EP1016785A1 - Dispositif d'equilibrage excentrique des rotors a ailettes coulissantes et son utilisation - Google Patents

Dispositif d'equilibrage excentrique des rotors a ailettes coulissantes et son utilisation Download PDF

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Publication number
EP1016785A1
EP1016785A1 EP98922579A EP98922579A EP1016785A1 EP 1016785 A1 EP1016785 A1 EP 1016785A1 EP 98922579 A EP98922579 A EP 98922579A EP 98922579 A EP98922579 A EP 98922579A EP 1016785 A1 EP1016785 A1 EP 1016785A1
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Prior art keywords
sliding vane
sliding
equilibrium
eccentric
rotor
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EP98922579A
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German (de)
English (en)
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EP1016785A4 (fr
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Junyan Song
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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
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
    • F01C1/344—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F01C1/3441—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F01C1/3442—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • F01C11/004—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle and of complementary function, e.g. internal combustion engine with supercharger
    • 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
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/02—Radially-movable sealings for working fluids

Definitions

  • This invention relates to an eccentric sliding vane equilibrium rotor device, and in particular it relates to an eccentric sliding vane equilibrium rotor device such as a fluid displacement compressor, pump, blower, and motor, as well as its applications.
  • eccentric sliding vane rotors used in pumps, compressors, and pneumatic and hydraulic motors use divided-type sliding vanes, and when the rotors are rotating, the movement of the tips of the sliding vanes pressed against the cylinder wall produces very great friction and the sliding vanes are easily worn down. This increases waste and shortens the life of the motor.
  • Eccentric sliding vane rotor machines once attracted long-term attention in the engineering field and produced many different kinds of improved schemes. In some low-lift oil pumps for aircraft, integrally crossed sliding vanes were used, the contour of the inner wall is formed by splicing together several sections of arcs, and there is some improvement of the stress conditions of the sliding vanes compared with the stress of non-integral sliding vanes.
  • Reciprocating piston machines began from the bellows used in China's metallurgical industry of antiquity, and they have continuously developed in the manufacturing of steam engines and internal combustion engines.
  • the thermal efficiency of steam engines is lower than 22%
  • the thermal efficiency of gasoline engines is about 26-40%
  • the thermal efficiency of diesel engines is about 30-46%, and furthermore, it is most difficult to try to raise the thermal efficiency and relative power.
  • people have explored many kinds of rotating piston engines, among which the most famous is the Wankel rotary engine which uses a cycloid-shaped cylinder.
  • the first aim of the present invention is to design a kind of eccentric sliding vane equilibrium rotor (abbreviated as ESVER) device that can balance the inertial force of the movement between the sliding vanes or between the sliding vanes and the equilibrium units, so as to reduce or eliminate the dynamic pressure of the tips of the sliding vanes on the cylinder wall and of the sliding vanes on the sliding paths, to lower the waste from friction, and to improve the seal environment.
  • ESVER eccentric sliding vane equilibrium rotor
  • the second aim of the present invention is to use the ESVER device in a presently-existing sliding vane cold engine, to improve its major performance indicators, such that it can be competitive with and achieve superiority to other fluid displacement cold engines, and to develop blower-type products and other cold engine products using ESVER, so as to expand the scope of use of sliding vane machines.
  • the third aim of the present invention is to use the ESVER device to develop many kinds of energy-saving fuel engines; that machine should combine the total advantages of traditional fluid displacement machines and traditional impeller machines, that is, it should have the piston engine's correspondingly fixed compression ratio and expansion ratio under different rotation speeds, as well as rotation speed, torque, and power output characteristics when used in an automobile, and it should also have the impeller machine's separation of compression process and expansion process of the working medium, mutually independent combustion chambers, and characteristics such as high relative power and equilibrium; its thermal efficiency should be higher than that of the present traditional heat engines, and it should be an engine with high performance and low emission of pollutants.
  • the ESVER device is realized in the following manner:
  • An eccentric sliding vane equilibrium rotor device including a rotor body placed eccentrically inside a cylinder body, eccentricity e , and a radial sliding path evenly spaced on the rotor, characterized in that: the rotor body has a hollow part, there is at least one pair of equally-weighted members moving perpendicular to each other in the radial sliding path of the rotor body, and at least one of them is an integrally intersected sliding vane; there are central studs or shaft holes on said equally weighted members crossing the centers of mass of said equally-weighted members and running parallel with the axis of the rotor body, and they are connected by a movement restraining unit; and the inertial force of the movement of said equally-weighted members is mutually balanced through said movement restraining unit.
  • the ESVER device of the present invention also can be realized through the following schemes:
  • the central studs or shaft holes of said equally-weighted members are connected by a rigid, flexible or pliable movement restraining unit, said movement restraining unit is a coupling ring, and the coupling ring is fitted outside the central studs of said equally-weighted members, so as to constrain the optimal center distance between the two central studs to e .
  • Said movement restraining unit has a connecting rod protruding in both directions and running parallel to the studs, two protruding studs are located on both sides of the connecting rod body, and their optimal center distance is e .
  • One of said equally-weighted members is an integrally intersected sliding vane, the other is a member causing a balancing action, and they can form a single-sliding vane-type eccentric equilibrium rotor device.
  • Said equally-weighted members both are integrally intersected sliding vanes, and they can form a dual-sliding vane or four-sliding vane or six-sliding vane or multiple-sliding vane-type eccentric equilibrium rotor device.
  • Said integrally intersected sliding vane is constituted by a sliding vane frame and a sliding vane sealing unit or scaling unit assembly;
  • the sliding vane frame includes two sliding vane bodies, a linking cross member between the two sliding vane bodies, and a protruding stud or shaft hole in the center of the linking cross member;
  • the sliding vane frame can be a single component, or it can be an integrated member composed by suitably processing a plurality of components, and the eccentric sliding vane equilibrium rotor device has at least one sliding vane frame;
  • the sliding vane sealing unit or sealing unit assembly includes an elastic element and a linkage unit, a T-shaped sealing unit or wear-resistant spring-type sealing unit sealing the tip of the sliding vane, and a self-expanding-type sealing sheath or self-expanding-type quasi-surface contact sealing sheath sealing the entire sliding vane body.
  • Said rotor body can have a half-hollow part or have a single hollow part or have a plurality of hollow parts.
  • Application of said eccentric sliding vane equilibrium rotor device in all kinds of compressors, pumps, blowers, and motors results in an energy-saving multiple-fuel rotary engine, utilizing an eccentric sliding vane-type equilibrium rotary compressor and an eccentric sliding vane-type equilibrium rotary gas motor being cascaded coaxially, and being connected by a combustion chamber therebetween.
  • Figure 1 is the first preferred embodiment of the present invention; it is a dual-sliding vane ESVER compressor, vacuum pump or gas motor.
  • Figure 1 there is a pair of integrally intersected and mutually perpendicular equally-weighted sliding vanes placed in the sliding path of the rotor body, sliding vane S1 situated in the vertical position and sliding vane S2 situated in the horizontal position (composed of two units S2' and S2'' spliced together).
  • the rotor body is a two-unit spliced type, and there is a cavity in the center.
  • sliding vane S2 (S2' and S2'') resembles two narrow letters "I" (in Figure 1-A, only the cross section of the linking cross member can be seen), the widths of its sliding vane body and linking cross member being only half those of the vertical sliding vane, and the sum of the weights of the two horizontal sliding vanes being comparable to that of the vertical sliding vane.
  • the two horizontal sliding vanes are spliced together, the central part forms a rectangular hole, and each has a central stud a2' and a2'' extending inward, running parallel with the axis of the rotor body and following the central axis of the sliding vanes. Since sliding vanes S1 and S2 are centrally axi-symmetric components with even weight distribution, their centers of mass are necessarily on the point of intersection of each central axis and the central horizontal sectional plane of the cylinder body.
  • the central horizontal sectional plane of the cylinder body also is the plane of motion of the centers of mass of the sliding vanes.
  • the above-mentioned rotor with sliding vanes and coupling ring is eccentrically installed into an approximately isochordal curve-shaped cylinder body, and the eccentricity is e .
  • a sealing arc is processed out at the location of contact of the rotor with the cylinder body; a seal slot is processed out at the top part of the sliding vane, and a graphite or polytetrafluoroethylene seal F is inserted so as to be capable of sliding freely following the radial direction.
  • the entire rotor also can rotate freely from the front and back cylinder heads and bearing support.
  • Figure 2 shows a comparison of pressure distribution of the sliding vanes on the cylinder wall in the present technology and an ESVER device; the traditional divided-type sliding vanes all have dynamic pressure on the entire cylinder wall (Figure 2-A), the traditional intersected-type sliding vanes partially have dynamic pressure on the lower half of the cylinder wall ( Figure 2-B), and when the sliding vanes in the ESVER device do not have a seal installed, the tips of the sliding vanes very rarely contact the cylinder wall, and the cylinder wall does not receive dynamic pressure (Figure 2-C).
  • Figure 3 is a planar isochordal curve and its characteristics; four ends of a pair of sliding vanes in the above-mentioned rotor during planetary rotational movement created the basic form of the cylinder body of the ESVER machine -- the planar isochordal curve; it can be seen that the isochordal curve is a kind of cycloid.
  • Figure 3-B shows a family of planar isochordal curves when A changes from 2 to 8.
  • B and e generally are constants, and ⁇ is the angle variable, among which:
  • Figure 4 is a concept drawing of an integrally intersected sliding vane in an ESVER machine; an integrally intersected sliding vane in an ESVER machine is mainly constituted by a sliding vane frame and a sealing unit.
  • the sliding vane frame the main part of a sliding vane having a central stub or shaft hole used in an ESVER is called the sliding vane frame.
  • the sliding vane frame assumes the shape of the letter "I", the entirety is composed of three parts, being a central stud a , a linking cross member b , and two sliding vane bodies v and v '; four units can be used, two units per group spliced relatively as in Figure 4-B, to constitute the pair of mutually perpendicular ESVER sliding vanes used in Figure 7 and Figure 8.
  • the sliding vane frame receives cyclic loading, fatigue-resistant, robust materials and skilful manufacturing should be adopted, and the central studs and inside of the sliding vane body should be wear-resistant; to make the inertial moments of the sliding vane frame on the O-O axis and the M-N axis both zero, they must have the optimal mass distribution and equilibrium effect, otherwise a linkage unit should be installed between each group of sliding vanes to make them become an integrated whole, a seal slot is opened at the tip of the sliding vane body, and a seal F made of wear-resistant material is installed therein; a seal slot can also be opened on the end face of the sliding vane body, and an end face seal or angle piece can be fitted (all kinds of sealing schemes of Wankel rotary engines can serve as reference).
  • a rippled spring can be installed in the seal slot in order to reinforce the sealing effect of the seal when at low rotational speed.
  • Figure 5 is seven different kinds of ESVER sliding vanes and sealing schemes.
  • Figure 5-A is a sliding vane without a sealing ring; the sliding vane is constituted only by a sliding vane frame, and it can be used in fluid pump-type machines; since leaks are easily produced and it requires comparatively high processing precision, it is generally not recommended.
  • Figure 5-B is a simple seal ribbon scheme; a seal slot is processed out on the tip of the sliding vane body, a ribbon-shaped seal called a seal ribbon is inserted therein, the seal ribbon can expand and contract radially following the sliding vane so as to compensate for gaps and wear.
  • Advantages simple, easy to manufacture, suitable for all kinds of compressors, pumps, blowers, and motors; Figure 1 uses this scheme.
  • Figure 5-C is a T-shaped sealing unit scheme; a T-shaped slot is processed out on the tip of the sliding vane and a T-shaped sealing unit is inserted therein, the sealing unit can slide radially, but its wear compensation is a limited value.
  • An approximately isochordal curve-shaped cylinder body is selected to match, the machine is subjected to a period of breaking-in operation, the seal gap tends toward a stable value, and the sealing unit and the inner wall of the cylinder wall come into quasi-contact condition. It is suitable for sealing a high-rotational speed ESVER machine of large dimensions.
  • Figure 5-D is a wear-resistant spring-type sealing unit scheme; a spring of composite material is fixed to the tip of the sliding vane body, an approximately isochordal curve-shaped cylinder body is selected for best match, and the inner wall of the cylinder body is spray-coated with polytetrafluoroethylene.
  • Figs. 5-E, F, G, and H are self-expanding sealed sliding vanes, and they are recommended schemes for experimental engines. Their common features are: the main sliding face of the sliding vane is constituted by a single sliding vane-sheathing sealing unit, a part with expanding angle in the form of a "jaw” has flexibility, under pressure the two outer surfaces of the "jaw” can return to a parallel state and it can be inserted into the sliding path of the rotor body, and a sufficient gap is left between the sealing sheath and the sliding vane body so as to prevent gripping during thermal expansion of the components.
  • Sealing of the two side faces of the sliding vane and compensation for wear are ensured by flexibility and self-expanding property of the sliding vane-sheathing sealing unit, and a flexible element can be installed inside the sliding vane body so as to increase the pressure of the tip of the sliding vane sheath on the cylinder wall; the sliding vane sheath can expand and contract radially, and it can form a seal between the tip of the sliding vane and the cylinder wall and compensate for wear.
  • Figure 5-E is a simple self-expanding-type sealing sheath scheme; it can be used on the earliest experimental machine so as to observe the sealing effect and wear conditions, a wedge-shaped angular piece sealing sheath can also be matched so as to reinforce the seal of the end face of the sliding vane.
  • Figure 5-F is a masthead-shaped self-expanding sealing sheath scheme;- the angle at the top surface of the sealing unit is changed to a pin roller, the sliding friction is changed to rolling friction, and a fixed wear-resistant unit of hard alloy or corundum can also be installed on the top.
  • Figs, 5-G and H are self-expanding quasi-surface contact sealing sheath schemes; a wear-resistant pin that can rotate at a specific angle is installed on the tip of the sealing sheath, the linear contact of the sealing unit is changed to approximately columnar surface to columnar surface contact, or it is called quasi-surface contact sealing, and such is convenient for forming oil film lubrication and is useful for reducing or avoiding the formation of cracks on the cylinder wall.
  • Figure 5-G shows the radial axis of the sliding vane and the symmetric axis of the cylinder body positioned overlapping as in Figure 13-B, and at this time the pressure between the sliding vane and the cylinder wall is about zero degrees
  • Figure 5-H shows when the radial axis of the sliding vane and the symmetric axis of the cylinder body are positioned perpendicularly as in Figure 13-A, and at this time the pressure between the sliding vane and the cylinder wall has about reached the maximum value.
  • Figure 6 is a typical ESVER hollow rotor body and sliding vane placement scheme; the sliding vanes in the drawing are all simplified to the forms in Figure 5-A, and the sealing units and coupling rings are omitted and are not drawn; different hollow rotor bodies and sliding vanes can have different kinds of combinations, but here only typical examples are presented,
  • FIG. 6-A is a half-hollow rotor body, sliding vane and coupling ring placement scheme; the drawing shows a half-hollow ESVER device consisting of one half-hollow rotor body, two sliding vanes, and one coupling ring (abbreviated as 2S1R); in the drawing, S1 and S2 respectively are identical equally-weighted vertical and horizontal sliding vanes, a coupling ring R is installed around the outside of the central stud a of the two sliding vanes, and it is required that the inertial moments of the sliding vanes on the O-O axis and M-N axis both be zero in order to be able to ensure good equilibrium of the whole rotor; one consisting of two bearing supports has a half-hollow rotor body with a cross-shaped sliding groove and a half axle, the sliding vanes and coupling ring assembly can be conveniently installed into the half-hollow rotor body from the right side; that structure is simple, and it is suitable for compact-type cold engine products such as
  • Figure 6-B is two spliced-type hollow rotor body ESVER devices one with a single sliding vane and one with dual sliding vanes; it is the most typical ESVER device, and there are many kinds of sliding vane and coupling ring placement schemes; for example two-vane two-ring type, abbreviated as 2S2R, as in Figure 1, Figure 7, and Figure 8; one-vane two-ring type -- IS2R, as in Figure 10 and Figure 13.
  • 2S2R two-vane two-ring type
  • Figure 6-C is a four-sliding vane-type ESVER device; in the drawing, there are two kinds of sliding vanes, two vanes of each kind, two vanes vertically as one pair, the four sliding vanes in the rotor body are evenly spaced at a mutual angle of 45°, and thus is constituted one four-vane two-ring ESVER device, abbreviated as 4S2R; it is required that the inertial moments of the sliding vanes on the O-O axis and M-N axis both be zero in order to be able to ensure good equilibrium of the whole rotor.
  • 4S2R four-vane two-ring ESVER device
  • Fig 6-D is a six vane three ring-type ESVER device; the spliced sliding vanes situated on the two sides in the four vane three ring-type rotor in Figure 9 are respectively made independent, their sliding vane bodies are extended to equal width with the rotor body, the six sliding vanes are evenly spaced, each vane is at a mutual angle of 30°, and thus is constituted a six vane three ring-type ESVER device as in Figure 6-D.
  • Figure 7 is the second embodiment of the present invention, being a dual-sliding vane ESVER blower and large-scale pneumatic motor; in this, for one pair of integrally intersected sliding vanes, four identical sliding vanes relatively spliced together to become as in Figure 4-B are used, and between them are used two coupling rings, mutually balanced.
  • Sliding vanes of the types in Figs. 5-B, C, and D can be used to manufacture a blower. That structure also can be used in the manufacture of a dual-sliding vane ESVER steam or gas motor, only the working medium is changed to pressurized steam or combustion gas.
  • cylinder body In order to reduce the corrosive action of high-temperature water vapor and reduce waste from friction, all components such as cylinder body, cylinder cap, rotor body, sliding vane groove, and sliding vane set should be spray coated with polytetrafluoroethylene, and if the temperature of the combustion gas is too high, the cylinder body should be water cooled.
  • This structure can be cascaded in multiple stages to manufacture a high-pressure compressor, or to serve as an intermediate experimental machine for a multistage ESVER high-pressure steam motor; it can also be independently used in a blast furnace blower or a drive motor for blast furnace coal gas overpressure power generation or low-heat steam power generation.
  • Figure 8 is the third embodiment of the present invention, being a dual-sliding vane ESVER fluid pump and hydraulic motor; the structure is the same as in Figure 7, and since the fluid cannot be compressed, the inlet and outlet should be modified; the sliding vanes in Figs. 5-A, B, and C can be used during manufacturing.
  • a four-vane machine scheme can be used or an accumulator can be placed in the channel; that scheme is suitable for use in cases of special applications such as thick oil pumps, gas-fluid two-phase pumps for mixed transfer of petroleum and natural gas, and water-oil two-phase pumps.
  • the whole cylinder body, cylinder cap, rotor body, sliding vane groove, and sliding vane set should be spray coated with polytetrafluoroethylene or they should be manufactured using corrosion-resistant materials.
  • Figure 9 is a concept drawing of the fourth embodiment, being a four-sliding vane three-ring-type gas compressor; two groups of mutually perpendicular integrally intersected sliding vanes are placed evenly spaced in the rotor body, it is required that the weight distribution of equally-weighted sliding vanes S3 and S4 placed at 45° angles in the drawing can ensure that the center of mass is situated at the point of intersection of the central shaft and the central horizontal sectional plain of the cylinder body, and the inertial force of the two sliding vanes can be balanced using one coupling ring R1 between them; sliding vanes S1 and S2 are mutually balanced through coupling rings R2 and R3; four-vane machines have many kinds of structural schemes, and because the cylinder body is divided into eight chambers, it is useful in increasing the compression ratio and reducing redundant compression.
  • Figure 10 is the fifth embodiment, being a single-sliding vane ESVER gas motor (when backward-rotating, it is a compressor); there is only one sliding vane in the rotor, another sliding vane is converted into an equally-weighted guide pillar, and the two top surfaces of the guide pillar no longer extend from the round columnar surface of the rotor body, by this the length of the sealing line is reduced, and it can have comparatively greater compression ratio or expansion ratio; when used as a compressor, a cheek valve generally must be placed at the gas outlet, or an exhaust groove is opened on the round columnar surface of the rotor, and when arriving at the predefined compression ratio, the gas inside the compression chamber is jointly exhausted through the exhaust groove and the gas outlet; at other rotational angles, the gas outlet is closed by the round columnar surface of the rotor.
  • the length of the gas intake groove opened on the round columnar surface of the rotor body or the corresponding rotational angle determines the gas expansion ratio.
  • This scheme can independently manufacture products, but the main purpose is to serve as an intermediate experimental version of an ESVER engine.
  • Figure 11 is a stereo view of the sixth embodiment, being a dual-sliding vane ESVER with restraining unit as connecting rod; the drawing shows that there is a shaft hole in the central position of sliding vanes S1 and S2, the central shaft movement restraining unit is a connecting rod L protruding in both directions and running parallel with the studs, and the optimal center distance of the two studs is equal to e .
  • the two shaft journals of the connecting rod respectively should be able to be fitted with the central shaft hole and be able to rotate freely, and the inertial force of the movement of the two sliding vanes can be mutually balanced through this connecting rod. That scheme is suitable for use in mass-produced products in which the central shaft hole of the sliding vanes can be directly pressure cast.
  • Figure 12 is a concept drawing of the seventh embodiment, being a multistage expansion ESVER steam motor; high-temperature high-pressure steam supplied from furnace Q first enters the first stage in the center, after the action of expansion it enters steam superheater H to raise the temperature, furthermore it continues to expand up to the last stage outside, and the discharged spent steam and water are recirculated back to the furnace and are converted into high-temperature high-pressure steam for reuse.
  • the main structural characteristics of that machine are: a plurality of ESVER pneumatic motors placed coaxially becomes in a symmetrical placement, the high-pressure cylinder has a small bore and is situated in the center, the cylinder bores at each stage extending in both directions are gradually increased, the low-pressure cylinder has the greatest bore and is situated at the outermost side of the two sides, adjacent cylinder bodies are placed respectively apart at 180°, the gas inlets and outlets between each stage are placed staggered and symmetrically, and as long as the diameter and length of the rotor are suitably designed, the radial gas pressure acting on the main shaft bearing of the rotor can be reduced or eliminated.
  • the radial pressure of the gas on the rotor in the high-pressure stage of that machine can achieve comparatively better equilibrium, and since comparatively better thermodynamic periodic duty can be selected, operation at low speed also can have comparatively better thermal efficiency.
  • the use of coal gas and nuclear energy as alternate energy supplies to drive large-scale ships could be a condition for development and manufacturing of large-scale multistage ESVER steam engines. Reverse operation of that scheme can be used in manufacturing high-pressure compressors.
  • Figure 13 is a concept drawing of the eighth embodiment; it uses an ESVER device to develop an energy-saving multiple-fuel rotary engine; the structural principles and embodiments of the ESVERs previously described were mainly preparations made for developing ESEVER engines. Many kinds of engines can be formed by using the afore-described ESVER gas compressor and ESVER gas motor cascaded coaxially and connecting a combustion chamber therebetween.
  • Figure 13 is an engine designed using a single-sliding vane ESVER device;
  • Figure 13-A is a horizontal sectional view of a single-sliding vane gas motor,
  • Figure 13-B is a horizontal sectional view of a single-sliding vane compressor, and
  • Figure 13-C is a vertical sectional view of the whole machine.
  • a fuel injection nozzle 2 is provided on the left end of the combustion chamber, and it can inject many kinds of fuel, and there are two spark plugs 1 above the combustion chamber.
  • the capacity of the combustion chamber, speaking of the compressor, has a compression ratio of 8, and speaking of the gas motor, its expansion ratio is 11.2 (8 x 1.4).
  • On the lower right side of the combustion chamber there is provided a gas inlet channel 5 connected with the compressor, and on the lower left side of the combustion chamber, there is provided a gas outlet channel 4 connected with the gas motor.
  • a gas inlet port is provided on the lower right side of the compressor; on the round columnar surface of the compressor rotor, there are opened two gas inlet grooves following in the clockwise direction starting from the two sides of the sliding vane and continuing for about a 75° rotational angle; a gas outlet port is provided on the upper left of the gas motor; on the round columnar surface of the gas motor rotor, there are opened two gas outlet grooves following in the counter-clockwise direction starting from the two sides of the sliding vane and continuing for about a 105° rotational angle.
  • Figure 14 is an elementary concept diagram of the operation of the ESVER engine; (A-A) and (B-B) in the drawing correspond respectively to the A-A and B-B sectional views in Figure 13, and they respectively represent the gas motor and gas compressor components. Above them, there is drawn an enlarged combustion chamber, and they are connected with the compressor and the gas motor using gas inlet and outlet channels beneath both the left and right ends thereof. A fuel injection nozzle is drawn on the left end of the combustion chamber and there are two spark plugs at the top.
  • the rotor in Figure 14 is simplified as rotor bodies having gas inlet and outlet grooves opened thereon and flat sliding vanes that can move freely, and the other structures are not drawn.
  • the combustion gas inside the combustion chamber which is not yet exhausted and has a pressure of 0.25-0.35MPa is squeezed through the gas outlet channel into the expansion chamber of the gas motor, and the rotational angle of the simultaneously open gas inlet channel connecting the combustion chamber with the compressor and gas outlet channel connecting with the gas motor is as large as about 10° (this angle still requires experimental optimization), and it is called the combustion chamber scavenging iteration angle.
  • the squeezed out gas freely expands and works inside the chamber at the lower right of the gas motor as in Figure 14-C.
  • the gas outlet channel of the combustion chamber being connected to the gas engine is closed by the round columnar surface of the rotor and is kept at about a, 75° rotational angle.
  • the gas inside the compressor is continuously pressed into the combustion chamber, and the sealed adiabatic compression process is gradually completed.
  • the fuel injection nozzle injects fuel (fuel injection can be earlier, and the optimal early angle of fuel injection requires experimental confirmation), and the spark plugs spark as in Figure 14-D; during the period when the sparks ignite and burn, the temperature and pressure inside the combustion chamber are raised under nearly isovolumetric conditions.
  • the first ESVER experimental compressor uses steel sliding vanes and a double coupling ring, it was test operated at three rotational speeds of 825, 1460, and 260Orpm, and the amounts of emissions were respectively 2.2, 4, and 7m 3 /min; during testing, the ESVER operated stably and freely, there were no marks from contact friction on the tips of the sliding vane frames and the inner wall of the gas cylinder, there was low vibration and low waste, and this demonstrates good potential for raising the speed and capacity of the rotors and potential for increasing the external dimensions of the machine body; the rotational speed can be changed using the same components such as cylinder body and rotor to develop a series of products.
  • the second ESVER experimental compressor also uses steel sliding vanes; the amount of emissions was 11.5m 3 /min when at 1470rpm, and the amount of emissions was 22m 3 /min when at 2920rpm.
  • Specimens such as a compact-type experimental compressor, vacuum pump, and fuel-less compressor, a medium-sized compressor having 3Om 3 /min emissions and 0.8MPa pressure, a blower having about 150-300m 3 /min emissions, as well as an oil transfer pump and gas-liquid two-phase pump are presently under test development.
  • an ESVER device is a kind of eccentric equilibrium rotating piston, it has the major characteristics of a fluid displacement machine; it is also similar to a completely balanced eccentric turbine (the blades can expand and contract), and at the same time it has a few of the major characteristics of turbine machines, therefore it can be suitable for developing many kinds of commonly used mechanical products similar to the two types described above.
  • the ESVER device Since its structure is simple and the manufacturability is comparatively better, the ESVER device will first be used in all kinds of products such as compressors, pumps, blowers, and pneumatic motors (including large-scale gas motors using blast furnace coal gas overpressure power generation), furthermore it may gradually promote expansion of the scope of application, and through continuous improvements of structures, materials, and manufacturing techniques, its rotational speed and external dimensions may be gradually increased, and the ESVER may be used in such fields as ships and power stations to flying machines, and it also may form a new type of mechanical system between traditional piston machines and traditional turbine machines.
  • products such as compressors, pumps, blowers, and pneumatic motors (including large-scale gas motors using blast furnace coal gas overpressure power generation)
  • the ESVER may be used in such fields as ships and power stations to flying machines, and it also may form a new type of mechanical system between traditional piston machines and traditional turbine machines.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP98922579A 1997-05-23 1998-05-25 Dispositif d'equilibrage excentrique des rotors a ailettes coulissantes et son utilisation Withdrawn EP1016785A4 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CN9700051 1997-05-23
WOPCT/CN97/00051 1997-05-23
PCT/CN1998/000078 WO1998053210A1 (fr) 1997-05-23 1998-05-25 Dispositif d'equilibrage excentrique des rotors a ailettes coulissantes et son utilisation

Publications (2)

Publication Number Publication Date
EP1016785A1 true EP1016785A1 (fr) 2000-07-05
EP1016785A4 EP1016785A4 (fr) 2002-01-09

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Country Link
EP (1) EP1016785A4 (fr)
CN (1) CN1074816C (fr)
AU (1) AU7519198A (fr)
WO (1) WO1998053210A1 (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20020081838A (ko) * 2001-04-20 2002-10-30 한상국 베인 회전체를 이용한 엔진
WO2004022919A1 (fr) * 2002-09-09 2004-03-18 Ibrahim Sinan Akmandor Moteur rotatif a palettes et cycle thermodynamique associe
WO2006127535A1 (fr) * 2005-05-20 2006-11-30 Gilbert Staffend, Inc. Moteur a combustion a aube rotative
WO2007049226A1 (fr) * 2005-10-24 2007-05-03 Botha Stephanus Christoffel He Moteur à palettes rotatives pour combustion externe
DE102008058891A1 (de) 2008-04-03 2009-12-17 Eduard Demmelmaier Rotationskolbenmaschine mit mehreren axial hintereinander angeordneten Arbeitsbereichen
FR2944829A1 (fr) * 2009-04-28 2010-10-29 Vache Conseils Et Participatio Moteur rotatif a explosion equipe de pales coulissantes
US9881706B2 (en) 2013-08-23 2018-01-30 Global Energy Research Associates, LLC Nuclear powered rotary internal engine apparatus
US9947423B2 (en) 2013-08-23 2018-04-17 Global Energy Research Associates, LLC Nanofuel internal engine
US11450442B2 (en) 2013-08-23 2022-09-20 Global Energy Research Associates, LLC Internal-external hybrid microreactor in a compact configuration
US11557404B2 (en) 2013-08-23 2023-01-17 Global Energy Research Associates, LLC Method of using nanofuel in a nanofuel internal engine

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CN102345604A (zh) * 2011-07-30 2012-02-08 浙江鸿友压缩机制造有限公司 叶片式平动转子压缩机
CN104033329B (zh) * 2013-03-06 2017-04-19 宁波高新协力机电液有限公司 径向滚柱高速变量油马达
CN103133066A (zh) * 2013-03-21 2013-06-05 高天祥 偏置转子式蒸汽轮机
TWI499750B (zh) * 2014-06-10 2015-09-11 Round Shine Industrail Co Ltd 多滑片式壓縮機以及分段式壓縮方法
CN106151033A (zh) * 2015-04-17 2016-11-23 雷衍章 一种滚动摩擦的滑片式压缩机或膨胀机
CN109931182B (zh) * 2019-04-25 2024-02-20 西安航空学院 偏心滑片式燃气轮机

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH137829A (de) * 1927-05-07 1930-01-31 Zoller Arnold Exzenter-Drehkolben-Verdichter und Verfahren zur Herstellung desselben.
FR710884A (fr) * 1931-01-29 1931-08-31 Moteur rotatif à palette radiale
US1994245A (en) * 1931-09-03 1935-03-12 Jr John O Gette Compressor and supercharger
US2314056A (en) * 1939-02-22 1943-03-16 Sobek Andre Rotary vane vacuum pump or compressor
DE851879C (de) * 1951-03-02 1952-10-09 Juergen Clausen Kolben fuer Drehkolbenmaschinen
DE1007468B (de) * 1953-02-26 1957-05-02 Rene Martial Georges Delafonta Drehkolbenmaschine mit sichelfoermigem Arbeitsraum
US3858559A (en) * 1970-12-04 1975-01-07 Jr Albert Raymond Thomas Coupled vane rotary fluid device
US3989011A (en) * 1974-01-25 1976-11-02 Minoru Takahashi Constant pressure heating vane rotary engine
JPS59203890A (ja) * 1983-05-02 1984-11-19 Yoichi Mori ベ−ンポンプモ−タ−
US5560741A (en) * 1994-06-28 1996-10-01 Edwards; Thomas C. Non-contact vane-type fluid displacement machine with rotor and vane positioning

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4410305A (en) * 1981-06-08 1983-10-18 Rovac Corporation Vane type compressor having elliptical stator with doubly-offset rotor
DE3504547A1 (de) * 1985-02-11 1986-09-11 Armatec FTS-Armaturen GmbH & Co KG, 7988 Wangen Rotationsverdichter mit festverbundenen schieberhaelften
US4958995A (en) * 1986-07-22 1990-09-25 Eagle Industry Co., Ltd. Vane pump with annular recesses to control vane extension
US4929159A (en) * 1987-10-16 1990-05-29 Hitachi, Ltd. Variable-displacement rotary compressor
CN1130240A (zh) * 1995-02-28 1996-09-04 李天宝 容积式泵或压缩机的滑片

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH137829A (de) * 1927-05-07 1930-01-31 Zoller Arnold Exzenter-Drehkolben-Verdichter und Verfahren zur Herstellung desselben.
FR710884A (fr) * 1931-01-29 1931-08-31 Moteur rotatif à palette radiale
US1994245A (en) * 1931-09-03 1935-03-12 Jr John O Gette Compressor and supercharger
US2314056A (en) * 1939-02-22 1943-03-16 Sobek Andre Rotary vane vacuum pump or compressor
DE851879C (de) * 1951-03-02 1952-10-09 Juergen Clausen Kolben fuer Drehkolbenmaschinen
DE1007468B (de) * 1953-02-26 1957-05-02 Rene Martial Georges Delafonta Drehkolbenmaschine mit sichelfoermigem Arbeitsraum
US3858559A (en) * 1970-12-04 1975-01-07 Jr Albert Raymond Thomas Coupled vane rotary fluid device
US3989011A (en) * 1974-01-25 1976-11-02 Minoru Takahashi Constant pressure heating vane rotary engine
JPS59203890A (ja) * 1983-05-02 1984-11-19 Yoichi Mori ベ−ンポンプモ−タ−
US5560741A (en) * 1994-06-28 1996-10-01 Edwards; Thomas C. Non-contact vane-type fluid displacement machine with rotor and vane positioning

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 009, no. 073 (M-368), 3 April 1985 (1985-04-03) & JP 59 203890 A (YOUICHI MOURI), 19 November 1984 (1984-11-19) *
See also references of WO9853210A1 *

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20020081838A (ko) * 2001-04-20 2002-10-30 한상국 베인 회전체를 이용한 엔진
EP2088285A3 (fr) * 2002-09-09 2012-08-01 Ibrahim Sinan Akmandor Moteur de propulsion modulaire
WO2004022919A1 (fr) * 2002-09-09 2004-03-18 Ibrahim Sinan Akmandor Moteur rotatif a palettes et cycle thermodynamique associe
US7314035B2 (en) 2002-09-09 2008-01-01 Ibrahim Sinan Akmandor Rotary vane engine and thermodynamic cycle
EP2088285A2 (fr) 2002-09-09 2009-08-12 Ibrahim Sinan Akmandor Moteur de propulsion modulaire
US7556015B2 (en) 2004-05-20 2009-07-07 Staffend Gilbert S Rotary device for use in an engine
WO2006127535A1 (fr) * 2005-05-20 2006-11-30 Gilbert Staffend, Inc. Moteur a combustion a aube rotative
WO2007049226A1 (fr) * 2005-10-24 2007-05-03 Botha Stephanus Christoffel He Moteur à palettes rotatives pour combustion externe
DE102008058891B4 (de) * 2008-04-03 2010-06-24 Eduard Demmelmaier Rotationskolbenmaschine mit mehreren axial hintereinander angeordneten Arbeitsbereichen
DE102008058891A1 (de) 2008-04-03 2009-12-17 Eduard Demmelmaier Rotationskolbenmaschine mit mehreren axial hintereinander angeordneten Arbeitsbereichen
FR2944829A1 (fr) * 2009-04-28 2010-10-29 Vache Conseils Et Participatio Moteur rotatif a explosion equipe de pales coulissantes
US9881706B2 (en) 2013-08-23 2018-01-30 Global Energy Research Associates, LLC Nuclear powered rotary internal engine apparatus
US9947423B2 (en) 2013-08-23 2018-04-17 Global Energy Research Associates, LLC Nanofuel internal engine
US11450442B2 (en) 2013-08-23 2022-09-20 Global Energy Research Associates, LLC Internal-external hybrid microreactor in a compact configuration
US11557404B2 (en) 2013-08-23 2023-01-17 Global Energy Research Associates, LLC Method of using nanofuel in a nanofuel internal engine

Also Published As

Publication number Publication date
CN1255186A (zh) 2000-05-31
WO1998053210A1 (fr) 1998-11-26
CN1074816C (zh) 2001-11-14
AU7519198A (en) 1998-12-11
EP1016785A4 (fr) 2002-01-09

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