WO2003004833A1 - Rotationskolbenmaschine - Google Patents
Rotationskolbenmaschine Download PDFInfo
- Publication number
- WO2003004833A1 WO2003004833A1 PCT/EP2002/006476 EP0206476W WO03004833A1 WO 2003004833 A1 WO2003004833 A1 WO 2003004833A1 EP 0206476 W EP0206476 W EP 0206476W WO 03004833 A1 WO03004833 A1 WO 03004833A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- crankshaft
- rotary piston
- housing
- chamber
- piston
- Prior art date
Links
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
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/102—Adjustment of the interstices between moving and fixed parts of the machine by means other than fluid pressure
-
- 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
- F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F01C1/06—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents of other than internal-axis type
-
- 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
- F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
- F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
-
- 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
- F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
- F01C20/18—Control of, monitoring of, or safety arrangements for, machines or engines characterised by varying the volume of the working chamber
- F01C20/22—Control of, monitoring of, or safety arrangements for, machines or engines characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
Definitions
- the invention relates to a rotary piston machine.
- a rotary piston machine with the feature group a of claim 1 is known from EP 0644981 B1, the complete contents of which are referred to in order to understand the generic type of machine.
- the piston has on its circumference one or more pairs of convex and concave surfaces which come into and out of chamber-forming engagement on associated concave and convex surfaces of a circumferential wall of the housing.
- the convex surface of the piston on the concave surface of the peripheral wall and the concave surface of the piston on the convex surface of the peripheral wall seal tightly along a chamber and close off a chamber which also laterally, in the case of the cited document with side walls of the housing, sealed is.
- the volume of the chamber changes during rotation during the operation of the arm, with an advantageously very large compression ratio.
- Such a machine can, as described in the cited document, be used for different purposes, e.g. as a pump, as a brake force machine and in particular as a gas compressor that can achieve very high compression in one stage, ie in one chamber.
- crankshafts which are mounted in the piston. These must be stored at a distance and thus take up a lot of space in the piston and limit the design options considerably. Furthermore, the crank pin bearings in the piston, since they must be spaced apart, must be arranged on the edge of the piston, that is to say in the vicinity of the chambers formed on its circumference, and are subject to high thermal loads there. This leads to machine durability problems.
- a rotary piston machine with the feature group b of claim 1 is known from DE 32 31 756 AI. It is a machine with a spiral piston which, as in the aforementioned known construction, is driven to rotate in parallel.
- Figures 3 and 4 of this document it is shown that as a holding device for parallel guidance of the piston a spaced from the course Bearing intended storage device is used. This bearing device is structurally much simpler than that from the first-mentioned document, which consists of additional crankshafts.
- the bearing device can be embodied in the alternative of FIGS. 3 and 4 of DE 32 31 756 A1, wherein either the piston is rotatably mounted on a parallel slide or is longitudinally displaceable in a rotatably mounted slide.
- the object of the invention is to provide a rotary piston machine with the advantages of the two known constructions mentioned, but with variable kinematics of the piston movement.
- the running kinematics of the piston can be adjusted by adjusting the distance between the crankshaft and the pivot bearing of the bearing device in such a way that, at a greater distance, the running movement more closely approximates the tilt-free, strict parallel rotation, or a larger one at a shorter distance Tilting movement results.
- the tilting movement increases or if there is a deviation from a normal length for which the chamber surfaces are adapted, there are leaks in the chambers. This can be used to advantage, for example to let the machine run idle with a high level of leakage, i.e. with low power consumption and smooth running.
- the piston can be constructed in a known manner in accordance with the above-mentioned specification.
- the handrail starts at a suitable point and leads to the distant storage facility.
- crank pins are preferably to be arranged in the piston at a point which is not subject to high thermal loads, that is to say at a distance from the chamber-forming walls.
- the features of claim 3 known per se from DE 195 00 774 AI are therefore preferably provided. So that the crank pin bearing is completely removed from the piston and placed next to it.
- the thermal problems on the crank pin bearing can be solved extremely effectively if the crank pin bearing is arranged, for example, at a location through which fresh air flows.
- a piston / cylinder arrangement provides the displaceability required for the bearing device.
- the pivot bearing can also be provided in a simple manner, either by pivoting the support rod in the piston after the old of a connecting rod bearing or by pivoting the cylinder on the housing.
- the piston / cylinder arrangement can be used as a further compression or expansion chamber, for example as a compression stage of a compressor.
- the single figure shows a section transverse to the crankshaft through a rotary piston machine according to the invention.
- the rotary piston machine shown has a stationary housing 1, which encloses an interior 2 with an inner peripheral wall 3. Parallel to the plane of the drawing, the interior 2 is closed with a flat side wall 4 lying below the plane of the drawing. In parallel, there is a side wall, not shown, lying above the drawing plane.
- a crankshaft with center M1 is mounted in side wall 4 and the other side wall parallel to it, which has a radially offset crank pin 5 with center M2.
- the crank pin 5 rotates with its center M2 on the dashed circular line around the center M1 of the crankshaft.
- a rotary piston 6 is mounted on the crank pin 5.
- a holding rod 8 is fastened in this in a bore 7.
- the free end of the support rod 8 is mounted on a rotary bearing 9, with an axis parallel to the crankshaft, in a reciprocating piston 10 which runs in a cylinder 11 which is attached to the housing 1. With its cylinder axis directed towards the area of the crankshaft.
- crank pin 5 rotates by M1
- the piston / cylinder arrangement 10, 11 thus forms one Bearing device for the rotary piston 6, which holds it essentially at an angle to the housing 1, wherein it only performs a slight tilting movement during its parallel shot. This depends on the distance between the crankshaft and the bearing device 9, 10, 11. With a large distance, the tilting movement is negligibly small, so that there is approximately a true parallel rotation.
- a first pair of surfaces is provided on the circumference of the rotary piston 6, consisting of a convex surface 12 and an adjacent concave surface 13.
- a chamber has just been closed between the surface pairs 12, 13 and 14, 15 by sealing the convex surface 12 on the concave surface 14 at A and the concave surface 13 on the convex surface 15 at B, and by the side walls 4.
- the convex surface 12 of the rotary piston runs sealingly on the concave surface 14 of the peripheral wall.
- the concave surface 13 of the rotary piston runs on the convex surface 15 of the peripheral wall.
- the chamber formed between the walls continuously reduces its volume because the sealing points A and B move towards each other.
- the rotary piston 6 lifts off the peripheral wall 3 and opens the chamber, in order then to again close the large volume chamber in the position shown in the figure.
- a chamber thus results which closes again and again with a large volume, then reduces the volume and then opens.
- This construction can be used as a compressor.
- gas with a low pressure flows through an inlet opening 16 into the interior 2 of the housing 1, is enclosed when the chamber closes and is compressed as the rotary piston 6 continues to rotate.
- the point of smallest chamber volume lies at a point at which an outlet valve 17 is provided, which can be provided as a simple outward-opening check valve and which is connected to a high-pressure duct 18 through which the compressed gas is discharged via suitable connection means.
- a further pair of surfaces is provided on the rotary piston 6 and on the housing 1, which in the same way forms a second chamber.
- the above explanations also apply to this chamber.
- the parts of this chamber are provided with the reference symbols of the previously explained chamber, which are each identified by a comma.
- the second chamber works out of phase. When one chamber closes and compresses, the other chamber is open and can draw fresh gas through the inlet opening 16 '.
- the bearing device 9, 10, 11, for the rotationally secured mounting of the rotary piston 6, is designed with a reciprocating piston 10 and cylinder 11.
- This piston / cylinder arrangement can be used as a compression or expansion chamber, for which purpose the cylinder space under the reciprocating piston 10 is to be designed with inlet and outlet channels (not shown) and corresponding valves.
- the two chambers formed on the rotary piston 6 by the surface pairs can be designed with different sizes and operate as pre-compression and post-compression stages, while the piston / cylinder arrangement 10, 11 is used as the third post-compression stage.
- the bearing device at the free end of the support rod 8 can, however, be designed in a completely different way, it being only necessary to ensure that both a tilting movement and a reciprocating movement in the direction of the crankshaft M1 are permitted there.
- a simple alternative in the piston / cylinder arrangement 10, 11 shown is, for example, that the holding rod 8 is rigidly attached to the reciprocating piston 10 and the cylinder 11 is pivotally mounted on the housing 1.
- the bearing device can also be designed with the same kinematics, but without the formation of a piston / cylinder unit.
- the rotary piston 6, in contrast to the known constructions, is only supported on a crank pin 5, this can be arranged anywhere in the piston. In particular, it can be arranged very far away from the chamber-forming surfaces 12, 13 or 12 ', 13'. The heat transfer from the very hot chambers to the bearings of the crank pin 5 and the crankshaft is thus reduced and these are thermally relieved.
- the crankshaft can be arranged outside the rotary piston 6 at a thermally well protected location. This is shown in dashed lines in the figure. The crankshaft is supported at M1 'in a lateral bulge 3' of the peripheral wall 3.
- crank pin 5 ' is mounted in a bearing eye 19 which is attached to the rotary piston 6 by an arm 20 or another extension thereof. At this point, in the area of fresh air and far away from the chamber-forming surfaces, the crankshaft is arranged in a very thermally protected manner.
- crank pin can also be arranged at a different location as far as possible from the thermally stressed area of the rotary piston 6 in a manner not shown.
- the distance between the crank pin bearing 19 and the bearing device 9, 10, 11 should preferably be as large as possible in order to minimize the tilting movement of the rotary piston 6.
- the crankshaft bearing is therefore preferably to be provided on the side of the rotary piston facing away from the bearing device.
- the holding rod 8 can be made adjustable in the bore 7 of the rotary piston 6, so that it can be adjusted, for example, from the end position 8 'to 8 ". There is a reduction in the adjustment from the position 8' to the position 8" the distance of the bearing device to the crankshaft and thus an increase in the tilting movement. If the chamber-forming surfaces on the rotary piston 6 and on the peripheral wall 3 are calculated at position 8 ', they can no longer seal completely at position 8 ".
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP02751019A EP1402150A1 (de) | 2001-06-30 | 2002-06-13 | Rotationskolbenmaschine |
JP2003510576A JP2004533574A (ja) | 2001-06-30 | 2002-06-13 | ロータリピストンマシン |
US10/481,799 US20040213691A1 (en) | 2001-06-30 | 2002-06-13 | Rotary piston machine |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10131819.7 | 2001-06-30 | ||
DE10131819A DE10131819C1 (de) | 2001-06-30 | 2001-06-30 | Rotationskolbenmaschine |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2003004833A1 true WO2003004833A1 (de) | 2003-01-16 |
Family
ID=7690198
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2002/006476 WO2003004833A1 (de) | 2001-06-30 | 2002-06-13 | Rotationskolbenmaschine |
Country Status (6)
Country | Link |
---|---|
US (1) | US20040213691A1 (de) |
EP (1) | EP1402150A1 (de) |
JP (1) | JP2004533574A (de) |
CN (1) | CN1518634A (de) |
DE (1) | DE10131819C1 (de) |
WO (1) | WO2003004833A1 (de) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102008025185A1 (de) | 2008-05-23 | 2009-11-26 | Manfred Max Rapp | Massenausgleich für eine Drehkolbenmaschine |
DE102008025186B4 (de) | 2008-05-23 | 2010-04-29 | Manfred Max Rapp | Drehkolbenmaschine |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1962109A1 (de) * | 1968-12-13 | 1970-07-23 | Worthington Corp | Arbeitsmittelmaschine |
JPS5939987A (ja) * | 1982-08-30 | 1984-03-05 | Mitsubishi Heavy Ind Ltd | 回転式流体機械 |
DE3506376A1 (de) * | 1984-02-21 | 1985-09-05 | Mitsubishi Jukogyo K.K., Tokio/Tokyo | Rotationsmaschine fuer fluessigkeiten |
US4610610A (en) * | 1984-08-16 | 1986-09-09 | Sundstrand Corporation | Unloading of scroll compressors |
US5359892A (en) * | 1993-07-26 | 1994-11-01 | Felt Thomas W | Flowmeter measuring chamber |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3231756C2 (de) * | 1982-08-26 | 1985-08-01 | Pierburg Gmbh & Co Kg, 4040 Neuss | Rotationskolbenmaschine für Fluide |
DE4218847A1 (de) * | 1992-06-09 | 1993-12-16 | Manfred Max Rapp | Kolbenmaschine |
DE19500774A1 (de) * | 1995-01-13 | 1996-07-18 | Adolf Dr Ing Hupe | Rotationskolbenmaschine |
-
2001
- 2001-06-30 DE DE10131819A patent/DE10131819C1/de not_active Expired - Fee Related
-
2002
- 2002-06-13 WO PCT/EP2002/006476 patent/WO2003004833A1/de not_active Application Discontinuation
- 2002-06-13 US US10/481,799 patent/US20040213691A1/en not_active Abandoned
- 2002-06-13 CN CNA028123492A patent/CN1518634A/zh active Pending
- 2002-06-13 EP EP02751019A patent/EP1402150A1/de not_active Withdrawn
- 2002-06-13 JP JP2003510576A patent/JP2004533574A/ja active Pending
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1962109A1 (de) * | 1968-12-13 | 1970-07-23 | Worthington Corp | Arbeitsmittelmaschine |
JPS5939987A (ja) * | 1982-08-30 | 1984-03-05 | Mitsubishi Heavy Ind Ltd | 回転式流体機械 |
DE3506376A1 (de) * | 1984-02-21 | 1985-09-05 | Mitsubishi Jukogyo K.K., Tokio/Tokyo | Rotationsmaschine fuer fluessigkeiten |
US4610610A (en) * | 1984-08-16 | 1986-09-09 | Sundstrand Corporation | Unloading of scroll compressors |
US5359892A (en) * | 1993-07-26 | 1994-11-01 | Felt Thomas W | Flowmeter measuring chamber |
Non-Patent Citations (1)
Title |
---|
PATENT ABSTRACTS OF JAPAN vol. 008, no. 143 (M - 306) 4 July 1984 (1984-07-04) * |
Also Published As
Publication number | Publication date |
---|---|
EP1402150A1 (de) | 2004-03-31 |
DE10131819C1 (de) | 2002-10-24 |
CN1518634A (zh) | 2004-08-04 |
US20040213691A1 (en) | 2004-10-28 |
JP2004533574A (ja) | 2004-11-04 |
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