WO2013017232A2 - Mise en forme de la cuvette du piston d'une machine à piston rotatif - Google Patents

Mise en forme de la cuvette du piston d'une machine à piston rotatif Download PDF

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Publication number
WO2013017232A2
WO2013017232A2 PCT/EP2012/003184 EP2012003184W WO2013017232A2 WO 2013017232 A2 WO2013017232 A2 WO 2013017232A2 EP 2012003184 W EP2012003184 W EP 2012003184W WO 2013017232 A2 WO2013017232 A2 WO 2013017232A2
Authority
WO
WIPO (PCT)
Prior art keywords
piston
recess
rotary piston
edge
rotary
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.)
Ceased
Application number
PCT/EP2012/003184
Other languages
German (de)
English (en)
Other versions
WO2013017232A3 (fr
Inventor
Alexander MACHOLD
Andreas Ennemoser
Josef Ruetz
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.)
AVL List GmbH
Original Assignee
AVL List GmbH
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 AVL List GmbH filed Critical AVL List GmbH
Publication of WO2013017232A2 publication Critical patent/WO2013017232A2/fr
Publication of WO2013017232A3 publication Critical patent/WO2013017232A3/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F01C1/22—Rotary-piston machines or engines of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth- equivalents than the outer member
    • 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B55/00—Internal-combustion aspects of rotary pistons; Outer members for co-operation with rotary pistons
    • F02B55/02—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B55/00—Internal-combustion aspects of rotary pistons; Outer members for co-operation with rotary pistons
    • F02B55/14—Shapes or constructions of combustion chambers
    • 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
    • F04C2250/00—Geometry
    • F04C2250/20—Geometry of the rotor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the invention relates to a rotary-piston machine with at least one rotary piston which rotates in one housing about a centrically or eccentrically mounted axis.
  • a housing is generally understood to be a vehicle-mounted or even vibration-damping within the vehicle, for example a spring-suspended element, which forms a cavity for accommodating the rotary piston.
  • a rotary piston is understood to mean a centrically or eccentrically revolving element which can mechanically interact on its surface with a gas in its surroundings,
  • a rotary piston machine of the type considered is preferably used as the sole drive in a motor vehicle, but may for example also be provided in addition to an electric motor in a hybrid drive.
  • the output shaft of the rotary piston machine can either be connected directly to the mechanical drive train, or the output shaft is connected to an electrical generator which generates electrical energy for operating the electric motor and / or for charging a battery.
  • the rotary piston machine can also be designed relatively small compared to the electric motor and, in conjunction with a generator, merely serve as an additional power source to a
  • a rotary piston engine of the type considered is operated as an internal combustion engine with a fuel-air mixture, which is either sucked into the combustion chamber and compressed there, or the fuel is directly in the
  • the combustion chamber is between the
  • Inner wall typically has the shape of a trochoid. This will be the Combustion chamber during the eccentric rotation of the rotary piston into a plurality, with the rotation displacing and changing in size combustion chambers divided. In this - the fuel-air mixture is sucked in the case of a fuel-compressing machine, this is compressed there and ignited by means of one or more spark plugs, and the resulting combustion gases are discharged again from the combustion chamber.
  • the rotary piston has in this case in the axial direction everywhere substantially the same cross section and has on its peripheral wall at least two
  • Vertex edges on, at least between two on the
  • Piston peripheral wall adjacent vertex edges extending a piston flank wall Preferably, the rotary piston has three vertex surfaces and is referred to in this case as a triangular piston. Furthermore, the rotary piston has two parallel to its plane of rotation side surfaces.
  • piston flank wall of the rotary piston has a so-called
  • Piston flank wall to selectively increase the combustion chamber formed between the piston skirt wall and the housing inner wall and to improve the course of the combustion of the fuel-air mixture after ignition.
  • each piston flank wall of the rotary piston has a similar piston recess.
  • the shape and position of the piston recess in particular also affect the turbulence level during combustion in the combustion chamber, which in turn affects the combustion process, thereby the internal efficiency of the rotary piston engine and thus the fuel consumption, with a high turbulence level leads to improved combustion.
  • piston recesses are considered whose outline on the piston flank wall has a substantially rectangular basic shape with four contour edges, namely two substantially parallel to the direction of rotation extending longitudinal edges, a substantially perpendicular to the direction of rotation, seen in the direction of rotation front leading edge and a rear edge substantially perpendicular to the direction of rotation, seen in the direction of rotation rear edge.
  • the longitudinal edges are curved inwardly such that the contour of the piston recess is narrower at a throat between the two longitudinal edges with respect to its extension perpendicular to the direction of rotation than at the leading edge and is at the trailing edge.
  • a constriction point thus refers in the present context to a substantially perpendicular to the rotational direction and thus substantially parallel to the leading and trailing edge extending connecting path between a point on one and a point on the other longitudinal edge of the piston recess, the outline of the piston recess with respect to its extension perpendicular to the direction of rotation between these two points is particularly narrow, preferably even at the narrowest, d. H. the length of said connecting path is shorter than the leading edge and shorter than the trailing edge of the piston recess.
  • FIGS. 19 to 22 show further embodiments of such a piston recess.
  • the piston recess is arranged here in the trailing part of the piston skirt wall and constricted at about the beginning of its rear third to about a quarter of its width (FIG. 18B).
  • the piston recess has a flat in the area before the constriction Bottom, in the region behind the constriction a slightly rounded bottom and in the region of the constriction a nearly semicircular profile (FIG. 18C), wherein the depth of the piston depression decreases significantly towards the constriction point and is lowest at the constriction point (FIG. 18A).
  • the present invention is based on the object, the course of the
  • a rotary piston machine is characterized in that the width of the contour of the piston recess at the constriction is at least half the length of the leading edge or the length of the trailing edge, wherein the lengths of the leading and trailing edge substantially due to the rectangular basic shape of the outline of the piston recess are the same.
  • Rotary piston engine increases and ultimately fuel can be saved.
  • the ignition angle is understood to be the angle of rotation of the rotary piston relative to a specific starting position, in which case for a specific starting position
  • Hybrid vehicle is to be used, it is thereby possible, the
  • Rotary piston machine to provide in tow mode as additional brake is "reversed" by the electric drive motor is operated as a generator, while generating power to drive the connected to the range extender generator, which is used in this case as a motor, and this mechanically drives the rotary piston engine, which in Tow operation runs and thereby generates the required mechanical resistance.
  • the depth of the piston recess increases in the direction of rotation from the point of constriction in the direction of the front edge and / or in the direction of the trailing edge. This also contributes to the formation of a high level of turbulence.
  • the bottom of the piston recess can also be substantially planar, possibly up to a curvature which essentially corresponds to the curvature of the piston flank wall.
  • Constriction is located in the respect to the extent of the piston recess in the direction of rotation rear half of the piston recess.
  • piston recess can also in
  • the piston recess is substantially symmetrical with respect to a median plane through the
  • Rotary piston which runs parallel to the side walls of the rotary piston. This is expedient, as well as the remaining construction of the
  • Rotary piston and the housing inner wall and thus also the combustion chamber with respect to this center plane is symmetrical.
  • At least one extending from an outline edge of the piston recess downwardly extending wall of the piston recess to the interior of the piston recess is inclined.
  • This division of the inclination of the rear piston bowl wall offers in the manner described above the possibility of constructively "adjusting" the drag torque of the rotary piston.
  • the invention can be applied in the same way to a mixture-compressing as well as to a fuel injection rotary piston engine.
  • FIG. 1 shows a section through a rotary piston machine according to the invention
  • Fig. 2 an oblique view of a rotary piston with three different
  • FIG. 3 shows a plan view of the piston flank walls shown in FIG. 2;
  • FIG. 4 shows a diagram in which the indicated moment of the rotary piston machine is plotted as a function of the firing angle for piston barrel molds according to the invention in contrast to those of the prior art;
  • Fig. 5 a diagram in which the kinetic energy of turbulence in the
  • Combustion chamber as a function of the rotation angle of the rotary piston for the same piston mold shapes as shown in Fig. 4 is applied.
  • Rotary piston machine 1 in which the invention can be used, as essential components, the housing 2 having a plurality of cooling channels, an inlet opening 7 for the fuel-air mixture and an outlet opening 8 for the combustion gases and the rotary piston 3, which three vertex edges and according to three piston flank walls 11 each having a piston recess 12 shown.
  • the rotary piston 3 eccentrically revolves around a fixed axis 4 with an external toothing 5, wherein it has an internal toothing 6 rolls on the external teeth 5.
  • the rotary piston 3 rotates clockwise.
  • two spark plugs are arranged in the housing wall at the positions designated 9 and 10. Due to the rotational position of the rotary piston 3 in the interior of the housing 2 (again in a clockwise direction) four combustion chambers 13, 14, 15 and 16 are defined, which in this order the intake, compression, Zünd,. Output stroke are assigned.
  • Fig. 2 shows in an oblique view four - for better clarity, axially juxtaposed - triangular rotary piston 3 with the internal teeth 6 and with three piston flank walls 11, in each of which a piston recess 12 is inserted. It is assumed that the rotary piston 3 rotates forwards and downwards (see arrow).
  • the four trough shapes are labeled A, B, C and D from left to right.
  • the trough forms A, B and C are trough forms according to the invention, while the triangular trough form D is known from the prior art and serves only for comparison purposes.
  • FIG. 3 shows an enlarged plan view of the piston flank walls 11 from FIG. 2, in which the four trough shapes can be seen from above.
  • the rotary piston 3 rotates downwards (see arrow).
  • the three trough molds A, B and C according to the invention have a substantially rectangular shape with two longitudinal edges 20 and 21, a front edge 22 and a rear edge 23. They each have different degrees of constrictions, the width of the piston recess 12 in the troughs A, B and C at the
  • Constriction 24 corresponds to approximately 80, 75 or 60% of the non-constricted width.
  • the constriction point 24 is in the trailing half of the piston recess 12.
  • the piston recesses 12 are in contrast to a central position seen in the rotational direction on the
  • Piston flank wall 11 clearly shifted in the forward direction, which
  • Trough shape A is also the rear edge 23 relatively strongly curved outwards, while the edge at the transition of the flat to the steep part of the inner wall at the trailing edge 23 is again almost straight.
  • the bottom of the molds A, B and C has in the region of the constriction point 24 in each case its highest point and falls from there in the direction of the front edge 22 and the trailing edge 23 with approximately constant slope.
  • Longitudinal edges 20 and 21 between the constriction point 24 and the leading edge 22 and the trailing edge 23 are not straight, but slightly curved outward in all three mold shapes A, B and C.
  • All three well shapes A, B and C are symmetrical with respect to the center plane of the rotary piston 3 parallel to the direction of rotation.
  • Fig. 4 is the qualitative course of the indicated moment of
  • Rotary piston engine 1 plotted as a function of the firing angle for three different trough shapes, the curves shown reflect the course from an earlier to a later ignition timing.
  • the solid curve labeled “base” in FIG. 4 corresponds to a triangular mold of the prior art, while those labeled "variant 1" and "variant 2"
  • dotted or dotted curves correspond to different variants of the invention Muldenformen.
  • Trough shapes produced kinetic energy of turbulence over that produced by the prior art trough mold, which is sometimes more than double, over much of the applied rotor angle range.
  • FIGS. 4 and 5 therefore prove that it is possible with the aid of the invention
  • Trough shapes succeed in keeping the indexed moment at a high level over a wide ignition angle range or in significantly increasing the kinetic energy of the turbulence.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)

Abstract

L'invention porte sur une machine à piston rotatif (1), dans laquelle les parois latérales (11) du piston présentent des cuvettes de piston (12) ayant une forme de base sensiblement rectangulaire, dont les bords longitudinaux (20, 21) sont incurvés vers l'intérieur de telle sorte que, dans une zone de rétrécissement (24) s'étendant entre les deux bords longitudinaux (20, 21), le contour de la cuvette de piston (12) est plus étroit, relativement à son extension mesurée perpendiculairement à la direction de la rotation, qu'au bord avant (22) et au bord arrière (23). Selon l'invention, la largeur du contour de la cuvette de piston (12) vaut, dans la zone de rétrécissement (24), au moins la moitié de la longueur du bord avant (22) ou de la longueur du bord arrière (23). Avec cette forme de cuvette, il est possible d'obtenir un niveau de turbulence particulièrement élevé du mélange carburant-air dans la cuvette de piston (12) et, de cette façon, dans la chambre de combustion. Ceci conduit à une propagation plus rapide et plus favorable de la flamme et, de cette façon, à une meilleure combustion du mélange carburant-air. De cette façon, le degré de rendement thermique du moteur à piston rotatif (1) peut être amélioré et le carburant peut être économisé.
PCT/EP2012/003184 2011-08-04 2012-07-26 Mise en forme de la cuvette du piston d'une machine à piston rotatif Ceased WO2013017232A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA1127/2011A AT512369B1 (de) 2011-08-04 2011-08-04 Rotationskolbenmaschine
ATA1127/2011 2011-08-04

Publications (2)

Publication Number Publication Date
WO2013017232A2 true WO2013017232A2 (fr) 2013-02-07
WO2013017232A3 WO2013017232A3 (fr) 2013-10-10

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2012/003184 Ceased WO2013017232A2 (fr) 2011-08-04 2012-07-26 Mise en forme de la cuvette du piston d'une machine à piston rotatif

Country Status (2)

Country Link
AT (1) AT512369B1 (fr)
WO (1) WO2013017232A2 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3361046A1 (fr) * 2017-02-09 2018-08-15 Pratt & Whitney Canada Corp. Moteur à combustion interne rotatif à rapports volumétriques inégaux
EP3597882A1 (fr) * 2018-07-17 2020-01-22 Mazda Motor Corporation Moteur à piston rotatif

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1451857A1 (de) 1965-12-15 1969-08-21 Ustav Pro Vyzkum Motorovych Vo Kreis- oder Drehkolben-Brennkraftmaschine
DE2502931A1 (de) 1974-01-25 1975-07-31 Siak Hoo Ong Rotationskolbenmaschine
JPS59141727A (ja) 1983-02-03 1984-08-14 Fujio Inoue ロ−タリ−エンジン

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1401994A1 (de) * 1962-07-25 1968-11-21 Daimler Benz Ag Rotationskolben-Brennkraftmaschine in Trochoidenbauart
DE1296872B (de) * 1962-08-25 1969-06-04 Krupp Gmbh Kreiskolben-Brennkraftmaschine
US3359955A (en) * 1966-04-18 1967-12-26 Curtiss Wright Corp Rotary engine combustion chamber
JPS4946660B2 (fr) * 1972-07-10 1974-12-11
JPS49123406U (fr) * 1973-02-23 1974-10-23
JPS49117812A (fr) * 1973-03-15 1974-11-11
JPS50135412A (fr) * 1974-04-16 1975-10-27
US3976035A (en) * 1974-09-26 1976-08-24 Texaco Inc. Rotary engine and method of operation

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1451857A1 (de) 1965-12-15 1969-08-21 Ustav Pro Vyzkum Motorovych Vo Kreis- oder Drehkolben-Brennkraftmaschine
DE2502931A1 (de) 1974-01-25 1975-07-31 Siak Hoo Ong Rotationskolbenmaschine
JPS59141727A (ja) 1983-02-03 1984-08-14 Fujio Inoue ロ−タリ−エンジン

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3361046A1 (fr) * 2017-02-09 2018-08-15 Pratt & Whitney Canada Corp. Moteur à combustion interne rotatif à rapports volumétriques inégaux
US10526961B2 (en) 2017-02-09 2020-01-07 Pratt & Whitney Canada Corp. Rotary internal combustion engine with unequal volumetric ratios
EP3892818A1 (fr) * 2017-02-09 2021-10-13 Pratt & Whitney Canada Corp. Moteur à combustion interne rotatif à rapports volumétriques inégaux
US11261781B2 (en) 2017-02-09 2022-03-01 Pratt & Whitney Canada Corp. Rotary internal combustion engine with unequal volumetric ratios
EP3597882A1 (fr) * 2018-07-17 2020-01-22 Mazda Motor Corporation Moteur à piston rotatif
US10982592B2 (en) 2018-07-17 2021-04-20 Mazda Motor Corporation Rotary piston engine

Also Published As

Publication number Publication date
WO2013017232A3 (fr) 2013-10-10
AT512369B1 (de) 2013-10-15
AT512369A1 (de) 2013-07-15

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