EP0066255A1 - Souffleur à piston rotatif à axe externe - Google Patents

Souffleur à piston rotatif à axe externe Download PDF

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Publication number
EP0066255A1
EP0066255A1 EP82104605A EP82104605A EP0066255A1 EP 0066255 A1 EP0066255 A1 EP 0066255A1 EP 82104605 A EP82104605 A EP 82104605A EP 82104605 A EP82104605 A EP 82104605A EP 0066255 A1 EP0066255 A1 EP 0066255A1
Authority
EP
European Patent Office
Prior art keywords
shut
sleeve
rotor
hollow cylinder
tooth
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
EP82104605A
Other languages
German (de)
English (en)
Inventor
Dankwart Eiermann
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.)
Wankel GmbH
Original Assignee
Wankel 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 Wankel GmbH filed Critical Wankel GmbH
Publication of EP0066255A1 publication Critical patent/EP0066255A1/fr
Ceased legal-status Critical Current

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Classifications

    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/14—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using rotating valves
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids 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
    • F04C18/20—Rotary-piston pumps specially adapted for elastic fluids 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 blower with a housing formed from at least two overlapping parallel-axis cylindrical inner spaces, each of which is penetrated by a shaft, with on one shaft a cylindrical working space providing a ring-shaped working space with a shut-off tooth and forming a ring with the surrounding housing wall the other shaft rotating in the opposite direction has a cylindrical shut-off rotor running against the housing wall and rolling on the working rotor with a recess for the contact-free passage of the shut-off tooth and the body of the working rotor is a hollow cylinder, which temporarily comes into cover with a control opening provided in the shut-off teeth or with a further control opening in a fixed sleeve arranged in the hollow cylinder during its circulation.
  • the working rotor and the shut-off rotor run against each other with a toothing which is interrupted by the toothed teeth which cooperate with the recesses of the shut-off rotor and which otherwise occupy their entire axial surface, so that a synchronous gear is not required.
  • DE-OS 22 22 500 Another such machine is described in DE-OS 22 22 500, in which only one shut-off tooth and one shut-off rotor are provided, which are driven in opposite directions by a 1: 1 gearbox.
  • the object of the invention is to avoid the described flow obstructions due to accumulation and pressure vibrations and the power losses caused thereby, and also to avoid the leakage paths between the housing side walls and the shut-off rotor while allowing a greater axial play of this rotor, but at the same time a very simple and accordingly inexpensive overall construction to find.
  • this object is achieved in that the hollow cylinder is mounted in a first part of the housing and is fixedly and coaxially connected to the drive shaft mounted in the other side part of the housing, and that the sleeve, which is sealed by the hollow cylinder and is fixed in the first side part, is also provided their entire interior is an inlet channel for the intake air and that in this in the direction of rotation of the back side of the hollow shut-off tooth there is an inlet opening for the working gas into the suction space and in the housing jacket an outlet channel for the delivered working gas, which is essentially tangential to the movement of the working area Direction runs.
  • a better degree of filling, in particular at high speeds, namely of about 20 to 30% and a corresponding improvement in efficiency can be achieved in that in the wall of the cylindrical space facing the outlet duct, in which the shut-off rotor rotates, a connecting duct from this cylindrical space is provided for the outlet channel with an axial length of about 80 to 90% of the length of the shut-off rotor, which widens after the outlet channel and which is too open after the cylindrical space in which the working rotor rotates.
  • an inner bearing is arranged in the hollow cylinder, an equally large inflow cross section for the working gas can be obtained by the fact that the hollow cylinder is mounted in the inner flange in the outer flange in the first side part, that a central passage opening for the sucked-in working gas and a plurality of lateral passage openings for the working gas surrounding this central passage opening have bearing through the inner bearing and the sleeve Webs are separated, and that an annular space surrounding the inner bearing is formed in the side part, via which the lateral passage openings are connected to openings in the wall of the hollow cylinder.
  • the sealing of the working chambers among themselves and the sealing of the pressurized ejection chambers can be improved in that the right side wall has a recess which is coaxial with the shaft and into which a cylindrical extension of the hollow cylinder which is coaxial with this recess engages without contact, the fit in the recess is narrower in the radial direction than in the axial direction.
  • the sleeve In order to be able to improve the delivery pressure or delivery quantity of the working gas, it is proposed to design the sleeve so that it has a plurality of axially directed slots in its part which blocks the control opening of the hollow cylinder, and that the sleeve has a further one which can be rotated arbitrarily from the outside about its longitudinal axis
  • Sleeve encloses, which has a control opening corresponding to the control opening of the first sleeve as well as axial shut-offs in its shut-off part corresponding to the shut-off part of the first sleeve, which, when this additional sleeve is rotated, come into congruence with the slots of the first sleeve or can shut them off.
  • the closed side of the shut-off tooth facing the working space has an angle of 20 to 30 ° with respect to the radial central axis of the shut-off tooth both on its inner wall and on its outer wall in radial section.
  • the blower shown in Fig. 1,2 and 3 has a housing 1 that consists of two overlapping parallel-axis cylindrical spaces 2 and 3, which are formed by a housing shell 4 and side parts 5 and 6, the latter side part integral with the shell part connected is.
  • a housing shell 4 and side parts 5 and 6 In the larger space 3 protrudes axially and concentrically in the right side part 6 in the ball bearing 7 drive shaft 8, to which a coaxial hollow cylinder 9 is welded in the interior of the space 3, which forms the body of the working runner 10.
  • This hollow cylinder 9 is supported from the outside at its left end on a further ball bearing 11 arranged in the side part 5.
  • a sleeve 12 is screwed to an outer flange 13, which projects coaxially into the cylinder 9 almost to its end.
  • a shut-off tooth 15, which together forms the working runner 10 is screwed together, which runs along the jacket raceway 16 of the housing jacket 4 with its edges 17 without contact, but forming a very small gap.
  • the working tooth 15 is fastened to the hollow cylinder 9 with screws.
  • the shut-off tooth On its rear side in the direction of rotation, the shut-off tooth has an inlet opening 19 for the entry of the working gas into the space 3, which takes up the entire available axial width and radial height of the working tooth 15.
  • a control opening 20 is provided which takes up the entire base of the interior of the shut-off tooth 15.
  • This control opening 20 is in register with a further control opening 21 in the sleeve 12 in the intake stroke.
  • the control opening 21 has the same axial width as the control opening 20 in the hollow cylinder 9 and an extent in the circumferential direction of 40 ° to 325 ° after the TDC position of the workman, that is to say the position shown in FIG. 1.
  • the open side of the sleeve 12 in FIG. 2 is the inlet 22 for the working gas, at which a suction nozzle can be arranged.
  • a shut-off rotor 23 which starts at its jacket raceway with a very small clearance is arranged coaxially, which has the same radial diameter as the hollow cylinder 9 and rolls on it.
  • the shut-off rotor 23 is mounted on shaft ends 24, 25 in ball bearings 26, 27 in side parts 5, 6. In radial cross section, it has a circular arc-shaped recess 28 for the passage of the shut-off tooth 15.
  • the axial extent of the space 2 is wider than that of the space 3.
  • the side parts 5 and 6 accordingly have recesses 29, 30 into which the shut-off rotor projects laterally. The purpose of this is to achieve a better seal.
  • the cylinder wall of the stopper 23 and the recesses 29 and 30 can be fitted much more closely to a narrow gap than the necessary clearance between the side walls 31 and 32 of the stopper 23 and the counter surfaces 33, 34 of the recesses 29, 30 allow.
  • This axial play can therefore be that of the commercially available ball bearing, i.e. about 0.5 mm.
  • the shut-off rotor 23 has cavities 35 on its side opposite the recess 28 and recesses 36, 37 on its side walls 31, 32. Tie rods are provided at 38 and 39.
  • the shut-off tooth 15, which is made of cast aluminum, does not need to be balanced, since its weight corresponds to the material of the hollow cylinder 9 removed to produce the control opening 20, which is made of steel.
  • the drive shaft 8 of the working rotor 10 and the stub shaft 25 of the shut-off rotor 23 are non-positively connected by a gear 42 consisting of two gear wheels 40, 41 in a ratio of 1: 1.
  • the outlet channel 43 for the working gas is arranged in the housing jacket 4 directly in front of the line of intersection of the cylindrical spaces 2 and 3 and has its axis in a tangential direction to the direction of rotation of the working rotor 10 in order to allow an unobstructed discharge of the working gas without a significant change in direction.
  • the transition from the jacket raceway 16 to the outlet duct 43 is rounded off at 44 in order to avoid a vortex-forming edge.
  • FIG. 3 a The mode of operation of the blower is shown in the position diagrams of FIG. 3:
  • FIG. 3 a the preceding expulsion of the working gas is completed and in FIG. 3 b the intake stroke begins with the opening of the control opening 21 in the sleeve 12 through the control opening rotating about it 20 in the shut-off tooth 15, while the shut-off rotor 23 divides the annular working space into a suction chamber 45 and an ejection or compression chamber 46.
  • Figures 3 h, a, b. show the passage of the shut-off tooth 15 through the shut-off rotor 23, whereby no squeezing currents can occur in the working gas due to the acute-angled tooth shape and the narrow radial contact surface of the shut-off tooth.
  • control opening 21 in the sleeve 12 can be shortened accordingly, but the best results are achieved with the indicated values of 40 to 320 °.
  • the described embodiment is very simple and extremely cheap to manufacture in mass production. All parts that come into contact with one another have the shape of circular arcs, which enables simple manufacture by drilling and round milling, and which also allows very precise adjustment.
  • the shut-off tooth is a simple casting. The axial clearances do not require any special tolerance and, finally, the ratio between drive power and throughput is much more favorable than with other known solutions.
  • FIG. 6 shows a left side part 105, in which the hollow cylinder runs in an inner bearing 111 against the sleeve 112.
  • an outer flange 113 is arranged, which has a central passage opening 114 for the working gas, and lateral passage openings 115, between which webs 116 are provided which support the inner bearing 111.
  • the sleeve 112 is also fastened to the fixed part of this bearing and the hollow cylinder 109 to its movable part.
  • the annular space 117 is also provided, through which the working gas entering the side inlet openings 115 passes through the openings 118 gets into the hollow cylinder 109.
  • This arrangement is necessary at high speeds, since an outer bearing with the diameter as shown in FIG. 2 would be overloaded.
  • the reduction in the cross section of the inlet opening in the hollow cylinder 109 through the inner bearing 111 is compensated for by the measures described.
  • Figs. 7 and 8 show the arrangement of an internal controller.
  • the sleeve 212 which has three axially directed slots 214 in its shut-off part 213, encloses a further sleeve 215 which can be rotated arbitrarily from the outside about its longitudinal axis and which in turn has axially directed slots 216 in its shut-off part 217. Both sleeves have corresponding control openings 218 and 219.
  • FIG. 8 shows a preferred embodiment with three slots 214 and 216 each, the axial center lines of the slots 214 being 34 ° apart.
  • FIG. 7 also shows a floating mounting of the hollow cylinder 221 in a double bearing 222 which ( * The sleeve 215 is rotated with a pin arranged at 225, which engages through a slot in the outer flange 226.
  • the angle which the closed outer wall of the shut-off tooth facing the working space has on its inside as well as on its outside in radial section with respect to the radial central axis of the shut-off tooth is most suitably approximately 20 °. This avoids squeezing flows and tests have shown that the best flow conditions and efficiencies can be achieved with the angular dimensions mentioned.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary-Type Compressors (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP82104605A 1981-05-29 1982-05-26 Souffleur à piston rotatif à axe externe Ceased EP0066255A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3121269 1981-05-29
DE3121269 1981-05-29

Publications (1)

Publication Number Publication Date
EP0066255A1 true EP0066255A1 (fr) 1982-12-08

Family

ID=6133423

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82104605A Ceased EP0066255A1 (fr) 1981-05-29 1982-05-26 Souffleur à piston rotatif à axe externe

Country Status (3)

Country Link
US (1) US4464102A (fr)
EP (1) EP0066255A1 (fr)
JP (1) JPS5832989A (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0137421A2 (fr) * 1983-10-10 1985-04-17 Wankel, Felix, Dr. h.c. Machine à piston rotatif à axe externe
GB2315098A (en) * 1996-07-10 1998-01-21 Tried Applied Technology Limit Rotary machine
US6612382B2 (en) 1996-03-25 2003-09-02 Halliburton Energy Services, Inc. Iterative drilling simulation process for enhanced economic decision making
DE102004005468B4 (de) * 2004-02-03 2013-11-21 Franz-Harro Horn Rotationskolbenmaschine

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3340202A1 (de) * 1983-11-07 1985-05-15 Wankel Gmbh, 1000 Berlin Parallel- und aussenachsiges im kaemmeingriff arbeitendes rotationskolbengeblaese
JPS6148746U (fr) * 1984-09-05 1986-04-01
US5466138A (en) * 1993-07-22 1995-11-14 Gennaro; Mark A. Expansible and contractible chamber assembly and method
US5518382A (en) * 1993-07-22 1996-05-21 Gennaro; Mark A. Twin rotor expansible/contractible chamber apparauts
US5364249A (en) * 1993-10-28 1994-11-15 Link Donald M Rotary steam engine having rotor side plates
US8794945B2 (en) * 2008-04-10 2014-08-05 Fritz Forgy Rotary pump or motor with orbital piston aspiration
US9267504B2 (en) 2010-08-30 2016-02-23 Hicor Technologies, Inc. Compressor with liquid injection cooling
US8794941B2 (en) 2010-08-30 2014-08-05 Oscomp Systems Inc. Compressor with liquid injection cooling
US9127548B2 (en) * 2011-03-23 2015-09-08 Arthur Ryuji Ishii 3-stroke/6-stroke rocket jet engine

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE68978C (de) * G. H. WESTON in Boston, Massachusetts, V. St. A Abdichtungsvorrichtung für Maschinen mit zwei innerhalb eines Doppelgehäuses in gleicher Axenebene sich gegeneinander drehenden, einander an ihrem Umfange berührenden cylindrischen Kolben
DE303623C (fr) *
GB359691A (en) * 1930-10-14 1931-10-29 Torsten Ramen Improvements in rotary machines
FR1071861A (fr) * 1952-11-17 1954-09-06 Appareil rotatif tel que compresseur, <<soufflante>>, pompe, ou autre provoquant ou travaillant par le déplacement d'un fluide
GB784554A (en) * 1955-08-30 1957-10-09 Clifford Edmund Brewer Improvements in or relating to rotary motors, compressors or the like
FR2277255A1 (fr) * 1974-07-02 1976-01-30 Compair Ind Ltd Machines a piston rotatif
US4144004A (en) * 1977-09-29 1979-03-13 Edwards Ray B Intermeshing gear rotary engine with valved inlet

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1640727A (en) * 1923-11-16 1927-08-30 Electrol Inc Gear pump
US2690869A (en) * 1950-09-02 1954-10-05 Arthur E Brown Rotary mechanism for use with fluids
US2829925A (en) * 1956-04-17 1958-04-08 Monteil Jean Andre Fan or blower, especially for use in pneumatic conveyor equipment
US3182900A (en) * 1962-11-23 1965-05-11 Davey Compressor Co Twin rotor compressor with mating external teeth
US3304838A (en) * 1965-02-12 1967-02-21 Harry W Mcdonald Fluid operated motor for drilling mechanism
US3472445A (en) * 1968-04-08 1969-10-14 Arthur E Brown Rotary positive displacement machines
US3601514A (en) * 1969-07-23 1971-08-24 Kermit J Afner Rotary machine

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE68978C (de) * G. H. WESTON in Boston, Massachusetts, V. St. A Abdichtungsvorrichtung für Maschinen mit zwei innerhalb eines Doppelgehäuses in gleicher Axenebene sich gegeneinander drehenden, einander an ihrem Umfange berührenden cylindrischen Kolben
DE303623C (fr) *
GB359691A (en) * 1930-10-14 1931-10-29 Torsten Ramen Improvements in rotary machines
FR1071861A (fr) * 1952-11-17 1954-09-06 Appareil rotatif tel que compresseur, <<soufflante>>, pompe, ou autre provoquant ou travaillant par le déplacement d'un fluide
GB784554A (en) * 1955-08-30 1957-10-09 Clifford Edmund Brewer Improvements in or relating to rotary motors, compressors or the like
FR2277255A1 (fr) * 1974-07-02 1976-01-30 Compair Ind Ltd Machines a piston rotatif
US4144004A (en) * 1977-09-29 1979-03-13 Edwards Ray B Intermeshing gear rotary engine with valved inlet

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0137421A2 (fr) * 1983-10-10 1985-04-17 Wankel, Felix, Dr. h.c. Machine à piston rotatif à axe externe
EP0137421A3 (fr) * 1983-10-10 1985-05-15 Wankel, Felix, Dr. H.C.
US6612382B2 (en) 1996-03-25 2003-09-02 Halliburton Energy Services, Inc. Iterative drilling simulation process for enhanced economic decision making
GB2315098A (en) * 1996-07-10 1998-01-21 Tried Applied Technology Limit Rotary machine
US6079386A (en) * 1996-07-10 2000-06-27 Tried Applied Technolog Limited Rotary machine
DE102004005468B4 (de) * 2004-02-03 2013-11-21 Franz-Harro Horn Rotationskolbenmaschine

Also Published As

Publication number Publication date
US4464102A (en) 1984-08-07
JPS5832989A (ja) 1983-02-26

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Inventor name: EIERMANN, DANKWART