EP0069604A1 - Verbesserungen an hydraulischen Pumpen oder Motoren mit Schneckenartigen Zahnrädern (Schneckenturbinen) - Google Patents

Verbesserungen an hydraulischen Pumpen oder Motoren mit Schneckenartigen Zahnrädern (Schneckenturbinen) Download PDF

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Publication number
EP0069604A1
EP0069604A1 EP82400972A EP82400972A EP0069604A1 EP 0069604 A1 EP0069604 A1 EP 0069604A1 EP 82400972 A EP82400972 A EP 82400972A EP 82400972 A EP82400972 A EP 82400972A EP 0069604 A1 EP0069604 A1 EP 0069604A1
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EP
European Patent Office
Prior art keywords
stator
rotor
turbine
screw
turbine according
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Withdrawn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
EP82400972A
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English (en)
French (fr)
Inventor
Bernard Girette
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Individual
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Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0069604A1 publication Critical patent/EP0069604A1/de
Withdrawn legal-status Critical Current

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    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
    • F04C2/1071—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • F04C11/003—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle having complementary function

Definitions

  • the rotary piston (s) have the geometry of screws generated by a deformed epicycloid or hypocycloid curve, movable in a stator which itself has the geometry of a screw generated by the curve of the same family as the rotor, but of parameter (n + 1) when the rotor is of parameter n, and of pitch h (n + 1) when the pitch of the rotor is of pitch hn. so that both screw surfaces are always tangent along (n + 1) continuous lines along the screws.
  • the known applications all relate to uses or applications as pumps or high pressure motors, the use of these devices for large flows and low pressures having hardly been implemented.
  • the present invention relates to the application of these devices to the use of low-drop hydraulic power. This is in particular the transformation of hydraulic energy from tides or rivers.
  • low-drop hydraulic energy can be transformed into mechanical energy, heat energy or energy.
  • hydraulic with different characteristics as well as mechanical energy can be transformed into low-drop hydraulic energy,
  • the device is designated by the expression screw turbine, so as not to distinguish a priori the operation in motor and the operation in pump.
  • the turbine according to the invention is for this purpose characterized in that the stator screw comprises, in the zones of change of radius of curvature of the same stage of the elements guides such as idle rollers slightly projecting from the surface of the stator and on which the rotor screw comes into contact, the stator comprising a succession of stages with guide elements placed side by side over its entire length, and the geometries of the rotor and the stator being determined so that there remains a clearance in the contact cloths between rotor and stator, this clearance being substantially equal to the prominence of the guide elements.
  • stage is meant a section perpendicular to the axis of the screw and of sufficient thickness for the housing of the guide element (roller or other).
  • the rotor and the stator are produced by helical stacking of identical sections between them, with cylindrical walls parallel to the axis of the screw and the stages of guide elements coincide with the sections of the screw (stator and rotor).
  • rollers housed in the wall of the stator and with an axis parallel to the axis of the screw, or balls or rollers, or projecting pads or other arrangements known in hydraulic technology under the term of hydraulic wedges.
  • Another arrangement of the invention consists in that the rotor screw is mounted rotating freely around an axis (crank) connected at its ends by crank arms to the turbine shaft, the shape of which thus resembles that of a crankshaft.
  • stator axis and the rotor axis remain strictly parallel, which is obtained by rigidly fixing the crank to the two arms of the crankshaft and by dimensioning it so that the torsional forces to which it is subjected creates parallelism faults less than the expected clearance (total deviations of the ends of the crank from the exact parallelism).
  • the low-drop hydraulic energy can thus be transformed by simple and efficient means into mechanical energy (and vice versa), with very rough construction means.
  • This mechanical energy can be used directly but it can also, according to a provision of the invention be transformed into hydraulic energy by the creation of a secondary current of higher pressure and lower flow rate by means of a positive displacement pump which can also be a screw pump.
  • the invention provides for this application the use of a turbine with two screws, in which the rotor of the first screw serves as a hollow envelope for the second screw, the water inlet being common to the two screws while the outputs are separate.
  • the ratio of the pressure at the outlet of the second turbine to the pressure at the inlet of the first is the inverse of the ratio of the unit volumes of the two turbines (closed volume between stator and rotor over one revolution of screw).
  • the water thus pumped can be stored in a tank placed at a level above the reach in the same relationship to the initial height of fall.
  • the pump driven by the first turbine can also be a positive displacement pump sucking water from a reservoir to discharge it into the same reservoir via a valve and a load breaker, the opening of this valve being controlled by the level of the upstream reach and the hot water intake made on the pump discharge circuit upstream of the valve.
  • the turbine of FIGS. 1 and 2 consists of a hollow casing forming a stator 1 in which a rotor screw 2 moves.
  • the screw 2 is formed from a stack of circular discs 3, the stator 1 being formed from a disc stack 4 each comprising an oblong opening 5.
  • the relative geometric shapes of the discs 3 and the openings 5 are the shapes known and described in the prior art cited above,
  • the turbine according to the invention intended for low falls, is of large diameter relative to its axial length which is generally less than the diameter.
  • the diameter could be of the order of 4m, for a length of 2m,
  • each assembly formed by an internal disk 3 and an external disk 4 constitutes a stage and the internal face of the opening 5 of a stage of the stator 1 comprises, in each zone for changing the radius of curvature of a guide element 6, roller, ball or roller, or hydraulic wedge, slightly projecting from the internal surface of the stator, while the radius of the disc 3 is slightly less than the radius of curvature of the curved parts of the opening 5 .
  • the rotor screw comes to bear successively on the rollers of each stage during a fraction of its orbital movement which depends only on the unit angle which separates the position of a disc 3 from the following around the axis of the turbine.
  • the guidance of the rotor screw is therefore analogous to that of a wheel 7 moving on a succession of rollers 8 as shown in FIG. 3.
  • the invention provides on the one hand to give the rollers an elasticity of suspension (for example elastically repelled rollers) or active or rolling surface (elastomer surface) and on the other hand to produce in flexible and elastic material the surface of at least one of the two screws, for example to produce the discs 3 with a thickness or edge of rubber or other elastomer, preferably cellular.
  • suspension for example elastically repelled rollers
  • active or rolling surface elastomer surface
  • the shaft 8 of the turbine has the form of a crankshaft whose crank 9 constitutes the shaft around which the rotor 2 freely rotates, this crank being connected to the shaft 8 by the arms 10.
  • the disks 3 will be mounted on a hollow sleeve 11 swiveling around the shaft 9 secured to the arms 10 themselves secured to the shaft 8.
  • crankshaft 8, 9, 10 must be very rigid so that the torsional forces to which it is subjected do not reduce the advantages resulting from this play. More precisely, the crank 9 and the arms 10 will be calculated on which it is rigidly fixed so that the distance between its ends with respect to the exact parallelism cannot exceed the chosen value of the clearance under the conditions of service provided.
  • This mode of constitution of the screw turbine allows the production of very bulky machines with very rough means for inexpensive energy recovery despite very low heights of fall, of the order of 1 meter for example.
  • the dimensions to which this adaptation leads can be very large and pose an implementation problem with regard to the lower bearing which must support the weight of the rotor 2 plus the pressing force,
  • this difficulty is overcome by providing a rotor provided with cavities filled with air and such that the density of the rotor is less than that liquid of the fall,
  • the cavities will be of adjustable volume, for example in the form of tight ballasts with controllable filling, making it possible to adjust the density; but we can also use a rotor inside which are arranged volumes of cellular material. Such volumes or ballasts are shown in dotted lines at 12 in FIG. 2.
  • a turbine as shown in FIG. 1, having an external diameter of 108 m, a disc diameter 3 of 40 m, a stator height 1 of 40 m can accept a flow rate of 5000 m 3 / sec. under a drop height of 2 mt, with a clearance between rotor and stator allowing the passage of solid impurities of the order of 10 cm.
  • Such a machine is capable of providing 100 megawatts of raw power. It can be carried out with very crude means such as the means of shipbuilding.
  • the profile to be given to each stage can be that of a simple stair step as shown in Figure 4 (section along a plane passing through the axis of the rotor) . It is also possible to cut the stages along the dotted lines 13 and 14 (FIG. 5), that is to say according to the surface generated by the segment joining two homologous points 15 and 16 of two discs of two successive stages. Such an arrangement is more expensive to make but allows greater play for the same leak rate.
  • the speed of rotation of the shaft 8 can be very low, of the order of a few revolutions per minute, and too irregular, at due to variations in flow, to be used directly as mechanical energy. But it can then be used to drive a similar machine for the production of hydraulic energy which can be used as such or serve for the production of heat, for example for the production of a flow of hot water.
  • Figure 6 illustrates such a hydraulic power transformer.
  • a pump with screw constituted by the helical screw 19 rotating relative to the helical space 20 is a pump with screw constituted by the helical screw 19 rotating relative to the helical space 20.
  • the present invention provides for the use of one of the motor spaces and of the other pump space, the mechanical energy resulting from the motor operation being used to drive the pump, and the spaces volumetric having a ratio corresponding to the pressure ratio to be obtained.
  • the inputs 21 and 22 are common but the outputs 23 and 24 are separated and the liquid entering the external screw turbine 17-18 serves to supply the mechanical compression energy of the pump formed by the assembly 19-20 so that at the outlet of the pump 19-20, a liquid is obtained whose pressure is, relative to the pressure, determined by the height of fall which is available in the turbine 17-18 , in the same proportion as the volumetric ratios of the closed enclosures of screws 17-18 relative to those of screws 19-20,
  • the invention provides for using for the screw 17-18 a geometry of transformed or deformed hypocycloids with at least three vertices while the pump 19-20 has a geometry of transforms of hypocycloids with 1 and 2 vertices,
  • the invention provides for giving the internal screw 19-20 a smaller center distance than that of the screw 17-18, which results in shorter crank arms 10b. that arms 10a,
  • the solution shown in Figures 6 and 7 can be adopted;
  • the external shape (stator 17) can be made of concrete with a flat bottom 42, the surface of which can be coated with a smooth material such as a sheet of stainless steel.
  • the rotor screw 17 is provided with a rubber skirt 43 which slides over this surface and seals between the pressurized water of the cavity 23 and the pressureless water of the cavity 24.
  • This bottom has separate orifices outlet: on the one hand, the three orifices 38 which discharge downstream, via the underground passages 24, the water having passed through the turbine 17-19; on the other hand, the orifice 40, in the center, connected by the underground 23 at the place of use of the water thus pressurized by the screws 19-20.
  • FIG. 8 illustrates the use of such a hydraulic energy transformer as a heat generator.
  • the mechanical energy resulting from the operation of a low-drop turbine 25 such as that of FIG. 1 is used in the drive 26 of a positive displacement pump 27 working in a closed circuit in a tank 28, insulated at 39
  • the pump 27 draws the liquid at 29 to return it to the reservoir at 30 by means of a valve-nozzle 31, that is to say a valve transforming the pressure into speed, and dissipating this speed into turbulence by any circulation in the reservoir 28; the liquid is then taken up in 29 to undergo the same cycle again, Under these conditions the water heats up and it becomes possible to take from the high pressure stage at 32, a flow of hot water corresponding to the production of machine calories: at the low pressure stage, at 33, the same quantity of cold water will be reinjected into the circuit.
  • the invention provides a regulation system consisting in regulating the closing of the valve 31 as a function of the level of the upstream reach 34, by means of the float 36 connected to the valve 31 by the linkage 37.
  • the valve 31 opens.
  • the pressure in the high pressure stage of the pump system 27 reservoir 30 decreases, which allows the speed of the turbine 25 to be increased, which thereby , absorbs more water. This is in contrast to the upstream water rise movement which reduced the pressure on the high pressure stage.
  • a lowering of the upstream level 34 causes the valve 31 to close and the outlet pressure of the pump 27 to rise, which requires the turbine 25 more energy than it can supply.
  • the turbine 25 will slow down its movement, thus absorbing less flow, which is opposed to lowering the upstream level 34.
  • This regulation therefore makes it possible to operate the system in a very wide range of related flows while maintaining the level upstream at the maximum level authorized by the site, the turbine 25 and the entire system operating as an upstream level regulator.
  • the flow of calories available in 32 will vary with the flow of the river. In winter, it may be sufficient for a central heating installation or a substantial supplement, in summer it may be sufficient for the consumption of hot water for toilet or household use.
  • a hydraulic power transformer with a large operating range consisting of a turbine according to the invention operating as a motor, and driving a positive displacement pump 27 whose resistive torque is regulated by a valve 31 as a function of the upstream level, the recovery thus being optimized by maintaining the potential of the fall at its optimum level.
  • the pump 27 can be the compressor. gas from a heat pump type system, that is to say that the energy transformer and the regulation thus described also apply in the case of the drive of a heat pump.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Rotary-Type Compressors (AREA)
  • Hydraulic Motors (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
EP82400972A 1981-06-01 1982-05-26 Verbesserungen an hydraulischen Pumpen oder Motoren mit Schneckenartigen Zahnrädern (Schneckenturbinen) Withdrawn EP0069604A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8110781A FR2506861A1 (fr) 1981-06-01 1981-06-01 Perfectionnements aux pompes ou moteurs hydrauliques a engrenages helicoidaux (turbines a vis)
FR8110781 1981-06-01

Publications (1)

Publication Number Publication Date
EP0069604A1 true EP0069604A1 (de) 1983-01-12

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EP82400972A Withdrawn EP0069604A1 (de) 1981-06-01 1982-05-26 Verbesserungen an hydraulischen Pumpen oder Motoren mit Schneckenartigen Zahnrädern (Schneckenturbinen)

Country Status (3)

Country Link
EP (1) EP0069604A1 (de)
JP (1) JPS5813101A (de)
FR (1) FR2506861A1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1382853A1 (de) * 2002-07-17 2004-01-21 Adeleth Investments Inc. Rotierende Schraubenmaschine und Methode zur Umwandlung einer Bewegung in einer solchen Maschine
WO2005005838A1 (en) * 2003-07-14 2005-01-20 Elthom Enterprises Limited Rotary screw compressor with multiple stages

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2951773B1 (fr) * 2009-10-22 2012-04-27 Thomas Eleaume Unite de production d'energie a rendement eleve
KR102628748B1 (ko) 2015-04-30 2024-01-24 닛산 가가쿠 가부시키가이샤 코팅 조성물 및 광학부재

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR787711A (fr) * 1934-05-02 1935-09-27 Mécanisme à engrenages perfectionné, utilisable comme pompe, compresseur, moteur ou simple dispositif de transmission
FR1373732A (fr) * 1963-07-31 1964-10-02 Machine volumétrique notamment compresseur, moteur à combustion interne ou pompe
DE2715576A1 (de) * 1977-04-07 1978-10-12 Streicher Foerdertech Exzenterschneckenpumpe
FR2384136A1 (fr) * 1977-03-19 1978-10-13 Streicher Foerdertech Pompe a plateaux d'excentriques

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR787711A (fr) * 1934-05-02 1935-09-27 Mécanisme à engrenages perfectionné, utilisable comme pompe, compresseur, moteur ou simple dispositif de transmission
FR1373732A (fr) * 1963-07-31 1964-10-02 Machine volumétrique notamment compresseur, moteur à combustion interne ou pompe
FR2384136A1 (fr) * 1977-03-19 1978-10-13 Streicher Foerdertech Pompe a plateaux d'excentriques
DE2715576A1 (de) * 1977-04-07 1978-10-12 Streicher Foerdertech Exzenterschneckenpumpe

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1382853A1 (de) * 2002-07-17 2004-01-21 Adeleth Investments Inc. Rotierende Schraubenmaschine und Methode zur Umwandlung einer Bewegung in einer solchen Maschine
WO2004007967A1 (en) * 2002-07-17 2004-01-22 Elthom Enterprises Limited Volume screw machine of rotary type
WO2004007963A1 (en) * 2002-07-17 2004-01-22 Elthom Enterprises Limited Volume screw machine of rotary type
WO2004007964A1 (en) * 2002-07-17 2004-01-22 Elthom Enterprises Limited Rotary screw machine and method of transforming a motion in such a machine
US7553138B2 (en) 2002-07-17 2009-06-30 Elthom Enterprises Limited Rotary screw machine of volume type and method of transforming a motion in a volume screw machine
WO2005005838A1 (en) * 2003-07-14 2005-01-20 Elthom Enterprises Limited Rotary screw compressor with multiple stages

Also Published As

Publication number Publication date
FR2506861B1 (de) 1984-06-15
JPS5813101A (ja) 1983-01-25
FR2506861A1 (fr) 1982-12-03

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