EP1005604B1 - Drehkolbenmaschine - Google Patents

Drehkolbenmaschine Download PDF

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Publication number
EP1005604B1
EP1005604B1 EP98949923A EP98949923A EP1005604B1 EP 1005604 B1 EP1005604 B1 EP 1005604B1 EP 98949923 A EP98949923 A EP 98949923A EP 98949923 A EP98949923 A EP 98949923A EP 1005604 B1 EP1005604 B1 EP 1005604B1
Authority
EP
European Patent Office
Prior art keywords
rotary piston
piston machine
machine according
shut
unit
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
EP98949923A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1005604A1 (de
Inventor
Felix Arnold
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.)
ARNOLD Felix
Original Assignee
Arnold Felix
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Filing date
Publication date
Application filed by Arnold Felix filed Critical Arnold Felix
Publication of EP1005604A1 publication Critical patent/EP1005604A1/de
Application granted granted Critical
Publication of EP1005604B1 publication Critical patent/EP1005604B1/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
    • F01C3/00—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members
    • F01C3/06—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees
    • F01C3/08—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • 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
    • F01C3/00—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members
    • F01C3/06—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees
    • F01C3/08—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F01C3/085—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing the axes of cooperating members being on the same plane

Definitions

  • the invention relates to a rotary piston machine according to the Genus of the main claim (e.g. WO 93/12325).
  • a rotary lobe machine is known (DE P 42 41 320.6; DE G 92 18 694.7; PCT / DE 92/01025) where all lines forming the running direction transverse to the running direction of cycloid part and control part in their extension by the Intersection of the axes of rotation. So there are restrictions the expansion and compression behavior of the work rooms, connected, which is the adaptation of the lathe different working media and application limits puts.
  • the subject of the invention with the characterizing features of the main claim the advantage that the suction and exhaust behavior of the work rooms through the Phase shift is directed and thus an undesirable Backflow or a mixture of sucked and ejecting working medium is reduced.
  • a further advantageous embodiment of the invention are the working spaces by positive locking between flanks and Tooth combing of the opposing teeth of the parts separated so that the tooth combs of the control part by the Difference in the number of teeth on the flanks of the teeth of the Run along the cycloid part and the backflow of the fluid goes to zero and also the cycloid control part is drivable.
  • control channel for the entry of the working medium on Outside diameter and the control channel for the exit of the Working medium on the inside diameter of the toothing arranged so that in turbine or engine operation, the pulse and Mass forces of the working medium rectified with the Displacement direction of the work area. Moreover the leakage losses are thereby reduced and the Efficiency improved.
  • the working positions of the axes of rotation of the existing parts can be changed independently. It is also according to the invention conceivable that further additional wheel pairs are present, being at least. one of the parts also one on the back Has spur gearing, which in turn with another single or double toothed rotating part cooperates. The prerequisite is that it encloses these rotating parts Housing has a radial seal to these.
  • For the drive and output can be waves or sprockets in a known manner serve, which are connected to the rotating parts, or on these are arranged and with further drive or Interact output device.
  • Cycloid part or control part duplicated and between these duplicate parts with the other part as a ring double-sided forehead trim or cycloid treads arranged, at least according to a further embodiment two working spaces on both sides of the ring are connectable.
  • This control section can vary depending on whether it is a pump or a motor acts, have a drive or output device, or the drive and / or.
  • Downforce can be duplicated Cycloid parts are made.
  • the housing can serve as a stator in which both driven under the appropriate working angle Cycloid parts are stored, between which freely taken pro
  • the control part rotates on the face side with a tooth difference.
  • the radial lateral surface of the parts is spherical, these Parts on a correspondingly spherical inner surface of the Radially sealing housing are guided.
  • This outer or inner radial sealing, spherical workspace wall can be with control or Be connected to the cycloid part and rotate and center with it the parts to each other.
  • Another advantageous embodiment of the invention is its Application as a compressor with speed-independent control, especially by changing the phase shift of the two rotating parts to the channels of the working media. apart from the advantageous great centrifugal stability of the moving Parts and the small dimensions with high machine performance, can the compression ratio by the phase shift stepless control, especially control independent of speed.
  • This makes such a compressor for charging Internal combustion engines are particularly suitable because they have high speeds, especially very different speeds take place, the Mass of the loader should be as small as possible, especially the rotating masses to be driven, and the performance independently must be regulated by the speed.
  • Another advantageous embodiment of the invention is its Application in the hydrostatic field as a pump, motor or Transmission. This also has an extremely favorable effect here Ratio of size to volume sales.
  • the simple one Kinematics, the speed stability of the construction and the very These machines also make large cross-sections of the rinsing channels suitable for highest speeds.
  • the internal flow resistance the machine according to the invention is extremely low.
  • the high dimensional stability of the Parts advantageous. Wear also only affects the kind of as a kind of grinding between the moving parts takes place.
  • the machine is for the highest working pressures suitable.
  • When used as a hydraulic motor the equal advantages, but especially the small ones accelerating masses, the good starting behavior and the high Volumetric efficiency.
  • When used as a hydrostatic The small construction volume has a particularly advantageous effect on the transmission and the compact connectivity of the pump and Hydraulic motor.
  • Another advantageous embodiment of the invention is its Use as an engine or chiller, in particular according to the Stirling principle.
  • they work together assigned working spaces shifted by 90 °.
  • Two rotating cycloid parts in connection with a rotating Control section form pairs of chambers, each by 90 ° Work out of phase with each other.
  • a room becomes warm pressurized, the other cooled, a regenerator is in the Integrated control section.
  • the walls of the cold and hot work rooms are isolated from each other, although they are spatially close.
  • Extremely interpretable ratio of convection area / work space volume is due to the high form rigidity workspace-forming parts possible.
  • One of the rotating parts can be used as a rotor of a linear generator of the sterling motor or a linear motor of the Stirling refrigerator. So it is possible to hermetically seal the machine and for a very high charge pressure with low leakage losses of the To design working gas.
  • the phase shift, the performance of the Stirling engine, is very easy with this design realize.
  • Chiller the amount of heat transported regardless of the Speed can be regulated.
  • the power section 1 On the right side of Figure 1 are the power section 1 and Input or output shaft 2 shown. Not here Shown mounted drive or output shaft 2nd carries the power section 1 at one end.
  • the power section 1 consists of a spherical layer 3, the drive or Output shaft 2 is limited by a flat base 4 while its end face 5 has a spiral cycloid toothing having.
  • the cycloid 6 becomes - in contrast to the conventional Construction of a cycloid - formed by a circle intersection line 7 between spherical surface 8 and base surface 4 is unrolled and the point describing the cycloid 6 this Circle is always on the spherical surface 8.
  • the Cycloid 6 is the guide curve required to produce the gearing.
  • the shut-off part 10 shown on the left side of FIG. 1 has a similar geometry.
  • a shaft 11, which is also mounted in the housing, not shown, carries the spherical-layer-shaped shut-off part 10, which is delimited by a base surface 12 toward the shaft 11 and whose outer contour corresponds to a spherical surface 13.
  • the end face 14 of the shut-off part 10 has a spiral toothing, the number of teeth of which is greater by one than the number of cycloids 6 of the power part 1.
  • the contour of the teeth corresponds to the tangents to the cycloids 6 during the synchronous rotation of the power section 1 and the shut-off section 10.
  • the contour of the teeth can also be chosen so that there is always a certain distance between the cycloid and the teeth of the shut-off section 10. Then the displacement machine changes into a fluid machine. This is advantageous if, for. B. the working medium would be damaged by crushing ind sealing lines 9 or the momentum and inertial forces of the working medium should be used.
  • the axes of rotation of the shut-off part 10 and the power part 1 are at an operating angle 15 to one another. It is of no importance for the invention whether the cycloid toothing is arranged on the end face of the power section 1 as shown here and the corresponding toothing on the shut-off section 10 or vice versa.
  • power section 1 and shut-off section 10 are in their Installation position shown.
  • There are two sealing lines 9 in the Drawing are shown as points of contact, of power section 1 and Shut-off part 10 recognizable.
  • Shut-off part 10, power part 1 and Housing 17 form several, depending on the number of cycloids Working rooms 16, two of which are visible.
  • When through the two arrows indicated direction of rotation of power section 1 and Shut-off part 10 expand the work spaces 16 in the shown section of the rotary movement. Accordingly it will Volume of the work space on the second, not shown Half of the rotation is compressed.
  • the sealing lines 9 wander, depending on Direction of rotation, from outside to inside or vice versa and effect thereby promoting the working medium or driving the Output shaft 2.
  • the control openings not shown in the Housing 17 will meet the process requirements certainly. This is how the pump operation with the direction of flow from the inside outwardly positioned the inlet opening in the housing 17, at which the sealing line 9 is different from the inside diameter of the Replacement of gearing.
  • the external gearing takes the place of the Housing placed on the work space 16 the desired Volume.
  • the performance of the rotary lobe machine can constant speed can be controlled by the shut-off part 10 is moved relative to the power section 1. The remains Axis of rotation of the shut-off part 10 always on a conical surface, the Cone angle corresponds to the working angle 15.
  • FIG. 3 shows a simplified top view of the power section 1 shown.
  • four spiral generating lines 18 which is the construction of the spiral Cycloid toothing should clarify.
  • Generating lines 18 are placed on the highest points of the cycloids.
  • the spiral angle 19 is about 170 ° in the example shown.
EP98949923A 1997-08-21 1998-08-20 Drehkolbenmaschine Expired - Lifetime EP1005604B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19736397 1997-08-21
DE19736397 1997-08-21
PCT/DE1998/002428 WO1999010626A1 (de) 1997-08-21 1998-08-20 Drehkolbenmaschine

Publications (2)

Publication Number Publication Date
EP1005604A1 EP1005604A1 (de) 2000-06-07
EP1005604B1 true EP1005604B1 (de) 2002-07-31

Family

ID=7839729

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98949923A Expired - Lifetime EP1005604B1 (de) 1997-08-21 1998-08-20 Drehkolbenmaschine

Country Status (9)

Country Link
EP (1) EP1005604B1 (ja)
JP (1) JP4132660B2 (ja)
KR (1) KR100551525B1 (ja)
CN (1) CN1093592C (ja)
AU (1) AU9620398A (ja)
BR (1) BR9811964A (ja)
CA (1) CA2300812C (ja)
DE (3) DE19837729A1 (ja)
WO (1) WO1999010626A1 (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1749145B1 (de) * 2004-05-25 2013-07-17 Robert Bosch GmbH Spaltverluststromsteuerung einer drehkolben- zahnradmaschine

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10163801A1 (de) * 2001-12-22 2003-07-17 Heptec Gmbh Radialverdichter, insbesondere Kompressor für Beatmungsgeräte, Laufrad sowie Beatmungsgerät
DE10393551D2 (de) 2002-08-02 2005-06-30 Cor Pumps & Compressors Ag Drehkolbenmaschinen mit verschiebbarem Innengehäuse
US8834140B2 (en) 2004-05-25 2014-09-16 Cor Pumps + Compressors Ag Leakage loss flow control and associated media flow delivery assembly
WO2009026882A1 (de) * 2007-08-31 2009-03-05 Cor Pumps + Compressors Ag Verfahren zur umwandlung von druckluftenergie in elektrische energie und durchführung des verfahrens mit einem druckluftmotor
DE102011084828B4 (de) * 2011-10-19 2024-02-15 Robert Bosch Gmbh Förderaggregat
CN105756800B (zh) * 2016-04-20 2018-04-06 吉林大学 一种摆线针轮传动的可变压缩比活塞

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3856440A (en) * 1974-03-19 1974-12-24 E Wildhaber Rotor pair for positive fluid displacement
JP3853355B2 (ja) * 1991-12-09 2006-12-06 アーノルト・フェリックス 回転ピストン機械

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1749145B1 (de) * 2004-05-25 2013-07-17 Robert Bosch GmbH Spaltverluststromsteuerung einer drehkolben- zahnradmaschine

Also Published As

Publication number Publication date
DE19837729A1 (de) 1999-05-20
AU9620398A (en) 1999-03-16
EP1005604A1 (de) 2000-06-07
KR100551525B1 (ko) 2006-02-13
BR9811964A (pt) 2000-08-15
CN1267355A (zh) 2000-09-20
DE59805024D1 (de) 2002-09-05
DE19881218D2 (de) 2000-07-13
JP2001514352A (ja) 2001-09-11
WO1999010626A1 (de) 1999-03-04
CA2300812A1 (en) 1999-03-04
CA2300812C (en) 2007-01-09
CN1093592C (zh) 2002-10-30
JP4132660B2 (ja) 2008-08-13
KR20010022963A (ko) 2001-03-26

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