EP2825776B1 - Rotationsverdichter mit mindestens einem seitenkanal - Google Patents

Rotationsverdichter mit mindestens einem seitenkanal Download PDF

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Publication number
EP2825776B1
EP2825776B1 EP13715318.5A EP13715318A EP2825776B1 EP 2825776 B1 EP2825776 B1 EP 2825776B1 EP 13715318 A EP13715318 A EP 13715318A EP 2825776 B1 EP2825776 B1 EP 2825776B1
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Prior art keywords
rotor
blades
channel
fluid
series
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EP13715318.5A
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English (en)
French (fr)
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EP2825776A2 (de
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Michel Chiaffi
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D23/00—Other rotary non-positive-displacement pumps
    • F04D23/008—Regenerative pumps

Definitions

  • the invention relates to the field of volumetric compressors and more specifically volumetric compressors known as peripheral or regenerative compressors. These machines are intended to compress a fluid, in particular a gas, between an inlet opening (or inlet) and an outlet opening (or outlet) in the manner of a dynamic compressor.
  • the performances of the peripheral compressors are between those of the vane compressors and those of the centrifugal compressors.
  • the aerodynamics of the peripheral compressors are therefore based on the rotation of vanes in an annular channel.
  • the movement imparted to the fluid is a relatively complex helical movement, which induces compression comparable to that of a multi-stage compressor.
  • a high compression ratio and low rotation speeds are the technical characteristics of this type of compressor.
  • FIG. 1 schematically illustrates this type of machine that can be likened to a centrifugal compressor with partial and multi-stage injection. Yields of the order of 50% are obtained with this type of machine, having a flow rate of 4000 m3 / h and a compression ratio of about 1.6.
  • the rotor speeds are relatively low, of the order of 100m / s which reduces the wear problems of the parts. The low speeds of the rotor make it possible to use any type of metal for the blades.
  • this technological evolution did not have the expected commercial success because the value of the energy efficiency was still insufficient to compete with the best performing centrifugal machines; Applications were limited to cases where mechanical simplicity was favored
  • compressors as illustrated on the figure 2 , improvements to those of the figure 1 because with several side channels.
  • These compressors may comprise two so-called lateral channels because each is arranged symmetrically on either side of the main plane of the rotor.
  • the figure 2 shows an example with three channels peripherals: two lateral and one radial. Each of the thus arranged channels has its own inlet and outlet ports. If the output of the first channel is associated with the input of a second channel, the fluid is compressed twice so that the flow rate being that of a single channel compressor, the compression will be doubled.
  • the compressor has two side channels disposed on either side of the plane of the rotor, the two inputs and the two fluid outlets are twinned, which doubles the flow of the compressor.
  • the invention aims to overcome the drawbacks of the state of the art and in particular to provide a side channel compressor of simple design, whose performance is improved; leaks are also greatly diminished and are not very significant.
  • the respective configurations and shapes of the rotors, the peripheral channels and the series of blades are such that the ratio A / R2 is between 6% and 16%.
  • the compressor according to the invention may comprise a third series of vanes disposed on an opposite lateral face of said rotor and within a given specific channel.
  • This characteristic dimensioning makes it possible in particular to optimize the compression of the fluid in the compressor.
  • the blades accelerate the fluid in a movement both tangential to the rotor and perpendicular to this tangential motion.
  • the fluid flow induces multiple fluid passages between the blades over several turns, resulting in improved compression ratio and relatively low rotational speeds.
  • said at least one first series of blades has a dimension h measured parallel to or perpendicular to the axis XX of rotation of the rotor, said dimension h being such that the ratio h / R is between 5% and 15%.
  • This feature aims to improve the performance of the compressor.
  • said housing of said at least one peripheral channel and / or said static core has internal reliefs intended to modify the direction of the fluid flowing inside said peripheral channel, in particular between two juxtaposed blades.
  • a flow rectifying effect is here obtained preferentially in conjunction with the shape of the vanes, which are not planar.
  • a separating piece is disposed in said at least one peripheral channel, between the inlet and the outlet of said fluid, said separating piece having a shape and means for progressively lowering the pressure of said fluid before recirculation. Since the fluid passes several times between the vanes before being evacuated from the channel in question, this separation piece between the inlet and the outlet of the channel in question is important for the good recirculation of the fluid and especially in order to reduce the losses. charge.
  • the blades constituting said at least one first series of blades have a so-called circumferential orientation, generally parallel to the axis of said rotor.
  • a third series of blades of the same orientation but arranged symmetrically with respect to the plane of the rotor can be provided without departing from the scope of the invention.
  • Each series of blades is disposed in a specific associated peripheral channel, externally defined by a housing.
  • each of these embodiments has the dimensional characteristics defined at the head, in particular to increase the yield.
  • said rotor has a multiplicity of through holes for balancing the induced axial pressures.
  • the compressor comprises at least one inlet pipe for the fluid, which opens in said at least one peripheral channel and orienting said fluid in a direction opposite or perpendicular to the direction of rotation of said rotor.
  • peripheral channels When several peripheral channels are provided, they may have cross sections A of different or identical values. The skilled person will choose according to the constraints associated with the case envisaged.
  • Figures 1 and 2 relate to compressors provided respectively with a lateral channel and three peripheral channels, two lateral and one radial. Of known structure in itself, these compressors are part of the invention from the moment when characteristic dimensional ratii are provided.
  • such compressors comprise a wheel or rotor 1 in the form of a circular disk of radius R, to which a series of blades 2 are attached.
  • the series of blades may consist of a set of non-planar blades 2 which have a so-called circumferential orientation, that is to say in a plane more or less close to a circumference of the rotor 1.
  • figure 3 schematically this option.
  • the housing 3 of the rotor 1 which substantially conforms to the shape while providing an axial clearance corresponding to leakage zones and pressure drops.
  • the figure 2 illustrates an embodiment of the invention according to which, typically, the respective arrangements and shapes of the rotors, peripheral channels and blade series are such that the ratio A / R2 is between 6% and 16%; the compressor comprises a third series of blades disposed on an opposite lateral surface of the rotor and in a specific specific channel.
  • the rotor 1 has a set of through holes 30 for balancing the various induced axial pressures.
  • the blades 2 are housed in an annular ring-shaped channel 4 which, moreover, houses a static core 5 which is also annular and coaxial with the rotor 1.
  • the annular channel 4 is advantageously coaxial with the rotor 1 and is termed a 'peripheral' because radial end of the rotor 1.
  • peripheral channels may be provided, arranged symmetrically vis-à-vis the main plane of the rotor 1 or at the distal and radial end of the rotor 1.
  • the flow of the fluid in the channel or channels 4 is three-dimensional and complex.
  • the figure 4 shows by a cross section of one of the channels 4, the decomposition of the flow from the inlet 10 of the fluid in the channel 4 to its outlet 20.
  • a flow called circulatory d is generated from the passage between the blade 2. It is a helical flow which causes the fluid to flow several times through the blades 2 before exiting at the outlet 20.
  • a so-called tangential flow c is also created, laminar at the inner wall This flow is created by the blades 2 and its slowing down inside the annular channel 4 creates the pressure in the compressor.
  • a separation part 6 is in particular provided with holes 60 which, associated with its specific shape, make it possible to lower the pressure of the fluid which will recirculate between the outlet 20 and the inlet 10.
  • the arrows f and g of the figure 4 symbolize anterior leakage and so-called posterior leakage respectively.
  • the invention relates to ratii A / R2 where A is the cross sectional area of at least one of the peripheral channels, and where R is the radius of the rotary wheel 1.
  • the area A corresponds to globally the passage section offered to the fluid to travel the channel, from the inlet 10 to the exit 20.
  • a ratio A / R2 between 8% and 16% allows optimize the efficiency of the compressor.
  • the figure 5 illustrates several ratii that fall within the scope of the invention.
  • the size of the free channel 4 can vary in the characteristic proportions of the invention. It is the dimensions of the blades 2 which, at equal size, make it possible to be in a configuration according to the invention.
  • the clearance (distance) between the blades 2 and the core 5 may be constant or not.
  • width h of the blades 2 relative to the radius R of the rotor 1 must remain in such proportions that h / R is between 5% and 15%.
  • width is meant the dimension of a blade 2 measured either parallel to or perpendicular to the axis XX of rotation of the rotor 1; parallel in the case where the vanes are oriented circumferentially to the axis XX of the rotor as illustrated by the Figures 1, 3 , 5 or 6 ; perpendicular to the axis XX in the case of blades oriented along the main plane of the rotor 1.
  • This feature is particularly interesting for increasing compressor performance by decreasing the relative share of leaks.
  • an inlet pipe 11 opens into the channel 4 with a preferred orientation; this orientation must be different from the perpendicular to the plane of the rotor 1. It will preferentially choose an orientation of the inlet pipe 11 in the retrograde direction of the wheel, that is to say in opposition to the direction of rotation of the wheel 1.
  • the mean helical flow of the fluid in the channel 4 is disturbed, especially since the inlet port 10 is important.
  • the inlet opening 10 is placed below the core 5, for example as illustrated by the square 4 on the figure 1 .
  • the exit opening 20 it is preferentially placed above the core 5, that is to say at a point marked 1 in the square of the figure 1 .
  • the orientation of the outlet pipe 21 associated with the opening 20 will be almost tangential, highly progressive (depending on the direction of rotation of the rotor). It is thus sought to minimize the pressure drop and induce a movement close to that of the mean flow.
  • the figure 7 is a solid surface showing the progression of the fluid in a peripheral channel, more particularly the flow between the blades 2 and around the static core 5, from the inlet 10 to the outlet 20 of the channel.
  • the graphs at different points of the flux correspond to the total velocity of the fluid combining the circulation around the nucleus (ordinate) as a function of its progression between the inlet 10 and the exit 20 (abscissa) at certain points of the channel 4.
  • figure 8 schematically illustrates the effects of this feature to optimize the flow from the output of a blade to the entry at the next dawn. It's about optimizing velocities and pressures at each point of the flow and decrease turbulence losses between two different pressure zones to reduce their variations when passing between two blades.
  • peripheral channels their respective dimensions are not necessarily equal; the areas A of each channel considered may be different; however, each area A in particular responds to the ratio A / R2 characteristic of the invention.
  • the compressor according to the invention achieves adiabatic efficiencies of about 60%.
  • Many types of gas can be used according to the invention: pure gases, corrosive, explosive or flammable.
  • the pressure variation can reach 40 bars and the compression ratio is greater than 3. These performances are little affected by the operating conditions.
  • the inlet pressure can reach a value up to 200 bars with a temperature of the order of 200 ° C., a flow rate of 60,000 Nm3 / h.
  • the rotational speeds are low, of the order of 100m / s.
  • the seals used may be carbon seals.
  • Such a compressor is economical because it requires reduced maintenance, small dimensions and low installation costs.
  • the lubrication system is very simple to implement and, contrary to the centrifugal compressors, no anti-pumping system is necessary.
  • the invention can be integrated in a regeneration circulator of a drying sieve.
  • the compressors according to the invention can for example be used for the supply of TAG.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (8)

  1. Rotationsverdichter, der einen Rotor (1) in Form einer Scheibe mit dem Radius R umfasst und am Umfang mindestens eine erste Serie von nicht planaren Schaufeln (2) trägt, die auf einer Seitenfläche des Rotors (1) angeordnet sind, um das zu verdichtende Fluid zwischen einem Einlass (10) und einem Auslass (20) zu beschleunigen, wobei ein Gehäuse (3) außerhalb mindestens einen Kanal (4) definiert, der am Umfang des Rotors (1) liegt und eine allgemeine toroidale Form aufweist, wobei der mindestens eine Kanal koaxial ist, am radialen Ende des Rotors (1) angeordnet ist und die Schaufeln (2) aufnimmt, wobei ein statischer und ringförmiger Kern (5) innerhalb des mindestens einen toroidförmigen Kanals (4) angeordnet ist, um mit dem Gehäuse (3) einen freien Querschnitt A zu definieren, wobei der Verdichter ein Trennstück (60) umfasst, das in dem mindestens einen Umfangskanal (4) zwischen dem Einlass (10) und dem Auslass (20) des Fluids angeordnet ist, wobei das Trennstück (60) eine Form aufweist, die es ermöglicht, den Druck des Fluids vor dem Einlass des Fluids allmählich zu senken, dadurch gekennzeichnet, dass er eine zweite Serie von Schaufeln umfasst, die in der radialen Verlängerung des Rotors und in einem gegebenen spezifischen Kanal angeordnet sind, und dass die jeweiligen Anordnungen und Formen des Rotors (1), mindestens eines Umfangskanals (4) und der mindestens einen ersten Serie von Schaufeln (2) und einen zweiten Serie von Schaufeln derart sind, dass das Verhältnis A/R2 zwischen 6 % und 16 % liegt.
  2. Rotationsverdichter nach Anspruch 1, dadurch gekennzeichnet, dass die mindestens eine erste Serie von Schaufeln (2) eine Abmessung h aufweist, die parallel oder senkrecht zur Drehachse XX des Rotors gemessen wird, wobei die Abmessung h derart ist, dass das Verhältnis h/R zwischen 5 % und 15 % liegt.
  3. Rotationsverdichter nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass das Gehäuse (3) des mindestens einen Umfangskanals (4) und/oder des statischen Kerns (5) Reliefs aufweist, die dazu bestimmt sind, die Richtung des im Inneren des Umfangskanals (4) strömenden Fluids, insbesondere zwischen zwei nebeneinander angeordneten Schaufeln, zu ändern.
  4. Rotationsverdichter nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die Schaufeln (2), welche die mindestens eine erste Serie von Schaufeln bilden, eine sogenannte Umfangsausrichtung aufweisen, die im Allgemeinen parallel zur Achse des Rotors (1) verläuft.
  5. Rotationsverdichter nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass er zwei Serien von Schaufeln umfasst, die symmetrisch auf beiden Seiten der Hauptebene des Rotors angeordnet sind, wobei jede Serie in einem spezifischen Umfangskanal angeordnet ist.
  6. Rotationsverdichter nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass der Rotor (1) eine Vielzahl von Durchgangsbohrungen aufweist, die dazu bestimmt sind, die induzierten axialen Drücke auszugleichen.
  7. Rotationsverdichter nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass er mindestens einen Einlassstutzen (11) für das Fluid umfasst, der in den mindestens einen Umfangskanal mündet und das Fluid darin in eine entgegengesetzte Richtung oder senkrecht zur Drehrichtung des Rotors leitet.
  8. Rotationsverdichter nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass er mehrere Umfangskanäle mit freien Querschnitten A unterschiedlicher Werte umfasst.
EP13715318.5A 2012-03-14 2013-03-14 Rotationsverdichter mit mindestens einem seitenkanal Active EP2825776B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1252301A FR2988145B1 (fr) 2012-03-14 2012-03-14 Compresseur rotatif muni d'au moins un canal lateral
PCT/FR2013/050531 WO2013136016A2 (fr) 2012-03-14 2013-03-14 Compresseur rotatif muni d'au moins un canal lateral.

Publications (2)

Publication Number Publication Date
EP2825776A2 EP2825776A2 (de) 2015-01-21
EP2825776B1 true EP2825776B1 (de) 2019-09-04

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EP13715318.5A Active EP2825776B1 (de) 2012-03-14 2013-03-14 Rotationsverdichter mit mindestens einem seitenkanal

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US (1) US20150167680A1 (de)
EP (1) EP2825776B1 (de)
FR (1) FR2988145B1 (de)
WO (1) WO2013136016A2 (de)

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Publication number Priority date Publication date Assignee Title
GB606127A (en) * 1944-10-30 1948-08-06 Bendix Aviat Corp Blowers
DE2405890A1 (de) 1974-02-07 1975-08-14 Siemens Ag Seitenkanal-ringverdichter
IT1057591B (it) * 1975-03-27 1982-03-30 Rateau Soc Macchina periferica per fluido
US4261685A (en) * 1978-03-31 1981-04-14 The Garrett Corp. Energy transfer machine
US4325672A (en) * 1978-12-15 1982-04-20 The Utile Engineering Company Limited Regenerative turbo machine
GB2036870A (en) * 1978-12-15 1980-07-02 Utile Eng Co Ltd Regenerative Turbo Machine
SU1359437A1 (ru) * 1986-03-25 1987-12-15 Ленинградский Кораблестроительный Институт Вихрева турбомашина
FR2664333B1 (fr) * 1990-07-04 1994-08-12 Bertin & Cie Electro-soufflante de circulation d'un fluide gazeux, tel que de l'air par exemple.
US5143511A (en) * 1990-09-28 1992-09-01 Lamson Corporation Regenerative centrifugal compressor
US5137418A (en) * 1990-12-21 1992-08-11 Roy E. Roth Company Floating self-centering turbine impeller
RU2032836C1 (ru) * 1992-12-29 1995-04-10 Владимир Николаевич Хмара Вихревой компрессор
US7033137B2 (en) * 2004-03-19 2006-04-25 Ametek, Inc. Vortex blower having helmholtz resonators and a baffle assembly

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP2825776A2 (de) 2015-01-21
WO2013136016A2 (fr) 2013-09-19
US20150167680A1 (en) 2015-06-18
WO2013136016A3 (fr) 2013-11-14
FR2988145B1 (fr) 2016-09-30
FR2988145A1 (fr) 2013-09-20

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