Rotary Working Machine Provided with an Assembly of Working Chambers and Periodically Variable Volume, In Particular a Compressor

Abstract

A rotary working machine is provided. The machine includes an assembly of working chambers with periodically variable volume disposed in a central block defining a stator. The inside surfaces of the stator direct a pendulum motion of one or more blade-type working elements disposed in respective one or more cylindrical sockets of a cylindrical rotator that is disposed within an interior of the camshaft form stator. The rotator is connected to an external prime mover for providing torque thereto. An angle of contact between a front cylindrical surface of the blade-type working elements and the internal curved space of the camshaft form stator defines a working chamber of variable volume, the working chamber of variable volume is connected during rotator revolution correspondingly with an inside pipe of a camshaft and an annular slot that is configured to evacuate compressed gas disposed within the working chamber of variable volume. The outline of a cross-sectional of opening of the camshaft form stator disposed in a vertical plane to with respect to an axis of the cylindrical rotator constitutes the equidistant line to a curve that is described on an immobile plane perpendicular to the axis of the cylindrical rotators by a Radziwill curve. A defined relationship exists between the rotation angle of the cylindrical rotator and the deflection angle of an axis of the working element/

Description

RELATED APPLICATIONS

This application is a continuation-in-part of U.S. application Ser. No. 12/326,162, filed on Dec. 2, 2008, which was a continuation of U.S. application Ser. No. 10/592,455, filed on Sep. 7, 2006 and issued as U.S. Pat. No. 7,458,791 on Dec. 2, 2008, which claimed priority from PCT Application No. PCT/PL2005/000014, filed on Mar. 8, 2005, which claimed priority from EPO Application No. 04460001.3, filed on Mar. 9, 2004, the entirety of which are each fully incorporated by reference herein.

BACKGROUND

This disclosure relates to a rotary working machine provided with an assembly of working chambers with periodically variable volume, in particular a compressor.

Since 1908 blade type working machines have been known, employed particularly as a compressor, consisting of a rotor, eccentrically supported inside a stationary block and of a set of blades, slidable in grooves of the rotor. Rotation of the rotor causes the blades moving in and out, which are controlled by an inner surface of the cylindrical block, thus permitting formation of working chambers with periodically variable volume, enabling intake and compression of a medium.

A disadvantage of blade-type working machines is in energy losses due to friction of the rotating blades against walls of the cylindrical block, negatively affecting the efficiency and a durability of such machines, particularly at higher speeds.

Since 1927 Pneumaphore type blade compressors have been known, which work based upon a principle of oil injection into compressed air, permitting a partial reduction of energy losses and a blade wear. This and similar compressor designs have featured blades made of light aluminum and, since 1964, even lighter plastics. Blade compressors of such designs generally exclude, however, high speed uses, being in considerably lower strength of the blades.

U.S. Pat. No. 5,379,736 discloses a combustion engine consisting of an air compressor, a similarly designed exhaust gas decompressor and a combustion chamber positioned between the compressor and the decompressor. The compressor is provided with two rotating cylinders: an outer cylinder and an inner cylinder, respectively, interconnected and fixed on a common driveshaft, eccentric both in relation to the driveshaft's axis and between them. An intermediate unit is positioned between the rotating cylinders and the intermediate unit is provided with blades, swiveling on pivots fitted around an axis of the unit, wherein the blades during rotation of the eccentric cylinders take positions forming, between neighbouring blades and surfaces of the cylinders, chambers with periodically variable volume. A movement of the blades is forced by planetary gears, connecting the driveshaft with the pivots, being axes for the blades' rotation. Furthermore, the intermediate unit is provided with inlet and outlet flanges with valves, controlled by cams fixed on the driveshaft. The blades are rotating in the same direction as the driveshaft, but at half of the driveshafts' angular speed. Such design reduces considerably the expenditure of energy to overcome friction, but a certain amount of energy is consumed to overcome inertia moments of the numerous moving parts of the machine.

German Patent DE 1 551 101 describes a rotary combustion engine, featuring oscillating working elements that are set on pivots in a rotating ring and controlled by specially shaped two- or four-lobe cams, located on both sides of the ring. Working elements have, in a section, a shape of triangles with convex sides, the tops of which slide on surfaces of both cams, forming working chambers with periodically variable volume, causing intake and compression of a medium. During a rotation of the driveshaft, each oscillating working element is pressed by a centrifugal force against an inner surface of one cam, and at the same time tightened in relation to the central cam's outer surface by means of sealing strips, pressed against it.

A disadvantage of such engine, prevailing in other rotary engines, is in considerable frictional energy losses of numerous working elements against surfaces of cams, and in the difficulty of sealing the extremities of working elements in relation to the cams' working surfaces.

Polish Patent PL 109 449 and its German equivalent DE 1526408 disclose a rotary combustion engine, featuring an elliptic cylinder, inside which is moving a system of five pistons, connected by joints to create a closed chain, while between inner concave surfaces of the pistons and the elliptic surface of the cylinder, working chambers with periodically variable volume are formed. Pistons, being approximately triangular in section, are interconnected by sealed setting pins, placed in recesses in neighbouring pistons and provided with sealing strips, pressed against the elliptic surface of the engine's cylinder. A movement of the pistons is controlled by two rotors or discs, formed by joint-connected five segments with axes constituting extensions of axes of setting pins, located on both sides of the engine and transmitting torque to the engine's driveshaft.

A disadvantage of such construction, and other similar designs of working machines, in which kinematically connected working elements form a closed chain, is in a presence of variable moments of inertia, increasing friction losses, and thus reducing efficiency of the machines.

International Patent Application WO00/42290 describes a rotary combustion engine, consisting of an engine block and of a rotor, located inside it and featuring four movable pistons, in the form of double-arm levers that oscillate around axes parallel to a central axis of the block and at the same time revolving together with the rotor. The pistons are provided with thrust rolls, which during movement along a circumference of the engine block, are driven by a system of cams, consisting of an outer cam and an inner cam. Mating of the thrust elements of the pistons with cam surfaces forces, during the common rotation, oscillating of the pistons around semicircular projections on the rotor. The pistons are sealed against each other by means of toothed contact surfaces, while between their working surfaces and an inner cylindrical surface of the engine block are formed chambers with periodically variable volume, enabling intake and compression of a medium.

A disadvantage of such design is in considerable friction forces, generated between the concave surface of pistons and the semicircular projections on the rotor, in connection with important mutual pressures between mating surfaces. Considerable frictional losses arise also on the thrust elements of pistons, driven in a slot between the two cams.

German patent DE 622 554 relates to a working machine with oscillating pistons, swivel fitted in sockets of a rotor's body. The pistons each include, along with a surface of the rotator's body, working chambers with periodically variable volume, which are sickle-shaped. The oscillating pistons are provided with counterweights, swivel on their pivots in the rotating rotor's body, and slide with their sealing edge, which close the working chamber, in an eccentric relationship to the rotor's axis circumference of a stator having circular cross section. Oscillating pistons are provided with counterweights, which position and size are selected in a way enabling the inertia moment of the piston (caused by a centrifugal force) to be substantially equal to a torque caused by an acceleration or deceleration of the oscillating piston.

Balancing of torque, resulting from an acceleration and deceleration of the piston's oscillation, can be done by appropriate adjustment of the oscillatory piston's counterweight only for one, determined rotational speed.

German patent DE 898 697 discloses a working machine that includes with oscillating pistons disposed in sockets on an outer circumference of a cylindrical rotator. The pistons are provided with rolls, which move on an inner cam surface of a stator surrounding the rotator and control an oscillating motion of the pistons. A surface of the rotator along with a surface of the stator form working chambers with periodically variable volume. The oscillating motion of the pistons is limited by stop members, which are mounted on an outer surface of the pistons and guided in grooves, in order to avoid a contact between large surface areas of the pistons and the stator. In another embodiment, oscillating pistons are disposed in cylindrical sockets on an inner outline of an annular rotator surrounding a stator. A cylindrical outer surface of the stator is eccentric in relation to a rotator's axis and forms a guiding surface for sealing edges of the pistons. In both embodiments, the oscillating motion is forced by a centrifugal force resulting from a displacement of a mass centre of the pistons in relation to their oscillating axis, or from a rolls action, or from a special load.

Disadvantages of that working machine arise from a large motion resistance of the rolls, a motion resistance of the pistons in the sockets and a friction between edges of the pistons and the surface of the stator.

BRIEF SUMMARY

It is an object of the invention to provide a rotary working machine, and equipped with a group of working chambers of changeable volume and placed in the block, in which the rotor rotates with pendulum pistons—working elements, seated in cylindrical sockets and sliding during rotation in the internal part of the block constituting a special curve, which ensures significantly less losses caused by friction, and thus correspondingly increase is the efficiency of the action of the machine.

Experimental and computational research has shown that it is possible to considerably limit the energetic losses that result in known rotary machines with oscillating pistons, of forces acting on individual components of these, by such a correlation of kinematic connection system of the oscillating pistons with distribution of their masses, as to reduce, for any rotation speed of the machine, movements of these oscillating pistons to resonance oscillations in the field of centrifugal force. The resonance character of the oscillating pistons' oscillations enables maintaining the motion by solely overcoming a minor resistance of their replacement in relation to the rotor.

The disclosure provides a rotary working machine that is assembled with a block of which the central part is provided with a stator in the form of a camshaft, the internal surface of which constitutes the surface guiding the pendulum motion of the blade type oscillating pistons in cylindrical sockets of the cylindrical rotor placed inside this stator in camshaft form and propelled with the aid of a separate engine, in which the contact edges of these blade type oscillating pistons are guided by the internal surface of the camshaft form of creating, between this surface, and the intake apertures of the controlling cam and possibly the surface of the cradle type oscillating piston, working chambers of changeable volume connected during the rotor rotation to the corresponding insight pipe of the camshaft and annular slot evacuating compressed medium, in which the outline of the cross-section of the camshaft forms a stator vertical plane to the axis of the rotor that constitutes an equally distant line to the curve, as defined by two parametric equations:

X(φ)=l sin φ+r sin(φ+γ+θ(φ)

Y(φ)=l cos φ+r sin(φ+γ+θ(φ))

where:

φ is a rotation angle of the rotator from a position of minimum potential energy, that is from a position, in which points O, O1, S are on a single straight line determining an axis OY, as shown in FIG. 5;

X(φ) denotes an abscissa of a position of a vertex point of each of the oscillating pistons of the working element in a co-ordinate system having a centre in the point O being the cylindrical rotator's axis of rotation, after its rotation through the angle φ;

Y(φ) denotes an ordinate of a position of a vertex point of each of the oscillating pistons of the working element in a co-ordinate system having a centre in the point O being the cylindrical rotator's axis of rotation, after its rotation through the angle φ;

l is a distance OO1 of the working element oscillation axis from the cylindrical rotator's axis of rotation;

r is a distance of the vertex point from the oscillation axis of the working element;

γ is a constant angle formed between the axes O1S and O1C, where S is a mass centre of the working element; and

θ(φ) is an angle by which the axis O1S deflects during the rotator's movement through the angle φ,

wherein a relation between the rotation angle φ of the cylindrical rotator and the deflexion angle θ of the axis O1S of the working element is expressed by an equation:

$\theta \left(\varphi \right)=2\arcsin \left(\sin \frac{{\theta }_0}{2}\sin \Psi \left(\varphi \right)\right)$

where a relation between the angles φ and Ψ is described by tabulated values of elliptic integrals.

Rotary working machine, in particular a compressor according to the invention, is characterized by a compactness of its design, expressed in that a ratio of total change of the working chambers' volume (equivalent of a displacement volume) to a volume of inner outline of the machine's moving part is close to one. Furthermore, an implementation of the compressor has proven that thanks to the elimination of losses to overcome frictional forces and motion resistance that occur in similar conventional machines, it achieves efficiency in an order of 90%. In some embodiments, it is necessary for the ratio of the working element resonance oscillation frequency to the frequency of the rotator's revolutions to remain, at steady state, constant for all speeds of the rotator. In this situation, the machine is relatively highly efficient, independent of the rotator's rotational speed.

Another representative object of the disclosure is provided. The object includes rotary working machine provided with an assembly of working chambers with periodically variable volume, in particular a compressor, placed in block of which the central block 1 in is supplied with a camshaft form stator 4 the inside surface of which constitutes the surface guiding the pendulum motion of the blade-type working elements 10 seated pendulously in cylindrical sockets 22 of the cylindrical rotator 8 placed in the interior of this camshaft form stator 4 and propelled with the aid of a separate engine, in which the angle of contact of these blade-type working elements 10 are conducted through the internal curved space of the camshaft form stator 4 creating, between this surface and the front cylindrical surface 31 and possibly the side cylindrical surface 30 of the blade type working element 10, working chambers of variable volume connected during rotator revolution correspondingly with inside pipe of the camshaft 19 and annular slot 21 evacuating compressed medium, in which the outline of the curved cross-section of opening of the camshaft form stator 4 vertical plane to axis 17 of the cylindrical rotator 8 constitutes the equidistant line to curve K_R which is described on an immobile plane perpendicular to the axis of the cylindrical rotators by two parametric equations:

X(φ)=l sin φ+r sin(φ+γ+θ(φ))

Y(φ)=l cos φ+r sin(φ+γ+θ(φ))

where:

φ is a rotation angle of the rotator from a position of minimum potential energy, that is from a position, in which points O, O₁, S are on a single straight line determining an axis OY in FIG. 4;

X(φ) denotes an abscissa of a position of a vertex point of each of the oscillating pistons of the working element 10 in a co-ordinate system having a centre in the point O being the cylindrical rotator's axis of rotation, after its rotation through the angle φ;

Y(φ) denotes an ordinate of a position of a vertex point of each of the oscillating pistons of the working element 10 in a co-ordinate system having a centre in the point O being the cylindrical rotator's axis of rotation, after its rotation through the angle φ;

l is a distance OO₁ of the working element 10 oscillation axis from the cylindrical rotator's axis of rotation;

r is a distance of the vertex point from the oscillation axis of the working element 10;

γ is a constant angle formed between the axes O₁S and O₁C, where S is a mass centre of the working element 10; and

θ(φ) is an angle by which the axis O₁S deflects during the rotator's movement through the angle φ.

wherein a relation between the rotation angle φ of the cylindrical rotator and the deflexion angle Θ of the axis O₁S of the working element 10 is expressed by an equation:

$\theta \left(\varphi \right)=2\arcsin \left(\sin \frac{{\theta }_0}{2}\sin \Psi \left(\varphi \right)\right)$

where a relation between the angles φ and Θ is described by tabulated values of elliptic integrals, marked on this cross-section plane by the vertex point of the blade-type working element 10, moving with regard to this cylindrical rotator cylinder with the oscillating motion with a resonance frequency during its full rotation at which the moment of inertia the blade-type working element 10 has a value ensuring its resonance frequency of own oscillations with regard to cylindrical rotator 8 and it is expressed by the following equation:

$I_{O_1}={\left[\frac{\pi }{2{\mathrm{vK}}_{\left(\frac{{\theta }_0}{2}\right)}}\right]}^2·l·s·m$

where:

v is a natural number expressing a ratio of frequency of the resonance oscillation of the working element 10 to a frequency of the rotation of the cylindrical rotator, where v=1, 2, 3 . . . ;

l is a distance of the working element 10 oscillation axis from the cylindrical rotator's rotation axis;

s is a distance of a mass centre of the working element 10 from an oscillation axis of the working element 10;

m is a mass of the working element 10;

θ₀ is an angle corresponding to an amplitude of the working element 10 oscillation in relation to the rotator.

A machine according to claim 1, characterized in that, its blade-type working element 10 as the form of an arched wedge narrowing from side surface of side cylindrical surface 30 to the side cylindrical surface 30′ through which joining by front cylindrical surface 31, it constitutes a sector of the cylinder of a radius equal to the radius of the cylindrical rotator 8.

Another representative machine is provided wherein the machine is characterized in that its blade type-working element 10 is seated rotationally on axis 23 mounted in projection 29 of cylindrical sockets 22 on the cylindrical rotator 8 in this manner, that the front cylindrical surface 31 of the blade-type working element 10 is covered by the surface of the cylindrical rotator 8.

Another representative machine is provided wherein the machine is characterized in that its cylindrical rotator 8 is supplied with at least two or more cylindrical sockets 22 of the blade-type working elements 10, the axes of which are parallel to the axis 17 of rotation of the cylindrical rotator 8.

Another representative machine is provided wherein the machine is characterized in that its cylindrical rotator 8 is supplied with four cylindrical sockets 22 of the blade-type working elements 10, the axes of which are parallel to the axis 17 of rotation of the cylindrical rotator 8.

Another representative machine is provided wherein the machine is characterized in that cylindrical sockets 22 are distributed equally on the circumference of the cylindrical rotator 8.

Another representative machine is provided wherein the machine is characterized in that an axis of the inside pipe of the camshaft 19 and annular slot 21 an angle of approx 90 degrees.

Another representative machine is provided wherein the machine is characterized in that an axis of controlling nozzle 33 of oil spray creates with the nearer edge an inlet channel of inside pipe of the camshaft 19 an angle of approx. 90 degrees.

Another representative machine is provided wherein the machine is characterized in that its housing is composed of a central block 1 supplied with a camshaft form stator 4 and tightly connected to it with the aid of a screw 18 the cover block 1a and the flange of the rear block 1b.

Another representative machine is provided wherein the machine is characterized in that an inside pipe of the camshaft 19 and annular slot 21 have the form of openings executed inside parts of the central block 1.

Another representative machine is provided wherein the machine is characterized in that the central block 1 and possible cover block flanges 1a and rear block 1b having the view from the front a shape approaching a square.

BRIEF DESCRIPTION OF THE DRAWINGS

A rotary working machine according to the disclosure, provided with a system of working chambers with periodically variable volume, constituting a compressor, will now further be explained with reference to exemplary embodiments in the accompanying drawings, in which:

FIG. 1 is a side cross-sectional view of a representative compressor equipped with a set of four working chambers, each of which is equipped with a pendulum seated blade type working element.

FIG. 2 is a cross-sectional view about section A-A of FIG. 1,

FIG. 3 is an exploded view of the compressor of FIG. 1.

FIG. 4 is a Radziwill curve K_R constituting the basis of the outline of the curve controlling the compressor opening according to FIG. 2.

FIG. 5 is a perspective exploded view of a cylindrical socket in rotor together with pendulum blade type oscillating piston seated in it.

DETAILED DESCRIPTION OF THE DRAWINGS AND THE PRESENTLY PREFERRED EMBODIMENTS

The rotary compressor presented in FIGS. 1-3 is equipped with three part housing, consisting of central block 1, and cover block 1a and also of rear outside block 1b, also wedged in it on the controlling cam of the cylindrical rotor 8. The block 1 is supplied with camshaft form stator 4, of which the transverse cross-section constitutes the further referred to Radziwill curve K_R (FIG. 4). Furthermore in the block 1 is the inside pipe of the camshaft 19 through which the compressor sucks in the compressed medium and also the annular slot 21 evacuating compressed serving to conduct away compressed medium under high pressure. The block 1 is tightly closed on both sides with the aid of the flange of the cover block 1a and the rear block 1b connected with it with the aid of the screw 18. The cylindrical rotator 8 is wedged on the controlling cam 5, of which the pivots 13, 14 of the working unit are seated in needle type rolling bearings 15 and 16. The cylindrical rotator 8 furthermore is equipped on its internal surface 24 with four cylindrical sockets 22 symmetrically placed in its circumference with seated in them on axes 23 of the oscillating blade type-working elements 10. Blade type working elements 10 are rotationally seated on axes. Axes 23 of working elements 10 are mounted in projections 29 protruding from rotator interior surface cylindrical sockets 22 (FIG. 5).

Blade type working elements 10 have the form of a two armed lever seated rotationally in axis 23. This lever is created by two side cylindrical surfaces 30, 30′ of radius equal or somewhat less than the radius of the internal surface 24 of the cylindrical socket 22. This lever is also created by front cylindrical surface 31 of radius equal to the radius of the cylindrical rotator 8 and rear surface 32 is of the outlet aperture of the controlling cam closing and giving the rotator the form of an arched wedge increasing in the direction of the side cylindrical surface 30 of the working element 10. In intersection of side cylindrical surface 30 and front cylindrical surface 31 of the working element 10 is a set of vertex points C creating the working age of this element cooperating with the surface of camshaft form stator 4, constituting in the cross-section the Radziwill curve K_R. The configuration of each of the blade type working elements 10 especially its form, dimensions and material thickness of which it is a security and the distance of the centre of its axis 23 from the rotation axis 17 of the cylindrical rotator should be so selected in order that the relationship of the frequency of the blade type working element 10 (for the specified chosen amplitude of oscillations) is the frequency of rotary movement of the cylindrical rotator 8 expressed as a natural number e.g.: 1, 2, 3:

This condition is fulfilled, when the moment of inertia I_O1 of the blade type-working element 10 with regard to the axis of oscillation O₁ fulfils the equation:

$I_{O_1}={\left[\frac{\pi }{2{\mathrm{vK}}_{\left(\frac{{\theta }_0}{2}\right)}}\right]}^2·l·s·m$

where:

v is a natural number expressing a ratio of frequency of the resonance oscillation of the working element to a frequency of the rotation of the cylindrical rotator, where v=1, 2, 3 . . . ;

l is a distance of the working element oscillation axis from the cylindrical rotator's rotation axis;

s is a distance of a mass centre of the working element from an oscillation axis of the working element;

m is a mass of the working element; and

θ₀ is an angle corresponding to an amplitude of the working element oscillation in relation to the rotator.

In order to ensure continual contact of a set of the vertex points C of blade type working element 10 (creating the contact edge) with the surface of the camshaft form stator 4 of the block 1 transverse cross section of this opening (vertically to axis 17 of the cylindrical rotator 8) must constitute the geometric place of points forming the closed track of movement, which marks on the immobile plane of the vertex point C cross section of the blade type working element 10 moving with pendulum motion with the movement resonance frequency of the blade type working element 10 during the time of complete rotation of the cylindrical rotator 8. The geometrical place is the Radziwill curve K_R o defined in the system of two parametrical equations:

X(φ)=l sin φ+r sin(φ+γ+θ(φ))

Y(φ)=l cos φ+r sin(φ+γ+θ(φ))

where:

φ is a rotation angle of the rotator from a position of minimum potential energy, that is from a position, in which points O, O₁, S are on a single straight line determining an axis OY in FIG. 5;

X(φ) denotes an abscissa of a position of a vertex point of each of the oscillating pistons of the working element in a co-ordinate system having a centre in the point O being the cylindrical rotator's axis of rotation, after its rotation through the angle φ;

Y(φ) denotes an ordinate of a position of a vertex point of each of the oscillating pistons of the working element in a co-ordinate system having a centre in the point O being the cylindrical rotator's axis of rotation, after its rotation through the angle φ;

l is a distance OO₁ of the working element oscillation axis from the cylindrical rotator's axis of rotation;

r is a distance of the vertex point from the oscillation axis of the working element;

γ is a constant angle formed between the axes O₁S and O₁C, where S is a mass centre of the working element; and

θ(φ) is an angle by which the axis O₁S deflects during the rotator's movement through the angle φ.

A relationship between the rotation angle φ of the cylindrical rotator and the deflexion angle Θ of the axis O₁S of the working element is expressed by an equation:

$\theta \left(\varphi \right)=2\arcsin \left(\sin \frac{{\theta }_0}{2}\sin \Psi \left(\varphi \right)\right)$

where a relation between the angles φ and Θ is described by tabulated values of elliptic integrals.

The above parametric equations describing the Radziwill curve KR concerns the case of pendulum movement of the blade type-working element 10 around axis 23 of the rotation of this element 10 connected immovably with the cylindrical rotator 8.

The condition for the closure of the vertex movement track point C of the blade type working element 10, moving whether pendulum motion with regard to the cylindrical rotator 8 with resonance frequency is the fulfillment of the condition in order that the relationship of the oscillation frequency period of this blade type working element 10 (for the accepted value of oscillation amplitude) to the frequency of rotation movement of the cylindrical rotator 8 expressed as a natural number and amounts at the most beneficial to 1 or 2. In actual construction of the compressor the movement track in the immobile vertical plane to the axis of the cylindrical rotator 8 (with regard to the arising abrasion force) does not affect vertex point C, but the rounding of the age of contact of the surface 32. The rounding of surface 32 constitutes the set of contact points C with the surface of the camshaft form stator 4 (equidistant from this vertex point C). In connection with this the outline of the cross-section of the camshaft form stator should constitute the equidistant curve with drawn to the centre from curve KR, ensuring in this manner continuous contact of points of the rounded surface 32 of the appropriate surface points of the camshaft form stator 4. In order to reduce friction of the surface referred to, the contact surface should be lubricated with an oil jet through nozzle of the intake slot of the controlling nozzle 33 on the surface of the blade type-working element 10. The oil jet shall occur beneficially during the air suction phase.

In the exemplary construction depicted in FIGS. 1-3, the cylindrical rotator 8 is supplied on its internal surface with four sockets in which are seated blade type working elements 10. Other numbers of sockets are also possible within the scope of this disclosure. Providing differing numbers of sockets would require the corresponding construction adaptation of the location of the inside pipe of the camshaft and the annular slot evacuating compressed medium within the machine.

The operation of the machine depicted in the figures is discussed herein. Inside the camshaft form stator 4 opening of block 1 of the external surface 24 of the cylindrical rotator 8 and the intake apertures of the front surface 31 of the blade shaped working element 10 during its rotation for the working chamber A of variable volume. In the setting presented on FIG. 2 for its clockwise rotation direction the volume of chamber A1 increases causing suction of the compressed medium through the inside pipe of the camshaft 19. After rotation of the cylindrical rotator 8 by a central angle of 90 degrees the volume of the chamber increases to the maximal value. Simultaneously in this setting of the rotator, this chamber is closed by the vertex points C of adjacent working elements 10. During further rotation of the cylindrical rotator 8 follows the reduction of the volume of chamber A3, and simultaneously oil jet through oil jet nozzle 33. Supplied working chamber to A3 the oil fulfils a triple function, because it lubricates the rear surface 32 of the blade type working element 10 creating a curved opening from the surface of camshaft form stator 4 a wedge of oil reducing friction, simultaneously sealing these surfaces and also conducting away heat being the result of the compression process to invisible coolers. In this last movement phase, corresponding to the further rotation of the rotator by a following angle of next 90 degrees follows the opening the annular slot 21 evacuating compressed medium and conducting away the compressed medium to peripheral appliances of the compressor.

Experimental operation of a prototype compressor built according to the design disclosed herein confirmed that its optimal operation compression corresponds to a large extent of rotation frequencies of the cylindrical rotator 8. But after exceeding a defining boundary value of these frequencies further increase of rotation speed causes a proportional growth of compressor output. For example driving the compressor with an engine of 3 kW power a working pressure of 11×105 Pa and output of approx. 300 dm3/min. was obtained.

It will therefore be understood by those skilled in the art that the present is not limited to the embodiment shown and that many modifications are possible without departing from the scope of the present invention as defined in the appending claims.

Claims

1. A rotary working machine comprising: θ  ( ϕ ) = 2  arcsin  ( sin   θ 0 2  sin   Ψ  ( ϕ ) ), I O 1 = [ π 2  vK ( θ 0 2 ) ] 2 · l · s · m.

an assembly of working chambers with periodically variable volume disposed in a central block that comprises a camshaft form stator, an inside surface of the camshaft form stator defines a surface guiding pendulum motion of one or more blade-type working elements disposed pendulously in respective one or more cylindrical sockets of a cylindrical rotator that is disposed within an interior of the camshaft form stator, the rotator is connected to an external prime mover for providing torque thereto,

an angle of contact between a front cylindrical surface of the blade-type working elements and the internal curved space of the camshaft form stator defines a working chamber of variable volume, the working chamber of variable volume is connected during rotator revolution correspondingly with an inside pipe of a camshaft and an annular slot that is configured to evacuate compressed gas disposed within the working chamber of variable volume,

wherein an outline of a cross-sectional of opening of the camshaft form stator disposed in a vertical plane to with respect to an axis of the cylindrical rotator constitutes the equidistant line to a curve that is described on an immobile plane perpendicular to the axis of the cylindrical rotators by two parametric equations: X(φ)=l sin φ+r sin(φ+γ+θ(φ)) Y(φ)=l cos φ+r sin(φ+γ+θ(φ)), and

wherein a relationship between the rotation angle φ of the cylindrical rotator and the deflection angle Θ of the axis O1S of the working element is expressed by an equation:

wherein a relationship between the angles φ and Θ is described by tabulated values of elliptic integrals, marked on this cross-section plane by the vertex point of the working element. moving with regard to this cylindrical rotator cylinder with the oscillating motion with a resonance frequency during its full rotation at which the moment of inertia the blade-type working element has a value ensuring its resonance frequency of own oscillations with regard to cylindrical rotator and it is expressed by the following equation:

2. The machine of claim 1, wherein the working element is an arched wedge that narrows from a side surface of a first side surface to an opposite second side surface, with the first and second side surfaces joined by a front cylindrical surface that forms a sector of the cylinder with a radius substantially the same as a radius of the cylindrical rotator.

3. The machine of claim 2, wherein the blade type working element is seated rotationally on an axis mounted within a cylindrical socket disposed upon the cylindrical rotator, wherein the front cylindrical surface of the blade type working element is covered by the surface of the cylindrical rotator.

4. The machine of claim 1, wherein the cylindrical rotator comprises two or more sockets and blade type working elements, the axes of which are each substantially parallel to an axis of rotation of the cylindrical rotator.

5. The machine of claim 4, wherein the cylindrical rotator comprises four cylindrical sockets and blade type working elements.

6. The machine of claim 4, wherein the cylindrical sockets are disposed upon the cylindrical rotator with equal spacing between each neighbouring cylindrical socket.

7. The machine of claim 5, wherein an axis through the inside pipe of the camshaft is disposed approximately perpendicularly to an axis through the angular slot.

8. The machine of claim 5, wherein an axis through a controlling nozzle for spray is disposed approximately perpendicularly to an axis through the inside pipe of the camshaft.

9. The machine of claim 1, wherein the housing is fixed to a cover blank and a flange of a rear block.

10. The machine of claim 9, wherein the inside pipe of the camshaft and the annular slot each comprise openings defined within the central block.

11. The machine of claim 1, wherein the central block defines a substantially square shape.

12. The machine of claim 11, wherein t central block, a cover block, and a rear block each define the substantially square shape.

13. The machine of claim 1, wherein the working chambers of variable volume further are defined by the first side cylindrical surface of the blade type working element.