EP0289561A1 - Dispositifs a pistons rotatifs - Google Patents

Dispositifs a pistons rotatifs

Info

Publication number
EP0289561A1
EP0289561A1 EP19870907403 EP87907403A EP0289561A1 EP 0289561 A1 EP0289561 A1 EP 0289561A1 EP 19870907403 EP19870907403 EP 19870907403 EP 87907403 A EP87907403 A EP 87907403A EP 0289561 A1 EP0289561 A1 EP 0289561A1
Authority
EP
European Patent Office
Prior art keywords
housing
piston
curve
quadrant
point
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Withdrawn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
EP19870907403
Other languages
German (de)
English (en)
Inventor
Hubert Petutschnig
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.)
Individual
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
Publication of EP0289561A1 publication Critical patent/EP0289561A1/fr
Withdrawn legal-status Critical Current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
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/40—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and having a hinged member
    • F01C1/44—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and having a hinged member with vanes hinged to the inner 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
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
    • 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
    • F04C2250/30—Geometry of the stator
    • F04C2250/301—Geometry of the stator compression chamber profile defined by a mathematical expression or by parameters

Definitions

  • the invention relates to a rotary piston assembly for a motor, a pump, a compressor or the like.
  • at least two pistons are pivotally mounted on arms in the longitudinal center in a housing, the arms being rotatably connected to an input or output shaft, the The center of the housing is the center point and the origin of the coordinates, the piston ends sealingly abutting the inner wall of the housing, the inner wall or contour of the housing being divided into four quadrants, of which opposite quadrants have mirror-image inner contours, the inner contour of the housing being symmetrical in each quadrant With respect to the respective coordinate axis running through the quadrant, and the end points being the
  • the aim of the invention is to achieve the most uniform possible running of the pistons and to make the efficiency of the engine, the pump or the compressor as large as possible. Furthermore, the lowest possible friction and a good seal should be achieved between the piston and the inner wall of the housing.
  • FIG. 1 shows a section through a rotary piston arrangement
  • FIGS. 2-6 different possibilities for the inner contour of the housing
  • FIG. 7 a rotary piston
  • FIG. 8 a sealing strip for a rotary piston
  • FIG. 9 an inner contour of the housing for a rotary piston with rounded sealing strips.
  • Fig. 1 shows schematically a section through the piston arrangement of an engine or a pump or a compressor.
  • the housing 1 has an inner contour 2, against which at least two rotary pistons 3 rest, each of which is pivotally mounted with its pivot point S on a boom 4 which is connected in a rotationally fixed manner to an input or output shaft 5 which is about its center, which is also the center of the housing , rotates. With 3 'is the other, opposite the piston 3. Piston shown on the boom 4 '.
  • the center of the housing 0 is also the center of a coordinate system with x and y axis.
  • the coordinate axes also represent axes of symmetry for four quadrants I, II, III, IV, into which the inner contour 2 of the housing 1 is divided to facilitate its construction, and which are essentially determined by the piston length 1.
  • the pivot point S of the piston 3 lies in the longitudinal center of the piston 3 between its two end points 6 and 7, with which the piston 3 bears against the inner contour 2 of the housing 1.
  • the inner contour 2 of the housing 1 is designed in a certain manner for a given length 1 of the piston 3.
  • the points P and Q lie in the coordinate system with the x and y axes
  • Coordinates origin and have the coordinates £ y i Furthermore, the positive y-axis forms an axis of symmetry for the curve section between the points P and Q, which limit the quadrant I.
  • the subsequent quadrant II of the housing 1 is delimited by the points Q and R, the point R being the coordinates £) and the positive x-axis is the axis of symmetry for this curve section in Quadrant II.
  • the following Quadrant III is from the points R and T limited and has the negative y-axis as an axis of symmetry.
  • Quadrant IV is delimited by points T and P.
  • the distance d between the pivot point S and the point Po is selected. Furthermore, a signed segment m with a positive or negative sign is selected, which is to be plotted on the y-axis from origin 0. If the sign is positive, the distance m is plotted in the direction of the negative y-axis; if the sign of the distance m is negative, it is plotted in the direction of the positive y-axis.
  • the distance + d + m corresponds to the generalized radius r of the curve between the points P and Q.
  • the parameter n is decisive for the curvature of the curve section between the points P and Q, in particular also for the entry of the curve section into the points P and Q and thus for the tangential angle ⁇ , which is measured between the tangent at points P and Q and the connecting line between the piston turning points 6.
  • the curve between the points Q and R in quadrant II is obtained by moving the piston 3 around the origin 0 rotated, its trailing end point 6 sliding along the selected curve KI and the leading piston end point 7 starting from
  • Point Q describes the subsequent curve KII. This mapping continues until the piston end point 6 comes to rest in point Q and piston end point 7 is located in point R. This defines the inner contour of the housing 1, since opposing quadrants I or III and II or IV are mirror images of one another.
  • the shape of the inner contour 2 influences the specific conditions of the rotary piston for the pump, the motor or the compressor, in particular with regard to the compression volume, sliding properties, etc.
  • the curve parameter n and the tangential angle are related to some extent and it is expedient, if preferred, and where ⁇ is the desired tangential angle of the curve at its end points P, Q RT and ⁇ ⁇ 15 °, preferably 20-40 °.
  • ⁇ is the desired tangential angle of the curve at its end points P, Q RT and ⁇ ⁇ 15 °, preferably 20-40 °.
  • the curves are curved more strongly in the region of the end points P, Q, but are flattened considerably in the central region. However, they show a not so favorable relationship between the volumes delimited by the piston 3 and the inner wall of the housing.
  • the sizes d and m as well as n determine the curve shape, which in turn is determined on the basis of the lowest possible friction or in view of a favorable ratio of the volumes in the individual quadrants.
  • n ⁇ 2 m between to preferably approximately for n ⁇ 3 m between to preferably approximately at g_, for n ⁇ 4 m between to preferably approximately for n ⁇ 5 m between to preferably approximately for for n ⁇ 6 m between to preferably about for for n ⁇ 7 m between to preferably about for and for n ⁇ 3 m between to preferably about lies, or d ate.
  • the curve curve to be calculated between P and Po is determined and this curve is mirrored with respect to the positive y-axis.
  • the curve between the curves P and Q can be mapped onto the second quadrant II either by point-by-point mapping or by calculation with corresponding mapping equations.
  • the selected curve in quadrant I and the subsequent curve in quadrant II have the same tangential angle at point Q, which ensures a continuous or jerk-free merging of the curves.
  • the determination of the curve can begin in any quadrant, since the quadrant mirrors are symmetrical or the curve in the following quadrants is obtained by imaging.
  • the selected curve can be displayed on any side.
  • the curves given according to the invention give good conditions with regard to the tangential angle, the sliding of the piston 3 on the envelope curve or inner contour, and to achieve good relationships between the. volumes 8, 9 delimited by the piston 3 in the individual quadrants.
  • curve K in FIG. 5 it should be noted that an illustration of the selected curve K in quadrant II results in a curve which, in practice, cannot be used well due to the curl present in the curve and the piston swings that occur. With increasing values of n, it is therefore expedient to make the values d smaller, which is also shown by the curve K "in FIG.
  • Fig. 7 shows a pivot piston 3 which is mounted on a pivot pin 10 with the pivot point S.
  • the end points of the sealing strips 11, 12, which are carried by the piston ends, are designated by 6 and 7 and lie in quadrant I on the housing inner wall 2, which is formed by the selected curve.
  • the surface 13 of the piston 3 facing the wall of the housing 1 has almost the same curvature as the selected curve in quadrant I or III.
  • the sealing strips 11, 12 can be resiliently mounted in their bearing recesses 14 with indicated springs 14 'and can be pressed with these springs 14 against the inner wall 2 of the housing 1.
  • Sealing strip 11 is rounded on the surface 15 facing the housing.
  • Fig. 9 shows schematically a piston 3 with such sealing strips 11, 12 arranged in a housing 1.
  • Quadrant I shows the selected curve from point Po to point Q.
  • the sealing strip 12 lies with its lateral area 17 facing the pivot point S of the piston 3 on the inner wall of the housing, or the curvature of the surface area 17 is adapted to the curvature of the inner contour 2 of the housing 1 in this area.
  • Mirror-image conditions apply to the indicated sealing strip 11.
  • the tip 6 of the sealing strip 12, indicated by dashed lines in FIG. 8, would come to rest at point Q; however, since the surface 15 of the sealing strip 12 is rounded, the curved surface 15 ends at a short distance from the point Q.
  • the curve in quadrant II of the housing 1 is now e.g. determined by mapping how the curves 41 in quadrant II of FIGS. 1-6, but it should be noted that the curve 40 obtained is shifted somewhat in the direction of the coordinate origin 0, since the point 16 generating the curve does not remain fixed in position, but instead the curve is determined from the outermost point of the curved surface 15 of the sealing strip 11. It can be seen from the areas 15 'drawn in that the area 15 of the sealing strip 11 leads over the developed curve or that another point of the area always touches the illustrated curve until it comes to a point in the middle of it at point Qo . When the sealing strip 12 moves further, it slides
  • the distance a between the center of the curved surface 15 of the sealing strips 11, 12 and the points P, Q selected on the curve is approximately 1/50 to 1/400 of the piston length. (Fig.8).
  • the rotary pistons are driven by the shaft 5.
  • Suction and outlet openings are provided in the housing, preferably on the circumferential line of the housing shell, the outlet openings in the region 27 (FIG. 1a) and 24 being in the upper piston position depending on the clearance space and the inlet openings 22 and 26 depending on the outlet openings are in area 28.
  • the deviation or the range 27 is selected so that the piston 3 with its trailing end only crosses (releases) the rear edge 29 of the outlet slot 20 when the compressed gas located in the harmful space 8 has expanded to ambient pressure (1 bar).
  • (Damaged space volume between the piston curvature and the housing at top dead center, or in addition the space 30 between the compression space and check valve in space 20).
  • the rotary compressor works as a typical 2-cycle machine, namely suction and compression, with each cycle extending over 90 °, so that each of the two pistons produces 2 work cycles per shaft revolution.
  • a 2-piston compressor therefore produces a total of 4 work cycles per shaft revolution.
  • the volume space 9 is filled through the opening 22.
  • the compression stroke begins when the trailing piston end on the sealing element exceeds the edge 31.
  • a pressure which is greater than the counterpressure which acts on the valve at 24 on the opposite side, the compressed gas leaves the chamber through the opening in area 24.
  • the residual gas remaining in the contaminated space expands to ambient pressure when the piston continues to rotate, with work being carried out; through inlet 26, the next cycle begins with a new intake stroke.
  • the required inlet and outlet cross-section is achieved by the required area in the form of an elongated hole (slot) is stretched as far as possible transversely to the direction of rotation, so that the distance between the front and rear edges of this slot in the direction of rotation becomes as small as possible.
  • slot elongated hole
  • a fluid pump conveys (preferably) liquid media.
  • the entire interior 31, which is only limited by the two (schematically indicated) piston undersides 32/32 'and the housing inner wall 2, and is therefore subject to a change in volume of approximately twice the volume 9 per revolution by 90 ° (1/4 revolution), is used as 3rd work space. Due to the incompressibility of the liquid media, the "stroke volume" of the machine per shaft revolution is approximately doubled.
  • the drive shaft 5 is turned clockwise, the two chambers 9/33 are filled through the openings 22 and 26 and the full interior 31 is emptied through the openings 30 and 24. If the two pistons simultaneously exceed the 90 ° and 270 ° position, the two chambers 9 and 33 are filled to the maximum or the interior 31 is emptied to the maximum. Upon further rotation to 180 ° or 360 °, the chambers 9 and 33 are emptied and the interior 31 is filled to the maximum. A displacement of the openings 20, 22, 24, 26 by the amount 27 or 28 as in the compressor is not necessary.
  • the embodiment for internal combustion engines sees in the range 0 ° or. 360 ° at least one spark plug in front, in the range of approx. 125 ° - 165 ° an exhaust opening and an intake opening in the range of approx. 200 ° - 240 ° when turning to the right

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Dispositif à pistons rotatifs prévu pour un moteur, une pompe, un compresseur etc., dans lequel au moins deux pistons, situés dans un boîtier, sont maintenus de manière à pivoter, par le centre de leur axe longitudinal, sur des consoles. Les consoles sont reliées, de manière à résister à la rotation, avec un arbre d'entraînement ou un arbre entraîné, dont le point milieu constitue le point central du boîtier et l'origine des coordonnées, les extrémités des pistons étant appliquées de manière étanche contre la paroi intérieure du boîtier. La paroi intérieure, ou le contour du boîter, est divisée en quatre quadrants, dont les quadrants opposés présentent un contour intérieur inversé. Ledit contour intérieur du boîtier est symétrique dans chaque quadrant par rapport à l'axe de coordonnée correspondant qui traverse le quadrant. Les points extrêmes du contour intérieur dans chaque quadrant sont déterminés par les points (P, Q, R, T) qui, par rapport au point milieu du boîtier, présentent, comme origine de coordonnée, les coordonnées x, y x = U l/2 et y = U l/2, où l représente la longueur du piston. Selon l'invention, le point de pivotement (S) du piston (3) situé sur la console (4) à la hauteur de la ligne de liaison se trouve entre les extrémités d'attaque (7) et de fuite (6) du piston (3). Le contour intérieur de l'un des quadrants (I, II, III, IV) est formé par une ligne courbe qui satisfait à l'équation xn + (y+M)n = rn entre les points extrêmes (P, Q) du quadrant (I).
EP19870907403 1986-11-14 1987-11-13 Dispositifs a pistons rotatifs Withdrawn EP0289561A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT304386 1986-11-14

Publications (1)

Publication Number Publication Date
EP0289561A1 true EP0289561A1 (fr) 1988-11-09

Family

ID=3544423

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19870907403 Withdrawn EP0289561A1 (fr) 1986-11-14 1987-11-13 Dispositifs a pistons rotatifs

Country Status (3)

Country Link
EP (1) EP0289561A1 (fr)
AU (1) AU8232687A (fr)
WO (1) WO1988003601A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU726791B1 (en) * 2000-05-12 2000-11-23 Peter A. Szorenyi Hinged rotor internal combustion engine
US6315538B1 (en) * 2000-05-26 2001-11-13 Masahiro Tagami Driven equipment for fluid machinery
ATE335913T1 (de) * 2003-06-03 2006-09-15 Giovanni Donato Endothermischer motor mit drehenden kolben

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE637476A (fr) *
ES490268A0 (es) * 1980-04-02 1981-02-16 Martin Artajo Jose Ignac Maquina termodinamica de embolos sateloidales articulados
EP0160040A1 (fr) * 1983-10-13 1985-11-06 Hubert Petutschnig Moteur rotatif, compresseur rotatif

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8803601A1 *

Also Published As

Publication number Publication date
WO1988003601A1 (fr) 1988-05-19
AU8232687A (en) 1988-06-01

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