EP0240491B1 - Rotationsmotor - Google Patents

Rotationsmotor Download PDF

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Publication number
EP0240491B1
EP0240491B1 EP85905507A EP85905507A EP0240491B1 EP 0240491 B1 EP0240491 B1 EP 0240491B1 EP 85905507 A EP85905507 A EP 85905507A EP 85905507 A EP85905507 A EP 85905507A EP 0240491 B1 EP0240491 B1 EP 0240491B1
Authority
EP
European Patent Office
Prior art keywords
expansion
working
expansion space
curve
annular surface
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 - Lifetime
Application number
EP85905507A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0240491A1 (de
Inventor
Michael L. Zettner
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.)
ZETTNER, MICHAEL L.
Original Assignee
Zettner Michael L
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 Zettner Michael L filed Critical Zettner Michael L
Publication of EP0240491A1 publication Critical patent/EP0240491A1/de
Application granted granted Critical
Publication of EP0240491B1 publication Critical patent/EP0240491B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F01C1/356—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 outer member
    • F01C1/3566—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 outer member the inner and outer member being in contact along more than one line or surface
    • 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

Definitions

  • the invention relates to a rotary motor for converting the expansion pressure of working gases into a mechanical rotary movement.
  • the expansion section in the form of a ring section corresponds to the cylinder space of a reciprocating piston engine.
  • a reciprocating piston engine there are no problems in sealing the round piston against the round cylinder. This sealing takes place by means of one or more sealing rings with a corresponding preload, which can compensate for different temperature expansions of the material, or with a correspondingly small piston cross section, without any piston rings.
  • EP-AS 0 080 070 A1 (Zettner).
  • an internal combustion engine is described with a rotor with a circular cross-section and a ring-shaped stator (inner rotor) surrounding the rotor, which is designed so that recesses in the form of expansion sections are present in the peripheral surface of the rotor as expansion spaces, at one end of which a combustion chamber is arranged and the other end ends in a ramp.
  • Flaps are pivotally mounted on the inside of the stator, which can be folded into the recesses of the rotor to absorb the forces of the expanding combustion gases and can be folded back into the stator by the ramp.
  • the expansion space has a rectangular shape in an axial section in the longitudinal direction of the axis, with the result that rectangular edges which have to be sealed in the circumferential direction and in the radial direction occur both on the ramps and on the flaps.
  • the simultaneous sealing of these edges both in the circumferential direction and in the radial direction is permanently impossible.
  • the invention is therefore based on the object of developing a sealing system for rotary motors which have an annular expansion space, which is seen in the circumferential direction and is limited by a fixed and a moving part, the wear behavior of which is at least comparable to the cylinder sealing system of reciprocating piston engines and that does not negatively affect the efficiency of rotary motors.
  • the invention proceeds as prior art from a rotary engine for converting the expansion pressure of working gases into a mechanical rotary movement, with an engine inner part with a cylinder-like outer peripheral surface, an engine outer part surrounding the engine inner part with a cylindrical inner peripheral surface, the outer peripheral surface and the inner peripheral surface opposite each other, bearings with which the inner and outer parts of the motor are rotatably supported against one another, at least one working cam located on one of the cylindrical peripheral surfaces, which is sealed off from the other cylindrical peripheral surface and transmits the expansion pressure of the working gases to the one engine part, at least one section-shaped recess in the same cylindrical circumferential surface in connection to the working cam as an expansion space for the working gases, an inlet and an outlet opening in each expansion space for the inflowing and outflowing working gases, at least one counter-pressure part movably mounted on the other cylindrical peripheral surface, projecting into the expansion space and transmitting the expansion pressure of the working gases to the other engine part, which closes the outlet opening in each expansion space for the working gases in the una
  • the invention consists in that the two circumferential surfaces have the shape of complementary ring surfaces, being seen in an axial section in the longitudinal axis direction through the ring surface and through the working cams, the one ring surface having the shape of a concave parabolic curve and the other ring surface having the shape of a convex parallel-like curve has and both ring surfaces with a close sliding fit parallel to each other to their outer edges, which form two circular slots.
  • the circumferential surface as a parabolic ring surface, all edges to be sealed both in the circumferential direction and in the radial direction in the interior of the motor and the associated sealing problems in the motor are avoided.
  • FIG. 1 shows a center section perpendicular to the motor axis along the half center line I-I of FIG. 2 through a rotary motor 100.
  • the rotary motor 100 is a first embodiment of this type of motor, which is described in more detail below.
  • the rotary motor 100 consists of an inner motor part 101 with a cylindrical outer circumferential surface 102 and an outer motor part 123 surrounding the inner motor part 101 with a cylindrical inner circumferential surface 124, the outer circumferential surface 102 and the inner circumferential surface 124 being close to one another as can be seen in FIG.
  • section-shaped recesses are provided as expansion spaces 107, 108, 109 for the working gas driving the rotary motor 100.
  • part of the cylindrical peripheral surface forms the working cam 104.
  • the rotary motor 1 has three expansion spaces 107, 108, 109 and thus three working cams 104, 105, 106.
  • the expansion space 107 is sealed off from the cylinder-like inner circumferential surface 124 in the circumferential direction by a seal 116. This makes it possible for the working cam 104 to transmit the expansion pressure of the working gases as a torque to the engine inner part 101.
  • the expansion spaces 108, 109 are sealed in the same way by seals 117, 118.
  • An inlet opening 110 for the working gases driving the rotary motor 1 opens into the expansion space 107. The same applies to the other expansion rooms 108, 109.
  • Compressed air, water vapor, organic vapors and also exhaust gases can be used as working gases, which are fed directly to the inlet openings 110, 111, 112.
  • liquid or gaseous fuels can be placed in an external combustion chamber with an oxidizer, e.g. Atmospheric oxygen, burned and the combustion gases are introduced through the inlet openings into the expansion rooms.
  • an oxidizer e.g. Atmospheric oxygen
  • spark plugs which, for example, in the direction of rotation, are seen in the rear of the working cams 104; 105, 106 can be arranged to ignite and burn.
  • a counter pressure part 126 which projects into the expansion space 107 and transmits the expansion pressure of the working gases to the motor outer part 123.
  • a total of four counter pressure parts 126, 127, 128, 129 are present on the motor outer part 123.
  • the counter-pressure part 126 also prevents the working gases from leaving the expansion space 107 from the outlet opening 113 until the relative rotation of the two motor parts 101, 123 relative to one another caused by the expansion of the working gases causes the counter-pressure part 126 to evade the working cam 106 and the Release outlet 113. This can be done in such a way that the working cam 106 is pressed back into a recess 136 against the pressure of a spring 132, 133, 134, 135 by the ramp 120, 121, 122 or the like shown in FIG.
  • FIG. 1A shows the rear edge 130 of the counterpressure part 126 with respect to the relative direction of rotation of both motor parts 101, 123, which can be designed as a wiping edge 130 and conveys the deposits in the expansion spaces to the respective outlet opening.
  • 1B shows a second possibility, which consists in providing the scraper edge 141 on the seal 137 of the counterpressure part 126.
  • FIG. 2 shows a first axial section in the longitudinal direction of the axis through the rotary motor 100 along the line 11-11 of FIG. 1. It can be seen from the section through the two circumferential surfaces 102, 124 that these have the shape of complementary ring surfaces, one ring surface 102 having the shape of a concave parabolic curve on average and the other ring surface 124 having the shape of a convex parabolic curve .
  • the term “parallel-like curve” means the parabola, the parabola-like curve described in FIG. 2A and the hyperbola.
  • the annular surfaces 102, 124 are obtained by rotating one of these parabolic curves around the axis of rotation of the motor 1, wherein the axis of symmetry of the parabolic curve can be at any angle on the axis of rotation.
  • the two ring surfaces 102, 124 run parallel to one another with a close sliding fit up to their outer edges 103, 125, which form two circular slots 148, 149.
  • the term "sliding fit”, which is generally known in the art, is to be understood that the distance d between the edges 103, 125 corresponds at least to the largest of the following three values: twice the mean roughness depth of the ring surface material or the radial and axial runout of the Ring surfaces 102, 124 or the differences in the thermal expansion coefficients of the ring surfaces 102, 124 which are effective during operation.
  • the radial sealing of the slots 148, 149 from the outside is additionally effected by the labyrinth seals 150, 151, since the ring surface parts corresponding to the curve branches of the parabolic curve as Laby rinth seals work.
  • the labyrinth seals 150, 151 consist of a seal with a single deflection of the outflow path for the working gases by 180 °.
  • the labyrinth seal can be seen in an axial section in the longitudinal direction of the axis, at any angle to the motor axis.
  • the recess 119 in the motor outer part 123 serves to receive a suspension of the counter-pressure parts and / or to cool the motor.
  • FIG. 2A shows the “parabola-like curve 144” mentioned above.
  • the parabola-like curve 144 consists of an arc 145, to which two straight lines 146, 147 adjoin. If the straight lines 146, 147 are extended beyond the circular arc 145, the straight lines 146, 147 enclose an angle ⁇ .
  • the angle ⁇ is always less than 180 °.
  • FIG. 3 shows a second axial section in the longitudinal axis direction through the rotary motor 100 along the line 111-111 from FIG. 1.
  • This section shows how a seal 117 is arranged in the outer circumferential surface 102 of the inner motor part 101, which, viewed in the circumferential direction, seals the outer circumferential surface 102 against the inner circumferential surface 124 of the outer motor part 123.
  • the expansion space 107 in the region of the working cam 104 is thereby sealed.
  • a special property of the seal 117 which can be readily understood from FIG. 3, is to be practically wear-free after the initial running-in process, since the motor outer part 123 and the motor inner part 101 can rotate relative to one another with any desired accuracy without play due to the bearings 141, 142.
  • FIG. 4 shows a third axial section in the longitudinal direction of the axis through the rotary motor 100 along the line IV-IV of FIG. 1.
  • Figure 4 is thus a section through the expansion space 108 for the working gases.
  • the expansion space 108 also has the concave shape of a parabola, a parabola-like curve described in FIG. 2A or a hyperbola.
  • the wall of the expansion space 108 merges continuously into the outer peripheral surface 102.
  • At one end of the expansion space 108 is the inlet opening 111 for the working gases flowing into the expansion space 108 and at the other end the outlet opening 114 for the expanded working gases.
  • FIG. 5 shows an axial section in the longitudinal axis direction along the line V-V of FIG. 1.
  • This section shows the counter pressure part 126 in the expansion space 107.
  • the counter pressure part 126 has a shape complementary to the wall of the expansion space 107 and is sealed against the wall of the expansion space 107 by a seal 137. It can also be seen here that there are no edges to be sealed in the circumferential direction between the counterpressure part 126 and the expansion space 107.
  • the spring 132 is part of the control device.
  • the head 131 of the counter pressure part 132 rests with four approximately conical surfaces on the surfaces of a recess 136 in the motor outer part 123.
  • the inner motor part 101 can be the stator and the outer motor part 123 can be the rotor.
  • the inner motor part 101 is the rotor and the outer motor part 123 is the stator.
  • FIG. 6 shows a section perpendicular to the central axis along the half center line VI-VI of FIG. 7 through a rotary motor 200.
  • the rotary motor 200 consists of a motor inner part 201 with an outer circumferential surface 202 and a motor outer part 204 surrounding the motor inner part 201 with an inner circumferential surface 206, the outer circumferential surface 202 and the inner circumferential surface 206, as can be seen from FIG. 7, lying closely opposite one another in the form of two ring surfaces.
  • Part of the inner peripheral surface 206 is between two section-shaped expansion spaces
  • Working cams 207, 208, 209 have been left standing.
  • the working cam 207 is sealed off from the annular outer peripheral surface 202 by a seal 213. This makes it possible for the working cam 207 to transmit the expansion pressure of the working gases as torque to the outer motor part 205.
  • An inlet opening 211 for the working gases opens into the expansion space 210.
  • a counterpressure part 203 which projects into the expansion space 210 and transmits the expansion pressure of the working gases to the engine inner part 201, is mounted.
  • the counter pressure part 203 is sealed off from the inner circumferential surface 206 by a parabolic seal 213.
  • the counter pressure part 203 covers an outlet opening 212 for the expanding working gases until the relative rotation of the two motor parts 201, 205 caused by the expansion against one another via a control, for. B. a ramp 219, which causes the counter-pressure part 203 to evade the working cam 207.
  • Each counter pressure part 203 is pressed by the pressure of a spring 204 against the inner surface 206 or the wall of the expansion space 210, the sealing being carried out in the circumferential direction by a seal 214.
  • the seal 214 has the same shape as the seal 137.
  • FIG. 7 shows a first axial section in the longitudinal direction of the axis through the rotary motor 200 along the line VII-VII of FIG. 6. From this section, it can be seen that the outer peripheral surface 202 and the inner peripheral surface 206 have the shape of complementary ring surfaces, the outer peripheral surface 202 having the convex shape and the inner peripheral surface 206 having the concave shape of the parabolic curves described above.
  • the convex and concave annular surfaces 202, 206 corresponding to the curves run, as has also been described above, with a sliding fit up to their outer edges, which appear as two circular slots 215, 216.
  • FIG. 8 shows a second axial section in the longitudinal direction of the axis through the rotary motor 200 along the line VIII-VIII of FIG. 6. This figure shows a section through a section-shaped expansion space 210 and corresponds to FIG. 4.
  • FIG. 9 finally shows a third axial section in the longitudinal direction of the axis through the rotary motor 200 along the line IX-IX of FIG. 6. From this section it can be seen that the counter pressure part 202 moves into the expansion space 210 and is held there by the spring 204. The counter pressure part 202 is sealed in the circumferential direction against the wall of the expansion space 210 by the seal 214, which is visible in cross section in FIG. 6. This seal 214 corresponds to the seal 137 from FIG. 5 and is described there in detail. The deflection of the counter-pressure part 203 when the inner motor part 201 rotates relative to the outer motor part 205 when the working cam 207 approaches is effected by a ramp 219 .
  • the difference between the rotary motor 100 and the rotary motor 200 is that in the rotary motor 100 the outer peripheral surface 102 has the concave shape and the inner peripheral surface 124 has the convex shape, while in the rotary motor 200 the outer peripheral surface 202 the convex shape and the inner peripheral surface 206 has the concave shape.
  • FIG. 14A shows the first embodiment of the Wenzel motor 70 with the expansion space 71, the working cam 72 and the counter pressure part 73.
  • This first embodiment corresponds to the motor principle shown in FIGS. 1 to 5.
  • FIG. 14B shows the second embodiment of the Wenzel motor 80, in which the counterpressure part 83 is fastened to the inner part, the working cam to the outer part and which corresponds to the motor principle shown in FIGS. 6 to 9.
  • the rotary motor 80 has the expansion space which can only be specified in cross section 81, the working cam 82 and the counter-pressure part 83.
  • the working gases enter the expansion space through the slot 84 from the inner part of the motor.
  • the expansion space can therefore only be specified in a cross-sectional line 81, since it is in the in Figure 14B is cut away outer motor part.
  • the labyrinth seal 85 is in this case firmly attached to the motor outer part 86.
  • FIG. 15 shows the Zettner motor 90 with the expansion space 91, the working cam 92, the counter-pressure part 93 and the inlet opening 94 for the working gases into the expansion space 91.
  • the rotary motor 90 works, for example, as an external rotor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Hydraulic Motors (AREA)
  • Supercharger (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Sealing Devices (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
  • Permanent Magnet Type Synchronous Machine (AREA)
  • Power Steering Mechanism (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)
EP85905507A 1985-10-02 1985-10-02 Rotationsmotor Expired - Lifetime EP0240491B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP1985/000513 WO1987002096A1 (en) 1985-10-02 1985-10-02 Rotary engine

Publications (2)

Publication Number Publication Date
EP0240491A1 EP0240491A1 (de) 1987-10-14
EP0240491B1 true EP0240491B1 (de) 1990-03-07

Family

ID=8165063

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85905507A Expired - Lifetime EP0240491B1 (de) 1985-10-02 1985-10-02 Rotationsmotor

Country Status (11)

Country Link
US (1) US4890990A (pt)
EP (1) EP0240491B1 (pt)
JP (1) JPS62502205A (pt)
AT (1) ATE50822T1 (pt)
AU (1) AU577422B2 (pt)
BR (1) BR8507295A (pt)
DE (1) DE3576381D1 (pt)
IL (1) IL80159A (pt)
RU (1) RU1789036C (pt)
WO (1) WO1987002096A1 (pt)
ZA (1) ZA867452B (pt)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29513194U1 (de) * 1995-08-17 1995-11-23 Heidenescher, Ferdinand, 49143 Bissendorf Rotationskolben-Verbrennungsmotor

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2254888B (en) * 1991-03-05 1995-04-05 Ian Alexander Giles Rotary positive-displacement pump and engine
BE1010391A3 (fr) * 1996-06-27 1998-07-07 Orphanidis Michalis Machine a effet volumetrique a piston rotatif et moteur derive d'une telle machine.
ES2544579T3 (es) 2002-07-30 2015-09-01 Takasago International Corporation Procedimiento de producción de un beta-aminoácido ópticamente activo
BRPI0621488A2 (pt) * 2006-05-09 2013-02-13 Okamura Yugen Kaisha motor de combustço interna de pistço giratàrio
JP5147134B2 (ja) * 2006-05-09 2013-02-20 オカムラ有限会社 回転型流体機械
CN101864991A (zh) * 2010-06-10 2010-10-20 姚镇 星旋式流体马达或发动机和压缩机及泵
IL216439A (en) 2011-11-17 2014-02-27 Zettner Michael Rotary engine and process for it
ITBL20120010A1 (it) * 2012-11-30 2014-05-31 Ruggero Libralato Motore endotermico rotativo a doppio centro di rotazione, perfezionato con pareti arquate e scarichi differenziati
US9291095B2 (en) * 2013-03-15 2016-03-22 Randy Koch Rotary internal combustion engine
US9464566B2 (en) 2013-07-24 2016-10-11 Ned M Ahdoot Plural blade rotary engine
CN110005606A (zh) * 2019-03-28 2019-07-12 云大信 一种卡槽泵装置和流量调节方法

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1349096A (en) * 1970-11-05 1974-03-27 Timex Corp Electrically operated watch having means for increasing the power supply voltage

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US1442198A (en) * 1914-06-24 1923-01-16 Arthur Kitson Rotary pump, engine, or meter
GB113697A (en) * 1917-03-27 1918-03-07 Nikolai Demianovitch Shelikof An Improved Rotary Engine.
US1625233A (en) * 1922-08-23 1927-04-19 Cheever J Cameron Rotary engine
US1770141A (en) * 1927-05-31 1930-07-08 Albert J Meyer Pump
US1859618A (en) * 1929-09-18 1932-05-24 Ward W Cleland Rotary internal combustion engine
US2796030A (en) * 1953-05-29 1957-06-18 Nebel Franz Philip Rotary pump for handling viscous materials
US3249096A (en) * 1962-10-12 1966-05-03 Franceschini Enrico Rotating internal combustion engine
US3181512A (en) * 1963-04-22 1965-05-04 Fred J Hapeman Rotary internal combustion engine
GB1349521A (en) * 1970-01-01 1974-04-03 Oppenheim H Rotary-piston machines
AR212382A1 (es) * 1977-11-16 1978-06-30 Quiroga P Motor rotativo con pistones de accion lateral
US4561834A (en) * 1983-07-13 1985-12-31 Poss Design Limited Rotary vaned pumps with fixed length and shearing knife-edged vanes

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1349096A (en) * 1970-11-05 1974-03-27 Timex Corp Electrically operated watch having means for increasing the power supply voltage

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29513194U1 (de) * 1995-08-17 1995-11-23 Heidenescher, Ferdinand, 49143 Bissendorf Rotationskolben-Verbrennungsmotor

Also Published As

Publication number Publication date
RU1789036C (ru) 1993-01-15
JPS62502205A (ja) 1987-08-27
ATE50822T1 (de) 1990-03-15
BR8507295A (pt) 1987-11-03
US4890990A (en) 1990-01-02
WO1987002096A1 (en) 1987-04-09
IL80159A0 (en) 1986-12-31
EP0240491A1 (de) 1987-10-14
JPH0229841B2 (pt) 1990-07-03
AU5013185A (en) 1987-04-24
AU577422B2 (en) 1988-09-22
DE3576381D1 (de) 1990-04-12
IL80159A (en) 1992-07-15
ZA867452B (en) 1987-05-27

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