RU2627760C2 - External combustion engine piston drive - Google Patents

Abstract

FIELD: engines and pumps.

SUBSTANCE: on the inner cylindrical surface of the oblique washer there are leading surfaces in the form of a groove, and the outer cylindrical surface for removing the power has fastenings for permanent magnets of the rotor electric current generator. The unfolding of the grooves guide on the inner and outer cylindrical surfaces of the oblique washer is a sinusoid. The grooves of the inner cylindrical surface are cyclically rolled by the rollers entering the grooves or fingers of two pairs of opposing piston rods inside the oblique washer, and grooves of the outer cylindrical surface are rolled by rollers or fingers of the power take-off mechanisms. The opposing ends of the rods can carry pistons, working and displacing, or counterbalancing weights, passive or active. One of the opposite pairs of pistons can serve as a heat pump, when the pistons' motions of the motor and heat pump pairs balance each other. A phase displacement of the working and displacing pistons is possible. The engine has a symmetrical body, two opposing parts of which are connected by flanges of the crankcase into a single hermetic unit, which allows to maintain the high pressure of the gas working medium longer.

EFFECT: mechanism downsizing.

50 dwg

Description

The invention relates to the field of engine building, in particular to external combustion engines operating on the Stirling thermodynamic cycle.

Known crank and rhombic drives of pistons of an external combustion engine of the Stirling type, providing coordinated movement and phase shift of the pistons relative to each other by means of cranks, rods, traverses and rods of the working and displacement pistons, when the rods of the working pistons are passed with the possibility of cyclic reciprocating movement through channel seals in the crankcase walls between the volumes of the cylinders and the crankcase, and the piston-displacer rods, in the case of a rhombic drive, are missed NOSTA cyclic reciprocating motion through passages therethrough in sealing rods of the working pistons. Due to the geometric dependences determined by the magnitude of the piston stroke, the known crank and rhombic drives are large relative to the cylinder-piston group and occupy a large volume, which determines the significant dimensions and weight of the crankcase in which the drives are located, and the engine as a whole. In addition, crank and rhombic drives limit the range of the phase shift of piston movement by a sinusoidal law, which narrows the selection of duty cycle parameters (see G. Walker, Stirling Engines, Moscow, Mashinostroenie publishing house, 1985, p. 234) .

A known piston drive of a double-acting Stirling engine with an oblique washer mounted in the crankcase with the possibility of rotation about an axis parallel to the axes of movement of the pistons and rods, made in the form of a disk mounted on an axis at an angle to it, containing passed through with the possibility of cyclic reciprocating through channel seals in the crankcase walls from volumes of cylinders parallel to each other to the crankcase volume rods, each carrying a piston at one end in the cylinder volume, and a card at the other end a - crosshead, which accepts lateral loads on the rod and piston, as well as hemispherical cam followers located in hemispherical recesses of the pusher, sliding their driven surfaces along leading opposite surfaces of the oblique washer (see G. Walker, Stirling Engines, Moscow, vol. in "Engineering", 1985, p. 244).

The specified device does not make it possible to coordinate the movement of precisely coaxial working and displacement pistons located in one cylinder, restricting the use of double-acting Stirling engines, which by definition have at least three cylinders, which leads to significant dimensions, volume and, accordingly, crankcase and engine weight in whole.

The technical problem solved by the present invention is to reduce the size of the drive and the crankcase volume relative to the cylinder-piston group with equal to the known actuator stroke values of the coaxial working and displacement pistons moving in a common cylinder, the possibility of expanding the boundaries of the phase shift of the pistons.

The problem is solved in that the oblique washer installed in the crankcase with the possibility of rotation is made in the form of a cylinder, whole or composite, the end or adjacent wall surfaces of which are used to accommodate the sliding or rolling bearings that allow the cylinder to rotate, the inner cylindrical surface for matching synchronous movements of the pistons has leading surfaces in the form of a groove or two grooves, the outer cylindrical surface for removing power has mounts for of melted magnets of the rotor of an electric current generator, or cams, or a gear rim, or leading surfaces of one or several grooves, the recess of the groove guide on the inner and outer cylindrical surfaces of the oblique washer is a sinusoid or a variation of a sinusoid from a combination of sections of different curvature, the distance between the extrema of the sinusoid determines the magnitude of the piston stroke and the amplitude of the motions of the power take-offs, the groove forming determines the profile of the leading surfaces of the grooves, cycling driven by the driven surfaces of the rollers or fingers on the rods and power take-off mechanisms and entering into the grooves so that the axis of rotation of the rollers or the axis of the fingers of two mutually opposed pairs of rods inside the oblique washer are perpendicular to the axes of movement of their bearing rods and lie in common planes, the angle between these planes can be constant or adjustable, direct, sharp or obtuse, determining the range of phase displacement of the working and displacement pistons and the position of the counterbalancing antiphase of the opposing pistons, the pistons of one of the opposite vapor can serve as a heat pump or can be replaced by balancing balances, passive or active, for example magnets and power generating coils.

Structurally, the oblique washer can be made as a whole or as a component to facilitate assembly. In the second case, the parts of the oblique washer are pulled together as a whole by a cylindrical sleeve, thread or otherwise, for example, they are pressed by mechanical bearings by the walls of the crankcase, and the outer cylindrical surface of the oblique washer and, accordingly, the inner cylindrical surface of the tightening sleeve are provided with mutually coincident locking protrusions and depressions slipping parts of the oblique washer relative to each other. In the case of a whole oblique washer, piston rods can be made integral to facilitate assembly.

To remove the energy produced by the engine, electric or mechanical, the outer cylindrical surface of the oblique washer or the tightening sleeve may have one or more flanges with holes, dovetail sockets or other means for attaching permanent magnets to the rotor of a brushless or collector electric current generator, the stator of which can be placed on the inner surface of the crankcase, or ring gear, or cams, or groove, the scan of which is closed sinusoidal a curve or a line consisting of a closed combination of sections of different curvatures. The forming groove may have a spherical, rectangular, trapezoidal or other shape, allowing cyclic rolling around the walls of the groove with rollers or fingers, the forming of which corresponds to the forming groove, mounted, for example, at the ends of the connecting rods, the axes of which are pulled out of the crankcase outwards through seals and are rigidly connected to external connecting rods, so that external connecting rods can perform mechanical work. Rollers or fingers cycling around the walls of the groove on the outer cylindrical surface of the oblique washer or the tightening clutch can also be mounted on sliders located on the crankcase walls or on the rods of hydraulic cylinders and in these cases power is taken through seals in the crankcase or through a hydraulic conduit. The generatrix of the leading surfaces of the grooves cyclically rolled around by the driven surfaces of the rollers or fingers on the rods and power take-offs may have a spherical, rectangular, trapezoidal or other shape. The generatrix of the driven surfaces of the rollers or fingers corresponds to the generatrix of the leading surfaces of the grooves. Due to the fact that the connecting rods and their axes make only alternating turns by angles not exceeding 90 °, their seals are simpler and more reliable than the seals of the power take-off shafts of known engines that rotate a full revolution.

The symmetry of the mating surfaces of the opposite pairs of rods is such that for the protruding parts of the rods there are corresponding recesses on the opposite rods, providing unhindered possibility of oncoming reciprocating movements of the rods relative to each other and, correspondingly, connected with the rods of the coaxial pistons in accordance with the position of the rollers or fingers in the groove or slanting washer grooves.

In FIG. 1a shows the drive assembly at the position of the working pistons (working pistons and displacement pistons are shown without piston rings) at the corresponding “bottom dead points”, in FIG. 1b, the working pistons are at the “top dead center”; in FIG. 2a shows a sectional view of the drive assembly also with the position of the working pistons (working pistons and displacement pistons shown without piston rings) at the corresponding “bottom dead points”, in FIG. 2b is an external sectional view of FIG. 2a the actual drive; in FIG. 3a shows a sectional view of the drive assembly at the position of the working pistons (working pistons and displacement pistons are shown without piston rings) at the corresponding “top dead points”, in FIG. 3b is an external sectional view of FIG. 3a the actual drive; in FIG. 4 and 5 respectively show the projection and view of a composite oblique washer with rods, end bearings and rollers without pistons and channels in the crankcase walls; in FIG. 6a and on an enlarged scale in the detail view of FIG. 6b shows a possible design of a half composite oblique washer with half of the oblique annular groove rolled by the rods of the opposing piston opposing piston rods and fixing protrusions on the outer cylindrical surface for mating with corresponding depressions on the inner cylindrical surface of the tightening sleeve; in FIG. 7a and 7b show the case of perpendicularity of the planes in which the axis of rotation of the opposed rollers or the opposed axis of the fingers lie on the rods of the opposed pistons inside the oblique washer; in FIG. 8 shows the interlocking geometry of the working piston rods and the piston-displacer piston rod slider included in the working piston rod groove (rollers not shown); in FIG. 9a shows the interlocking geometry of the opposing piston-displacer rods, enabling them to meet reciprocating movements by the amount of piston stroke; in FIG. 9b, 9c and 9d show the interlocking geometry of the opposing piston rods of the working pistons, providing them with the possibility of oncoming reciprocating movements by the magnitude of the piston stroke; in FIG. 10a, 10b, 10c, 10g shows in detail the geometry of the piston rod of the working piston with a through channel made in its body and a flat groove for passing the rod of the displacer piston and its slider, in remote views of FIG. 10e and 10e - detailing the placement on the protrusion of the shaft of the axis of the roller (it can also serve as a finger in the groove); in FIG. 11a, 11b, 11c shows in detail the geometry of the piston-displacer rod and its integral part — the slider — a special protrusion moving in the flat groove of the piston rod and designed to neutralize the tangential forces, and the axis of the roller on the slider that mates with the through channel in the body of the working piston rod in FIG. 11g and 11e - detail placement on the rod and on the slider of the roller axis (it can also act as a finger in the groove), in Fig. 11d - end projection of the piston-displacer rod; in FIG. 12a, 12b, 12c show assembly views of a composite oblique washer tightening its couplings with a central flange for fastening the permanent magnets of an electric current generator, collector or brushless, rollers running around the internal groove of the oblique washer, in FIG. 12g shows a view of a tightening coupling with a central flange for attaching permanent magnets to an electric current generator, collector or brushless, a roller rolling around the internal groove of the oblique washer; in FIG. 13a, 13b, 13c show projections of a half of a composite oblique washer, in FIG. 13g and 13d show views of half of a composite oblique washer; in FIG. 14a and 14c show projections of a tightening sleeve with a central flange with holes for mounting permanent magnets of an electric current generator and with fixing troughs on the inner cylindrical surface for interfacing with an oblique washer, integral or integral, in FIG. 14b is a view of a tightening coupling with a central flange with holes for mounting permanent magnets of an electric current generator and with fixing troughs on the inner cylindrical surface for interfacing with an oblique washer, integral or integral; in FIG. 15a shows a projection and view of a possible embodiment of a tightening sleeve with an oblique groove with a spherical generatrix for removing the mechanical energy of the engine and with fixing depressions on the inner cylindrical surface for interfacing with an oblique washer, integral or integral, in FIG. 15b shows a projection and view of a possible embodiment of a tightening coupling with an oblique groove with a rectangular generatrix for removing the mechanical energy of the engine and with fixing depressions on the inner cylindrical surface for interfacing with an oblique washer, integral or integral, in FIG. 15c shows a projection and view of a possible embodiment of a tightening coupling with an elliptical cam groove in the central flange with a rectangular generatrix for removing the mechanical energy of the engine and with fixing troughs on the inner cylindrical surface for interfacing with an oblique washer, integral or integral, in FIG. 15g shows a view of a possible embodiment of a tightening coupling with two end flanges with holes for mounting permanent magnets of an electric current generator and with fixing troughs on the inner cylindrical surface for interfacing with an oblique washer, integral or integral; in FIG. 16a and 16b show projections of a variant of an entire oblique washer with two symmetrical grooves on the inner cylindrical surface, each of the two grooves matches the movements of only one of the opposed pairs of the working and displacing pistons and, therefore, is rolled around only by two rollers - the working piston rod and the displacing piston rod in FIG. 16c and 16d show more illustrative views of a variant of an entire oblique washer with two symmetrical grooves on the inner cylindrical surface (for simplicity, flanges with holes for attaching the rotor magnets of the electric current generator and grooves for removing mechanical energy are not shown in Fig. 16); in FIG. 17 shows a possible case of non-perpendicularity of the planes in which the axis of rotation of the rollers or the axis of the fingers lie on the rods of the working pistons and pistons-propellants inside the oblique washer; in FIG. Figure 18 shows the continuous sinusoidal line of the scan of the generatrix of the groove on the inner cylindrical surface of the oblique washer, the dots indicate the extrema of the generatrix of the groove, coinciding with the so-called "Dead points" of the piston stroke, the distance between the parallel dashed lines passing through the extrema of the generatrix of the groove is equal to the magnitude of the piston stroke of the engine.

The piston drive of the Stirling engine contains piston rods 1a and 1b, passed with the possibility of cyclic reciprocating through the channel seals in the walls of the crankcase 2a and 2b between the cylinder and crankcase volumes (the crankcase is partially represented by walls with channels, the housing is not shown, the channel seals are not shown ), opposed working pistons 3a and 3b, opposed displacing pistons 4a and 4b, opposed piston rods 5a and 5b of the displacing pistons, a composite oblique washer from symmetrical parts 6a and 6b, a tightening sleeve 7, an end ball dshipnik 8, mutually opposed rollers 9a and 9b working piston rods, mutually opposed rollers 10a and 10b, the piston rods propellants.

The proposed technical solution is based on the principle of symmetry and opposites, when two opposed parts of the body with heaters, regenerators and refrigerators are connected by crankcase flanges into a single sealed unit, which allows you to maintain high pressure of a gas working fluid, such as hydrogen or helium, for longer (heaters, regenerators, refrigerators and the case is not shown in the drawings, because they have no significant differences from the known structures). The mutually opposing rods 1a and 1b of the working opposing pistons 3a and 3b, respectively, pass through the channels 2a and 2b in the crankcase walls from the cylinder volumes into the crankcase volume through seals (not shown) with the possibility of reciprocating movements. Through the seals in the channels (not shown) of the reciprocal opposing rods 1a and 1b of the working pistons 3a and 3b also from the cylinder volumes, the reciprocal opposing rods 5a and 5b of the opposing pistons-displacers 4a and 4b, respectively, pass with the possibility of reciprocating movements. In the crankcase volume at the ends of the rods inside the oblique washer, perpendicular to the axis of their movement, the axis of rotation of the rollers or fingers are installed, which enter the groove or grooves of the oblique washer on its inner cylindrical surface, and the axis of rotation of the rollers or the fingers of mutually opposed rods also form mutually opposed pairs, for example, a mutually opposed pair of rollers 9a and 9b mounted on mutually opposed rods 1a and 1b, respectively, and a mutually opposed pair of rollers 10a and 10b mounted on mutually opposed rods 5a and 5b, respectively governmental. The variant with fingers is not shown in the drawings, since the fingers represent only a particular, “degenerate”, case of axes of rotation of the rollers and are less preferable in view of the more significant energy expenditure on friction when moving in a groove or in grooves.

Since the reaming of the guide grooves is a sinusoid (see Fig. 18) or a variation of the sinusoid, it is necessary for the axis of rotation of the rollers 9a and 9b to lie in one common plane to achieve the position of the counterbalancing antiphase of the opposite pairs, and the axis of rotation of the rollers 10a and 10b to lie in another plane common to them (see Fig. 6b). In order to achieve the most theoretically advantageous and often used phase angle of 90 ° between the working piston and the displacing piston, it is necessary that the angle between the planes of movement of the axes of rotation of the rollers 9a and 10a, as well as the opposite rollers 9b and 10b, be equal to 90 ° (see Fig. 7a and 7b). Changing this angle in the range from acute to obtuse, from a value of less than 90 °, to a value of greater than 90 °, you can vary the phase angle of the displacement of the working piston and the displacing piston relative to each other in a fairly wide range. The value of this angle can be predetermined for the entire life of the engine by selecting and executing the constant geometry of the flat grooves in the rods of the working pistons and the sliders included in these flat grooves on the rods of the piston-displacers (see Fig. 17), but it can also be regulated by a special mechanism (not shown) directly during engine operation. In FIG. 6b shows in detail how all four rollers run around part of the groove of half of a composite oblique washer and how the symmetrical geometry of the mating surfaces of the rods provides unhindered cyclic reciprocal reciprocating movements of the rods relative to each other and, correspondingly, connected with the rods of coaxial pistons or counterweights in accordance with the position rollers in the groove of the oblique washer. The magnitude of such cyclic counter reciprocating movements of the rods is determined by the distance between the points of the extrema of the groove forming in FIG. 18 and is equal to the stroke of the pistons. In the case of the execution of an oblique washer with two symmetrical grooves (see Fig. 1b), only the rollers of one opposite pair of rods enter and run into each groove, but the phase dependences indicated above are preserved.

Since the extrema of the forming groove correspond to the dead points of the working pistons, to start the engine, it is necessary that the rollers of the rods of the working pistons are in a position different from the extrema of the grooves when the pressure of the working fluid on the working piston is transmitted through the rod to the roller and the walls of the groove of the oblique washer, decomposes into two components: the reaction force in the direction of the axis of movement of the pistons and the tangential force that causes the oblique washer to rotate. To overcome the dead spots, it is necessary to turn the oblique washer either by external mechanical action through the power take-off mechanisms, or by switching the electric current generator to electric motor mode. The direction of the subsequent rotation of the oblique washer will depend on the position of the rollers of the working pistons relative to the points of the extrema of the forming groove given by the external mechanical or electrical effect. Under the influence of the pressure of the gas working fluid on the working pistons, the reaction of the leading surfaces of the rollers of the rods of the working pistons to the driven surfaces of the slanting washer groove occurs, resulting in the decomposition of the forces to the forced rotation of the slanting washer, which, in turn, leads to the reaction of the surfaces of the groove of the slanting washer leading for driven surfaces of the rollers of the piston-displacer rods, and the force directed along the axis of movement of the pistons forces the displacer pistons to move behind or ahead by a phase angle (depending from the initial position) from the working pistons. In this case, the tangential force exerted by the walls of the groove of the oblique washer on the rollers of the piston-displacer rods is jointly neutralized by the mating surfaces of the rods and the profiled sections of the rods and channels themselves in the crankcase walls, which allow them to pass, excluding the rotational movements of the rods and pistons.

The list of positions (the same type of opposed parts in the drawings have a common position number and differ in letter designations a and b):

1. The piston rod;

2. The channel in the walls of the crankcase;

3. The working piston;

4. Displacement piston;

5. The piston-displacer rod;

6. Slanting washer;

7. The tightening coupling;

8. Face ball bearing;

9. The roller of the piston rod;

10. The roller of the piston-displacer rod.

Claims (1)

A Stirling engine piston drive, comprising working piston rods passed with the possibility of cyclic reciprocating through the channel seals in the crankcase walls between the cylinder and crankcase volumes, piston-displacer rods passed with the possibility of cyclic reciprocating through the seals in the working piston rod channels , oblique washer mounted in the crankcase with the possibility of rotation, matching with its leading surfaces the synchronous movements of the pistons by means of driven surfaces on the piston rods, characterized in that, in order to reduce the size of the drive relative to the cylinder-piston group when the piston stroke is equal to the known drives and expand the range of phase angles, the oblique washer is made in the form of a cylinder, whole or composite, end or adjacent to them the surface of the walls of which are used to accommodate the possibility of rotation of the cylinder of the sliding or rolling bearings, the inner cylindrical surface for matching synchronous movements of the piston it has leading surfaces in the form of a groove or two grooves, the outer cylindrical surface for removing power has fasteners for permanent magnets of the rotor of the electric current generator, or cams, or ring gears, or leading surfaces of one or more grooves, the reaming of the groove guide on internal and external the cylindrical surfaces of the oblique washer is a sinusoid or a variation of a sinusoid from a combination of sections of different curvature, the distance between the extrema of the sinusoid determines the magnitude of the piston stroke it and the amplitude of the movements of the power take-off mechanisms, the groove forming determines the profile of the leading surfaces of the grooves cyclically rolled around by driven surfaces in the form of rollers or fingers on the rods and power take-off mechanisms and entering into the grooves so that the axis of rotation of the rollers or the axis of the fingers of two mutually opposed pairs of rods inside the oblique washers are perpendicular to the axes of movement of their bearing rods and lie in their common planes, the angle between these planes can be constant or adjustable, straight, sharp or obtuse, determining the range n phase displacement of the working and displacement pistons and the position of the counterbalancing antiphase of the opposed pairs, moreover, the pistons of one of the opposed pairs can serve as a heat pump or can be replaced by balancing counterweights, passive or active, for example magnets and power generating coils.

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