CN1844642A - Rotary type capacity variable mechanism and rotary piston engine - Google Patents

Abstract

The invention relates to a capacity-changer and a rotation piston engine, which can continuously compress or expand, in annular cylinder, with step-less capacity change, high compress rate and continuous revolution. Wherein, the annular cylinder comprises several rotation pistons via revolution sleeves are connected to several guide devices with rotational guide rod; all guide rods are radiated vertically distributed and fixed on one driving axle; the driving axle is eccentric from the revolution center of cylinder to realize non-uniform loop distribution of piston; the driving axle via the force in same rotation is rotated; it can be used in compressor, vacuum pump, water generator and wind generator, etc. the compressor and expanding engine of engine can both use said revolution capacity changer, with transverse processes, to significantly improve the property of engine.

Description

Rotary type capacity variable mechanism and rotary piston engine

Technical field the present invention relates to a kind of capacity variable mechanism and rotary engine, relates in particular to a kind of rotary type capacity variable mechanism and the rotary-piston type gas engine that guide-bar mechanism is arranged that guide-bar mechanism is arranged.

Background technique is present, huge aircraft can fly blue sky at leisure, the long train of tens joints can shuttle on lofty mountains and steep hills, millions of kilowatts of electricity generating devices can be continuously to industrial or agricultural and urban district power supply, various vehicles can run quickly on expressway hastily, all are because they have equipped advanced strong motor on one's body.Yet, whether so just we can say that these technology have developed into the peak? the space that does not advance again, answer should be: be not.With regard to the most ripe and general gas turbine of present application, its thermal efficiency also only is about 45%.In fact, be not only gas turbine, also comprise all anxious to be improved necessary of ubiquity working efficiency or the thermal efficiency and may of machineries such as piston type fuel gas motor and various types of compact machine, vacuum pump, water turbine, steam turbine, wind-power electricity generation, nuclear energy power generation, because the current world is ubiquity severe energy waste and the not high big problem of energy utilization rate still.The wherein a kind of way that improves energy utilization rate is exactly to find a kind of working pressure height, continuous action, gearless, the in-fighting capacity variable mechanism that satisfies simultaneously such as little.

Gas turbine and piston type fuel gas machine all belong to the gas combustion motor.The characteristics of gas combustion motor are to be working medium with continuous-flow gas, gas compressor and turbine are independent separately, burner continuous burning, completely, pressure stability, be easy to control, pollutant emission is few, advantage is very outstanding, people dream of to utilize its these characteristics to design a kind of both steady, motor efficiently again, wherein the most key a kind of working pressure height, continuous action, gearless driving, the in-fighting capacity variable mechanism that satisfies simultaneously such as little that is to locate.

Present gas turbine and piston type fuel gas machine all have many separately advantages, but all also are not ideal engine in the people mind.The combustion gas turbofan engine is that present aviation field is used the most ripe and general gas combustion motor, but because the whole air-flow path between their turbine blade is penetrating fully, there is the working medium injection generation recoil impulse force of pressure to carry out gas compression or expand doing work by the high speed winds flabellum to working medium pushing or utilization, there is not packed-piston between blade, can not form airtight working room, can't utilize the transfiguration mode to carry out work, level pressure ratio and energy conversion efficiency are difficult to the transfiguration mode comparable, and it is impossible fully thinking to improve significantly again; The data introduction is arranged, also there is strong turbulent flow between the sound leaf of blade, also can produce strong noise during the gas turbine running up to 130 decibels, not only produce powerful noise pollution, and illustrate that there is the big pressure loss in it, in this case, still there is serious deficiency in gas turbine, is necessary to substitute the performance that just can significantly improve motor with new method.

The piston type fuel gas machine is the same with gas turbine, and also can having independently, cylinder is used as gas compressor or expansion working machine separately.Gas compressor provides pressurized air specially, and the expansion working machine is specifically designed to the energy that discharges conversion High Temperature High Pressure working medium, outputting power; Burner then obtains the fuel continuous burning to have the combustion gas of High Temperature High Pressure energy.At present, piston type fuel gas machine aspect has begun to be successfully applied to transport vehicles such as manufacturing automobile, but still the pressure height of failing to find a job, continuous action, gearless driving, the in-fighting capacity variable mechanism that satisfies simultaneously such as little, prior art back and forth fluctuation is big, vibration is fierce, can't join coldly, need inherent defect such as heat radiation grade, make the thermal efficiency of present piston type fuel gas machine also can't significantly improve again.

The piston type fuel gas motor divides reciprocating type and rotary type again, the advantage of reciprocating type gas engine is working room's good leak tightness, and powerful, inferior position are that reciprocating member motions such as piston, connecting rod, inlet and discharge valve are arranged, under the high-speed case, motional inertia is very big, also has bent axle to participate in carrying out work, and engine flame out is caused at the bent axle dead point easily under the low speed situation, stable working is poor, cylinder volume efficient is low, and discharge capacity is little, and incompatible big discharge capacity occasion is used.Although adopt the multi-cylinder form to take turns to operate, stationarity makes moderate progress, and the existing various disadvantages of reciprocating type working method still can't thoroughly be eliminated.The rotary-piston type gas engine has been concentrated the advantage of gas turbine and reciprocating type gas engine, make self both had the internal combustion rotation, the advantage of continuous burning, no reciprocating member motion, has the advantage that piston machine transfiguration compression and transfiguration are expanded and done work again, have good high speed performance and low-speed performance concurrently, to be ideal engine in a kind of people mind, be the focus and the direction of present engine research.

Wankel engine is the rotary engine of present a kind of maturation, but it does not have reciprocal inertia and be better than the present internal-combustion engine except that having continuous revolution, still not as good as internal-combustion engine, is difficult to extensive popularization at many aspect of performances, is difficult to replace existing internal-combustion engine.Wankel engine is not the gas combustion motor, moreover many aspect of performances such as discharge capacity can not be compared with the gas combustion motor fully.

Positive displacement compressor is the class compressor that people are familiar with very much, comprises reciprocal compressor, rotary sheet type compressor and screw compressor etc.Because they change working room's internal pressure by changing airtight working room internal volume size, so people are called variable displacement compressor with them, main frame is referred to as variable-displacement equipment or displacement-variable device.If the rate of change of swept volume of a single chamber size changes smoothly with the rotation of mechanism, then be called stepless transfiguration.Say that strictly displacement-variable device also comprises vacuum displacement pump and positive displacement expansion working machine etc., and all change the mechanism that working room's internal pressure is changed because of volume.Volume diminishes and is called the transfiguration compression, and the volume change is called transfiguration greatly and expands.The advantage of reciprocal compressor is working room's good leak tightness, the working pressure height, shortcoming is to have reciprocating member to move, have bent axle participation work, the dead point is arranged, stable working is poor, and noise is big, needs heat radiation, air-breathing and compression hockets, and makes the working speed of internal-combustion engine and the raising of the thermal efficiency be subjected to great restriction; The advantage of screw compressor is that work is carried out in the continuous revolution of rotor, the no reciprocal inertia of no reciprocating member motion, and running is steady, and shortcoming is that discharge capacity is little, and efficient is low, incompatibility gas engine usefulness.Had statement clearly in the 579th page of development course of " displacement compressor technical manual " the 4th piece of (rotary compressor) the 3rd chapter of a book (double-screw compressor) that this point was published by Yu Yongzhang chief editor (Beijing) China Machine Press as far back as in October, 2000 and developing direction one joint: " the thirties in 20th century (referring to nineteen thirty-seven); Sweden engineer Alf Lysholm is when studying gas turbine; wish to find a kind of compressor of doing rotation motion; require its rotating ratio piston compressor much higher;, and surge can not take place so that can directly drive by gas turbine.In order to achieve the above object, he has invented helical-lobe compressor.In theory, helical-lobe compressor has his required characteristics, but owing to must have the requirement that very large volume flow could satisfy gas turbine work, helical-lobe compressor does not obtain to use in this field "; The advantage of rotary sheet type compressor is that work is carried out in the continuous revolution of rotor, and volume flow is big, working room's good leak tightness, and the working pressure height, the efficient height, shortcoming is that radially reciprocating member motion is arranged, stationarity is poor.In aforementioned three kinds of transfiguration modes, the advantage of rotary sheet type is the most outstanding, is expected to become the breach of improving and greatly improving mechanical propertys such as existing compressor, vacuum pump, steamer and motor most.Structurally existing four the reasonable parts of present rotary sheet type compressor, Ying Yuyu keeps: one, circular cylinder is arranged; Two, rotation blade (or ring segment) is arranged; Three, there is a pair of working medium to import and export.Four, blade is rotated motion provides high-speed smooth work for mechanism place in the ring cylinder.Deficiency is: one, and rotation blade is telescopic slide in the chute of rotor, has produced radially reciprocating member motion and back and forth inertia, is unfavorable for running up, and is unfavorable for continuous operation; Two, rotor and circular cylinder off-centre are unfavorable for that blade moves in a circle; Three, there is not a cover to make each blade independently wave rotating mechanism, the circumferential distance that annulus section piston can only be maintained fixed in doing the rotation motion process all the time in the cylinder, circumferentially spacing can not change, in the time of can't between adjacent pistons, periodically producing and near close up, the time and separate the change procedure that zooms out, advantage can not brought into play.

Summary of the invention the objective of the invention is to overcome deficiency of the prior art, and a kind of stepless capacity variable mechanism and the gas combustion heat engine that guide-bar mechanism is arranged with guide-bar mechanism is provided.

In order to solve the technical problem of above-mentioned existence, the present invention is achieved by the following technical solutions: the annulus section piston in the capacity variable mechanism links to each other with guide-bar mechanism by the seal ring on the one, the guide rod of guide-bar mechanism is radial and fixedlys connected with live axle, live axle departs from cylinder shaft axis one distance and constitutes linking mechanism, make described annulus section piston periodically change rotation from fast to slow again from slow to fast, the annulus section cavity internal volume between the ring segment piston is changed to large period ground to little by zero again to zero with drive shaft turns is descending with the rotation of live axle, form and suck, compression or expansion, discharge the working room; Gas compressor in the gas combustion motor and expansion working machine have all adopted the rotary type capacity variable mechanism that guide-bar mechanism is arranged, the rotary type capacity variable mechanism of gas compressor makes atmosphere gas, boosts by compression, and the rotary type capacity variable mechanism of expansion working machine makes high temperature and high pressure gas externally expand acting, step-down.

The present invention can also be achieved through the following technical solutions: described annulus section piston links to each other with guide-bar mechanism respectively with upper sealing ring by seal ring on the one or one, linking mechanism makes described annulus section piston respectively with periodically changing rotation once from slow to fast again from fast to slow in each circumgyration scope of drive shaft turns, make in annulus section cavity internal volume each the circumgyration scope between the ring segment piston with drive shaft turns descending to zero again by zero to little to the variation of large period ground once, form and suck, compression or expansion, discharge the working room once.Described guide-bar mechanism is the guide-bar mechanism of revolution guide rod is arranged or the guide-bar mechanism of guiding groove revolution guide rod to be arranged or the guide-bar mechanism of revolution sheave is arranged.Described guide-bar mechanism by fixed component, crank, roll pin or slide block or guiding groove, guide rod constitutes; Cylinder body, frame, bearing support are formed the fixed component of guide-bar mechanism, rotary sealing ring one end face is provided with and rolls pin or fulcrum post, rolling the pin center is one of crank up point of guide-bar mechanism, the revolution guide rod is formed the guide rod member of guide-bar mechanism, has the guide rod of guiding groove or sheave to comprise guiding groove and two members of guide rod; The axis parallel that rolls pin leans on guide-bar mechanism one side or is provided with penetrating making by middle seal ring and roll the slotted eye that pin passes in the cylinder shaft axis; Frame is provided with bearing support, the parallel live axle of placing on the center line in the seat hole; The groove of revolution guide rod or sheave is the homogeneous radiation shape and distributes; A slide block or one are set on the groove of a guide rod or a sheave roll pin, slide block or roll the pin kink and on the groove of revolution guide rod or guide groove wheel, can slide along the groove of guide rod or guide groove wheel, the rolling the pin pin shaft hole or cooperate of the pin-and-hole of slide block or bearing pin and revolving sleeve end face, the groove number of guide rod or sheave is consistent with the rotary piston number and be more than 2 or 2, is advisable with 3; Piston corner Changing Pattern meets relation: β=arccos (lsin ²α+cos α √ (R ²-l ²Sin ²α))/R.Adjacent pistons place piston assembly roll pin gyration center or fulcrum post gyration center be symmetrically distributed in the cylinder gyration center when pointing to the both sides of live axle gyration center direction the adjacent face of described piston coincide each other, spacing is zero, described working medium is imported and exported and is distributed in the matching surface both sides, the matching surface both sides are working medium zone of high pressure and low pressure area separatrix, it is the circumferential direction extending circumferentially of starting point along cylinder with described separatrix respectively that working medium is imported and exported opening, the opening that low pressure is imported and exported may extend to adjacent two-piston and is symmetrically distributed in the position of leaning on low voltage side one end when the live axle gyration center points to cylinder gyration center direction both sides, the elongation of high pressure import and export opening is decided on mechanical compression ratio, should be less than or equal to the extended length that low pressure is imported and exported opening.Compression ratio gets 1 or greater than 1, and compression ratio gets 1 during liquid refrigerant work.Described gas compressor adopts a cover or the rotary piston displacement-variable device of guide-bar mechanism is arranged more than the cover, is advisable with a cover; Described expansion working machine adopts a cover or the rotary type capacity variable mechanism of guide-bar mechanism is arranged more than the cover, is advisable with two covers, and wherein a cover is used for the drive pressure mechanism of qi, and a cover is used for outside outputting power.

Compared with prior art, the significant beneficial effect of the present invention is:

1. can produce in the clutch release slave cylinder between adjacent pistons in the rotary type capacity variable mechanism and continue interior compression or interior expansion, stepless transfiguration, compression ratio is variable between 1～∞, the compression ratio height, compression ratio can be infinitely great theoretically, compression ratio can reach 100 or higher in the practical work process, and working pressure and working efficiency significantly improve.

2. the rotary type capacity variable mechanism inner carrier rotates continuously, does not have the reciprocating member motion fully, no inlet and discharge valve, gearless driving has good high speed performance and low-speed performance, highly versatile, use very extensively, comprise host configuration such as to be applied to vacuum pump, water turbine, wind-power electricity generation and nuclear energy uses.

3. rotary type capacity variable mechanism is simple in structure, and is in light weight, in addition parts are few, and cost is low.

4. good leak tightness in the rotary type capacity variable mechanism cylinder refluxes and lacks, and interior damage is little, volumetric efficiency height, energy-conservation, unit mass and volumetric specific power height.

5. rotary type capacity variable mechanism novel structure, integral rigidity is good, and structural capacity is strong, easily processing, the antisurging ability is strong, long service life.

6. as the gas combustion motor, can be provided with two expansion working machines, for the output of gas compressor required drive and power is equipped with the working machine that independently expands respectively.When external loading increases the gas consumption minimizing that causes the reduction of power output expansion working machine rotating speed, power output expansion working machine, have more a part of combustion gas and can distribute to the expansion working machine of gas compressor automatically, thereby strengthen the driving source of gas compressor, after gas compressor power increases, the gas compressor rotating speed is improved, and has strengthened gas compressor air gettering quantity and delivery pressure, has increased the driving source of power output conversely, increase the ability that overcomes load, contained mechanical further deceleration; When external loading reduces, as descending, cause power output expansion working machine rotating speed to improve, the gas consumption of power output expansion working machine increases, the combustion gas of expansion working machine of distributing to gas compressor is then less, gas compressor power diminishes, the corresponding reduction of gas compressor rotating speed, corresponding minimizing of gas compressor gettering quantity and delivery pressure and reduction, reduced to offer the pressure of power output conversely, weakened ability, contained mechanical further raising speed the load acting, motor is remained under the situation of identical throttle size, all the time can autobalance on a certain suitable rotating speed.If because go up a slope, slack-off being not suitable for of the speed of a motor vehicle needs, and the driver is as long as further open the throttle, need not painstakingly go gear shift,, both save the expensive automatic device of dialling as there being one to dial in work automatically, and for example fast, fuel-efficient with manually dialling the same dynamic response, and be difficult for dead fire.

7. as the gas combustion motor, no-cooling-water cover and cooling fan, available pressurized air is directly mixed cold, dilution air after being heated can directly use as power, save the energy, reduce radiation loss, simplified device simultaneously, adaptive capacity is more extensive, especially need not worry can't work and meet the trouble of bursting by freezing water tank below 0 ℃ because of lack of water causes motor.

8. as the gas combustion motor, the proportioning of discharge capacity and air can be set arbitrarily.

9. as the gas combustion motor, can directly use various fuel, comprise directly using coal or charcoal, just discontinuity increases fuel.

10. as the gas combustion motor, the tail gas back pressure is low, can be near normal pressure discharging or normal pressure discharging, and noise is little, and the de-noising process is easily simple or need not de-noising.

Description of drawings

Fig. 1 dissects stereogram for ring cylinder cylinder body three-dimensional.

Fig. 2 has the ring cylinder cylinder body three-dimensional of rotary sealing ring to dissect stereogram.

Fig. 3 has the ring cylinder cylinder body three-dimensional of annulus section piston to dissect stereogram.

Fig. 4, Fig. 5, Fig. 6 are respectively the 3 dimensional drawing of 3 piston assemblys.

Fig. 7 is the radial guide rod fixed combination of a present invention 3 dimensional drawing.

Fig. 8 is a bearing support 3 dimensional drawing of the present invention.

Fig. 9 is the frame 3 dimensional drawing.

Figure 10 is a rotary type capacity variable mechanism 3 dimensional drawing of the present invention.

Figure 11 is the ring cylinder structure sketch that the rotary piston assembly is arranged.

Figure 12 has the displacement-variable device front dimension sketch of guide-bar mechanism for the present invention.

Figure 13 has the displacement-variable device sectional drawing of guide-bar mechanism for the present invention.

Figure 14 is single guide-bar mechanism schematic diagram;

Figure 15 is single guide-bar mechanism geometrical analysis figure;

Figure 16 is the crank AB corner β of capacity variable mechanism and the graph of relation between guide rod corner α;

Figure 17 is the graph of relation between guide rod active force brachium AC and guide rod corner α;

Figure 18 is the relation curve comparison diagram between guide rod active force brachium AC and guide rod useful effect arm of force length and guide rod corner α;

Figure 19 is the useful effect arm of force length of two guide rods and the relation curve comparison diagram between guide rod corner α;

Figure 20 is the graph of relation between adjacent two-piston end distance circular arc angle and the guide rod corner α.

Figure 21 is that 2 piston mechanisms roll pin center working state when being symmetrical in cylinder gyration center and live axle gyration center line both sides.

Figure 22 is that 2 piston mechanisms roll pin center working state when forwarding on cylinder gyration center and the live axle gyration center line simultaneously.

Figure 23 is that the adjacent pistons of 3 piston mechanisms is rolled the pin gyration center and is symmetrically distributed in cylinder gyration center and live axle gyration center line both sides spacing working state when being zero.

Figure 24 is that the adjacent pistons of 3 piston mechanisms is rolled the pin gyration center and is symmetrically distributed in cylinder gyration center and live axle gyration center line both sides spacing working state when maximum.

Figure 25 is that 4 piston mechanisms have two groups of adjacent pistons to roll the pin gyration center to be symmetrically distributed in cylinder gyration center and live axle gyration center line both sides, working state when a spacing maximum, a spacing are zero.

Figure 26 is that 4 piston mechanisms have two-piston to roll pin center working state when forwarding on cylinder gyration center and the live axle gyration center line simultaneously.

Figure 27 is that the adjacent pistons of 5 piston mechanisms is rolled the pin gyration center and is symmetrically distributed in cylinder gyration center and live axle gyration center line both sides spacing working state when being zero.

Figure 28 is that the adjacent pistons of 5 piston mechanisms is rolled the pin gyration center and is symmetrically distributed in cylinder gyration center and live axle gyration center line both sides spacing working state when maximum.

Figure 29 is that 6 piston mechanisms have two groups of adjacent pistons to roll the pin gyration center to be symmetrically distributed in the maximum spacing of cylinder gyration center and live axle gyration center line both sides one spacing working state when being zero.

Figure 30 is that 6 piston mechanisms have two-piston to roll pin center working state when forwarding on cylinder gyration center and the live axle gyration center line simultaneously.

Figure 31 is that 8 piston mechanisms have two groups of adjacent pistons to roll the pin gyration center to be symmetrically distributed in the maximum spacing of cylinder gyration center and live axle gyration center line both sides one spacing working state when being zero.

Figure 32 is that 8 piston mechanisms have two-piston to roll pin center working state when forwarding on cylinder gyration center and the live axle gyration center line simultaneously.

Figure 33 turns over 60 ° of initial angle for a guide rod in the variable volume compressor structure scheme, working state when piston 3a, 3b roll the pin gyration center to be symmetrically distributed in the cylinder gyration center be zero with live axle gyration center line both sides spacing, and piston 3a enters normal pressure space and begins air-breathing.

Figure 34 is just locating expiratory phase for a guide rod in the variable volume compressor structure scheme turns over 120 ° of initial angle in the ring spacing between piston 3a, 3b.

When Figure 35 turns over 150 ° of initial angle for a guide rod in the variable volume compressor structure scheme, still locate expiratory phase between piston 3a, 3b in the ring spacing.

Figure 36 turns over 180 ° of initial angle for a guide rod in the variable volume compressor structure scheme, and piston 3a rolls the pin center and just in time is positioned on the elongation line that the live axle gyration center points to cylinder gyration center line, still locates expiratory phase between piston 3a, 3b in the ring spacing.

Figure 37 turns over 240 ° of initial angle for a guide rod in the variable volume compressor structure scheme, piston 3a, 3b roll the pin center and are symmetrically distributed in cylinder gyration center and live axle gyration center line both sides, expiratory phase end in the ring spacing between piston 3a, 3b, compression stage begins.

When Figure 38 turns over 270 ° of initial angle for a guide rod in the variable volume compressor structure scheme, between piston 3a, 3b in the ring spacing working medium be compressed, belong to interior compression.

When Figure 39 turned over 300 ° of initial angle for a guide rod in the variable volume compressor structure scheme, ring spacing working medium still had been compressed between piston 3a, 3b, belongs to interior compression.

When Figure 40 turned over 360 ° of initial angle for a guide rod in the variable volume compressor structure scheme, piston 3a rolled the pin center and just in time is positioned on the elongation line that the cylinder gyration center points to live axle gyration center line, and ring spacing working medium is also being carried out interior compression between piston 3a, 3b.

When Figure 41 turns over 390 ° of initial angle for a guide rod in the variable volume compressor structure scheme, between piston 3a, 3b in the ring spacing working medium also carrying out interior compression.

When Figure 40 turns over 420 ° of initial angle for a guide rod in the variable volume compressor structure scheme, between piston 3a, 3b in the ring spacing working medium all be compressed and enter the zone of high pressure, piston 3a successfully withdraws from from the zone of high pressure simultaneously, enters atmospheric area and restarts the new operation cycle.

When Figure 42 turned over 360 ° of initial angle for a guide rod in the variable volume compressor structure scheme, piston 3a rolled the pin center and just in time is positioned on the elongation line that the cylinder gyration center points to live axle gyration center line, and ring spacing working medium is also being carried out interior compression between piston 3a, 3b.

Figure 43 is the working principle sketch of single gas compressor list expansion working machine gas engine scheme among the present invention.

Figure 44 is the working principle sketch of the two expansion working machine gas engine schemes of single gas compressor among the present invention.

Figure 45 is the working principle sketch of single gas compressor list expansion working machine gas engine scheme among the present invention.

Figure 46 is the working principle sketch of the two expansion working machine gas engine schemes of single gas compressor among the present invention.

Parts 1-cylinder, parts 2-centration axis, parts 3a, 3b, the 3c-piston, parts 4,5-working medium is imported and exported, parts 6a, 6b, 6c, 6d, the 6e-revolving sleeve, parts 7-polished rod guide rod, parts 8a, 8b, 8c-rolls pin, parts 9a, 9b, 9c-has the guide rod of guiding groove, parts 10-bearing support, parts 11-live axle, parts 12-has the sheave of guiding groove, parts 13a, the penetrating arc-shaped slot of 13b-, parts 14-slide block, parts 15-frame, parts 24-slide block, parts 25-fixed component, parts 26-crank, parts 28-rotating guide, code name 29-trajectory, code name 30-corner β value change curve, code name 31-guide rod active force brachium change curve, code name 32-guide rod effective force brachium change curve, the guide rod effective force brachium change curve of 120 ° of phase places of code name 33-hysteresis, variable angle curve between code name 34-adjacent pistons, parts 41-gas compressor, parts 42-compressed air outlet, parts 43-burner, parts 44-suction port, parts 45-expansion working machine, parts 46-compressor air inlet machine mouth, parts 47-expansion working machine relief opening, the parts 48-turbine working machine that promptly expands, parts 49-turbine suction port, parts 50-high-pressure gas branched pipe.

Embodiment describes in further detail the present invention below in conjunction with accompanying drawing and embodiment.

Among Fig. 1, the annular groove in the circular cylinder body 1 is uncovered, the uncovered interior ring side that is selected in groove in the mode of execution, and annular groove is the operational site of cylinder 1.Center centration axis 2 and working medium are set on the cylinder 1 simultaneously import and export 4,5.

Among Fig. 2, the axial coaxial parallel of the annular groove open-mouth of cylinder 1 is shown rotary sealing ring 6a, 6b, 6c, 6d, 6e, make to form airtight annular cavity type in the cylinder 1, described seal ring 6a, 6b, 6c, 6d, 6e and airtight annular cavity type have same revolution shaft axis.

Among Fig. 3, annulus section piston 3a, 3b, 3c press annular cavity type in ring cylinder 1 circumferential ring has matching surface to be clearance seal or Sealing sealing state to distribution with cavity wall.

Among Fig. 4, annulus section piston 3a is fixedlyed connected with rotary sealing ring 6a, 6e and is integral, and constituting one can be around the rotary piston assembly of seal ring shaft axis rotation.Deviate from seal ring 6a one side on the seal ring 6e and be provided with the cylindrical pin 8a that rolls, roll pin 8a place standard pitch circle and be provided with penetrating horse shoe shaped through hole 13a.

Among Fig. 5, annulus section piston 3b is fixedlyed connected with rotary sealing ring 6b, 6d and is integral, constitute another can be around the rotary piston assembly of seal ring shaft axis rotation.Deviate from seal ring 6b one side on the seal ring 6d and be provided with the cylindrical pin 8b that rolls, roll pin 8b place standard pitch circle and be provided with penetrating horse shoe shaped through hole 13b.

Among Fig. 6, annulus section piston 3c is fixedlyed connected with rotary sealing ring 6c and is integral, constitute another can be around the rotary piston assembly of seal ring shaft axis rotation.Seal ring 6c one side is provided with the cylindrical pin 8c that rolls.

Figure 13 is the structure diagram of each part combination among Fig. 1～Fig. 6.Among Figure 13, the revolution shaft axis of cylinder 1 is provided with centration axis 2, the axial coaxial parallel of the annular groove open-mouth of cylinder 1 is shown some rotary sealing ring 6a, 6b, 6c, 6d, 6e, make and form airtight annular cavity type in the cylinder 1, described some rotary sealing ring 6a, 6b, 6c, 6d, 6e and airtight annular cavity type cylinder 1 have same revolution shaft axis, annulus section piston 3a, 3b, 3c presses the circumferential ring in chamber to distribution in described annular cavity type, having matching surface to be clearance seal or Sealing sealing state and to fixedly connected with one or more rotary sealing rings respectively with cavity wall is integral, piston 3a is fixedly connected on revolving sleeve 6a, on the 6e, piston 3b is fixedly connected on revolving sleeve 6b, on the 6d, piston 3c is fixedly connected on the revolving sleeve 6c, constitutes a plurality of rotary pair rotary piston rotary piston assemblies that independently have.Be respectively arranged with working medium on cylinder 1 inwall and import and export 4,5, import and export 4,5 and all extend along the ring direction of cylinder.With the b point is the boundary.The aperture distribution of import and export 5 is b → a, and the aperture distribution of import and export 4 is b → c, and both opening shapes can be perforate on the outer rim side, also can be the fan annular aperture.Because the mechanism difference of transfiguration, the effect of described import and export 4,5 are also different.When mechanism as compressor with and turn to when running by shown in Figure 1, importing and exporting 5 be suction port, import and export 4 are relief opening; When mechanism as the expansion working machine time spent, by reverse running shown in Figure 1, importing and exporting 4 be suction port, import and export 5 are relief opening.

Figure 14,15 has the displacement-variable device sketch of guide-bar mechanism for the present invention.Among the figure, cylinder 1, frame 15 and bearing support 10 fixedly fuse, and centration axis 2 is fixed on cylinder 1 body.Depart from cylinder 1 shaft axis left side or the bearing 10 of right side one distance and be coaxially arranged with single-revolution axle (being live axle 11) by support 15 supports, in perpendicular to the plane of live axle 11, be that the center is the homogeneous radiation shape and is fixedly connected with three guide rod 9a, 9b, 9c that guiding groove is arranged on the live axle 11, become starlike with the shaft axis of live axle 11.Fixedly connected cylindrical of revolving sleeve 6e end face is rolled in the guiding groove that pin 8a is placed on guide rod 9a, fixedly connected cylindrical of revolving sleeve 6d end face is rolled in the guiding groove that pin 8b is placed on guide rod 9b, and fixedly connected cylindrical of revolving sleeve 6c end face is rolled in the guiding groove that pin 8c is placed on guide rod 9c.Thereby, the annulus section piston in the ring cylinder by the rotary sealing ring on the described one link to each other with guide-bar mechanism respectively, the guide rod of guide-bar mechanism is radial and fixedlys connected with live axle 11, live axle 11 departs from cylinder 1 shaft axis one apart from formation transfiguration linking mechanism.Described guide rod also can or have the sheave of guiding groove for the polished rod guide rod, and the guide rod kink of this moment slide block, and a groove on guide rod or the sheave or a bar only are provided with one and roll pin or a slide block.Described pin or the slide block kink of rolling can slide along the groove of guide rod or guide rod or the groove of guide groove wheel on the revolution guide rod or in the guide groove of guide groove wheel, and the pin-and-hole of described slide block or bearing pin cooperate with the pin shaft hole that rolls pin 8a, 8b, 8c or slide block of revolving sleeve end face respectively.Live axle 11 is the public axle of each guide rod, and input or the power output that is used as power is used.There are the guide rod or the sheave of guiding groove to comprise guiding groove and 28 two members of guide rod; The axis parallel that rolls pin 8a, 8b, 8c turns round shaft axis in cylinder, near guide-bar mechanism one side or middle seal ring be provided with penetrating slotted eye 13a, 13b make roll pin 8a, 8b, 8c passes.Live axle 11 shaft axiss, roll all parallel and cylinder 1 shaft axis in pin center or slide block bearing pin or pin-and-hole center line and be offset to cylinder 1 shaft axis and roll the pin center or guide rod slide block pin-and-hole or slider pin shaft centre line between, make guide rod force bearing point arm of force length produce cyclically-varying, thereby the inhomogeneous in the form of a ring circumferential spacing of rotary piston is distributed with the rotation of guide rod live axle 11.Inner chamber in the airtight annular cavity type between adjacent pistons is mechanism acting cylinder working room, because any position pressure equalization in the same cylinder, so acting on the active force of adjacent pistons end face also just equates, but adjacent pistons place rotating guide stress action spot arm of force length is all inequality basically, the long place of arm of force guide rod has big relatively moment, thereby the running torque that produces.The groove number of guide rod or sheave is consistent with the rotary piston number and be more than 2 or 2, is advisable with 3.

Figure 16, the 17th carries out motion analysis to mechanism.Parts 25 are represented the fixed component of guide-bar mechanism among the figure, are combined by cylinder 1, frame 15, bearing support 10 and centration axis 2; Parts 26 are represented the crank of guide-bar mechanism, and what crank length equaled the rotary sealing ring rolls the pin center of circle turning radius, roll pin 8a, 8b, the 8c center of circle is guide-bar mechanism crank 26 revolving point; The guide rod of parts 28 representative organizations, the revolution guide rod is formed guide rod 28 members; Pin 8a, 8b, 8c or slide block 14 roll in parts 24 representative organizations, point A representative roll the bearing pin of pin or slide block 24 or pin-and-hole axle center, gyration center that some B represent crank 26, put C and represent the guide rod gyration center, α represents the angle of 25 of guide rod 28 and fixed components, and β is the angle of 25 of crank 26 and fixed components.The long AB of crank 26 bars immobilizes, and center B rotation is changeed in wraparound, but two revolving point of A, B are arranged; Fixedly the long BC length of the bar of structure bar 25 also immobilizes, and transfixion; Slide block 24 both can wraparound change central point A rotation, also can linearly walk up and down along guide rod 28; Round 29 is that slide block 24 fulcrum posts or revolution pin-and-hole gyration center point A change the trajectory that forms when center C moves in a circle with guide rod 28 wraparounds, is a standard round in the center of circle with gyration center point B in fact exactly.Gyration center C to revolving point A be the active force brachium of guide rod 28, but wraparound changes that center C is rotated and change and elongated or shorten with corner α.When α=0 °, the arm of force is the shortest, is line segment CD, the intersection point the when elongation line of live axle 11 revolution axial connecting lines is pointed in D point representative circle 29 and cylinder 1 revolution axle center; When α=180 °, the arm of force is the longest, is line segment CE, the intersection point the when elongation line of cylinders 1 revolution axial connecting line is pointed in E point representative circle 29 and live axle 11 revolution axle center; When α changed between 0 °～180 °, guide rod 28 active force brachiums changed between CD length and CE length.Described guide-bar mechanism is the guide-bar mechanism that rotating guide or sheave are arranged, and corner β and corner α have following relation: $\mathrm{\β}=\arccos [l{\sin }^2\mathrm{\α}+\cos \mathrm{\α}\sqrt{(R^2-l^2{\sin }^2\mathrm{\α})}]/R,$ (0≤α≤180 °, "  " the expression extraction of square root, be radicand in " () " of its back or " () ").The derivation of relation is as follows:

If the bar of crank 26 is long to be R, the active force brachium of guide rod 28 is r, and the bar of fixed component 25 is long to be l, can get according to triangle cosine law formula:

①R ²＝r ²+l ²-2rlcos(180°-α)

＝r ²+l ²+2rlcosα ---------------------------------------------(1)

②r ²＝R ²+l ²-2Rlcosβ ---------------------------------------------(2)

$r=\sqrt{({\mathrm{<figure-callout\; id="2"\; label="R"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">R</figure-callout>}}^2+{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^{2}2\mathrm{Rl}\cos \mathrm{\&beta;})}---\left(3\right)$

Formula (2), formula (3) substitution formula (1) can be got:

${\mathrm{<figure-callout\; id="2"\; label="R"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">R</figure-callout>}}^2={\mathrm{<figure-callout\; id="2"\; label="R"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">R</figure-callout>}}^2+l^2-2\mathrm{Rl}\cos \mathrm{\&beta;}+{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2+2l\cos \mathrm{\&alpha;}\sqrt{({\mathrm{<figure-callout\; id="2"\; label="R"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">R</figure-callout>}}^2+l^2-2\mathrm{Rl}\cos \mathrm{\&beta;})}---\left(4\right)$

Simplify arrangement formula (4), can get:

$\cos \mathrm{\&alpha;}\sqrt{({\mathrm{<figure-callout\; id="2"\; label="R"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">R</figure-callout>}}^2+l^2-2\mathrm{Rl}\cos \mathrm{\&beta;})}=R\cos \mathrm{\&beta;}-l---\left(5\right)$

Formula (5) both sides simultaneously square can get (note, may produce extraneous root):

cos ²α(R ²+l ²-2Rlcosβ)＝R ²cos ²β-2Rlcosβ+l ²?--------------------------(6)

Arrangement formula (6) can get:

R ²cos ²β-2Rlsin ²αcosβ-R ²cos ²α+l ²sin ²α＝0--------------------------(7)

Can try to achieve with equation:

$\cos \mathrm{\&beta;}=[2\mathrm{<figure-callout\; id="2"\; label="Rl\; sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">Rl</figure-callout>}{\sin }^{}{}^2\mathrm{\&alpha;}\&PlusMinus;\sqrt{(4R^2{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2{\sin }^4\mathrm{\&alpha;}+4{\mathrm{<figure-callout\; id="2"\; label="R"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">R</figure-callout>}}^2{\mathrm{<figure-callout\; id="2"\; label="cos"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">cos</figure-callout>}}^2\mathrm{\&alpha;}-4R^2{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&alpha;})}]/2{\mathrm{<figure-callout\; id="2"\; label="R"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">R</figure-callout>}}^2$

$=[\mathrm{<figure-callout\; id="2"\; label="l\; sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}{\sin }^{}{}^2\mathrm{\&alpha;}\&PlusMinus;\sqrt{({\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2{\sin }^4\mathrm{\&alpha;}+{\mathrm{<figure-callout\; id="2"\; label="R"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">R</figure-callout>}}^2{\mathrm{<figure-callout\; id="2"\; label="cos"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">cos</figure-callout>}}^2\mathrm{\&alpha;}-{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&alpha;})}]/R$

$=[\mathrm{<figure-callout\; id="2"\; label="l\; sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}{\sin }^{}{}^2\mathrm{\&alpha;}\&PlusMinus;\sqrt{({\mathrm{<figure-callout\; id="2"\; label="R"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">R</figure-callout>}}^2{\mathrm{<figure-callout\; id="2"\; label="cos"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">cos</figure-callout>}}^2\mathrm{\&alpha;}-{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&alpha;}{\mathrm{<figure-callout\; id="2"\; label="cos"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">cos</figure-callout>}}^2\mathrm{\&alpha;})}]/R$

$=[\mathrm{<figure-callout\; id="2"\; label="l\; sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}{\sin }^{}{}^2\mathrm{\&alpha;}\&PlusMinus;\cos \mathrm{\&alpha;}\sqrt{(R^2-{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&alpha;})}]/R---\left(8\right)$

Remove extraneous root, can get:

Thus, can derive guide rod 28 acting force arm formula according to triangle cosine law formula again:

${\mathrm{<figure-callout\; id="2"\; label="r"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">r</figure-callout>}}^2=R^2{l}^2-2\mathrm{Rl}\cos \mathrm{\&beta;}$

$={\mathrm{<figure-callout\; id="2"\; label="R"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">R</figure-callout>}}^2+l^2-2\mathrm{Rl}[\mathrm{<figure-callout\; id="2"\; label="l\; sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}{\sin }^{}{}^2\mathrm{\&alpha;}+\cos \mathrm{\&alpha;}\sqrt{(R^2-{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&alpha;})}]/R$

$={\mathrm{<figure-callout\; id="2"\; label="R"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">R</figure-callout>}}^2+l^2-2l[\mathrm{<figure-callout\; id="2"\; label="l\; sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}{\sin }^{}{}^2\mathrm{\&alpha;}+\cos \mathrm{\&alpha;}\sqrt{(R^2-{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&alpha;})}]$

$={\mathrm{<figure-callout\; id="2"\; label="R"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">R</figure-callout>}}^2+l^2-2{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&alpha;}-2l\cos \mathrm{\&alpha;}\sqrt{(R^2-{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&alpha;})}---\left(10\right)$

Extraction of square root can get:

$r=\&PlusMinus;\sqrt{[{\mathrm{<figure-callout\; id="2"\; label="R"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">R</figure-callout>}}^2+l^2-2{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&alpha;}-2l\cos \mathrm{\&alpha;}\sqrt{(R^2-{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&alpha;})}]}---\left(11\right)$

The r value can not be negative, casts out negative value, can get:

$r=\sqrt{[{\mathrm{<figure-callout\; id="2"\; label="R"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">R</figure-callout>}}^2+l^2-2{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&alpha;}-2l\cos \mathrm{\&alpha;}\sqrt{(R^2-{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&alpha;})}]}---\left(12\right)$

Because each piston action power F not exclusively becomes 90 ° (promptly vertical) to act on the arm of force of guide rod 28, real useful effect power should be its component F1, or obtains the useful effect arm of force rcos γ formula of guide rod 28, all can derive identical opplied moment.Useful effect arm of force formula at this guide rod 28 of only deriving.According to arm of force formula as can be known, the useful effect arm of force of guide rod 28 is AC*cos γ (being rcos γ), and the derivation of equation is as follows:

According to triangle cosine law formula, can get:

l ²＝r ²+R ²-2Rrcosγ ------------------------------------(13)

Arrangement formula (13) can get:

rcosγ＝(r ²+R ²-l2)/2R ---------------------------------(14)

With formula (10) substitution formula (14), can get the useful effect arm of force relation of guide rod 28:

$r\cos \mathrm{\&gamma;}=[{\mathrm{<figure-callout\; id="2"\; label="R"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">R</figure-callout>}}^2+{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2\mathrm{<figure-callout\; id="2"\; label="cos"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">cos</figure-callout>}2\mathrm{\&alpha;}-2l\cos \mathrm{\&alpha;}\sqrt{(R^2-{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&alpha;})}+R^2-l^2]/2R$

$=[{\mathrm{<figure-callout\; id="2"\; label="R"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">R</figure-callout>}}^2+l^2-2{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&alpha;}-2l\cos \mathrm{\&alpha;}\sqrt{(R^2-{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&alpha;})}+R^2-l^2]/2R$

$=[R^2-{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&alpha;}-l\cos \mathrm{\&alpha;}\sqrt{(R^2-{\mathrm{<figure-callout\; id="2"\; label="l"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">l</figure-callout>}}^2{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&alpha;})}]/R---\left(15\right)$

According to the relation of formula (9), formula (12), formula (15), depict Figure 18, Figure 19, Figure 20, Figure 21 plotted curve respectively with the computer drawing tools.

Among Figure 18, corner α value is the independent variable coordinate, and corner β value is the functional value coordinate.Curve 30 clearly demonstrates corner α variation tendency of corner β value during even variation between 0 °～360 °.When α at the uniform velocity increases between 0 °～50 °, the flat line that curve is comparatively smooth, β value amplification is little, illustrates that piston rotation is comparatively slow in guide rod uniform rotation process; When α changes between 50 °～130 °, curve becomes sharply and is bent upwards, it is big that β value amplification sharply becomes, explanation is in guide rod uniform rotation process, and the piston rotating speed becomes when sharply quickening α changes between 130 °～230 °, and curve becomes the straight line section, the β value at the uniform velocity increases, illustrate that guide rod is tending towards the uniform rotation process, the piston rotation speed change is little, and is keeping high rotating speed; When α changed between 230 °～310 °, curve became slowly and is bent upwards, and β value amplification sharply diminishes, and illustrates that guide rod is tending towards the uniform rotation process again, and the piston rotating speed becomes and sharply slows down; When α changes between 310 °～360 °, the flat line that curve becomes comparatively smooth, β value amplification is little, illustrates that in guide rod uniform rotation process, piston rotation tends to be steady substantially but be comparatively slow, and returns to the state of α in the time of 0 ° again.This feature helps us and utilizes piston to be carved with different rotating speeds when difference, forms a different spacing that changes with the guide rod corner between adjacent two-piston, produces the working room of different volume size.Help making the transfiguration process control of mechanism in airtight space, to be carried out, greatly improve the energy conversion efficiency of the compression ratio of mechanism and the acting of expanding.Concerning gas compressor or pressurization device, can be designed to air-breathing end with when two adjacent piston space spacings are maximum, begin pressurization, when two adjacent piston space spacing minimums are zero, are designed to compression and finish, begin to withdraw from from the zone of high pressure; Pilot process, piston space continue to carry out interior compression, until sending into the zone of high pressure.Concerning the expansion working machine, can be when when two adjacent piston space spacing minimums being zero, be designed to high-pressure gas or have pressure can working medium enter, begin the acting of expanding; When two adjacent piston space spacings are maximum, are designed to expand and finish beginning exhaust or discharging; Pilot process, piston space continue to carry out interior expansion, comprise external acting.The mechanism of this gearless driving does not have the reciprocating member motion fully.

Among Figure 19, corner α value is the independent variable coordinate, and the long r value of the guide rod arm of force is the functional value coordinate.R representative organization crank is long, and the fixed component of l representative organization is long.The situation of change of curve 31 clearly demonstrates corner α when changing between 0 °～180 ° long r of the guide rod arm of force.When α increased between 0 °～60 °, curve was comparatively smooth, and β value amplification is little, illustrated in the guide rod uniform rotation process, and it is comparatively slow increased by arm of force brachium; When α increased between 60 °～150 °, curve was precipitous, and r value amplification becomes and sharply becomes big, illustrated in the guide rod uniform rotation process, and guide rod is become by the arm of force brachium speed of rising sharply to accelerate; When α increased between 150 °～180 °, it is comparatively straight that curve becomes again, and r value amplification is little, is tending towards flat-top substantially, illustrates in guide rod uniform rotation process, and guide rod is slowed down by arm of force brachium growth rate to be tending towards stopping, and reaches the longest.This feature helps us and converts the uniform circular motion of guide rod to approach rotary-piston even speed change circular movement, help obtaining the very high high-voltage power supply of pressure in mechanism, also help the opplied moment that active force that high-temperature high-pressure fuel gas differs greatly pressure in the inflation process in carrying out converts equilibrium to and export in the expansion working machine as power with balanced dynamic action.

Among Figure 20, corner α value is the independent variable coordinate, and the effective force brachium rcos γ value of guide rod is the functional value coordinate.R representative organization crank is long, and the fixed component of l representative organization is long.The situation of change of guide rod effective force brachium rcos γ value that curve 32 clearly demonstrates corner α when changing between 0 °～180 °.When α increased between 0 °～50 °, curve was quite smooth, and β value amplification is very little, illustrated in the guide rod uniform rotation process, and effectively arm of force brachium does not have to change substantially; When α increased between 50 °～110 °, curve became comparatively rapidly, precipitous, and rcos γ value amplification becomes and sharply becomes big, illustrate in the guide rod uniform rotation process, and effective arm of force brachium becomes sharply elongated; When α increased between 110 °～155 °, it is very precipitous that curve becomes, and keeping same growth rate, and rcos γ value amplification sharply increases, and illustrates in the guide rod uniform rotation process, and effectively arm of force brachium becomes sharply elongated; When α increased between 155 °～180 °, it is comparatively straight that curve becomes again, and r value amplification is little, is tending towards flat-top substantially, illustrates in the guide rod uniform rotation process, and effectively the arm of force brachium speed of rising is slowed down and is tending towards stopping, and reaches the longest arm of force.Need to prove that the acting cylinder internal pressure between adjacent pistons equates the active force that adjacent pistons produces respectively, but turning effort moment direction is opposite.Among this figure, the plotted curve that curve 32 changes with corner α for the effective force brachium of a certain guide rod, the plotted curve that curve 33 changes with corner α for the effective force brachium of the guide rod that lags behind 120 ° of this guide rods.Can find out clearly that from Figure 20 when corner α changed between 60 °～240 °, the effective force brachium of curve 32 was all the time greater than the effective force brachium of curve 33, promptly power moment is all the time greater than resistance torque, thereby the running torque that can produce.

Among Figure 21, corner α value is the independent variable coordinate, and the guide rod arm of force is long to be the functional value coordinate.R representative organization crank is long, and the fixed component of l representative organization is long.The long situation of change of the guide rod arm of force when between 0 °～180 °, changing that curve 31,32 clearly demonstrates corner α.By contrast, be not difficult to find out that the α value is when 0 °, 180 ° two special positions, it all is the same with the guide rod useful effect arm of force that guide rod is subjected to arm of force brachium, but when changing between 0 °～180 °, the long growth rate of the useful effect arm of force lags behind the long growth rate of the arm of force.

Figure 22 is the change curve of adjacent pistons spacing angle Δ β, must treat that the relevant derivation of equation of back is finished rear analysis open to discussion.

Figure 23～Figure 34 is the piston process chart of 2 piston to 6 pistons and six kinds of mechanisms of 8 pistons being drawn out by two kinds of particular cases of the guide-bar mechanism principle that rotating guide is arranged with the computer drawing tools.A kind of be have one or two piston roll on the elongation line that pin just in time is positioned at annular cylinder revolution shaft axis and live axle shaft axis line the time, a kind of is when two adjacent pistons being arranged just in time symmetry being positioned on the elongation line of annular cylinder revolution shaft axis sensing live axle shaft axis line.More than the process chart of six kinds of pistons a common trait is arranged, their per two adjacent pistons when just in time symmetry is positioned on the elongation line that annular cylinder revolution shaft axis points to live axle shaft axis line between the adjacent both ends face spacing be zero.

Roll pin gyration center or the fulcrum post gyration center of adjacent pistons place assembly is symmetrically distributed in cylinder 1 gyration center the adjacent face of described piston coincide each other when pointing to the both sides of live axle 11 gyration center directions, spacing is zero in the displacement-variable device, working medium is imported and exported 4,5 and is distributed in the matching surface both sides, and promptly the matching surface both sides are working medium zone of high pressure and low pressure area separatrix.It is the circumferential direction extending circumferentially of starting point along cylinder with described separatrix respectively that working medium is imported and exported 4,5 openings.For gas compressor or pressurization device, can be understood as piston and just finish to calm the anger or pressurized operation, for the expansion working machine, can be understood as just in time be high-pressure gas or have pressure can working medium just begun to enter cylinder.The adjacent pistons place is rolled the pin center and is symmetrically distributed in that annular cylinder revolution shaft axis coincide between the adjacent pistons end face when pointing to the elongation line of live axle shaft axis line and spacing is zero, plane, matching surface place is the watershed of zone of high pressure and atmospheric area or low pressure area, and this point is very crucial.The anastomosis is imported and exported by high pressure can be set on the casing wall of high pressure side, imports and exports by low pressure can be set on normal pressure side or the low voltage side casing wall.Low pressure is imported and exported opening and be may extend to two adjacent pistons and be symmetrically distributed in live axle shaft axis position by the low voltage side piston end surface when pointing to the elongation line both sides of annular cylinder revolution shaft axis line; The elongation of high pressure import and export opening is decided on mechanical compression ratio, should be less than or equal to the extended length that low pressure is imported and exported opening, imports and exports the big or small compression ratio or the expansion ratio that can select gas compressor or decompressor easily of extension distribution of opening by regulating high pressure.Compression ratio is 1 during liquid refrigerant work.Adjacent two-piston just in time be symmetrically distributed in annular cylinder revolution shaft axis when pointing to the elongation line both sides of live axle shaft axis line piston end surface contact, spacing be zero, for compressor or pressure unit, just be that last cycle compression work finishes, back air-breathing beginning of one-period, for the expansion working machine, just for last cycle exhaust finishes, back one-period combustion gas begins to enter; Adjacent two-piston just in time is symmetrically distributed in elongation line both sides, piston space spacing that the live axle shaft axis points to annular cylinder revolution shaft axis line for maximum, for compressor, just for the compression beginning, for the expansion working machine, just begins for exhaust.Among Figure 16, Figure 17, when the just in time symmetrical elongation line spacing that is positioned at annular cylinder revolution shaft axis sensing live axle shaft axis line of the adjacent two-piston of 3 piston mechanisms is zero, be positioned on high-tension side that piston place guide rod and become 60 ° of angles with elongation line, be that initial angle is 60 °, and be positioned at that piston place guide rod of normal pressure side or low voltage side and the aforementioned elongation line 60 ° of angles that lagged behind, promptly initial angle is-60 °.According to aforementioned relation (9) and Figure 18 corner beta curve tendency as can be known, along with guide rod turning axle corner α value continues to increase, the corner of two-piston also can increase (supposing to rotate by direction as shown) simultaneously, but it is fast that the velocity ratio that is positioned on high-tension side that piston corner quickening is positioned at that piston of normal pressure side, thereby along with guide rod is rotated further, spacing between this adjacent pistons is increasing, increases to 180 ° of time sides up to guide rod turning axle corner α value and stops to increase.At this moment, described two adjacent piston spaces are apart from also reaching maximum.By above analysis, utilize aforementioned relation (9), can derive 3 piston mechanism adjacent pistons spacing angle Δ β formula: $\mathrm{\&Delta;\&beta;}=\arccos \{1(1+2{\cos }^2\mathrm{\&alpha;}+\sqrt{3}\sin 2\mathrm{\&alpha;})/4R+(\cos \mathrm{\&alpha;}-\sqrt{3}\sin \mathrm{\&alpha;})$

$\sqrt{[R^2-l^2(l+2{\mathrm{<figure-callout\; id="2"\; label="cos"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">cos</figure-callout>}}^2\mathrm{\&alpha;}+\sqrt{3}\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}2\mathrm{\&alpha;})]}/4R\}-\arccos \{l({\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&alpha;}+3{\mathrm{<figure-callout\; id="2"\; label="cos"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">cos</figure-callout>}}^2\mathrm{\&alpha;}-\sqrt{3}\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}2\mathrm{\&alpha;})/4R+$

$(\cos \mathrm{\&alpha;}+\sqrt{3}\sin \mathrm{\&alpha;})\sqrt{[R^2-l^2(l+2{\mathrm{<figure-callout\; id="2"\; label="cos"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">cos</figure-callout>}}^2\mathrm{\&alpha;}-\sqrt{3}\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}2\mathrm{\&alpha;})]}/4R\}-2\arccos [(6+\sqrt{3}/10)].$

Derivation is as follows:

If the bar of crank 26 length is R, the bar of fixed component 25 is long to be l, l: R=0.8: 1, and it is β that the high pressure side piston assembly rolls pin center to cylinder revolution shaft axis line and live axle shaft axis to the angle that cylinder turns round the shaft axis line _{+ 60}, it is β that normal pressure side piston assembly rolls pin center to cylinder revolution shaft axis line and live axle shaft axis to the angle that cylinder turns round the shaft axis line _-60, half piston circumference angle is β ₆₀, the angular bisector corner of angle between the guide rod that α is with adjacent pistons links to each other.Can get according to aforementioned relation (9):

$=\arccos \{l{(\sin \mathrm{\&alpha;}+\sqrt{3}\cos \mathrm{\&alpha;})}^2/4R+(\cos \mathrm{\&alpha;}-\sqrt{3}\sin \mathrm{\&alpha;})\sqrt{[R^2-l^2({\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&alpha;}+3{\mathrm{<figure-callout\; id="2"\; label="cos"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">cos</figure-callout>}}^2\mathrm{\&alpha;}+\sqrt{3}\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}2\mathrm{\&alpha;})]}/R\}$

$=\arccos \{l(l+2{\mathrm{<figure-callout\; id="2"\; label="cos"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">cos</figure-callout>}}^2\mathrm{\&alpha;}-\sqrt{3}\sin \mathrm{\&alpha;})/4R+(\cos \mathrm{\&alpha;}-\sqrt{3}\sin \mathrm{\&alpha;})\sqrt{[R^2-l^2(l+2{\mathrm{<figure-callout\; id="2"\; label="cos"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">cos</figure-callout>}}^2\mathrm{\&alpha;}+\sqrt{3}\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}2\mathrm{\&alpha;})]}/4R\}---\left(16\right)$

$=\arccos \{l{(\sin \mathrm{\&alpha;}-\sqrt{3}\cos \mathrm{\&alpha;})}^2/4R+(\cos \mathrm{\&alpha;}+\sqrt{3}\sin \mathrm{\&alpha;})\sqrt{[R^2-l^2({\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&alpha;}+3{\mathrm{<figure-callout\; id="2"\; label="cos"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">cos</figure-callout>}}^2\mathrm{\&alpha;}-\sqrt{3}\sin \mathrm{\&alpha;})]}/R\}$

$=\arccos \{l(l+2{\mathrm{<figure-callout\; id="2"\; label="cos"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">cos</figure-callout>}}^2\mathrm{\&alpha;}-\sqrt{3}\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}2\mathrm{\&alpha;})/4R+(\cos \mathrm{\&alpha;}+\sqrt{3}\sin \mathrm{\&alpha;})\sqrt{[R^2-l^2(l+2{\mathrm{<figure-callout\; id="2"\; label="cos"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">cos</figure-callout>}}^2\mathrm{\&alpha;}-\sqrt{3}\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}2\mathrm{\&alpha;})]}/4R\}---\left(17\right)$

$=\arccos [(6+\sqrt{3})/10]$

Δβ＝β ₊₆₀-β _-60-2β ₆₀

$=\arccos \{l(l+2{\mathrm{<figure-callout\; id="2"\; label="cos"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">cos</figure-callout>}}^2\mathrm{\&alpha;}+\sqrt{3}\sin \mathrm{\&alpha;})/4R+(\cos \mathrm{\&alpha;}-\sqrt{3}\sin \mathrm{\&alpha;})\sqrt{[R^2-l^2(l+2{\mathrm{<figure-callout\; id="2"\; label="cos"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">cos</figure-callout>}}^2\mathrm{\&alpha;}+\sqrt{3}\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}2\mathrm{\&alpha;})]}$

$/4R\}-\arccos \{l({\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2+3{\mathrm{<figure-callout\; id="2"\; label="cos"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">cos</figure-callout>}}^2\mathrm{\&alpha;}-\sqrt{3}\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}2\mathrm{\&alpha;})/4R+(\cos \mathrm{\&alpha;}+\sqrt{3}\sin \mathrm{\&alpha;})$

$\sqrt{[R^2-l^2(l+2{\mathrm{<figure-callout\; id="2"\; label="cos"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">cos</figure-callout>}}^2\mathrm{\&alpha;}-\sqrt{3}\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="A20051012113600211.png,A20051012113600212.png"\; state="\{\{state\}\}">sin</figure-callout>}2\mathrm{\&alpha;})]}/4R\}-2\arccos [(6+\sqrt{3})/10]---\left(16\right)$

According to formula (16), make following chart and plotted curve with computer tabulating method and auxiliary graphing method.

The corner parameter list
													Sequence number	α(°)	l	?R	β60°	sinα	sinα^2	?cosα	cosα^2	sin2α	β+60°	β-60°	Δβ(°)
1	5	80	?100	0.28	0.09	0.008	?0.996	0.9924	0.174	0.323	0.2453	0.290821
													2	10	80	?100	0.28	0.17	0.03	?0.985	0.9698	0.342	0.371	0.213	1.170189
3	15	80	?100	0.28	0.26	0.067	?0.9166	0.933	0.5	0.426	0.1841	2.657015

From the tabulation and Figure 22 as can be seen, when α=20 °, Δ β=4.776862 °, when α=30 °, Δ β=10.99928 ° are when α=120 °, Δ β=131.5613 °, when α=180 °, Δ β=175.4148 °, curve 34 has shown the situation that spacing angle Δ β value changes with guide rod corner α between adjacent pistons.What should be specifically noted that a bit is exactly, we can utilize tabulation and Δ β change curve to find and piston space end face angle when angle or expansion working machine end high-pressure gas enter clutch release slave cylinder between the slave cylinder piston end face when determining compression in the end of gas compressor or pressurization device (enter the pressurized gas that obtain in the hyperbaric chamber this moment), have promptly determined the compression ratio or the expansion ratio of gas compressor, pressurization device or expansion working machine.As select Δ β=175.4148 ° for gas compressor finish in compression and piston end surface angle when entering the high-pressure air that obtains in the hyperbaric chamber, then compression ratio is (175.4148 ° ÷ 175.4148 °)=1, as select Δ β=10.99928 °, then compression ratio is (175.4148 ° ÷ 10.99928 °)=15.948, as select Δ β=4.776862 °, then compression ratio is (175.4148 ° ÷ 4.776862 °)=36.721, as select Δ β=2.657015 °, then compression ratio is (175.4148 ° ÷ 2.657015 °)=66.0195 as selects Δ β=1.170189 °, and then compression ratio is (175.4148 ° ÷ 1.170189 °)=150.7575.When compression ratio was, the rotary piston displacement-variable device can be used for liquid kind transfiguration machinery, as water pump, water turbine etc.Spacing between adjacent two-piston is the compression cylinder or the expansion cylinder of mechanism of the present invention, the variation of cylinder volume and the linear variation relation of piston space circular arc spacing, research and analyse piston space circular arc spacing Changing Pattern, also just be equal to the Changing Pattern of having researched and analysed volume of cylinder.The Changing Pattern of three parameters of volume pressure temperature of working medium is same as the prior art in the cylinder, all repeats no more at this.

The quantity of piston is more than 2 or 2 in annular cylinder, is advisable with 3.Because in the time of 3, displacement-variable device has better simply structure and the highest compression ratio, still has good stationarity simultaneously.The hoop length sum of all pistons always less than the hoop girth of cylinder 1 itself, makes piston space that enough free backswing activity spaces can be arranged.Though because in the turning course, all pistons are all turning to rotation towards same, but, each piston is having under the guide-bar mechanism interlock of rotating guide, its spot speed changes with the position, makes a certain piston may bigger spacing be arranged with adjacent vanes or piston in a certain position, but may less spacing be arranged with adjacent blades or piston in the another location, even can be together adjacent, spacing is zero.Should to account for how many ratios of full annular cylinder girth be suitable for the annulus circumferential lengths sum of all pistons in the annular cylinder, needs to calculate or test could be determined through strict; But the revolution of the adjacent face of adjacent pistons is drawn close together and must be fitted like a glove each other, can be space curved surface or plane, preferably selects planar end surface for use, because the plane easily processes, easily ensures the quality of products and precision.Described cylinder 1 inwall, adjacent pistons end face and revolving sleeve surface three are encircled into the transfiguration working room of mechanism jointly.In sum, realize that it is with the distolateral guide-bar mechanism that is connected to of revolving sleeve 6c, 6d, the 6e of described rotary piston that piston space has different rotating speeds, sometimes fast and sometimes slow way, forms the guide-bar mechanism with rotating guide.

Figure 35～Figure 44 has showed the part working state of piston 3a when guide rod turns over 360 ° in the 3a piston variable volume compressor structure scheme.Piston 3a place guide rod is in normal pressure or low-pressure state when turning between 0 °～60 °; When guide rod turned between 60 °～180 °, piston 3a was in the suction state; When guide rod turned between 180 °～360 °, a piston 3a and a back piston were formed compression cylinder the working medium that sucks in are compressed, and comprise interior compression.In fact, each piston all is double-acting, and in other words, each piston is in rear end suction process, and its front end is compressing the working medium that previous piston sucks in previous piston simultaneously.Each piston withdraws from the process from the zone of high pressure at front end, and its rear end is still being carried out compression work with a back piston to the working medium that sucks in.

Among Figure 45, the compressed air outlet 42 of gas compressor 41 links to each other with the air inlet of burner 43, the high-temperature high-pressure fuel gas outlet of burner 43 links to each other with the suction port 44 of expansion working machine 45, fresh air enters from the suction port 46 of gas compressor 41, expansion working machine 45 tail gas is after hours discharged from the relief opening 47 of expansion working machine, gas compressor 41 and expansion working machine 45 all adopt the stepless displacement-variable device of oscillating piston, but mechanism is opposite.Gas compressor 41 is used for pressurized air, expansion working machine 45 be used for discharging high-temperature high-pressure fuel gas pressure can and heat energy produces operation power and power is exported.

With Figure 45 contrast, have more a turbine 48 among Figure 46.The high-temperature high-pressure fuel gas that burner produces was supplied gas to expansion working machine 45 and turbine 48 respectively by trident connecting tube 50.The high-temperature high-pressure fuel gas outlet that is burner 43 is except that with the suction port 44 of expansion working machine 45 links to each other, and many one links to each other with the suction port 49 of turbine 48 with high-pressure gas branched pipe 51, to turbine 48 supplying high temperature high-pressure gas.In fact, gas compressor 41 can adopt a cover, also can adopt many cover oscillating piston displacement-variable devices, is advisable to adopt a cover; Expansion working machine 45 can adopt a cover, also can adopt many cover oscillating piston displacement-variable devices, is advisable to adopt two covers, and two expansion working machines are set, for gas compressor required drive and power output are equipped with the working machine that independently expands respectively.When increasing, external loading cause power output expansion working machine rotating speed to reduce, when the gas consumption of power output expansion working machine reduces, have more a part of combustion gas and distribute to the expansion working machine of gas compressor automatically, thereby strengthen the driving source of gas compressor, after gas compressor power increased, the gas compressor rotating speed was improved, gas compressor air total amount and delivery pressure have been strengthened, increase the driving source of power output conversely again, increased the ability that overcomes load, contained mechanical further deceleration; When reducing to cause power output expansion working machine rotating speed, improves external loading, the gas consumption of power output expansion working machine increases, the combustion gas of expansion working machine of distributing to gas compressor is then less, gas compressor power diminishes, the corresponding reduction of gas compressor rotating speed, corresponding minimizing of gas compressor gas production and delivery pressure and reduction, reduced to offer the pressure of power output conversely, reduced ability to the load acting, contained mechanical further raising speed, motor is remained under the situation of identical throttle size, all the time can autobalance on a certain suitable rotating speed.If because go up a slope, slack-off being not suitable for of the speed of a motor vehicle needs, and the driver is as long as further open the throttle, need not painstakingly go gear shift,, both save the expensive automatic device of dialling as there being one to dial in work automatically, and for example fast, fuel-efficient with manually dialling the same dynamic response, and be difficult for dead fire.

From above analysis and each figure as can be seen, exactly because the cylinder inner carrier all turns round periodically changing with different speed all the time, every revolution produces a circulation for 360 °, make rotary piston that big spacing at a time may be arranged with adjacent piston, but constantly may less spacing be arranged with adjacent pistons at another, even can be together adjacent, spacing is zero, make described annulus section piston periodically change rotation from fast to slow again from slow to fast with the rotation of live axle 11, make ring segment piston 3a, 3b, annulus section cavity internal volume between the 3c changes to large period ground to little by zero again to zero with live axle 11 rotations are descending, form and suck, compression or expansion, discharge the working room, make us can successfully utilize these pistons in stepless transfiguration mode atmospheric air to be compressed effectively gently, send into the zone of high pressure, send into burner, utilize the adjacent pistons spacing to be zero again, make the piston of finishing the function of calming the anger in the zone of high pressure successfully retire from office out from the zone of high pressure, do not produce interior leakage, working efficiency is improved significantly.Air-breathing repeatedly, compression, air-breathing, recompression again, low-pressure gas enters from the compressor air inlet machine mouth, and pressurized gas are discharged from relief opening, realize that gas boosts; Expansion repeatedly, exhaust, expansion, exhaust more again, pressurized gas enter from expansion working machine suction port, and tail gas is discharged from relief opening, realizes the expansion acting or carries out wind-power electricity generation, hydroelectric power etc.As more can complete display in the three-dimensional artificial motion model of making of ProENGINEER computer graphics Software tool finding out the simulation work situation of whole volume-variation mechanism, the objectivity place that more can realize above analysis intuitively.

Whole invention novel structure, working pressure height, discharge capacity is big, the efficient height, mechanical operation is steady, and skill is strong, practical, energy-saving effect is remarkable, easily processing, and cost is low, greatly improved simultaneously the compressor stage pressure ratio and expanded that to discharge working machine be the energy conversion efficiency of turbine, reached and improved compressor, decompressor, water turbine, steam turbine, wind-force and solar thermal power generation machine, Reciprocating engine, greatly improve the purpose of gas combustion engine operation performance.

Claims (10)

1. rotary type capacity variable mechanism, the cylinder [1] that comprises annular groove, some annulus section piston [3a, 3b, 3c] and some rotary sealing ring [6a, 6b, 6c, 6d, 6e], the axial coaxial parallel of the annular groove open-mouth of cylinder [1] is shown some rotary sealing ring [6a, 6b, 6c, 6d, 6e] make and form airtight annular cavity type in the cylinder [1], described some rotary sealing ring [6a, 6b, 6c, 6d, 6e] with airtight annular cavity type same revolution shaft axis is arranged, some annulus section piston [3a, 3b, 3c] in described annular cavity type, press the circumferential ring in chamber to distribution, have matching surface to be clearance seal or Sealing sealing state with cavity wall and fixedly connected with one or more rotary sealing rings respectively be integral constitute some can be around the rotary piston assembly of seal ring shaft axis rotation, cylinder [1] inwall is provided with working medium and imports and exports [4,5], it is characterized in that, described annulus section piston links to each other with some guide-bar mechanisms respectively by the seal ring on the described one, the guide rod of described guide-bar mechanism [14] is radial and fixedlys connected with live axle [11], live axle [11] departs from cylinder [1] shaft axis one distance and constitutes linking mechanism, make described annulus section piston [3a, 3b, 3c] with the rotation periodically variation rotation from slow to fast again from fast to slow of live axle [11], make ring segment piston [3a, 3b, 3c] between annulus section cavity internal volume rotate with live axle [11] and descendingly change to large period ground to little by zero again to zero, form and suck, compression or expansion, discharge the working room.

2. according to the described rotary type capacity variable mechanism of claim 1, it is characterized in that, described annulus section piston [3a, 3b, 3c] link to each other with guide-bar mechanism respectively by a seal ring on the described one respectively, described linking mechanism makes described annulus section piston [3a, 3b, 3c] respectively with periodically changing rotation once from slow to fast again from fast to slow in each circumgyration scope of live axle [11] rotation, make ring segment piston [3a, 3b, 3c] between annulus section cavity internal volume each circumgyration scope of rotating with live axle [11] in descending to zero again by zero to little to the variation of large period ground once, form and suck, compression or expansion, discharge the working room once.

3. according to claim 1 or 2 described rotary type capacity variable mechanisms, it is characterized in that described guide-bar mechanism is the guide-bar mechanism that the revolution guide rod is arranged.

4. according to claim 1 or 2 described rotary type capacity variable mechanisms, it is characterized in that described guide-bar mechanism is the guide-bar mechanism that guiding groove revolution guide rod is arranged.

5. according to claim 1 or 2 described rotary type capacity variable mechanisms, it is characterized in that described guide-bar mechanism is the guide-bar mechanism that the revolution sheave is arranged.

6. according to claim 3 or 4 or 5 described rotary type capacity variable mechanisms, it is characterized in that, described guide-bar mechanism by fixed component [25], crank [26], roll pin [24] or slide block, guiding groove or guide rod [28] and constitute; Cylinder body [12], frame [15], bearing support [10] are formed the fixed component [25] of guide-bar mechanism, rotary sealing ring ring radius is formed crank [26], rotary sealing ring [6a, 6b, 6c, 6d, 6e] end face is respectively arranged with and rolls pin [8a, 8b, 8c] or fulcrum post, roll crank [26] revolving point that pin [8a, 8b, 8c] axle center is a guide-bar mechanism, the revolution guide rod is formed guide rod [28] member, has the guide rod of guiding groove or sheave to comprise guiding groove and [28] two members of guide rod; The axis parallel that rolls pin [8a, 8b, 8c] turns round shaft axis in cylinder, is provided with penetrating slotted eye [16a, 16b] near guide-bar mechanism one side or middle seal ring and makes and roll pin [8a, 8b, 8c] and pass; Frame [15] is provided with bearing support [10], the parallel live axle [11] of placing on the center line in the seat hole; The groove of described revolution guide rod [9a, 9b, 9c] or sheave is the homogeneous radiation shape and distributes; A groove on guide rod or the sheave [12] or a bar only are provided with one and roll a pin or a slide block [14], described pin or slide block [14] kink of rolling can slide along the groove of guide rod or guide rod or the groove of guide groove wheel on the revolution guide rod or in the guide groove of guide groove wheel [12], the pin-and-hole of described slide block or bearing pin respectively with the revolving sleeve end face roll pin [8a, 8b, 8c] or the pin shaft hole of slide block cooperates, the groove number of guide rod or sheave is consistent with the rotary piston number and be more than 2 or 2, is advisable with 3; The variation of piston corner meets relation: $\mathrm{\&beta;}=\arccos ({1\sin }^2\mathrm{\&alpha;}+\cos \mathrm{\&alpha;}\sqrt{(R^2-1^2{\sin }^2\mathrm{\&alpha;})})/R.$

7. according to the described rotary type capacity variable mechanism of claim 1, it is characterized in that, adjacent pistons place assembly roll pin gyration center or fulcrum post gyration center be symmetrically distributed in cylinder [1] gyration center when pointing to the both sides of live axle [11] gyration center direction the adjacent face of described piston coincide each other, spacing is zero, described working medium imports and exports [4,5] be distributed in the matching surface both sides, the matching surface both sides are working medium zone of high pressure and low pressure area separatrix, working medium imports and exports [4,5] opening is the circumferential direction extending circumferentially of starting point along cylinder with described separatrix respectively, the opening that low pressure is imported and exported may extend to two adjacent pistons and is symmetrically distributed in the position of leaning on the low voltage side piston end surface when live axle shaft axis sensing cylinder [1] turns round the elongation line both sides of shaft axis line, the elongation of high pressure import and export opening is decided on mechanical compression ratio, should be less than or equal to the extended length that low pressure is imported and exported opening.

8. according to the described rotary type capacity variable mechanism of claim 7, it is characterized in that described compression ratio is 1 or greater than 1, compression ratio is 1 during liquid refrigerant work.

9. rotary piston engine of implementing the described rotary type capacity variable mechanism of claim 1, comprise gas compressor [41], burner [43] and expansion working machine [45], the compressed air outlet [42] of described gas compressor [41] is connected with burner [43] air inlet, the high temperature of burner [43], the high-pressure gas outlet is connected with the suction port of expansion working machine [45], it is characterized in that, described gas compressor [41] and expansion working machine [45] have all adopted described rotary type capacity variable mechanism, the rotary type capacity variable mechanism of gas compressor [41] makes atmosphere gas, boost by compression, the rotary type capacity variable mechanism of expansion working machine makes the high temperature and high pressure gas acting of externally expanding, step-down.

10. according to the described rotary piston engine of claim 9, it is characterized in that described gas compressor [41] adopts a cover or the above rotary piston displacement-variable device of cover, is advisable with a cover; Described expansion working machine adopts a cover or the above rotary type capacity variable mechanism of cover, is advisable with two covers, and wherein a cover is used for the drive pressure mechanism of qi, and a cover is used for outside outputting power.

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