EP0571910A1 - Rotationskolbenmaschine - Google Patents

Rotationskolbenmaschine Download PDF

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Publication number
EP0571910A1
EP0571910A1 EP93108318A EP93108318A EP0571910A1 EP 0571910 A1 EP0571910 A1 EP 0571910A1 EP 93108318 A EP93108318 A EP 93108318A EP 93108318 A EP93108318 A EP 93108318A EP 0571910 A1 EP0571910 A1 EP 0571910A1
Authority
EP
European Patent Office
Prior art keywords
ring
machine according
shaft
housing
wing
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Withdrawn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
EP93108318A
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German (de)
English (en)
French (fr)
Inventor
Jürgen Dr. Kuechler
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 EP0571910A1 publication Critical patent/EP0571910A1/de
Withdrawn legal-status Critical Current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
    • F01C1/30—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
    • F01C1/34—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 relative reciprocation between the co-operating members
    • F01C1/344—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 relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F01C1/352—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 relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the vanes being pivoted on the axis of the outer member

Definitions

  • the invention relates to a rotary piston machine according to the preamble of claims 1 and 7.
  • Such machines can be designed as a pump, as a compressor or as a motor or combustion chamber turbine. Conventionally, they have in a housing an annular body which is eccentrically mounted with respect to a main shaft and which, in pumps and compressors, drives a chamber system which rotates as a whole, with vanes limiting variable chamber volumes.
  • CH 445 947 C1 describes a machine whose blades (called blades there) penetrate the ring body in a radially sliding manner and with their ends are guided along the housing wall and along an inner sleeve, as is also the case according to US Pat. No. 3,572,985 A1 is provided.
  • the somewhat cumbersome assembly is disadvantageous, but above all the storage and lubrication conditions as well as the design of the Ring body, which requires bulges and recesses at certain circumferential positions.
  • the wings are guided in sliding blocks or joint forks, which are located between segments of the ring body and can be rotated or pivoted so that the wings can assume different angular positions relative to one another during the rotation.
  • practical problems result from the fact that when a trailing wing is turned into a leading position, high edge pressure occurs on the inner wall of the casing body, which can lead to damage and highly undesirable deformations.
  • the disadvantages of such arrangements are avoided by a system according to EP 0 011 762 B1, which, however, requires a housing that deviates from the shape of a circular cylinder and therefore poses problems in terms of production technology.
  • the new machine is designed to be maintenance-friendly and to combine a favorable power-to-weight ratio with a wide range of speeds and torques as well as a wide range of possible uses. It also strives for quiet running, economical operation and a long service life.
  • each wing is assigned to a ring element, that these ring-wing elements are vertically offset, relatively movable components of a ring package and that the shaft, together with the ring body attached to it, or thus integral, is mounted centrally in the housing is.
  • each ring-wing element can move within a limited angular range independently of the neighboring elements, without any mutual interference taking place.
  • the angular positions occupied by the vanes determine the current dimensions of the rotating chambers, which continuously change their size due to the axis displacement of the ring body (in the case of compressor and pump) relative to the driven ring pack and convey the fluid entering a suction opening, compress it if necessary and then push out.
  • each ring-wing element has an inner ring and an outer ring concentric therewith, and each pair of inner and outer rings is rigidly attached to each wing, offset in height by at least one ring thickness, or is integral therewith. Thanks to this construction, the sealing problems are reliably solved in a very simple manner. In addition, the very compact ring package can be stored well.
  • the inner rings can be rotatably mounted on an eccentric pin according to claim 4, which is rigidly connected to the cover plate or in one piece, in particular according to claim 5. With regard to this pin, the ring elements are all centered, which further contributes to smooth running.
  • the machine can have a flat end plate or drive disk on the ring body, which is connected to it in one piece or rigidly and in turn is connected to the drive shaft.
  • a flat end plate or drive disk on the ring body which is connected to it in one piece or rigidly and in turn is connected to the drive shaft.
  • only flat parts slide against each other during the circulation, which ensures secure sealing with low friction losses.
  • the invention provides that the ring body has a cylinder coaxial to the shaft, which is guided in a cover plate eccentrically to the centrally arranged axis of a ring assembly, which the individual wings on mutually vertically offset and relatively movable ring wings Elements.
  • the axes of rotation of the ring body and ring pack are interchanged here, with an otherwise identical structure.
  • the ring-wing elements can also move within a limited angular range without mutual interference.
  • the ring body which separates the inner chambers from the outer, has a bearing and sealing function at the same time.
  • the shaft is preferably rigidly connected or in one piece.
  • each ring-wing element can consist of an inner ring and an outer ring concentric therewith, each pair of inner and outer rings on each wing being rigidly fixed or offset in one piece by at least one ring thickness.
  • the construction ensures high stability and smooth running.
  • cover plate is rigidly connected or integral with a central pin on which the inner rings of the ring packet can be rotatably mounted according to claim 11. Additional smoothness is obtained according to claim 12 in that the ring package is enclosed by a casing of the housing or is stored therein.
  • the ring body and / or the end plate or drive disk rests in a sealingly sliding manner on an end face of the housing, with minimal friction losses occurring due to the surfaces sliding past each other.
  • the cover plate located on the opposite side, screwed to the housing on the circumference has a cover surface on which the ring-wing element of the ring package which slides next to it slides, so that a friction-free and reliable support is also guaranteed there is.
  • the machine generally designated 10 of the embodiment of FIGS. 1 and 2 has a housing 12 with a bore 14 which receives a bearing 16 for a shaft 18. This is rigidly connected or in one piece to an annular body 20, which consists of a disk or plate 22 and of arcuate segments 24 which hold sliders 28 between recesses 26 (FIG. 2).
  • Wings 34 are guided in these sliding pieces 28, each of which is integral with an inner ring 32 and an outer ring 36, as illustrated in FIGS. 3 to 5 for two ring-wing elements a, b.
  • the individual ring-wing elements of such a ring package 30 (FIG. 1) are offset in angle with one another with their wings 34, as in FIG. 2 for six ring-wing elements a, b, c, d, e, f with their wings 34 emerges.
  • Fig. 3 a ring package with five ring-wing elements a, b, c, d, e is shown, of which the two ring-wing elements a and b in Fig. 4 and 5 each in one (axial ) Section are shown.
  • each ring element is rigidly connected or integrally connected to the associated wing 34 by at least one ring thickness w each offset in height; if, for example, the next ring-wing element c were shown in a figure following FIG. 5, it would have offset the inner and outer rings 32, 36 to the right by a further ring thickness w.
  • the inner rings 32 are mounted with their inner annular surface 50 on an eccentric pin 48 which is rigidly attached to a cover plate 40 or is integral with it. Its axis A is offset from the parallel shaft axis M by the dimension v, so that the ring packet 30 rotates eccentrically with respect to the ring body 20. Its lower or inner ends slide on an eccentric ring 38 which is flush with the cover plate 40.
  • a recess 44 forms the radially supporting boundary of the disk or plate 22, which rests on a flat end face 52 of the housing 12 such that it can slide.
  • Screws 46 arranged on the circumference connect the housing 12 to the cover plate 40, optionally with the interposition of spacers (not shown) which enclose the ring packet 30 in the form of a jacket.
  • the described embodiment forms a rotary pump with two pump circuits, outer chambers K receiving the pump medium via a suction opening (not shown).
  • An overflow channel (likewise not shown for the sake of clarity) allows the pump medium to flow into the inner chambers, which convey about two thirds of the volume of the outer chambers. If separate inflow and outflow openings are provided, the pump can also be designed with separate circuits.
  • the shaft 18 drives the ring assembly 30 via the ring body 20, the vanes 34 occupying different positions with respect to one another within a limited angular range, so that result in larger and smaller chamber volumes.
  • the pivoting of the wings is made possible by the sliders 28 in which the individual wings 34 are slidably guided. Since all ring-wing elements within the ring packet 30 rotate at the same speed, but continuously changing phase shift, tolerance-related deviations do not play a role; they are irrelevant and harmless to the overall system. The only slight twisting of the ring-wing elements a ... e or a ... f with each other also have the consequence that only slight friction losses occur. If necessary, sealing elements (not shown) can be provided along the outer edges of the wings 34 in order to further improve the sealing of the ring packet 30.
  • the entire pump system can be lubricated very well, both on the eccentric pin 48 for the inner rings 32 and - possibly via the ring body 20 - on the outer rings 36. Radial forces that occur are completely absorbed in the recess 44 of the housing 12 and, if appropriate, on the jacket parts.
  • the machine 10 operates extremely quietly, is not very susceptible to faults and is easy to maintain.
  • the same construction is suitable for operation as a compressor, only overflow channels (not shown) being arranged in the cover 40, which guide compressed air from the outer chambers into the inner circle. It is possible to intercool the first compression stage. The air is drawn through an outlet (not shown) in the fixed housing 12.
  • the housing 12 merges into a jacket 62 which is firmly connected to a cover plate 60 by screw connections 46.
  • This is preferably in one piece with a central pin 64 on which the inner rings 32 of a ring packet 30 are mounted, which in the present case has five individual ring-wing elements a, b, c, d, e.
  • a sliding washer 54 can be provided, which provides sealing support between the inner surface of the ring body 20 and the end face of the central pin 64 with low friction.
  • An annular groove 66 in the cover plate 60 slidably receives the inner end 68 of the cylinder 58.
  • the axes of the two systems 20 and 30 rotating at the same speed are again designated M and A and offset from one another by the dimension v.
  • the five wings 34 of the ring assembly 30 with the ring-wing elements a, b, c, d, e also move with a different phase shift with respect to the ring body 20, so that the desired pumping or compression effect is achieved by changing the volume of the chambers K is achieved.
  • the external and internal circuits can either form separate circuits or be connected in series to form a two-stage conveyor circuit.
  • a rotary piston machine which can be designed in particular as a pump or compressor, preferably has a housing 12 in which a driven shaft 18 is mounted, which rotatably drives an annular body 20, which has arcuate segments 24 with pivotable, axially parallel sliding pieces 28 and between cover surfaces 42 , 52 on the face is led.
  • Sliders 28 slidably guide wings 34, which limit the size-variable chambers K outside and / or inside the ring body 20.
  • Each wing 34 is in one piece with an inner ring 32 and a concentric outer ring 36.
  • the individual ring-wing elements a ... e and a ... f are each offset in height by a ring thickness w on the wings 34 and are relatively movable with respect to one another.
  • the inner rings 32 are rotatably mounted on a pin 48 or 64 which is fastened to a cover plate 40 or 60.
  • the axis A of the ring packet 30 is offset from the shaft axis M by the dimension v, so that the wings 34 assume different angular positions with respect to one another during their rotation.
  • the shaft 18 together with the ring body 20 can be arranged centrally in the housing 12 (FIGS. 1 and 2) or eccentrically (FIGS. 6 and 7), the ring packet 30 being guided eccentrically or centrally along the cover plate 40 or 60.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP93108318A 1992-05-26 1993-05-22 Rotationskolbenmaschine Withdrawn EP0571910A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9207087U DE9207087U1 (de) 1992-05-26 1992-05-26 Rotationskolbenmaschine
DE9207087U 1992-05-26

Publications (1)

Publication Number Publication Date
EP0571910A1 true EP0571910A1 (de) 1993-12-01

Family

ID=6879877

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93108318A Withdrawn EP0571910A1 (de) 1992-05-26 1993-05-22 Rotationskolbenmaschine

Country Status (3)

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US (1) US5332375A (ja)
EP (1) EP0571910A1 (ja)
DE (1) DE9207087U1 (ja)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CZ290702B6 (cs) * 1999-05-04 2002-09-11 Jiří Ing. Frolík Rotační stroj s oběžnými křídly, zejména pro kompresory nebo tepelné motory
US6659744B1 (en) * 2001-04-17 2003-12-09 Charles Dow Raymond, Jr. Rotary two axis expansible chamber pump with pivotal link
WO2010147979A1 (en) * 2009-06-17 2010-12-23 Green Partners Technology Holding Gmbh Rotary vane engines and methods
WO2012125572A2 (en) 2011-03-11 2012-09-20 Brooks Automation, Inc. Substrate processing tool
CZ23692U1 (cs) * 2012-03-12 2012-04-16 Frolík@Jirí Vodní náporová obtoková turbína
KR101697148B1 (ko) * 2016-03-04 2017-01-17 황광선 원심 흡입식 하이브리드 베인 유체기계
IT201700108572A1 (it) * 2017-09-28 2019-03-28 Ceruti Giambattista Emilio Sistema di tenuta indipendente da forza centrifuga e pressione per pompe e compressori a palette

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2891482A (en) * 1956-12-01 1959-06-23 Emanuel Di Giuseppe E Roberto Rotary machine adapted to operate as a pump or as a fluid motor
CH445947A (de) * 1964-10-23 1967-10-31 Svendia Dental Ind Ab Als Motor oder als Pumpe arbeitende Rotationsmaschine
US3572985A (en) * 1968-03-19 1971-03-30 Franz Joachim Runge Rotary piston machine
EP0011762A1 (de) * 1978-11-28 1980-06-11 Kuechler, Jürgen Dr. Rotationskolbenmotor
FR2590932A1 (fr) * 1985-12-02 1987-06-05 Valibus Alain Dispositif volumetrique et perfectionnements aux machines tournantes a palettes ou parois

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2071799A (en) * 1934-09-08 1937-02-23 Mabille Raoul Rotary engine
US2448233A (en) * 1943-11-02 1948-08-31 Mining Engineering Co Ltd Rotary intersecting vane engine and compressor
US3072068A (en) * 1958-10-13 1963-01-08 American Thermocatalytic Corp Vane pumps
DE1300523B (de) * 1964-07-10 1969-08-07 Degussa Verfahren zur Herstellung von Natriumboranat oder dieses enthaltenden Mischungen
US3401872A (en) * 1966-06-09 1968-09-17 Gen Motors Corp Fluid flow control mechanism
US3552895A (en) * 1969-05-14 1971-01-05 Lear Siegler Inc Dry rotary vane pump

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2891482A (en) * 1956-12-01 1959-06-23 Emanuel Di Giuseppe E Roberto Rotary machine adapted to operate as a pump or as a fluid motor
CH445947A (de) * 1964-10-23 1967-10-31 Svendia Dental Ind Ab Als Motor oder als Pumpe arbeitende Rotationsmaschine
US3572985A (en) * 1968-03-19 1971-03-30 Franz Joachim Runge Rotary piston machine
EP0011762A1 (de) * 1978-11-28 1980-06-11 Kuechler, Jürgen Dr. Rotationskolbenmotor
FR2590932A1 (fr) * 1985-12-02 1987-06-05 Valibus Alain Dispositif volumetrique et perfectionnements aux machines tournantes a palettes ou parois

Also Published As

Publication number Publication date
DE9207087U1 (de) 1992-11-26
US5332375A (en) 1994-07-26

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