angle de rotation limité, une zone d'étanchéité (18) étant formée entre la surface périphérique cylindrique circulaire du rotor de fermeture (3) et le pourtour de l'arbre (10) du rotor à piston supportant au moins un piston (4, 5), le rotor de fermeture (3) enfermant une cavité (22) dans laquelle est ménagé un logement (24) pour le piston (4,5) du rotor à piston (2), le volume de dégagement adjacent aux bords de limitation (26, 25) avant et arrière du logement (24), et destiné à éviter des écoulements de compression, étant plus grand que cinématiquement nécessaire pour le déplacement du piston (4, 5) à travers la cavité (22) du rotor de fermeture (3), et un bord de limitation (26) du logement (24) se déplaçant de manière étanche le long d'une surface (28) concave du piston, caractérisée en ce que l'autre bord de limitation (25) du logement (24) est décalé radialement vers l'intérieur à partir de la surface périphérique cylindrique circulaire du rotor de fermeture (3), et en ce que ce bord (25) décalé radialement vers l'intérieur se déplace de manière étanche le long d'une partie de surface (29) convexe extérieure radialement du piston (4, 5), une zone de bordure (23, 24) convexe, par rapport à l'axe de rotation, et qui tourne sur la partie de surface (29) du piston (4, 5) du rotor à piston (2), faisant suite à cet autre bord de limitation (25) dans la direction de la surface périphérique du rotor de fermeture (3).
2. Machine à piston rotatif selon la revendication 1, caractérisée en ce qu'une surface de limitation (21) de l'orifice (16) pratiqué dans l'arbre creux (10) forme une contre- dépouille pour le piston (4, 5) adjacent.
3. Machine à piston rotatif selon la revendication 2, caractérisée en ce que la zone de bordure (23) convexe se prolonge par la surface périphérique du rotor de fermeture, et passe sur un piston, jusqu'à la surface périphérique de l'arbre du rotor à piston.
4. Machine à piston rotatif selon la revendication 2, caractérisée en ce qu'il est prévu au moins un évidement (36) destiné à éviter des écoulements de compression, entre la zone de bordure (34) convexe et la surface périphérique (35) cylindrique circulaire du rotor de fermeture.
5. Machine à piston rotatif selon la revendication 2, caractérisée en ce que la zone de bordure (23) convexe se prolonge par la surface périphérique (35) du rotor de fermeture et en ce qu'il est prévu au moins un évidement (37) dans la zone de piston faisant suite radialement vers l'intérieur à la partie de surface (29) convexe extérieure du piston (4, 5).
6. Machine à piston rotatif selon la revendication 4 ou 5, caractérisée en ce qu'il est prévu plusieurs évidements juxtaposés dans la direction axiale de la machine, ces évidements étant séparés les uns des autres par une traverse.
7. Machine à piston rotatif selon la revendication 1, caractérisée en ce que le rotor de fermeture a la forme d'un fourreau.
8. Machine à piston rotatif selon la revendication 7, caractérisée en ce que les zones de bordure, parallèles à l'axe de rotation, du logement (24) du rotor de fermeture (3), sont formées par des barres (31, 33) fixées sur la paroi du fourreau.
EP84111533A 1983-10-10 1984-09-27 Machine à piston rotatif à axe externe Expired EP0137421B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84111533T ATE35020T1 (de) 1983-10-10 1984-09-27 Aussenachsige rotationskolbenmaschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH5516/83 1983-10-10
CH5516/83A CH663446A5 (de) 1983-10-10 1983-10-10 Aussenachsige rotationskolbenmaschine.

Publications (3)

Publication Number Publication Date
EP0137421A2 EP0137421A2 (fr) 1985-04-17
EP0137421A3 EP0137421A3 (fr) 1985-05-15
EP0137421B1 true EP0137421B1 (fr) 1988-06-08

Family

ID=4294930

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84111533A Expired EP0137421B1 (fr) 1983-10-10 1984-09-27 Machine à piston rotatif à axe externe

Country Status (6)

Country Link
US (1) US4626182A (fr)
EP (1) EP0137421B1 (fr)
JP (1) JPS60156901A (fr)
AT (1) ATE35020T1 (fr)
CH (1) CH663446A5 (fr)
DE (1) DE3471971D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007009291A1 (de) 2007-02-26 2008-08-28 Hagge, Stefan, Dipl.-Ing. Drehkolbenmotor

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6484687B1 (en) 2001-05-07 2002-11-26 Saddle Rock Technologies Llc Rotary machine and thermal cycle
US9664047B2 (en) 2012-08-23 2017-05-30 Mallen Research Limited Partnership Positive displacement rotary devices with uniquely configured voids
US8956134B2 (en) 2012-08-23 2015-02-17 Mallen Research Limited Fixed-vane positive displacement rotary devices
US9664048B2 (en) 2012-08-23 2017-05-30 Mallen Research Limited Partnership Positive displacement rotary devices with uniform tolerances
DE102013008103A1 (de) 2013-05-10 2014-11-13 Winfried Alfons Lampart Motorantriebe und Generatoren mit efektiverem Kühlsystem

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US426553A (en) * 1890-04-29 Rotary steam-engine
US1319456A (en) * 1919-10-21 Rotary engine
US417762A (en) * 1889-12-24 Rotary engine
US709597A (en) * 1902-03-21 1902-09-23 Samuel M Frank Rotary force-pump.
US866693A (en) * 1904-04-27 1907-09-24 Henry J Griest Rotary explosion-engine.
US1365245A (en) * 1918-06-04 1921-01-11 Charles E Hultgreen Rotary pump
US1418910A (en) * 1919-02-06 1922-06-06 Nelson E Funk Blower
GB958489A (en) * 1959-02-23 1964-05-21 John Wilmott Marshall Improvements in gas compressors and like rotary machines
DE1176351B (de) * 1960-10-07 1964-08-20 Rudolph Scheffus Maschinenfabr Strang- oder Bandpresse mit zwei walzen-aehnlichen Koerpern zum Zufuehren von Teigen, Pasten oder Fettmassen in die Druckkammer der Presse
FR1594801A (fr) * 1968-11-20 1970-06-08
DD96551A1 (fr) * 1972-01-05 1973-03-20
CH638866A5 (de) * 1979-03-27 1983-10-14 Wankel Felix Abdichtung am umfang eines laeufers einer rotationskolbenmaschine.
DE3018638C2 (de) * 1980-05-16 1986-10-16 Walter 4791 Schlangen Plöger Drehkolben-Brennkraftmaschine
CH661318A5 (de) * 1981-04-14 1987-07-15 Wankel Felix Rotationskolbenmaschine.
EP0066255A1 (fr) * 1981-05-29 1982-12-08 Wankel GmbH Souffleur à piston rotatif à axe externe
EP0088288A1 (fr) * 1982-03-03 1983-09-14 Wankel, Felix, Dr. h.c. Machine à piston rotatif à axe interne

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007009291A1 (de) 2007-02-26 2008-08-28 Hagge, Stefan, Dipl.-Ing. Drehkolbenmotor

Also Published As

Publication number Publication date
ATE35020T1 (de) 1988-06-15
EP0137421A2 (fr) 1985-04-17
EP0137421A3 (fr) 1985-05-15
JPH0429841B2 (fr) 1992-05-20
DE3471971D1 (en) 1988-07-14
CH663446A5 (de) 1987-12-15
US4626182A (en) 1986-12-02
JPS60156901A (ja) 1985-08-17

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