EP0219653A1 - Rotationskolbenmaschine - Google Patents

Rotationskolbenmaschine Download PDF

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Publication number
EP0219653A1
EP0219653A1 EP86111794A EP86111794A EP0219653A1 EP 0219653 A1 EP0219653 A1 EP 0219653A1 EP 86111794 A EP86111794 A EP 86111794A EP 86111794 A EP86111794 A EP 86111794A EP 0219653 A1 EP0219653 A1 EP 0219653A1
Authority
EP
European Patent Office
Prior art keywords
valve
piston machine
rotary piston
space
working
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Withdrawn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
EP86111794A
Other languages
German (de)
English (en)
French (fr)
Inventor
Otto Dr. Zimmermann
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 EP0219653A1 publication Critical patent/EP0219653A1/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Withdrawn legal-status Critical Current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
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • F01C11/004—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle and of complementary function, e.g. internal combustion engine with supercharger
    • 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
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines 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
    • F01C1/20—Rotary-piston machines or engines 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 a rotary piston machine according to the preamble of claim 1.
  • a rotary piston machine is known from EP 01 16 356, which goes back to the same applicant.
  • a feature of this known rotary piston machine is that both the motor part and the compressor part are assigned a long, continuous angle of rotation to the respective pistons, which results in a high uniformity of the drive or compression performance with low sealing losses.
  • the shaft on which the piston rotors are arranged was designed as a multi-spoke shaft, which is associated with a relatively high outlay.
  • a known shut-off valve was used as a shut-off device for the work space, which divides the work space into a suction space and a compression or expansion space or exhaust space.
  • the disadvantage of such a shut-off rotor is the associated drive mechanism and relatively high sealing losses, particularly in the area in which the piston rotor engages with its piston in an associated recess on the shut-off rotor.
  • the invention has for its object to develop a rotary piston machine of the type mentioned so that it has a much simplified structure is cheaper to manufacture and works with lower sealing losses.
  • the invention is characterized in that the shaft is designed as a hollow shaft, which only has end-to-end bearings on the housing, and that the shut-off element which controls the working space is designed as a lift or rotary valve controlled directly or indirectly by the piston.
  • a feature of the present invention is that instead of a multi-spoke shaft, a simple hollow shaft is used, on each of which a piston is arranged, so that a piston rotor is defined by each section of the hollow shaft with an associated piston, to which an associated, circular working space in the housing is allocated.
  • the design of the shaft as a hollow shaft thus results in a particularly simple and cost-saving construction, and the saving in the shut-off rotor results in a further simplification in construction and thus an inexpensive manufacture of the rotary piston machine as a whole.
  • shut-off rotor instead of the shut-off rotor, a lift or rotary valve controlled directly or indirectly by the piston is used, disadvantageous sealing losses are avoided, in particular a circumferential surface seal in the working area, as would otherwise have to be used with a shut-off rotor.
  • a lift or rotary valve which divides the work space into a suction space and a compression or expansion space.
  • shut-off device consists of a rotatable and slidably mounted on the housing, having at least three valve arms, valve disc, which is in rotational engagement with the piston and is lifted radially outwards from the sealing seat as it rotates.
  • control disks shown in European patent 01 16 356 can now be significantly reduced in number, or - in another embodiment - can even be completely omitted, being replaced by other valve mechanisms.
  • the necessary valve device is designed as a control disk, which is connected non-rotatably to the hollow shaft, which has openings distributed around the circumference, which have associated openings of overflow channels fixed to the housing can be brought to overlap.
  • the control disks can themselves be formed from the material of the hollow shaft, that is, be made of one piece with the hollow shaft.
  • a control disk is arranged on the hollow shaft in the compressor part only on the outlet side of each working space, because it has been found according to the invention that an inlet-side control disk can be omitted, because the inlet can remain constantly open to to be able to constantly suck in the working medium.
  • control disks can thus be significantly reduced, and this is a major advantage of the principle of a rotary piston machine according to the invention.
  • control disks are replaced by another valve device, this valve device being designed as a spring-loaded check valve, which is in each case in the overflow channel is arranged between two adjacent work rooms.
  • This check valve only allows the working medium to flow from a previous working area to a downstream working area, whereas a flow in the opposite direction is blocked.
  • a combined rotary piston machine is assumed in the following description of the drawing, wherein according to FIG. 1, a compressor part 52 is arranged on one and the same hollow shaft 6 together with an internal combustion engine 53 and a downstream exhaust stage part 54.
  • the end of the hollow shaft 6 is rotatably supported in bearings 51 in a fixed housing 1.
  • the internal combustion engine 53 can also be modified in such a way that water is injected before or during the expansion, which then creates a combustion steam engine.
  • an external thermal insulation can then be provided.
  • the housing 1 has partitions 2, 3 which separate the annular working spaces 4 from one another in a sealing manner. From the drawing it can be seen that the working spaces have an increasingly smaller volume in the area of the compression part 52, as will be described later.
  • the drive shaft 5 is in one piece with the hollow shaft 6. According to the invention, this hollow shaft 6 carries a control disk 7. The gaseous medium sucked in at the inlet 8 is compressed further and further in the compression part, which ends in the region indicated by arrow 9. This process, namely the interaction of the control disks and partitions in cooperation with the overflow channel 10, is described in EPC 01 16 356.
  • the working medium compressed for example in the first working stage of the six-stage compressor part 52, flows under high pressure via the two openings 42, 45 into an overflow duct 10 (see FIG. 1 below) and arrives there via an opening 43 in the partition 3 in the downstream second working space of the second stage of the compressor part 52.
  • the compression of the working medium works in an analogous manner in the successive further stages, each stage having a smaller volume than the previous stage, so that the working medium in the sixth stage is in a highly tensioned state and can either be introduced into the internal combustion engine 53 or for other purposes can be used.
  • the internal combustion engine 53 then follows, which in the exemplary embodiment ends in the area labeled with arrow 11.
  • three of the work spaces arranged in the expansion area are connected to the two exhaust work spaces, which are arranged as an exhaust stage part 54 in area 12.
  • the piston area of the working areas in the area 12 is approximately 9 times the size of the piston area in the working areas of the expansion area.
  • FIG. 2 shows schematically the section through a stage of the rotary piston machine, for example through a compression stage in the compressor part 52.
  • the hollow shaft 6 is designated as a rotary rotor.
  • a piston 13 is located on this hollow shaft within the working space. If the hollow shaft 6 or the rotary rotor with the piston 13 moves in the direction of arrow 14, then the working space, if it is a compression stage, is divided into the suction space 15 and the Compression chamber 16.
  • the compression chamber 16 is thus formed on the one hand by the control side 17 of the piston, which serves to raise the valve body 18 against the pressure of the valve spring 19 in the direction of the arrow 20 after the compressed gas has been pushed into the next working chamber with the control discs 7 in the appropriate position has been.
  • the rear of the piston 21 is then the further control surface 22 for the valve body 18 when it resumes its sealing seat on the hollow shaft 6.
  • Known seals 23 serve to seal the piston against the housing wall 1. Schematically shown in FIG. 2 is that the entire valves are arranged one behind the other on a control strip 24, which have the length of the hollow shaft 6.
  • the housing 1 is formed in two parts.
  • FIG. 6 schematically indicates the position of the control disk 7 arranged on the outlet side. Here are in the area of the working space 4, the openings 45 of a control disk 7 arranged on the outlet side are shown in dashed lines.
  • the openings 45 are arranged at a uniform distance around the radius 44 - as indicated in the drawing - only the openings in the upper area, as shown in FIG. 2, are missing in order to avoid a short circuit from the suction chamber 15 to the compression chamber 16.
  • the opening 42 in the partition 2 is also shown, through which the piston 13, with its front control side 17, pushes the high-tension medium into the overflow channel 10 located behind it in the partition. From the overflow channel 10, the medium flows through an opening 43, which is also indicated, into the work space of the subsequent compression stage.
  • the opening 43 is here made in the partition 3 of the housing 1.
  • FIGS. 3 to 5 show the further embodiment of a valve, which differs from the first-mentioned valve in that the first-mentioned valve is a globe valve, while the exemplary embodiment described below is a rotary valve.
  • the piston 13 of the machine separates the working space 4 from the suction space 15, the piston 13 rotating in the direction of the arrow 14.
  • Valve disc 25 is arranged, which in the rotational position according to FIG. 3 and FIG. 5 performs the sealing between the compression space 16 and the suction space 15 of the machine, while in the position according to FIG. 4 there is the same pressure in both spaces 16, 15 and a sealing effect of the valve is not is required.
  • the valve consists of a valve disk 25 which is rotatably mounted in the direction of arrow 33 in the recess 39 and which in the exemplary embodiment bears 4 valve arms 27, 28, 29, 30, which are each offset radially on the circumference by 90 degrees.
  • Corresponding sealing pieces 41 are arranged at the outer distal ends of these valve arms 27-30, which are omitted for the sake of simplicity in the representations of FIGS. 4 and 5.
  • valve disk 25 is arranged rotatably in the direction of arrow 33 on an associated ratchet disk 26, the ratchet disk 26 having corresponding projections which interact with assigned recesses in the region of the valve disk 25.
  • Valve disc 25 and pawl disc 26 together form a locking mechanism, which ensures that when the piston 1 rotates through 360 degrees in the housing 1, only one valve arm 27-30 in the direction of arrow 33 is advanced by 90 degrees.
  • valve disk 25 with the valve arms 28, 29, 30 is currently in sealing engagement with the housing, because the allocated sealing piece 41 lies against associated sealing seats 36, 37, 38 of the housing.
  • the compression space 16 is separated from the suction space 15 in a pressure-tight manner, and considerable pressure differences can exist between the two spaces.
  • overflow channels 10 are arranged in the area below the valve disk 25 at the same location in the housing as is shown in FIG.
  • valve disk 25 has moved from the old axis of rotation 32 into the raised position and is rotating about the axis of rotation 35 above it.
  • the piston now moves further in the direction of arrow 14 in FIG. 4, and after it is still in rotational engagement with the recess 31 between the two valve arms 28, 29, it rotates the entire valve disk 25 by a further 45 degrees, as a result of which this again falls into its lowered position and the valve arm 28 cooperates with its sealing piece 41, not shown, with the sealing seat 37, while the other valve arms 27, 29 cooperate with the sealing seats 36, 38 on the inner surface 40 of the recess 39.
  • the piston 13 then performs a revolution in the housing 1 until it returns to its position according to FIG. 3, as a result of which the previously described sequence of movements takes place again.
  • the exhaust-side control disks are omitted, because it is sufficient to arrange only one hole in the partition 3, because backflow of the medium through the valve 18 and the piston 13 is prevented.
  • control disks described can be completely dispensed with if a check valve is arranged in the respective overflow channel 10, as is shown only schematically in FIG. 6.
  • This check valve 46 opens due to the higher pressure flowing in the direction of arrow 50 and closes under spring force under the force of a spring 49.
  • the ball 47 of the check valve 46 is held in a cage-shaped valve seat 48 and is biased against the opening 42 by means of the spring 4.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Toys (AREA)
EP86111794A 1985-09-23 1986-08-26 Rotationskolbenmaschine Withdrawn EP0219653A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3533896 1985-09-23
DE19853533896 DE3533896A1 (de) 1985-09-23 1985-09-23 Rotationskolbenmaschine

Publications (1)

Publication Number Publication Date
EP0219653A1 true EP0219653A1 (de) 1987-04-29

Family

ID=6281705

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86111794A Withdrawn EP0219653A1 (de) 1985-09-23 1986-08-26 Rotationskolbenmaschine

Country Status (3)

Country Link
EP (1) EP0219653A1 (ja)
JP (1) JPS6275027A (ja)
DE (1) DE3533896A1 (ja)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021122124B3 (de) 2020-10-13 2022-03-03 Felix Thugutt Verbrennungsmotor und Verfahren zum Betrieb eines Verbrennungsmotors

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1949225A (en) * 1927-05-12 1934-02-27 Willem P Van Lammeren Rotary internal combustion engine
FR2227770A5 (en) * 1973-04-03 1974-11-22 Le Coutaller Louis Rotary internal combustion engine - has two elliptical rotors within a circular cylindrical stator
FR2309721A1 (fr) * 1975-05-02 1976-11-26 Theisen Alois Moteur rotatif
FR2317497A1 (fr) * 1975-07-05 1977-02-04 Kunieda Eiichi Moteur rotatif
DE2550360A1 (de) * 1975-11-10 1977-05-12 England Will Clarke Energieumsetzungsventil
EP0116356A1 (de) * 1983-02-15 1984-08-22 Otto Dr. Zimmermann Rotationskolbenmaschine

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2016845A1 (de) * 1970-04-09 1971-10-21 Umlauf, Norbert, 5800 Hagen Drehkolben Brennkraftmaschine mit Widerlager

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1949225A (en) * 1927-05-12 1934-02-27 Willem P Van Lammeren Rotary internal combustion engine
FR2227770A5 (en) * 1973-04-03 1974-11-22 Le Coutaller Louis Rotary internal combustion engine - has two elliptical rotors within a circular cylindrical stator
FR2309721A1 (fr) * 1975-05-02 1976-11-26 Theisen Alois Moteur rotatif
FR2317497A1 (fr) * 1975-07-05 1977-02-04 Kunieda Eiichi Moteur rotatif
DE2550360A1 (de) * 1975-11-10 1977-05-12 England Will Clarke Energieumsetzungsventil
EP0116356A1 (de) * 1983-02-15 1984-08-22 Otto Dr. Zimmermann Rotationskolbenmaschine

Also Published As

Publication number Publication date
DE3533896A1 (de) 1987-03-26
JPS6275027A (ja) 1987-04-06

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