DE3301726A1 - Heat engines with continuous or intermittent heat supply and improvements in thermodynamic cyclical processes for heat and power generation made possible by them - Google Patents

Abstract

Published without abstract.

Description

Heat engines with continuous or intermittent heat supply and thermodynamic improvements possible through them Circular processes in heat and power generation.

The invention relates to heat engines with continuous or intermittent heat supply and through it possible improvements thermodynamically he cycle processes in heat and Power generation.

A compressible fluid is used in one or more compressors compressed and thereby heated. Then it is brought into a room, where it can be further processed through combustion or heat exchangers Heat is supplied. In one or more prime movers, the pressurized fluid is expanded to atmospheric pressure.

It is characteristic of the machine systems that machines for compression and relaxation or between compression machines and combustion chamber or between combustion chamber and expansion machines are used, which, if desired, allow isochoric, isobaric or mixed isochoric and isobaric heat supply or removal in the ideal process, and are arranged in this way can that in the combustion chamber a continuous flow arises even with different Gasmengendurchsät zen constant or only slightly changing speeds.
Another designation is that for heat engines with

continuous or intermittent heat supply in one,

Heat exchangers connected between two expansion machines emit the working medium and the heat energy obtained in this way Thermal energy to heat up another medium? or the working medium is used in front of the combustion chamber.

Various designs are known as heat engines with internal continuous heat supply (IKV machines) and a gas as the working medium.
The most well-known and widespread design is the gas turbine. Gas turbines have a continuous gas flow

flow through the combustion chamber, but have the disadvantage that COPY

between two two turbo machines exclusively isobaric heat supply is possible (see EPA application 82100616). Isochore or mixed heat input, however, has a better thermodynamic effect Effectiveness.

Other machine arrangements are also known in which the heat supply can theoretically be selected as desired (EPA - Application 82100616, EPA - Application 82103232.3, Bri talus machine from: Osenga, Mj And now the Bri talus; Diesel Progress North American, Jan. 1982). A common disadvantage of such machine systems, however, is that the supply and / or discharge of the working gas into and out of the combustion chamber takes place discontinuously. The resulting pressure losses largely consume the advantages of the better thermodynamic process.
Another disadvantage of heat engines with internal continuous combustion (TKV machines) is that they are poorly suited for changing outputs. This is mainly due to the fact that there must be an almost constant gas velocity at the burner, so that the power can only be regulated poorly via the gas flow rate and therefore has to be done largely via the maximum temperature of the process. The thermodynamic efficiency depends strongly on the level of the maximum temperature of the process. ^ -

The invention aims to provide a remedy here. The invention as it is characterized enables isochoric, isobaric or mixed heat supply at will and enables a continuous gas flow through the combustion chamber, whereby the gas velocity at the burner can be kept almost constant even with different gas throughputs by changing the compression.
Rotary piston machines with angular or offset axes are known (for example German patent laid-open specification No. 26 55 649, EPA application 82 103 232.3). 2 shows the perspective view of two angular-axis rotary pistons. Two rotary pistons (10a, 10b) with sectors with a large radius (11a, 11b) and with sectors with a small radius (12a, 12b) are arranged in relation to one another in such a way that the sectors with a large radius (11a) of one piston (10a) pass through move the sectors of small radius (12b) of the other piston (10b) and vice versa.

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Figure 3 shows the movement of the large piston sectors (11a, 11b) as a projection of one or two wheel arch surfaces in a plane. The rotary pistons are surrounded by a housing (20) so that the large radius sectors (11a, 11b) move in a channel (13a, 13b) formed by the housing and piston and the channels of the two pistons intersect. In front of the intersection (14) of the two channels, spaces (= pressure spaces) (15a, 15b) are created that are made smaller, and behind the intersection spaces (= suction spaces 16a, 16b) that are enlarged. The front (17a, 17b) and the end effective surfaces (1Ca, 18b) of the pistons are bevelled so that the piston sectors can be moved without mutual hindrance (same piston speed), but the channel crossing remains closed except for a narrow gap.
As can be seen, the sum of the increases in the areas behind the intersection in a unit of time is constant (= moving both piston sectors (11a, 11b) in the direction of movement by the length I). The same applies to the areas in front of the intersection. If the rooms behind the intersection are permanently open to the same room via channels (22a, 22b) and if the rooms (15a, 15b) in front of the intersection are permanently open to the same room via channels (21a, 21b), a room is created in one room

uninterrupted suction, in the other room uninterrupted pressure. /

In claim 1 protection is sought for the fact that the suction chambers (16a, 16b) of a machine acting in this way is behind the combustion chamber an IKV machine, <= odass a continuous one to the combustion chamber Suction acts as required in the combustion chamber through the ratio of supply volume per unit of time / discharge volume per unit of time • Isochoric, isobaric or mixed isochoric-isobaric heat supply achieved can be; be placed.

In claim 2 protection is sought for the fact that the pressure chambers (ICa, 15b) of such an acting machine are placed in front of the combustion chamber of an I KV machine, so that a continuous pressure acts on the combustion chamber.
Fig. 1 shows an approach on which the global patent concept is based

35 order of several such machines.

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Several angular-axis rotary piston machines are arranged in such a way that a machine (51) draws in and compresses air from outside (50) or also only transported into a room (52) that is not open to the atmosphere (= no use of turbo machines). This room (52) can be a heat exchanger or just a short pipe section. A second machine (53) (which satisfies claim 2 or is just a turbo machine) sucks the air from this space (52) and conveys it absolutely continuously into dip combustion chamber (54). The pressurized flue gas flows from there likewise continuously in a third machine (55) (which satisfies claim 1) and arrives in a further room (56). the end In this space (56) the pressurized flue gas flows into two expansion machines (57, 58), one of which (57) is the first compressor machine (51) drives, the other (58) drives a generator (59) or another work machine or a vehicle.

The machines (53) and (55) (machine combination A) are through, for example a shaft (60) connected so that there is a constant speed ratio and thus a constant ratio of the flow rate results in (= specific volume in (55) / specific volume in (53)). Likewise have the machines (51) and (57) (= machine combination B) have a constant speed ratio.

The machine combination A should have a constant speed. This can e.g. controlled by valves (61, 62). If the speed becomes too low, valve (61) opens. This reduces the pressure behind the machine

(55) and rises in front of (53). The same result can be achieved with a valve which connects the space in front of and behind the machine (55). If the speed becomes too high, valve (62) opens. Then the pressure falls in front of (55) and rises behind (53).
Of course, the machine combination A can also be rotated by a constantly running machine or the speed can be kept constant in some other way.

The speed of machine combination B depends on the pressure in room (56). However, it cannot turn with unlimited speed, otherwise the pressure in space (52) rises too much and brakes.

On the one hand, this arrangement enables a continuous gas flow through the combustion chamber (as shown above), it allows

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but also a constant gas velocity at the burner, as will be shown briefly. Similar effects are obtained with MBT gas turbines observed where decreasing compression at low power also keeps the gas velocity at the burner almost constant.

Let U ₁ = speed of machine combination B

U_ = speed of machine _{combination AV 1} = throughput volume of the machine (51) per revolution

V «= throughput volume of the machine (53) per revolution 10

In space (52) gas of volume U ₁ -V _{1 is} supplied and gas of volume Up · V _{2 is} discharged. The following applies to the compression £:

β = (U ₁ - V ₁ V (U ₂ - V ₂ ) = U ₁ · constant The amount of gas flowing in is': m =? · U ₁ -V ₁ kg The continuity equation applies to the burner cross-section: mv = A «c with m = flowing gas mass in kg / sec

v = 1 / ($ £) m / kg = specific volume at the burner A = cross-sectional area on the burner in kg c = gas velocity on the burner in m / sec g = specific weight of the intake air in kg / m Then

c ^ '(mv) / A = (^ U ₁ -V ₁ -U ₂ -V ₂ V (JU ₁ -V ₁ -A) = (U ₃ V ₃ ) / A Da U ₂ , V _2. and A are constant, c is also constant.

You can also choose the ratio of the heat supply in the combustion chamber as desired. Because the isobaric magnification factor

W = (spez.Vol.hinter the Brennk.) / (Spez.Vol.vor the Brennk) can be prepared by the throughput volume p.Umdrehung V of the machine (53) and V ₄ of the machine (55) which are set ψ (^ = V ₄ A ^ o) -

Angle-axis rotary piston machines are special for such systems suitable because the volume throughput and the level of compression or relaxation vary regardless of the speed can be.

Fig.4 and Fig.5 show an embodiment of such devices. Fig.5 is again an illustration of the lying on two annular surfaces

OOU I / ΔΌ

Parts in one plane, Fig. 4 represents the section along the line O-O in Fig. 5.

The device behind the intersection (30,36,38) is used to regulate the volume of a fluid discharged from a space (56) by moving the slide (36). If the amount of gas being fed into the space (56) is constant and if the channel (38) is the only discharge option from the space (56), the pressure in the space (56) can be regulated via the slide (36). If there are several discharge options from the space (56), the slide (36) can be used to vary the proportion of the total amount of gas flowing out of the space (56) that flows out through the channel (39). However, the amount of gas supplied in (56) can also be changed indirectly by changing the pressure in (56).
The regulation can be done as follows, for example: At the level of the inner segment outer surface there are straps (30) which have openings at the level of the piston front surface (17b). If the front edge (31) of this opening slides over the channel (38), the suction space (16a) is opened to space (56). Between the belt (30) and the channel (38) there is a slide (36) which also seals the channel against the suction chamber. The space (56) thus remains open to the suction space until the rear belt opening edge (32) slides over the front slide edge (40). This closes the channel off again from the suction wheel. By moving the slide edge (40) it can be determined at which suction space volume the separation of suction space (16a) and space (56) takes place.

It is also possible to use slides (42) to influence the extent to which the compressible material is compressible Fluid in the machine is expanded. The suction space (16a) opens to space (64) exactly when the rear edge (44) of the Piston back surface (13a) moved past the slide edge (43). Even here, by moving the edge (43), the suction space volume can be varied when opening to space (64).

Likewise, the level of compaction can be varied by a device (33, 37, 39) in front of the intersection.
Here, too, is a band (33) with openings on the piston side. A slide (37) is again located between the band (33) and the channel opening (^). The pressure space (15a) is only opened to space (52) when the front

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whose belt edge (34) moves past the slide edge (41). Even here the opening volume can be adjusted by moving the slide edge (41) of the pressure space (15a) to space (52) can be changed.

Instead of the slide solution, the pressure space (15a) can also be opened to space (52) with the aid of a valve (39). The valve opens when the pressure in the pressure space (15a) is greater than that in the space (52) is.

Likewise, instead of the slide solution (42), a valve (45) can be used in the suction chamber (16a) open to space (64) when the pressure in (64) is greater than is in the suction chamber.

Another measure for angular rotary piston machines Fir the protection is sought (claim 11) serves to reduce the gap losses.

The systems described are primarily intended for larger capacities. In order to keep the plants small, for large air flow high speeds be possible for the sliding Some seals cannot be used. In addition to labyrinth seals, the following measures enable the gap losses to be reduced.

Are one or more compression or expansion machines with the same speed and with the same throughput volume (see Fig. 1 machine combination (53) - (5S)) or with different Throughput volume (see. Fig. 1 machine combination (51) - (57)), then the two or more intersections with three or more rotary lobes designed so (Fig.6 and Fig.7) that at least one piston (80) two or more channels (83, 84) of other pistons (81, 82) intersects. With machine combination B, the different throughput volumes must be adjusted with slide valves or valves, as shown above, be managed.

The special feature of the invention is that you can connect the channels to the different rooms in such a way that at an intersection as many as possible (ideally all four) openings to rooms are the same or similar Pressure.

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-I ₂ -.

Fig. 7 shows a possible solution for the machine combination A (B in brackets).

upper intersection suction chamber pressure chamber

Vertical channel from 52 (50) to 56 (64)

Horizontal channel from 52 (50) to 54 (52)

lower intersection

Senkr. Channel from 54 (56) to 54 (52)

Horizontal channel from 54 (56) to 56 (64)

To find an even better arrangement, in which only Rooms with high pressure or rooms with low pressure are in contact with an intersection and? O the gap losses are negligibly small in Fig. B a modified angular-axis rotary piston machine is provided, in which the two outer pistons (81, 82) function exclusively as shut-off parts.

Fig. 8 shows their channel image in the plane. As you can see, the The upper intersection of the suction chamber (16o) and the pressure chamber (15o) are only open to the atmosphere (50,64), so there are no gap losses there. At the lower intersection, the suction space (16 u) is opened to space (56), in which there is high pressure, which is the pressure space (15 u) Opened to space (52) in which the final compression pressure prevails. The only gap losses that can arise at the intersection exist in that from the space (56) gas flows into the space (52) and flows through the combustion chamber again. But that goes with the expended Only a fraction of the compression and heat energy is lost. To allow a reasonably steady flow / nuts at least two such arrangements work offset from one another.

If you want a favorable arrangement for very large air flow rates reach, this is also the case with the piston arrangements of Fig. 8 * and Fig. 9 possible.

Fig. 30 shows the principle of the arrangement. Each piston transports a Fluid in two directions (up - down / down - up or right? -Link = / left right?). This creates two in the arrangement shown

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closed, oppositely traversed cycles that always collide in the piston intersections. Since there is always a transport from a high-pressure room to a low-pressure room (Expansion) or from a room of low pressure to a room of high pressure (compression), a cycle consists of the individual steps low - high, high - low, low-high, high

If you place the two circuits so that the points of contact are always high or are always low, there are also very little gap losses.

Fig. 9 shows the two cycles, which consist of individual steps high (h) low (n) and low (n) - high (h) exist. The eight intersections (K1 - K8) are arranged, for example, so that at the odd intersections Exclusively high pressure pressure and suction spaces and at the straight intersections only low pressure pressure and suction spaces meet.

With the machines shown, all are thermodynamic cycle processes possible, which can also be achieved with gas turbine systems and, in addition, all variations that instead of purely isobaric heat supply or removal in the process also have isochoric or mixed isochoric and isobaric heat supply and removal in any ratio.

In addition , however, a cycle or variations of this cycle can also be implemented for which protection is also sought. These cycle processes can also be implemented with gas turbine systems with isobaric heat supply. The systems described above are particularly suitable because they are suitable for different heat supplies and for small outputs.
Fig. 10 shows an I KV machine for whose circuit protection is also sought.

As in conventional IKV machines with a heat exchanger behind the turbine, air is sucked in, compressed in one or more compressors (150), in a heat exchanger (151) (only in Altern. IuLII '. ~) Of the combustion chamber (152) to the maximum temperature heated up, possibly

already in a first heat exchanger (153) behind the combustion chamber down to a temperature permissible in front of the expansion machine

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cooled, whereby a medium to be heated is heated (e.g. the Steam generator of a steam power plant) (alternative III and IV) and then in at least two expansion stages (154,155) back to the Intake pressure expands.

The difference to conventional I KV machines with heat exchangers is that the flue gas does not expand until it reaches the suction pressure gives off its residual heat to the compressed gas (alternative I and III), but already between two expansion machines when it himself is still under pressure.

The other way is {alternative II and IV) that the heat exchanger (151) heats another medium between the two expansion stages (154, 155) and such an IKV machine is used exclusively or partially as a heater.
The main advantage of this process design lies in the fact that the heat exchangers can be kept smaller and thus considerably larger, with at least the same thermal efficiency. This is due, on the one hand, to the fact that the heat transfer coefficient of a compressed gas is higher than that of a relaxed one (see Dietzel, F .; Gasturbinen; Vogelr Verlag, Würzburg 1974; p.108, chapter 5.3.3), and on the other hand, it is also because that a significantly lower temperature gradient has to be processed in the heat exchanger (cf. Fig. 12). Fig. 11 and Fig. 12 show the p, V - and T,? - Diagrams of the ideal process for power generation (alternative I and III) with exclusively isobaric heat supply or removal. Mean:

1 - 2 adiabatic compression

2-3 isobaric heat supply in the heat exchanger (151) 3-4 isobaric heat supply in the combustion chamber (152) (Alt.III) 4-5 isobaric heat dissipation in the heat exchanger (153)

4-6

p. ^ Fradiabatic relaxation in expansion machine (154)

ο - ο

fi 7

₆ * ~ -isobaric heat dissipation in the heat exchanger (151)

7-8 adiabatic relaxation in expansion machine (155) 8 - Ί isobaric heat dissipation in the atmosphere The circular process 1 -2 "-3"-4-5'-6'-1 shown in dashed lines in the T, s diagram corresponds to a conventional ideal process Heat exchange

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shear behind the expansion machines.

In the example shown, the work capacity and the efficiency of both ideal processes are the same. As you can see, however, in the conventional process the heat gradient 5 ^X - G ' has to be removed via the heat exchanger, in the new process only the heat gradient 6-7 or 6 * - 7.

In the conventional Joule process, the heat exchanger has an efficiency of

7th - ^{1 K} ' ^1/1 V

Ώ ".. = suction temperature
T ₄ ; = maximum temperature
JC = pressure ratio
K = isentropic exponent
(See Cietzel, F .; gas turbines; ... p.24, chapter 1.5.1) For the new ideal process with an ideal heat exchanger, good (Altern. I> (T. = temperature at point i)

T ₇ ZT ₈

Because (T ₂ = T ₇ ): T ₄ -JTTgZT ₁ ) .Tq = C

The heat energy supplied is Q. = c (T ₄ - T ₃ ), the heat energy removed is Q = c (T ₅₃ -T ₁ ).
The following applies to the efficiency:

7th = CQ _1n - Q _from y Q _in =

= C Cp (T ₄ - T ₃ ) -.c _p (T ₈ - T ₁ ) V (Cp (T ₄ - T ₃ )) = = 1 -CT ₈ -T ₁ ) Z (T ₄ -T ₃ ) =

= 1 - T ₁ (T ₈ ZT ₁ - 1) Z (T ₃ T ₈ ZT ₁ - T ₃ ) =

This means that the efficiency of the process can be increased with any compression be kept very high. As you can see, however, a good degree of efficiency is at the expense of work capacity. With the arrangement of the heat exchanger for which protection is desired, a process can, however, be much cheaper than with previous arrangements design with - inexpensive heat exchangers,

- high efficiency,

- still favorable work ability, especially when mixed instead of exclusively isobaric or isochoric heat supply is realized.

Another possibility to use this process with an IHV machine, for which protection is also desired, is the heating of a medium, the temperature of which should be considerably higher than the intake temperature T _{1 of} the air.

This is the case, for example, in heating systems, where the water comes from the radiators should be heated from the high return temperature to the even higher flow temperature and the outside temperature is much lower. There is also the possibility of a sensible use in steam power plants or in melting processes.

The circuit i. «= T is shown in FIG. 10 in the alternative that the compressed air does not flow through the heat exchanger (151), but directly from the compressor (150) into the combustion chamber (152). Behind the combustion chamber, a heat exchanger (153) can heat up a medium and thereby cool the flue gases to a lower temperature in front of the 1st expansion machine (alternative IV). In alternative II, the flue gas flows directly from the combustion chamber (152) into the 1 .Expansionsmaschine (154), where it is expanded to a pressure Ij significantly above atmospheric pressure. The heat dissipated in the 2nd heat exchanger (151) is used to heat a medium to be heated, for example the heating water or the steam generator or feed water preheater of a steam turbine or the air blown in during melting processes. 13 and 14 show the p, V and T, s diagrams of heat engines with isobaric heat supply and removal, which are used exclusively for heat generation.

The cycle runs analogously to that shown in Fig. 11 and Fig. 12, only that here the pressurized flue gas in the 2nd heat exchanger

* ") PV

is cooled below the compression end temperature and then relaxed. This means that when the pressure is released to the suction pressure (ρ =

ans

Line? - 2 'in the T, s diagram) is the temperature at the end of the process less than that at the beginning.

The new cycle for heating purposes runs automatically, i.e. without any external input of work, when the one on the right Area 2-3-4-5-2 is equal to 1 -5-6-7-1 on the left.

For comparison, the "cyclic process" of the conventional Heizpro process is shown in dashed lines, in which air is brought to the burner in a more or less isobaric manner, where it is heated isobarically (1 "- 2 ')» then passed to heat exchanger surfaces (2' - 3 " ) and finally is discharged through the chimney.

With the same heating output ((4 - 6) = (2 '- 3 ")), the old process the heat (1 - 2 ') is supplied, but with the new one only the heat C 2 - 3).

In addition, there are significantly smaller and therefore cheaper heat exchanger surfaces needed because

- the heat transfer coefficients of compressed gases are higher than those of uncompressed (see above)

- the speeds at which the hot gases sweep past the heat exchanger surfaces through the machine construction can be set, but the heat transfer coefficient is almost linear with the Gas velocities increase (see e.g. Kuchling, H.j

Pocket b. d.Physics; Verl. H. Deutsch: Thun / Ffm 1970 p.615) Fig. 15 shows that the throughput of a machine (51) from the outside Air sucked in at constant speed can also be changed by placing a slide (48) in the duct side. The printing room (15a) is closed from the atmosphere when the front surface edge is (47) moved past the slide edge (49). By moving this edge (49) you can see the pressure space volume at the end change from the atmosphere and thus the amount of air brought into space (52).

This means that air throughput and performance can also be achieved at a high maximum temperature and steady gas flow at constant speed are varied at a constant speed of the four machines (51, 53, 55.57).

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Claims (1)

I ... ν ■ Thermal machine assembly with separate compressor (51, 53) and expansions! *? - τΐίϊΛ. (55,57,58) and intermediate chamber (54), in which a compressible fluid is continuously or intermittently supplied with heat, characterized, that behind the chamber (54) a machine (55) with this (54) opening, enlarging to a certain volume and then closing off the chamber (54) spaces (16a, 16b), in which the compressible fluid from the chamber (54) is discharged, works in such a way that a continuous flow is generated from the chamber (54) and the discharge volume per unit of time can be controlled ₍ and a machine (53) operates in front of the chamber (54), the supply volume of which can be controlled per unit of time, and thus the relation of discharge volume to supply volume per unit of time can be chosen so that isochoric, isobaric or mixed isochoric-isobaric heat supply as desired can be made in the chamber (54). I.
2. A machine system characterized under claim 1, additionally characterized in that that in front of the chamber (54) in which the working medium is supplied with heat a machine (53) is used, with the help of which a continuous gas flow into the combustion chamber is possible, and which is either a turbo-engine or which operates so that one space (15a, 15b) in the engine (53) is in another Chamber (50,52) is filled with a compressible fluid, then opened to chamber (54), then reduced in size and thereby its (15a, 15b) contents are pressed into chamber (54), then again from this chamber (54) and finished to the chamber (50,52) is geöT ^c net and then is increased again, and is thereby filled with the compressible fluid. s "" ilags thereby additionally gekfennzew. '-met, that the machine (53) in front of and the machine (55) behind the chamber (54) are interconnected so that the relation of the volume of the working medium supplied to that of the discharged Working medium remains constant. 4. One characterized under one or more of claims 1-3 Machine system or another IKV machine, additionally marked that depending on the flow rate of the compressed Fluids the compression £ in the (150) or the (51, 53) compressors is changed so that there is a constant speed in the chamber (152,54) with a constant cross-sectional area of the compressible fluid results. 5. One characterized under one or more of claims 1-4 Machine system, additionally characterized in that in front of the room (152,54), in which heat is supplied to the compressible fluid, two machines work, of which the first (51) e ": KomDressible? Fluid is sucked in and compressed or transported uncompacted into a space (52) and its throughput volume varies per unit of time and the second (53) has a constant volume flow rate per unit of time from space (52) to space (54). 6. A machine system characterized under claim 5, additionally characterized by that the machine in front of (53) and that behind (55) of the chamber (54) are connected to one another and have constant speed and the speed control is done by valves (61, 62) that increase the accelerating pressure and lower the braking pressure or increase the braking pressure and decrease the accelerating pressure or the speed control is carried out by a constantly rotating machine or some other measure. MAD ORIGINAL
COPY ^7th ί | Ί ^! : j: i "f '. ir, c-. ·:'! ι •"»'Je, ¹ ' · ^r ; i ·:. ·; . '' •• '• rc. ·' Rl =, - · - tv on'ε · '.' : ·! "■ .- '-' Ί - marked machinery, additionally characterized in that one or more angular-axis rotary piston machines are used in front of (53) or behind (55) the chamber (54) _{and in front of and in front of} (54). 8. One characterized under one or more of claims 1-7 Machinery, characterized to-ätzlich, that one or more winkelachsige rotary piston engine to Luftan eyes ^c and compressing (51) or as an expansion machine or as (57,58) both? be used. 9. An angular-axis rotary piston machine with which a fluid is made sucked into one room and transported to another room, or an angular-axis rotary piston machine with the one compressible Fluid is to be sucked in from one room, compressed and transported to another room, characterized, that by adjustable slide (37, 4B) or valves (39) in the housing the throughput quantity and / or the throughput volume from one room to the other varies independently of the rotation rate within limits can be or d-e compression of a compressible fluid in the machine can be varied while the machine is running or both. 10.A winkelachsige Rotationskolbenma ^c chine with the sucked-a komores fible = fluid from a space in which Ma chine and expands into another room to be ported a tear oll = ^c, 'characterized in that since <3 through adjustable slides (36, 42) or valves (45) in the housing the intake volume can be varied independently of the speed and / or relaxation in the machine while the machine is running can be varied. BAD ORIGINAL COPY • "■. I ι'It- Wl ^r ik £: l & C_ h ^:. ICK {--'- Οίο 'ιΤ;' Ί * 7-» · »ϋ." »· Γ ^Γ '.i." »- "rC» t -'- "- · / * - 'Vi .ij ·'';.·"."- ^f ..n' -re jkoU'r .. ι from: .wfc. or rne'ir cndst-ei gesc.niLi.en and with the compressible =. Fluid is to be transported both from rooms of low pressure? to rooms of high pressure and from rooms of high pressure to rooms of low pressure, characterized in that that the openings of the channels to the different rooms = o are arranged so that as many or only rooms of similar height as possible over the column formed in an intersection or low pressure. 12. A heat engine with internal continuous combustion (I KV machine) and at least two expansion machines, in which the flue gases continuously from the combustion chamber (152) flow into the first expansion machine (154), characterized, that between two expansion machines (154,155) that still pressurized flue gas heat in a heat exchanger (151) to the compressed fluid in front of the combustion chamber (152) or to a medium to be heated. 13.A machine characterized under claim 12, additionally characterized in that
that one or more of the machines which are characterized under one or more of claims 1-11 are used. 14. A machine characterized under claim 12 or 13, additionally characterized by that they also or exclusively for heating a heat carrier = is used, the temperature of which is above the temperature of the intake air ^ and / or for the discharge of cooling air. 15. A machine characterized under patent claims 12, 13 or 14, additionally characterized by that between the combustion chamber and 1. ExoanFi.on = machine da = working medium heats a heat carrier in a heat exchanger (153). BATH ORIGINAL OPY