EP0601218A1 - Machine à piston rotatif - Google Patents

Machine à piston rotatif Download PDF

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Publication number
EP0601218A1
EP0601218A1 EP92120263A EP92120263A EP0601218A1 EP 0601218 A1 EP0601218 A1 EP 0601218A1 EP 92120263 A EP92120263 A EP 92120263A EP 92120263 A EP92120263 A EP 92120263A EP 0601218 A1 EP0601218 A1 EP 0601218A1
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EP
European Patent Office
Prior art keywords
rotors
rotor
blade plates
channels
segments
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.)
Granted
Application number
EP92120263A
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German (de)
English (en)
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EP0601218B1 (fr
Inventor
Andro Caric
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Individual
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Individual
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Publication date
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Priority to EP19920120263 priority Critical patent/EP0601218B1/fr
Publication of EP0601218A1 publication Critical patent/EP0601218A1/fr
Application granted granted Critical
Publication of EP0601218B1 publication Critical patent/EP0601218B1/fr
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
    • F01C1/32—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 both the movement defined in group F01C1/02 and relative reciprocation between the co-operating members
    • F01C1/332—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 both the movement defined in group F01C1/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member
    • F01C1/336—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 both the movement defined in group F01C1/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member and hinged to the inner member

Definitions

  • HCM HCM
  • the inner rotor body (Fig.4 Part 1.1), which also serves as the drive axis, is based on two roller or slide bearings that are located in the housing.
  • the outer rotor is fixed in its axis of rotation by a plain bearing (Fig.4 part 8) or several wheels fixed in the housing, or by roller bearings.
  • a plain bearing (Fig.4 part 8) or several wheels fixed in the housing, or by roller bearings.
  • the working chamber moves from position 1 (Fig. 1) to position 2.
  • the volume of the chamber increases and allows the fluid to enter the chamber through the control disc on the side.
  • a work is done by the pressure of the fluid.
  • the machine works as a motor. If the fluid is sucked in, we have a pump. In positions 4 and 5 the chamber reaches the largest volume. In this area, no fluid flows through the control disc into the machine. The fluid is brought into the other half of the machine with decreasing chamber volume, where it then flows back into the motor or pump circuit.
  • CARICMOTOR also C-MOTOR
  • the outer and inner rotors move synchronously, e.g. clockwise.
  • the working chamber moves from position 1 (Fig. 1) to position 2.
  • the air in the chamber is compressed and positions 2 and 3 reduce the chamber volume.
  • the compression increases until the highest compression is reached in position 4.
  • positions 1, 2 or 3 smaller amounts of fuel can be injected according to the principle of the so-called lean-burn engine.
  • the fuel is atomized, mixed with the air and prepared for complete combustion during the expansion phase.
  • position 5 where the chamber walls of the two rotors touch, but do not rub against one another, since they have the same angular velocity, the chamber gas is conducted compressed into the vortex grooves.
  • the vortex groove is formed in position 5 by the side grooves coming together in the IR and AR chamber walls (Fig. 4, parts 1.6, 2.6), or it is located entirely in the chamber wall of the outer rotor.
  • fuel is injected into the swirl groove in a timely and quantitative manner.
  • An air / fuel mixture is created, which leads to optimal combustion with high gas pressure through self-ignition or spark ignition.
  • the blade plates in positions 6, 7 and 8 are pushed further in the circumferential direction, as a result of which the engine work is performed.
  • the outlet opening is reached.
  • the gas which is under high pressure, flows explosively out of the engine (Fig. 2).
  • all gas molecules receive momentum in the outlet direction and leave the working chamber.
  • the time required for purging and air supply charge is given, since the much more mobile gas does not have to follow the inertia of the piston.
  • the C-MOTOR has many working chambers, in our example 8, and with one engine revolution in all working chambers all operations are carried out (sucking in, compressing, expanding, discharging), it has a quieter run, which is a 4-stroke piston engine with 16 cylinders corresponds.
  • the vibration of the Wankel engine corresponds to a 4-stroke reciprocating engine with two cylinders. Nevertheless, a Wankel engine runs much more quietly than a reciprocating piston engine because no unbalance-generating mechanisms are required that convert the linear movement of the piston into rotation. This advantage is even more pronounced with the C-MOTOR.
  • the C-MOTOR Since the C-MOTOR has no reciprocating pistons that are accelerated and decelerated to high speeds several thousand times a minute, the components can be subjected to higher loads. Since there are neither valves nor massively oscillating forces, very high speeds can also be achieved. A further increase in speed is possible by charging.
  • the strength of the blade plates favors the following circumstance: there are stepped pressure drops between the working chambers, so that the blade plates are only loaded with the pressure difference. This enables a high working pressure.
  • the reciprocating engine is not as thermally and mechanically resilient as the C-MOTOR and the resilience of the Wankel engine is even lower.
  • a decisive advantage of the normal piston engine compared to the Wankel engine is that wall parts of the work space, which are exposed to the high temperatures of the combustion, come into contact with the low temperatures at the point of gas exchange in rapid, periodic alternation.
  • This advantage also applies to the C-MOTOR. This is because the blade plates, the partial cylinders and the chamber walls alternately come into contact with combustion gases and fresh gases.
  • the chamber area of the non-rotating side seal is small and lubricated with oil. The heat losses are therefore low.
  • the chamber walls of the C-MOTOR segments are made of simple cross-sections and are only stressed by the pressure during work, they can be made from light, heat-insulating (ceramic) materials.
  • Wankel and reciprocating engine lead to higher expenditure in the manufacture of the engine. At this point, the poorer engine starting with the Wankel engine must be mentioned, caused by poor sealing at low speeds.
  • the importance of the invention by F. Wankel is the proof that a rotary piston engine is preferred for many hundreds of thousands of drivers and can work well (Mazda RX7) even with extremely unfavorable sealing conditions and other unfavorable parameters compared to the sophisticated reciprocating engine.
  • the surface / volume ratio at the top dead center of a combustion chamber is much cheaper with the C-MOTOR than with a Wankel engine.
  • the surface / volume ratio at bottom dead center can be improved by larger dimensions in engine construction (the engine is still much smaller than a corresponding reciprocating piston engine). It should be mentioned here that during combustion, the gases and the chamber walls of the C-MOTOR have the same speed of rotation, i.e. rest relative to each other, as is the case with the reciprocating piston engine. In contrast, the flame of the Wankel engine must spread over the trochoid surface spread at high peripheral speed. This is inconvenient for complete fuel burning.
  • the round and flat surfaces of the motor elements, many of which have the same shape, are easier to manufacture. Therefore, the manufacturing costs for the C-MOTOR should be lower than for other engines. (see description of the machine for the hydraulics and p. 9).
  • the C-MOTOR is suitable for all types of fuel, depending on the modified version as a diesel, gasoline, steam, H2- etc. engine. Fuel injection and candle ignition on the side of the engine cover are easy. This is another benefit. Since the injection and ignition take place before position 5 (Fig. 1) and not in the phase of the highest chamber temperature (positions 5, 6 or 7), the injection nozzle and spark plug are not as heavily loaded as with a reciprocating or Wankel engine.
  • the injected fuel (in the diesel process) is not directed into the relatively stationary piston recess at the TDC point, but in an arc length of 45 o into the flanking lateral chamber wall recesses, called the swirl groove.
  • the gas is guided axially into a trough channel, which can be designed differently depending on the operating mode.
  • the C-MOTOR Fig. 4
  • the oil is let in by a pump through a channel in the middle of the inner rotor axis. Due to the strong centrifugal force, the oil passes from this channel through the distribution channels, which run radially from the center to the outside, into the synchronous spaces of the inner rotor.
  • the oil flows through the blade plates into the empty spaces of the outer rotor. There, the oil continues to flow out of the outer rotor from the engine through the channels and holes provided on the jacket side.
  • the parts in the inner and outer rotor are cooled by the strong oil flow.
  • the cooling and lubrication of the blade plate takes place as follows.
  • the blade plate in position 8 (Fig.1), the surfaces of which are heated up strongly in the previous work step, is first cooled with fresh gas.
  • the blade plate gradually dips into the spherical bearings of the inner and outer rotor and their oil spaces. Further cooling takes place through contact with the partial cylinders and the oil.
  • the surface is wetted by the oil again.
  • the oil is metered and sealed, cooling and lubricating to the relevant points by the pendulum movements of the blade plates and the cylinder segments.
  • the blade plate is still cooled from the inside by the strong oil flow in its channels.
  • the blade plate also serves as a conveyor bridge for AR cooling.
  • the number of screws and springs in the outer rotor should be significantly smaller than in the inner rotor. These springs and screws in the outer rotor are hardly loaded by the effect of centrifugal forces.
  • the screws can also be arranged offset (Fig. 7).
  • To fix the inner rotor walls screws with holes and nuts are necessary (Fig.7).
  • the number of retaining screws required is considerably greater than with the outer rotor due to the centrifugal forces acting differently here.
  • chamber walls, the support segments of the plain bearing and the partial cylinders can have different cavities and oil cooling channels.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
EP19920120263 1992-11-27 1992-11-27 Machine à piston rotatif Expired - Lifetime EP0601218B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP19920120263 EP0601218B1 (fr) 1992-11-27 1992-11-27 Machine à piston rotatif

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19920120263 EP0601218B1 (fr) 1992-11-27 1992-11-27 Machine à piston rotatif

Publications (2)

Publication Number Publication Date
EP0601218A1 true EP0601218A1 (fr) 1994-06-15
EP0601218B1 EP0601218B1 (fr) 1997-01-22

Family

ID=8210253

Family Applications (1)

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EP19920120263 Expired - Lifetime EP0601218B1 (fr) 1992-11-27 1992-11-27 Machine à piston rotatif

Country Status (1)

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EP (1) EP0601218B1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1138876A1 (fr) * 2000-03-31 2001-10-04 OTICE Establishment Moteur à combustion interne
US7438543B2 (en) 2003-11-08 2008-10-21 Beez Guenther Oscillating slide machine
DE102005017834B4 (de) * 2005-04-18 2012-03-29 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Zellenpumpe
EP2884046A1 (fr) * 2013-12-16 2015-06-17 Mahle International GmbH Pompe de tiroir-navette
WO2015197557A1 (fr) * 2014-06-27 2015-12-30 Mahle International Gmbh Système modulaire pour des rotors d'une pompe cellulaire à palettes à mouvement pendulaire
EP3249156A1 (fr) * 2016-05-24 2017-11-29 Robert Bosch GmbH Machine, en particulier pompe de pression d'huile
CN111608851A (zh) * 2019-11-19 2020-09-01 李光惠 一种摆动叶片液气动力装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015216989A1 (de) 2015-09-04 2017-03-09 Robert Bosch Gmbh Maschine, insbesondere Ölförderpumpe

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1618806A (en) * 1919-08-02 1927-02-22 Multi Vane Construction Compan Internal-combustion engine
US2029554A (en) * 1932-08-24 1936-02-04 Berggren Charles William Pump and compressor
GB973191A (en) * 1962-02-03 1964-10-21 Alan Arthur Jones Improvements in or relating to orbiting piston machines
EP0011762A1 (fr) * 1978-11-28 1980-06-11 Kuechler, Jürgen Dr. Moteur à pistons rotatifs
DE4117936A1 (de) * 1991-05-31 1992-12-03 Andro Caric Rotationskolbenmaschine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1618806A (en) * 1919-08-02 1927-02-22 Multi Vane Construction Compan Internal-combustion engine
US2029554A (en) * 1932-08-24 1936-02-04 Berggren Charles William Pump and compressor
GB973191A (en) * 1962-02-03 1964-10-21 Alan Arthur Jones Improvements in or relating to orbiting piston machines
EP0011762A1 (fr) * 1978-11-28 1980-06-11 Kuechler, Jürgen Dr. Moteur à pistons rotatifs
DE4117936A1 (de) * 1991-05-31 1992-12-03 Andro Caric Rotationskolbenmaschine

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1138876A1 (fr) * 2000-03-31 2001-10-04 OTICE Establishment Moteur à combustion interne
US6481988B2 (en) 2000-03-31 2002-11-19 Otice Establishment Internal combustion engine
US7438543B2 (en) 2003-11-08 2008-10-21 Beez Guenther Oscillating slide machine
DE102005017834B4 (de) * 2005-04-18 2012-03-29 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Zellenpumpe
EP2884046A1 (fr) * 2013-12-16 2015-06-17 Mahle International GmbH Pompe de tiroir-navette
JP2015117695A (ja) * 2013-12-16 2015-06-25 マーレ インターナショナル ゲゼルシャフト ミット ベシュレンクテルハフツングＭＡＨＬＥ Ｉｎｔｅｒｎａｔｉｏｎａｌ ＧｍｂＨ ペンジュラムスライダポンプ
US9752573B2 (en) 2013-12-16 2017-09-05 Mahle International Gmbh Pendulum slide pump with at least one communication channel
WO2015197557A1 (fr) * 2014-06-27 2015-12-30 Mahle International Gmbh Système modulaire pour des rotors d'une pompe cellulaire à palettes à mouvement pendulaire
EP3249156A1 (fr) * 2016-05-24 2017-11-29 Robert Bosch GmbH Machine, en particulier pompe de pression d'huile
CN111608851A (zh) * 2019-11-19 2020-09-01 李光惠 一种摆动叶片液气动力装置

Also Published As

Publication number Publication date
EP0601218B1 (fr) 1997-01-22

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