EP1811128A1 - Machine volumétrique pour fluides - Google Patents

Machine volumétrique pour fluides Download PDF

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Publication number
EP1811128A1
EP1811128A1 EP07100546A EP07100546A EP1811128A1 EP 1811128 A1 EP1811128 A1 EP 1811128A1 EP 07100546 A EP07100546 A EP 07100546A EP 07100546 A EP07100546 A EP 07100546A EP 1811128 A1 EP1811128 A1 EP 1811128A1
Authority
EP
European Patent Office
Prior art keywords
rotor
machine according
gap
stator
lobed
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Withdrawn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
EP07100546A
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German (de)
English (en)
Inventor
Morselli Giovanni
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 EP1811128A1 publication Critical patent/EP1811128A1/fr
Withdrawn legal-status Critical Current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
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/24—Rotary-piston machines or engines of counter-engagement type, i.e. the movement of co-operating members at the points of engagement being in opposite directions
    • F01C1/28—Rotary-piston machines or engines of counter-engagement type, i.e. the movement of co-operating members at the points of engagement being in opposite directions 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
    • 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
    • F01C1/082—Details specially related to intermeshing engagement type machines or engines
    • F01C1/084—Toothed wheels
    • 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
    • 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
    • F04C2220/00—Application
    • F04C2220/10—Vacuum

Definitions

  • This invention concerns a volumetric fluid machine, whose application can be either for liquids and for gas, especially in hydraulic machines, both as power generating machine (such as pumps and compressors) and as operating machine (such as hydraulic and gas turbines).
  • this invention concerns the field of volumetric machines, in which a defined volume, filled by a fluid, is periodically and alternatively put in communication with two separated surroundings at different pressures by the relative motion of mechanical parts.
  • the invention is related to the rotary volumetric machine class in which at least one has a rotatory motion.
  • volumetric machines in particular of type having rotating chambers, comprise one or more variable volume chambers which are periodically and alternatively put in communication with an intake room and with an exhaust room.
  • the volume variation of the chambers is obtained by means of the relative motion of same surfaces delimitating them.
  • This relative motion is achieved by different movement mechanisms, but having in any case a continuous relative motion between a stator and a rotor.
  • the chambers are defined by a properly shaped external profile of the rotor, and by a corresponding internal profile of the stator.
  • the chambers are generally enclosed at their sides by floating plates, to recover the play in order to avoid fluid leakage.
  • the chamber fluid sealing is achieved by one or more sliding contacts, realised between bulges or protuberances of the rotor and the stator internal surface, which avoid undesired fluid leakage from or into the chamber itself.
  • this system requires the presence of sliding elements subject to wear and deterioration over time, which contribute therefore to reduce the fluid tightness in the machine reducing the hydraulic efficiency.
  • volumetric machines with gears or conjugated profiles
  • two rotors are associated and put in rotation inside a stator, generally by driving a first rotor which actuates the second one.
  • the two rotors have an external profile shaped so as to delimit one or more chambers with constant section, and combine together, defining at least one contact point, always present during the machine operation.
  • a certain quantity of the fluid can remain trapped in correspondence of the contact point, for example due to surface deformability of the two rotors or due to irregularities of rotor profiles.
  • the quantity of fluid which is so trapped is restricted into a small volume and in case of a sudden reduction of available volume for example due to local deformabilities of rotors in contact, it could generate very high pressure leading to irregular functioning and even danger for the machine itself.
  • the technical object of this invention is therefore to realize a volumetric fluid machine capable to avoid the described disadvantages.
  • the principal aim of this invention is to realize a volumetric fluid machine which can limit fluid leakage without the use of sliding sealing parts.
  • Further aim of this invention is to realize a volumetric fluid machine which can avoid dangerous overpressures near the contact points between the rotating parts.
  • aim of this invention is to realize a volumetric fluid machine which does not require expensive mechanical processing in order to house the sealing parts.
  • volumetric fluid machine characterised in that it comprises one or more of the technical solutions presented hereafter.
  • FIG. 1 shows a front sectional view of a machine in a first embodiment, according to the invention
  • FIG. 2 shows a rear view of the machine of figure 1;
  • FIG. 3 shows a sectional view of a detail of the machine of figure 1
  • FIG. 4 shows a section view of another detail of the machine of figure 1
  • FIG. 5 shows a front sectional view of the machine, according to another embodiment.
  • volumetric fluid machine according to the invention is referred to with number 1.
  • the machine 1 comprises a stator 2 comprises the stationary part of the machine 1.
  • the stator 2 includes an external stiff casing 3, divided in a first portion 3a and in a second portion 3b, associated each other by a movable connection,
  • the external casing 3 presents an inner surface 4 which delimits, together with the machine sides (not depicted in the figures), an internal cavity 5 for housing a pair of rotors 6, 7.
  • the first rotor 6 and the second one 7 can rotate respectively around a first X and around a second rotational axis Y.
  • the two rotational axis X and Y are parallel.
  • the inner surface 4 is defined in part by the first portion 3a of the casing 3, and in a remaining part by the second portion 3b of the casing 3.
  • the inner surface 4 has a shape defined substantially by a partial overlapping of a first circular profile having a larger diameter, associated to the first rotor 6, with a second circular profile having a smaller diameter than the first, associated to the second rotor 7.
  • the cavity 5 communicates with the outside by an intake opening 8 and an exhaust opening 9, both of them located on the inner surface 4.
  • the two openings 8, 9 are placed near the intersections of the two above mentioned circular profiles which form the inner surface 4 of the casing 3.
  • the two openings 8, 9 communicate respectively with an intake pre-chamber 8a and with an exhaust pre-chamber 9a through two ducts 10 placed in the second portion 3b of the external casing 3.
  • the two openings 8, 9 are associated with unidirectional valves in order to avoid refluxes of fluid which could be very dangerous for the proper functioning of the machine 1.
  • the first rotor 6 has a substantially circular external profile 10 and presents a lobed part 10a that extends towards the inner surface 4 of the casing 3 and that is associated with the inner surface 4 itself.
  • such lobed part is cusped shaped with the vertex is associated with the inner surface 4 of the casing 3.
  • the second rotor 7 has an external profile 11 conjugated to the external profile 10 of the first rotor 6, so that the above mentioned external profiles 10, 11 are allowed to continuously associate each other during the rotation of the two rotors 6, 7.
  • the external profile 10 of the first rotor 6, with the mentioned lobed part 10a has the function of delimiting together with the inner surface 4 and with the external profile 11 of the second rotor 7, at least one chamber 12 whose variable volume cyclically varies from a maximum to a minimum value when rotor 6 rotates around the first axis X, in order to exchange energy with a moving fluid.
  • This chamber 12 is therefore intended to contain the fluid and, cyclically, to move it at least from the intake opening 8 to the exhaust opening 9.
  • the lobed part 10a together with the inner surface 4 of the casing 3, delimit a first gap 14 capable to guarantee fluid tightness between the first chamber 12 and the second chamber 13, as shown in figure 3.
  • the fluid sealing between the lobed part 10a and the inner surface 4 therefore relies therefore on the manufacturing accuracy of these parts.
  • the first gap 14 must have a width S1 as small as possible, measured in radial direction.
  • width S1 must be less than 1 mm.
  • the value of width S1 could be restricted to be above a proper low limit.
  • a suitable value for width S1 is therefore expected to be in the range between 0,02 to 0,05 mm.
  • the two rotors 6 and 7 do not operate with mutual contact.
  • the first rotor 6 and the second rotor 7 mutually define a second gap 15 in order to guarantee fluid tightness without causing scratching effects between the corresponding two conjugated profiles 10, 11.
  • the second gap 15 must have a constant width S2 measured in radial direction, i.e. along a segment connecting the the first and the second rotation axis X and Y, therefore along a segment connecting rotation centres of the two rotor 6, 7.
  • the second gap 15 allows the absence of contact between the two profiles 10, 11 of the two rotors 6, 7 thus avoiding every inconvenience that might arise and that have been already described referring to the affecting known devices.
  • machine 1 comprises means for motion transmitting motion 16, in order to mutually connect rotors 6, 7 in rotatory motion.
  • means for transmitting motion 16 generate a constant transmission ratio, according to the peculiar geometry of the profiles 10, 11 related to rotors 6, 7, which are conjugated and therefore they need to associate each other in periodic cyclic configurations.
  • this transmission ratio is preferably unitary in order to simplify the aboe mentioned means for transmitting motion 16 and to guarantee a perfect association between the profiles 10, 11 of the two rotors 6, 7, which can rotate with the same angular velocity.
  • the two rotors 6, 7 rotate in the same direction. Consequently, the two corresponding profiles 10, 11, have peripheral speed with opposite direction in correspondence of the second gap 15. This generates a parallel dragging of two thin layers of fluid in opposite directions, each thin layer of fluid being associated with one of the profiles 10, 11 of the two rotors 6, 7. This causes a "scraping" effect of the thin layer of fluid associated with the profile 10 of the first rotor 6, therefore reducing the leakage of fluid through the second gap 15.
  • the fluid sealing between the two profiles 10, 11 of the two rotors 6, 7 relies, as for the first gap, on the manufacturing accuracy of the mentioned profiles 10, 11 and in any case assumes that also the second gap 15 has a width S2, measured in radial direction, as small as possible.
  • Width S2 must be preferably not greater than 1 mm, for example in the range between 0,02 to 0,05 mm.
  • a toothed drive belt 18 is tied onto a pair of gear wheels 19, 19, each of which is associated with one of the two rotors 6, 7.
  • Each gear wheel 19 is connected and permanently fixed to one of rotors 6, 7, and can rotate around one of the above mentioned rotational axis X, Y.
  • tensioning devices 20 are employed, implemented simply by a tensioning wheel which engages on the external non-toothed surface of the drive belt 18, in order to guarantee a constant transmission ratio between the two rotors 6, 7. Furthermore, to assure this constant transmission ratio, gear wheels 19, 19 are required to have the same diameter.
  • a chain or gear transmission can be used as substitute for drive belt transmission 17.
  • the first chamber 12 has a volume substantially close to its minimum value while the second chamber 13 has a volume substantially close to its maximum value.
  • the first chamber 12 has a progressively increasing volume while the second chamber 13 has a progressively decreasing volume. This implies that the fluid is sucked up from the intake opening 8 into the first chamber 12, while the fluid contained in the second chamber 13 is pushed towards the exhaust opening 9, through which it moves out. A pumping action on the fluid is therefore produced from the intake pre-chamber 8a to the exhaust pre-chamber 9a.
  • the described functioning is supported by the rotation of the second rotor 7, which is clockwise, that contributes to guarantee the fluid sealing of the two chambers 12, 13.
  • the profile 11 of the second rotor 7 comprises a matching surface 21 made on purpose to continuously associate itself with the lobed part 10a.
  • a matching surface 21 defines on the second rotor 7 a truncated portion with reduced radial extension.
  • two lobed parts 10a are made on the profile 10 of the first rotor 6.
  • the two lobed parts 10a, 10b are preferably placed in diametrically opposite positions.
  • Such configuration envisages a third chamber 22 delimited by two lobed portions in cooperation with the profile 10 of the first rotor 10 and with the inner surface 4 of the casing 3.
  • Such chamber 22 due to its positioning, maintains constant its volume for a part of the revolution of the first rotor 6 during the functioning of the machine 1.
  • Each lobed part 10a is associated with the inner surface 4 of the casing 3 and, together with the inner surface 4, delimits a first gap 14 in accordance with the previously described first embodiment.
  • the second rotor 7 presents two matching surfaces placed in diametrically opposite positions, each of which associate always and only with one of the lobed parts.
  • the second rotor 7 presents one matching surface 21 only, that in turn can be associated with each lobed parts 10a, 10b.
  • the means for transmitting motion 16 must be modified, for example modifying the diameter size of one or both gear wheels 19.
  • a volumetric fluid machine can work either as an operating machine or as a mechanical power generator.
  • the operating power machine in particular a pump or a volumetric compressor
  • the mechanical power generator in particular a turbine
  • a functioning as a volumetric compressor is envisaged in internal combustion engines, while a functioning as a pump, in particular a vacuum pump, is used in aircraft pressurization equipments.
  • the intake opening 8 and the exhaust opening 9 change their role, respectively becoming the exhaust opening and the intake opening.
  • the same inversion occurs for the intake pre-chamber 8a and for the exhaust pre-chamber 9a.
  • This invention yields to important advantages.
  • the invention avoids any sliding contact actually present in known devices, ensuring a lasting functioning and reducing considerably the wear of the parts. Moreover this allows to eliminate possible overpressure effects that arise in known rotary devices near the contact points between the two rotors.
  • a fluid machine according to the invention considerably facilitates its manufacturing operations; in particular it does not require the realisation of radial slots to house the blades and the realisation of complex conjugated profiles, also with concave parts, as it happens in gearing volumetric machines whose manufacturing is difficult and very expensive.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP07100546A 2006-01-18 2007-01-15 Machine volumétrique pour fluides Withdrawn EP1811128A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ITMO20060015 ITMO20060015A1 (it) 2006-01-18 2006-01-18 Macchina volumetrica a fluido

Publications (1)

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EP1811128A1 true EP1811128A1 (fr) 2007-07-25

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EP07100546A Withdrawn EP1811128A1 (fr) 2006-01-18 2007-01-15 Machine volumétrique pour fluides

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EP (1) EP1811128A1 (fr)
IT (1) ITMO20060015A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR735814A (fr) * 1931-04-24 1932-11-16 Fried Krupp Germaniiawerft Ag Compresseur à pistons rotatifs
GB1135034A (en) * 1965-06-17 1968-11-27 David Herbert Blower Improvements in rotary piston internal combustion engines
DE9209641U1 (fr) * 1992-07-17 1992-11-19 Werner Rietschle Maschinen- Und Apparatebau Gmbh, 7860 Schopfheim, De
FR2690201A1 (fr) * 1992-04-17 1993-10-22 Py Marc Dispositif mécanique rotatif permettant la réalisation de compresseurs, de pompes ou de moteurs et moteurs selon ce dispositif.
DE4235559A1 (de) * 1992-10-22 1994-04-28 A Boeck Verbrennungsmotor
WO1998004809A1 (fr) * 1996-07-29 1998-02-05 Giovanni Morselli Machine a deplacement rotatif
US20040182357A1 (en) * 2001-06-25 2004-09-23 Dan Makler Rotary machine

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR735814A (fr) * 1931-04-24 1932-11-16 Fried Krupp Germaniiawerft Ag Compresseur à pistons rotatifs
GB1135034A (en) * 1965-06-17 1968-11-27 David Herbert Blower Improvements in rotary piston internal combustion engines
FR2690201A1 (fr) * 1992-04-17 1993-10-22 Py Marc Dispositif mécanique rotatif permettant la réalisation de compresseurs, de pompes ou de moteurs et moteurs selon ce dispositif.
DE9209641U1 (fr) * 1992-07-17 1992-11-19 Werner Rietschle Maschinen- Und Apparatebau Gmbh, 7860 Schopfheim, De
DE4235559A1 (de) * 1992-10-22 1994-04-28 A Boeck Verbrennungsmotor
WO1998004809A1 (fr) * 1996-07-29 1998-02-05 Giovanni Morselli Machine a deplacement rotatif
US20040182357A1 (en) * 2001-06-25 2004-09-23 Dan Makler Rotary machine

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Publication number Publication date
ITMO20060015A1 (it) 2007-07-19

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