WO2003055551A1 - Compresseur centrifuge radial pour appareils respiratoires - Google Patents

Compresseur centrifuge radial pour appareils respiratoires Download PDF

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Publication number
WO2003055551A1
WO2003055551A1 PCT/DE2002/004706 DE0204706W WO03055551A1 WO 2003055551 A1 WO2003055551 A1 WO 2003055551A1 DE 0204706 W DE0204706 W DE 0204706W WO 03055551 A1 WO03055551 A1 WO 03055551A1
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
blades
impellers
radial compressor
compressor according
Prior art date
Application number
PCT/DE2002/004706
Other languages
German (de)
English (en)
Inventor
Martin Baecke
Original Assignee
Seleon Gmbh
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 Seleon Gmbh filed Critical Seleon Gmbh
Priority to AU2002358449A priority Critical patent/AU2002358449A1/en
Priority to DE10296120.4T priority patent/DE10296120B4/de
Publication of WO2003055551A1 publication Critical patent/WO2003055551A1/fr

Links

Classifications

    • A—HUMAN NECESSITIES
    • A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
    • A61M—DEVICES FOR INTRODUCING MEDIA INTO, OR ONTO, THE BODY; DEVICES FOR TRANSDUCING BODY MEDIA OR FOR TAKING MEDIA FROM THE BODY; DEVICES FOR PRODUCING OR ENDING SLEEP OR STUPOR
    • A61M16/00—Devices for influencing the respiratory system of patients by gas treatment, e.g. mouth-to-mouth respiration; Tracheal tubes
    • A61M16/0057—Pumps therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
    • F04C18/54—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees
    • F04C18/56—Rotary-piston pumps 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
    • F04C18/565—Rotary-piston pumps 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C3/00—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type
    • F04C3/06—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees
    • F04C3/08—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type 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
    • F04C3/085—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type 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
    • A—HUMAN NECESSITIES
    • A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
    • A61M—DEVICES FOR INTRODUCING MEDIA INTO, OR ONTO, THE BODY; DEVICES FOR TRANSDUCING BODY MEDIA OR FOR TAKING MEDIA FROM THE BODY; DEVICES FOR PRODUCING OR ENDING SLEEP OR STUPOR
    • A61M16/00—Devices for influencing the respiratory system of patients by gas treatment, e.g. mouth-to-mouth respiration; Tracheal tubes
    • A61M16/0057—Pumps therefor
    • A61M16/0066—Blowers or centrifugal pumps

Definitions

  • the invention relates to a radial compressor, in particular a compressor for respirators, according to the preamble of claim 1, 5 an impeller according to the preamble of claim 11 and a ventilator equipped with such a radial compressor.
  • radial compressors are used, among other things, in ventilators, in particular CPAP devices.
  • CPAP continuous positive airway pressure
  • Suppliers of compressors suitable for CPAP devices are, for example, AMETEK ROTRON, PAPST, ebm, Micronel, Telemeter Electronic.
  • the compressors must be able to press the required amount of air through a thinner tube in order to maintain the therapy pressure in the mask.
  • the problem here is that a pressure is required that single-stage small turbines can hardly deliver.
  • the air flow must be pulsation-free and easy to control.
  • smoothness i.e. low noise, is required.
  • Classic piston compressors are ruled out due to their pulsed air emissions and the associated noise.
  • the radial compressors that have been predominantly used up to now have to be operated at a very high speed, which leads to annoying whistling noises.
  • two-stage radial compressors could be used.
  • the size increases in order to achieve the required air throughput. If one assumes the increased requirements that arise when using thinner hoses, there is no commercially available compressor that satisfies the criteria: pressure, volume flow, size, and noise emission in total satisfactorily.
  • a description for rotary lobe machines is also available at http://www.megasat.ch/wolfhart/pumpen.htm. This website describes rotary lobe machines according to the so-called "Wolfhart principle" with a force-free stroke movement and a bearing-free piston drive.
  • a piston rotor and a cylinder rotor rotate with each other around slightly, ie about 5 ° inclined axes.
  • the piston rotor typically has three to five cylinder bores that rotate on a circular path during operation.
  • the cylinder rotor has a corresponding number of cylinders. During operation, the cylinders in the piston bores move up and down due to the angle between the rotary axes of the piston rotor and the cylinder rotor.
  • a control mirror has usual channels for control, which lead to an inlet or outlet.
  • Such rotary lobe machines can be used as water or oil pumps up to about 100 bar. It is the object of the invention to provide a radial compressor, an impeller and a respirator which are capable of generating a higher pressure than in the case of radial compressors previously used in CPAP devices.
  • An advantage of the radial compressor according to the invention is that it realizes a two-stage compression. It combines the advantages of a radial compressor, namely pulsation-free, smooth delivery of large volume flows, with piston compression, namely high pressure build-up and no backflow.
  • the advantage of equipping an impeller with a hollow axis and the use of this axis as an inflow channel is that the centrifugal force also contributes to the compression of the fluid.
  • the advantage of using a sealing element is that blades penetrating the cavities cannot push the fluid back into the interior.
  • the drive of a gearwheel by positive locking with the other gearwheel eliminates the need for further drive elements for the first gearwheel and thus leads to a simplified structure.
  • the inclusion of magnets in the blades of the impellers so that the blades of one impeller repel the blades of the other impeller enables the one impeller to be driven by the other impeller without contact and thus leads to a reduction in noise. Furthermore, the magnets allow very small distances between the blades of the two impellers to be maintained without contact.
  • Fig. 1 shows a first section through a radial compressor according to the invention
  • Fig. 2 shows a second section through the radial compressor according to the invention.
  • the preferred embodiment of the invention is a rotary piston radial compressor.
  • the compressor consists essentially of a housing 6 and two impellers 1 and 2.
  • the housing is essentially mirror-symmetrical, the symmetry broken mainly by the different mounting of the impellers 1 and 2 becomes.
  • the impeller 1 has a hollow axis which forms an inflow channel 16.
  • the impeller 2 is driven by a drive shaft 12.
  • Two wheels 1 and 2 are arranged at a slight angle to each other. Their axes intersect in the plane of symmetry of the housing 6 and enclose the impeller angle 18. They are rotatably mounted, for example, in roller bearings 14 and 13. They have conical toothed blades 9 and 15 on the sides facing one another. In the compression area 3, these blades interlock so that the spaces between the blades 9 of the impeller 1 are filled by the blades 15 of the impeller 2.
  • the path of a blade 9 is tracked: in FIG. 2 rotating clockwise, the blades 9 of the Impeller 1 slowly out of the cavities between the blades 15 of the impeller 2 and vice versa. Air flows from the interior 5 into the cavities thus freed. The cavities are sealed on the outside by the housing 6. Up to the largest opening in position 7, the volume between the blades 9 which is not filled by shoveling the other impeller increases. Depending on the angle which the axes of the impellers enclose and the dimensions of the impellers and the blades, an additional volume 8 can even be formed. The additional volume is defined by the fact that the blades of the two impellers do not move through this space and that it lies within the housing 6.
  • Compression begins at position 7.
  • air can still be sucked in from the interior 5 here because the air located between the blades 9 and in the volume 8 is compressed by the radial acceleration. It also takes time to fill the cavities with air due to air resistance.
  • the negative pressure in a cavity in relation to the interior 5 does not become 0 in the position of the largest opening 7, but only somewhat later. After the position of the largest opening 7, the negative pressure in the cavity is reduced both by inflowing air and by the beginning compression. Up to this point, the function essentially corresponds to a radial compressor.
  • a sealing element 10 now seals off from the interior 5. Seen in the direction of movement of the impellers, the sealing element does not start at the position of greatest compression but somewhat later. Ideally, the sealing element begins at the position at which the air flow into the cavity is just 0. As stated above, this position is speed-dependent. The start of the sealing element is preferably optimized for the highest speed occurring during operation. But it can also be designed for the most common speed. In the preferred embodiment, the sealing element 10 is fastened to a holder which extends through the inflow channel 16 and is fastened to the outside of the housing 6.
  • the blades 9 and 15 of the impellers 1 and 2 narrow the cavities in the other impeller by penetrating into the opposing cavities and press the air out into the outflow channel 11 through which the air leaves the compressor. When the position of the largest compression 4 is exceeded, the compression stops and the suction process is initiated again.
  • the air supply can take place through the hollow axis of the impeller 1 forming the inflow channel 16.
  • the air can also be supplied through the additional volume 8.
  • the impellers are arranged at a particularly large impeller angle 18 so that the blades of the two impellers release a direct connection between the additional volume 8 and the interior 5. This direct connection means that no blade moves when the impellers are turned.
  • a holder for the sealing element 10 can be integrated here. So the impellers without a hollow shaft, i.e. be designed the same.
  • the housing can be seen in the direction of rotation of the impellers from a first angle after the position of the largest compression 4 to a second angle after the position of the largest opening on the outer circumference of the
  • Impellers form an inflow channel. This inflow channel enables the
  • This embodiment has the advantage that the sealing element is difficult to assemble
  • Embodiment no impeller with a hollow axle required.
  • the sealing element can be integrated into an impeller by the cavities of the impeller
  • Impeller between its blades are closed inwards to the axis of the impeller by walls.
  • the drive shaft 12 is attached to the impeller 2.
  • Both impellers 1 and 2 are preferably mounted in roller bearings 14 and 13, respectively.
  • Impeller 2 takes over the drive of impeller 1, in the simplest case by a simple positive fit.
  • the impellers are preferably made of plastic.
  • the impellers 1 and 2 contain magnetized components in the blades 9 and 15, which are magnetized in such a way that the blades 9 of the impeller 1 repel one another from the blades 15 of the impeller 2.
  • the Magnetic dipole moments are oriented from a blade into an adjacent cavity or in the opposite direction. This means that very close spacing tolerances can be maintained without friction, which is important for a quiet run.
  • the blades 9 and 15 can also consist of magnetized plastics. These are plastics into which small magnetized iron parts, so-called microferrites, are introduced, the ferrites being aligned in the desired manner, for example by an external magnetic field, when the plastic solidifies.
  • a radial compressor has been described above, in particular for use in CPAP devices. For this reason, air was always mentioned as the medium to be promoted. However, it is obvious to those skilled in the art that the above radial compressor can also be used to convey other media, such as water. Therefore, the term fluid is used in the claims as a generic term for gases and liquids. It is also clear to the person skilled in the art that liquids have a density that is about three orders of magnitude higher. On the one hand, this means that at the same speed, a much higher pressure can be built up solely by centrifugal force. On the other hand, the forces also increase by three orders of magnitude under otherwise identical conditions. The specialist in radial compressors for liquids will therefore not manufacture the blades from plastic, but preferably from more stable metal.

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  • Engineering & Computer Science (AREA)
  • Health & Medical Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Biomedical Technology (AREA)
  • Heart & Thoracic Surgery (AREA)
  • Hematology (AREA)
  • Anesthesiology (AREA)
  • Animal Behavior & Ethology (AREA)
  • General Health & Medical Sciences (AREA)
  • Public Health (AREA)
  • Veterinary Medicine (AREA)
  • Pulmonology (AREA)
  • Emergency Medicine (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un compresseur centrifuge radial pour appareils respiratoires, comportant deux rotors (1), (2), un boîtier (6) ainsi qu'un canal d'alimentation (16) et un canal d'évacuation (11). Les rotors sont placés sur le boîtier de sorte que les pales (9) d'un rotor (1) s'engagent dans les espaces vides entre les pales (15) de l'autre rotor (2). Une des pales repousse un volume plus ou moins important dans un des espaces vides lors de la rotation des rotors de sorte que le fluide est évacué par le canal d'évacuation (11) ou aspiré par le canal d'alimentation (16), pour produire une pression plus élevée qu'avec des compresseurs centrifuges radiaux à un étage classiques. L'invention concerne en outre un rotor pour un tel compresseur centrifuge radial, ainsi qu'un appareil respiratoire équipé d'un compresseur centrifuge radial selon l'invention.
PCT/DE2002/004706 2001-12-22 2002-12-20 Compresseur centrifuge radial pour appareils respiratoires WO2003055551A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AU2002358449A AU2002358449A1 (en) 2001-12-22 2002-12-20 Radial compressor for respirators
DE10296120.4T DE10296120B4 (de) 2001-12-22 2002-12-20 Radialverdichter für Beatmungsgeräte

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10163801.9 2001-12-22
DE2001163801 DE10163801A1 (de) 2001-12-22 2001-12-22 Radialverdichter, insbesondere Kompressor für Beatmungsgeräte, Laufrad sowie Beatmungsgerät

Publications (1)

Publication Number Publication Date
WO2003055551A1 true WO2003055551A1 (fr) 2003-07-10

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ID=7710751

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2002/004706 WO2003055551A1 (fr) 2001-12-22 2002-12-20 Compresseur centrifuge radial pour appareils respiratoires

Country Status (3)

Country Link
AU (1) AU2002358449A1 (fr)
DE (2) DE10163801A1 (fr)
WO (1) WO2003055551A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005046775A1 (fr) * 2003-10-15 2005-05-26 Airtechnologies S.A.S. Dispositif d’assistance respiratoire
WO2012034759A3 (fr) * 2010-09-14 2013-04-04 Robert Bosch Gmbh Unité de circulation
WO2013023916A3 (fr) * 2011-08-17 2013-12-12 Robert Bosch Gmbh Association pompe-moteur
RU2627753C2 (ru) * 2015-11-02 2017-08-11 Евгений Геннадьевич Иванов Роторная гидро-пневмомашина

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2701306C1 (ru) * 2018-04-09 2019-09-25 Евгений Геннадьевич Иванов Роторная объёмная машина

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2654322A (en) * 1948-09-15 1953-10-06 Horace W Olsen Pump
US2831436A (en) * 1952-08-19 1958-04-22 Garvenswerke Maschinen Pumpen & Waagenfabrik W Garvens Pump
FR1404962A (fr) * 1963-08-22 1965-07-02 Appareil de dosage et de mélange pour fluides
GB1099085A (en) * 1966-02-21 1968-01-17 Wildhaber Ernest Rotary positive displacement units
DE3925202A1 (de) * 1989-07-29 1991-01-31 Josef Gail Kegelzahnradpumpe
DE19837729A1 (de) * 1997-08-21 1999-05-20 Felix Arnold Drehkolbenmaschine

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19904119C2 (de) * 1999-02-03 2002-06-27 Draeger Medical Ag Rotationsverdichter für Beatmungssysteme

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2654322A (en) * 1948-09-15 1953-10-06 Horace W Olsen Pump
US2831436A (en) * 1952-08-19 1958-04-22 Garvenswerke Maschinen Pumpen & Waagenfabrik W Garvens Pump
FR1404962A (fr) * 1963-08-22 1965-07-02 Appareil de dosage et de mélange pour fluides
GB1099085A (en) * 1966-02-21 1968-01-17 Wildhaber Ernest Rotary positive displacement units
DE3925202A1 (de) * 1989-07-29 1991-01-31 Josef Gail Kegelzahnradpumpe
DE19837729A1 (de) * 1997-08-21 1999-05-20 Felix Arnold Drehkolbenmaschine

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005046775A1 (fr) * 2003-10-15 2005-05-26 Airtechnologies S.A.S. Dispositif d’assistance respiratoire
WO2012034759A3 (fr) * 2010-09-14 2013-04-04 Robert Bosch Gmbh Unité de circulation
US9046099B2 (en) 2010-09-14 2015-06-02 Robert Bosch Gmbh Delivery unit
WO2013023916A3 (fr) * 2011-08-17 2013-12-12 Robert Bosch Gmbh Association pompe-moteur
RU2627753C2 (ru) * 2015-11-02 2017-08-11 Евгений Геннадьевич Иванов Роторная гидро-пневмомашина

Also Published As

Publication number Publication date
DE10296120B4 (de) 2015-01-22
AU2002358449A1 (en) 2003-07-15
DE10296120D2 (de) 2004-11-11
DE10163801A1 (de) 2003-07-17

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