EP0790389A1 - Machine rotatif à déplacement positif - Google Patents

Machine rotatif à déplacement positif Download PDF

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Publication number
EP0790389A1
EP0790389A1 EP97830064A EP97830064A EP0790389A1 EP 0790389 A1 EP0790389 A1 EP 0790389A1 EP 97830064 A EP97830064 A EP 97830064A EP 97830064 A EP97830064 A EP 97830064A EP 0790389 A1 EP0790389 A1 EP 0790389A1
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EP
European Patent Office
Prior art keywords
vanes
machine
fluid
cavity
turn
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.)
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Application number
EP97830064A
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German (de)
English (en)
Inventor
Roberto Manzini
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Individual
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Individual
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Publication date
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Publication of EP0790389A1 publication Critical patent/EP0790389A1/fr
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    • 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
    • F01C1/063—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 with coaxially-mounted members having continuously-changing circumferential spacing between them
    • F01C1/077—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 with coaxially-mounted members having continuously-changing circumferential spacing between them having toothed-gearing type drive

Definitions

  • the present invention relates to a rotary positive displacement fluid machine for general use as a motor, pump, compressor or suction pump.
  • fluid machines are machines in which mechanical energy is mainly processed by means of forces applied to a compressible fluid (gas or vapour) or incompressible fluid (liquid).
  • Positive displacement machines represent a category within this general technical sector.
  • the fluid acts statically upon the mobile walls of vessels with variable volumes which the fluid alternately fills and from which it is then emptied.
  • the present invention relates to a rotary positive displacement fluid machine of the type which includes: (a) a casing with internal cavity, an axis about which the cavity is symmetrical and two sections, respectively for the infeed and discharge of the fluid in the cavity and (b) at least one pair of vanes, mounted inside the cavity in such a way as to divide it into a corresponding pair of separate chambers, designed to alternately receive and discharge the fluid.
  • the configurations of several such machines are generally known, in particular pumps and compressors, in which the variability of the volumes of the said chambers is obtained by the eccentric installation, in the cavity, of a rotor with radial vanes. More particularly, the rotor is fitted so that it is tangent to a generatrix of the casing and the vanes are contained in radial slots in the rotor.
  • the aim of the present invention is to provide a machine of the afore-mentioned type, in which the said disadvantages are overcome.
  • the numeral 20 is used to indicate as a whole a fluid machine which basically consists of a cylindrical casing 1, closed by two covers 25, 26, and having an internal cavity 2, which is symmetrical about a horizontal axis 3 and communicates with the external environment through two sections 4, 4a (see figures 6, 7, 8, 9) of the casing 1, respectively for the infeed and discharge of the fluid in the cavity 2.
  • a pair of vanes 5, 6 is mounted inside the casing 1.
  • the vanes are rigidly fixed to the ends of two coaxial shafts 10, 11, attached to one another in such a way that they can turn and aligned on the axis 3 of the cavity 2 (see figures 3 and 5).
  • vanes 5, 6 protrude crosswise to the axis 3 towards the internal surface la of the casing 1 and their free ends 5a, 6a make contact with the internal surface la of the casing 1, against which they form a seal against the fluid.
  • the vanes 5, 6, together and with the casing 1, divide the cavity 2 into a pair of opposite, complementary chambers 7, 8 which are not inter-communicating.
  • Figure 3 in particular shows that the vanes 5, 6 are mounted in the casing 1 in such a way that they can turn about an axis 3 and are independent of one another, so that they move relative to one another about the axis of rotation 3.
  • This allows (see figures 1 and 2) variations in the volumes of the chambers 7,8 located between the vanes 5, 6 according to the specific operating requirements of the machine 20, as is more clearly indicated in the following description.
  • the vanes 5, 6 are driven by specific means which include (see figures 3 and 4) two pairs Ea and Eb of identical elliptic gears 12a, 12b, 14a, 14b, reciprocally meshing in pairs.
  • Two first gears 12a, 14a of each pair Ea, Eb are fitted on a shared drive shaft 21, which is keyed to the gears 12a, 12b at one of the two focal points of the primitive ellipse of the said gears 12a, 14a.
  • the second two gears 12b, 14b of each pair Ea, Eb are rigidly keyed to the shafts 10, 11 which transmit the rotation to the vanes 5, 6. Again (see figure 4) the gears 12b, 14b are keyed to the shafts 10, 11 at one of the focal points of the primitive ellipse.
  • Figure 3 in particular shows that the two pairs Ea, Eb of elliptic gears 12a, 12b, 14a, 14b are fitted so that the respective first gears 12a, 12b (driving gears) are keyed to the drive shaft 21 in such a way that they are offset by 180°.
  • the drive means 12a, 12b, 14a, 14b described above cause the vanes 5, 6 to turn about the axis 3 of the cavity 2, having a speed which varies cyclically and being timed separately for each vane 5, 6.
  • the vanes 5, 6 move with a speed which varies cyclically and which is identical for both vanes 5, 6 but offset so that during a full turn of the vanes 5, 6 the said vanes 5, 6 periodically move towards and away from one another in a circle inside the casing 1 (see figures 1 to 9).
  • the machine functions as follows.
  • vanes 5 and 6 (see figures 1 and 2), rigidly fixed to the two respective hubs 27, 28 which are integral with the shafts 10, 11 (see figure 3) turn inside the cylindrical casing 1 about the same axis 3, creating a seal: on the hubs 27, 28 against the surface of the casing 1 and against the two covers 25 and 26 (see figure 3) which close the casing 1.
  • this configuration allows the creation of two chambers 7, 8 delimited by: the internal surface la of the casing 1, the two covers 25, 26, the two hubs 27, 28 and the two vanes 5, 6.
  • a variation in the volumes of the two chambers 7, 8 must be obtained (as one increases, the other is reduced), and, as a result, the fluid is acted upon mechanically.
  • This is obtained by making the vanes 5, 6 turn at relative speeds, meaning that they must turn at different speeds.
  • the vanes 5, 6 must both simultaneously complete a full 360° turn, to avoid impact with one another, they must turn at variable speeds.
  • Figure 1 shows two points labelled H and K (dead centres) at which the two vanes 5, 6 have the same rotation speed.
  • K considering, for example, a clockwise turn of the vanes 5, 6) vane 6 is decelerating whilst vane 5 is accelerating.
  • vane 6 continues to slow until it reaches the minimum speed at X (see figure 2), then begins to accelerate towards point K.
  • vane 5, having passed point K continues to accelerate until it reaches the maximum speed at Y, then begins to slow after passing that point and as it approaches point H.
  • vane 5 reaches point H vane 6 reaches point K and while both again turn at the same instantaneous speed, a half-cycle is completed.
  • the two vanes 5, 6 follow one another, moving towards and away from each other twice per turn; always turning at the same speed when at points H and K and, when one reaches the minimum speed at X the other reaches the maximum speed at Y.
  • both chambers 7, 8 reach their maximum volume Cmax and minimum volume Cmin, corresponding to the representation of the said chambers 7 and 8 in figure 1.
  • the Cmax/Cmin ratio defines the difference in pressure between the two chambers 7, 8. If one of the vanes 5, 6 is seen as if on a system of co-ordinates, it is evident that, on one side, the second vane 6 or 5 moves away, and on the other, the remaining vane simultaneously moves towards it along a circular arc subtended by a centre angle equal to S - R, then the motion is inverted as soon as the vanes arrive at the points marking the end of stroke (points H and K). If the said circular arc is developed along a straight line, the result is an alternating motion whose stroke is equal to the length of the said arc, as for a double action piston.
  • variable-speed rotary motion can be obtained mechanically in various ways.
  • a preferred embodiment indicated by way of example only and without limiting the application of the present invention, can be obtained with four identical elliptic gears 12a, 12b, 14a, 14b arranged in two pairs Ea, Eb (see figure 4) turning about a focal point F of the primitive ellipse.
  • the centre-to-centre I between the two pairs of gears 12a, 12b or 14a, 14b is constant, and the two gears 12a, 12b or 14a, 14b complete the same number of turns, although the gear ratio is variable within the 360° arc.
  • the pair of gears 12a, 12b which drives vane 5 is labelled Ea (see figure 3)
  • the pair of gears 14a, 14b which drives vane 6 is labelled Eb
  • the driving gear 12a, 14a turns at a constant speed
  • the driven gear 12b, 14b turns at a variable speed.
  • vane 6 is represented in the position corresponding to point X in figure 2, where the rotation speed is at its minimum. It may be noticed that the pair of elliptic gears Eb is at the point where the turns of shaft 21 have been reduced to the minimum; whilst, at the same time, vane 5 is in the position Y of maximum rotation speed: it may be noticed that its pair of elliptic gears Ea is at the point where the turns of shaft 21 have been increased to the maximum.
  • the major axis/minor axis ratio of the primitive ellipse of the said gears 12a, 14a is correlated with the value of angles R and S (see figure 1), and so also with the Cmax-Cmin value, that is to say, the displacement of the machine 20. If this ratio is increased, the value of angle R is reduced, and as a result Cmax-Cmin is increased. Therefore, the displacement is increased with the same number of turns. At the same time, Cmax/Cmin, i.e.: the difference in pressure between the two chambers 7, 8, increases.
  • the machine 20 may operate both as a driving machine or a machine in itself, becoming either a pump or a compressor/suction pump, depending whether or not the fluid is compressible.
  • vanes 5 and 6 turn at the same instantaneous speed, their relative speed is zeroed and, therefore, there is no difference in the volumes of the two chambers 7, 8, as is necessary for the changes in an incompressible fluid such as a liquid.
  • both vanes 5, 6 must be positioned exactly in front of the two holes 4, 4a and close them completely so as to avoid a direct connection between suction and delivery, which would prevent the pumping action.
  • the arrows indicate the direction of flow of the liquid for one clockwise turn of the vanes 5, 6.
  • Chamber 7, whose volume is increasing, is the suction chamber, and chamber 8, whose volume is reduced, is the pressing chamber.
  • the vanes 5, 6 are suitably shaped, it is possible to further reduce the minimum volumes of the chambers 7, 8 (Cmin) (figure 6) which represents the clearance volume. Even if the geometric shape of the vanes 5, 6 created for this purpose also reduces the Cmax, the Cmax-Cmin value (and so also the displacement) remains unchanged. In contrast, the Cmax/Cmin ratio (which has a directly proportional effect on the head at start-up when the pump contains no liquid) increases considerably, so that the pump has a strong self-priming action.
  • the circumference of the discharge section 4a (delivery) must be smaller, so that it opens only when the pressing chamber 8 is reduced to the point at which it has generated the desired internal pressure. Therefore, the smaller the discharge section 4a, the greater the output pressure.
  • the arrows indicate the direction of flow of the fluid for a clockwise turn.
  • Chamber 7 suction
  • chamber 8 pressing
  • the vanes 5, 6 must be shaped so that they have circular sectors, so that they also create a seal along the circumference of the casing 1 long enough to maintain the discharge section 4a (delivery hole) closed for the time necessary to obtain the desired pressure (see figure 9).
  • vanes 5, 6 must be shaped so as to reduce the value of the clearance volume to a minimum Cmin (see figure 8) and, finally, must allow the fluid infeed section 4 to open as soon as the volume of chamber 7 (suction) begins to increase, so as to fully exploit the expansion and, therefore, maximise the displacement (if used as a compressor) and vacuum (if used as a suction pump).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Chairs Characterized By Structure (AREA)
  • Special Chairs (AREA)
EP97830064A 1996-02-14 1997-02-14 Machine rotatif à déplacement positif Withdrawn EP0790389A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITBO960066 1996-02-14
IT96BO000066A IT1285896B1 (it) 1996-02-14 1996-02-14 Pompa/compressore/depressore a due pale rigide fissate sui rispettivi mozzi coassiali ruotanti a velocita' variabile all'interno di una

Publications (1)

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EP0790389A1 true EP0790389A1 (fr) 1997-08-20

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EP (1) EP0790389A1 (fr)
IT (1) IT1285896B1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000079102A1 (fr) * 1999-06-17 2000-12-28 Hugo Julio Kopelowicz Dispositif a deux rotors ou plus comportant chacun au moins un piston, se deplaçant dans la meme direction a des vitesses variables et alternativement opposees l'un par rapport a l'autre a l'interieur d'une chambre cylindrique independante ou formee par les rotors

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3398643A (en) * 1965-07-30 1968-08-27 Schudt Hans Rotary piston engine, pump or other machine
FR2244367A6 (en) * 1973-09-19 1975-04-11 Boes Jean Rotary vane type two rotor engine - rotors controlled by non-circular gears form variable vol chambers
EP0062087A1 (fr) * 1981-04-08 1982-10-13 Gerhard Rödiger Machine à piston rotatif à vitesse de rotation périodiquement variable
WO1986005548A1 (fr) * 1985-03-19 1986-09-25 Venturelli, Giacomo Moteur rotatif

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3398643A (en) * 1965-07-30 1968-08-27 Schudt Hans Rotary piston engine, pump or other machine
FR2244367A6 (en) * 1973-09-19 1975-04-11 Boes Jean Rotary vane type two rotor engine - rotors controlled by non-circular gears form variable vol chambers
EP0062087A1 (fr) * 1981-04-08 1982-10-13 Gerhard Rödiger Machine à piston rotatif à vitesse de rotation périodiquement variable
WO1986005548A1 (fr) * 1985-03-19 1986-09-25 Venturelli, Giacomo Moteur rotatif

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000079102A1 (fr) * 1999-06-17 2000-12-28 Hugo Julio Kopelowicz Dispositif a deux rotors ou plus comportant chacun au moins un piston, se deplaçant dans la meme direction a des vitesses variables et alternativement opposees l'un par rapport a l'autre a l'interieur d'une chambre cylindrique independante ou formee par les rotors

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Publication number Publication date
ITBO960066A1 (it) 1997-08-14
ITBO960066A0 (it) 1996-02-14
IT1285896B1 (it) 1998-06-26

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