DE2308832A1 - HEATING AND COOLING DEVICE WITH ROTARY DRIVE - Google Patents

Description

PitofrtMw Dr. Ing.Walter Abltz Dr. Dieter F. Morf 22. ΓΕΟ. 1373

726V7370

E. I. DU PONT DE NEMORS AND COMPANY 10th and Market Streets, Wilmington, Del. I9898, V.St.A.

Heating and cooling device with rotary drive

The present invention relates to a heating and cooling device with a rotary drive and, in particular, to one with a Power machine equipped heating and cooling system, di «in a closed bankine cycle works and which has a condenser and evaporator, which with the Engine is coupled to the same as a unit to run around.

According to the present invention, the heating and cooling device with rotary drive has a cylindrical housing which rotates around its axis and a rotating engine in the housing, which has a coaxial rotatable drive element, which is operated by the engine, a condenser system, which rests coaxially on one side of the housing and rotates with the housing as a unit, and a refrigerant compressor, which is rotatably arranged coaxially in the housing

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and driven by the drive member at a first predetermined speed to generate the refrigerant vapors to compress in the housing, wherein the capacitor device arranged coaxially adjoining a housing side with revolves around the housing as a unit and serves to compressed To condense refrigerant from the compressor, a - refrigerant expansion device, which in the housing for expansion of the refrigerant condensed in the condenser system is arranged, a device for supplying condensed Refrigerant to the said refrigerant expansion device, one coaxially connected to the other side of the housing arranged evaporator, which rotates with the housing as a unit and refrigerant from the expansion device receives and evaporates, a device for returning evaporated refrigerant from the evaporator to the housing, and a Gear arrangement arranged in the housing, which lies between the drive element and the housing and for driving the housing, of the condenser. and the evaporator as a unit with a second predetermined speed is used, which is essential is less than the first predetermined speed of the drive element and the compressor.

The present invention provides a new heating and cooling device with rotary drive available, which has a compact, uniform design and is characterized by quiet operation and good efficiency. The device can be hermetically sealed and does not require high speed seals, around sections of the device that work with different pressures or with different fluids, to separate from each other. The device can either use its own refrigerant and working medium or a single fluid for both the engine and the cooling process. The device is suitable for generating electrical or other performance in addition to cooling or heating a fluid. The device according to the invention works with isentropic expansion of the refrigerant fluid, which leads to

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additional power supplied to balance the load on the compressor while also increasing the cooling capacity of the coolant.

The present invention is then based on an in the drawings illustrated embodiment explained; show it:

Fig. 1 is a diametric section through an inventive » device equipped with a rotating heat engine, in which different fluids are used as boiler operating fluid and as refrigerant,

Fig. 2 is a cross section along the line 2-2 of Fig. 1,

3 shows an enlarged vertical diametrical partial section by the rotating heat engine according to the present invention,

3a shows a partial section, which shows an individual structural feature represents the invention,

Fig. 4 is a partial cross-section along line 4-4 of B ¹ Xg. 3>

5 shows a cross section on a considerably reduced scale along the line 5-5 of, Fig. 3,

6 shows an enlarged vertical diametrical partial section through the central hub section of the rotating heat engine ,

7 is a schematic view taken along line 7-7 of FIG Fig. 6 of the transmission with constant transmission ratio,

8 shows an enlarged partial view, partly in section, which fix the non-rotating lubricant

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Feed line within the rotating at high speed Shows the sun gear of the transmission shown in Fig. 6 with a constant gear ratio,

9 is an enlarged partial view taken along line 9-9 of FIG.

Fig. 10 is a partial cross-section along the line 10-10 of Fig. 3,

FIG. 11 is a view similar to FIG. 3 showing an alternative Shows the condenser system for the boiler working fluid and the refrigerant

FIG. 12 shows a section along the line 12-12 of FIG. 11,

13 shows an enlarged partial view, partly in section along line 13-13 of Fig. 11,

FIG. 14 is a view similar to FIG. 3, but showing a modified one Represents embodiment of the present invention, in which the same fluid is used for the boiler working fluid and the refrigerant,

FIG. 14a shows an enlarged partial view, partly in section, of part of FIG. 14,

14b shows a view similar to FIG. 14a of another part of FIG. 14,

15 is a perspective view showing the inventive Device together with lines and valves for cooling or for air conditioning a building in summer or in a warm climate,

FIG. 16 shows an illustration similar to FIG. 15, from which the pipes and valves for heating a building in

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Winter or in a cold climate can be seen, and

FIG. 17 is a partial vertical section, similar to that of FIG. 3i which is a modified design and arrangement of the refrigerant expansion device represents.

The illustrated embodiment of a heating and cooling device provided with a rotary drive according to the present invention comprises a rotating machine working in a closed fiankine circuit, which has a boiler B., a working fluid expansion device PX and a condenser C ^, which with a refrigerant compressor P, a refrigerant expansion device HX and an evaporator E_ is coupled. The individual components are on a common Axis arranged, wdbei the condenser C_ and the evaporator E at an axial distance on opposite sides of the boiler B, the expansion device PX, the compressor P and the expansion device EX are arranged, which in a compact Design are arranged in between in a coaxial housing H. The boiler B_, the condenser C_ and the evaporator E_ are arranged as a unit for coaxial circulation. The working fluid expansion device PX is driven by the pressure working fluid generated by the boiler B at a predetermined speed and in turn drives the refrigerant compressor P and an internal gear with constant ratio, which is connected to the boiler-condenser-evaporator unit in order to drive the latter at a predetermined lower speed. The entire unit is hermetically sealed and a torque anchor locked by a pendulum! Γ is for that Gear provided. The ones with a closed hankine circle working machine is intended for use with high molecular weight fluids, according to one embodiment of the invention, which is sometimes referred to as a two-circuit system, Fluids with different high molecular weights can be used for the boiler fluid and the refrigerant. In

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a second embodiment of the invention, which sometimes is referred to as a gap system, the same high molecular weight fluid is used for both the boiler working fluid and as a refrigerant.

In the two-circuit design according to the present invention, which in the drawings and in particular in ü'lg. 3 shown is, the rotating tank B_ is formed in one piece with the coaxial machine housing H and comprises a cylindrical, annular chamber a, which surrounds the housing H and which by an outer continuous, circumferential Wall 2, through side walls 3 and 4 and an inner, continuous wall 5 is formed, the latter being the peripheral wall of the machine housing H. The outer one Circumferential wall 2 of the boiler is preferably, as shown, provided with circumferentially extending ribs 6, many the Increase the thermal conductivity of the wall; the wall 2 can instead be designed so that an enlarged thermally conductive Surface is obtained as described in U.S. Patent 3,690 (issued September 12, 1972).

In addition to the peripheral wall 5, the machine housing has H axially spaced side wall sections 7 and 8. The machine housing H and the boiler B are for Rotation about their common axis with the help of shaft sections 9 and 10, each coaxially from opposite Side walls 7 and 8 of the housing extend outward. The outer end of the shaft 9 is supported by means of a bearing 11 in a stationary hub 12, which is supported by radial spokes 13 is held by a concentric Ring 14 run radially inward, this Hing in turn from a support 15 on a stationary base 16 of the machine is held. Similarly, the outer end of the shaft 10 is rotatable by means of a bearing 17 held in a stationary ring 18 which is carried by radial spokes 19 extending from a concentric

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king 20 extend inwardly, which in turn is held by a support 21 on the f it dividing base of the machine, as best from iig. 1 and 9 can be seen. From the previous one Description it can be seen that the cylindrical boiler B and the machine housing H together with the shafts 9 and 10 form a unitary arrangement, which by means of bearings 11 and 17 for coaxial rotation as a unit is arranged around the machine axis.

The revolving boiler rotates around its axis with a predetermined one Speed, which is designed in such a way that the required centrifugal force arises to the selected Boiler working fluid evenly distributed around the circumference and in contact with the inner surface of the outer peripheral To keep wall of the boiler, * which is designated in Fig. 3 with i, the is stable to a high degree and is essentially cylindrical and concentric to the axis of rotation of the boiler. The boundary layer i. is essentially on a given radius away from the axis of rotation of the boiler, so that high boiler, heat flows in addition to those caused by gravity, can be obtained.

It gets to the i'ig. 2 and 3 are referred to. The ring-shaped one Liquids in the boiler can evaporate to the necessary boiling temperature, for example by heating a fuel-air mixture in a stationary Combustion chamber 22 is burned, which surrounds the circumferential boiler chamber 1. The one for the incineration required fuel comes from a nozzle 23 in the required amount and below the necessary. Pressure in the Combustion chamber 22, while the air required for mixing with the fuel through a number of openings 24 in the peripheral wall 25 is fed into the combustion chamber will. A hood assembly 26 defines a chamber 27 into which air via a line 28 with the pressure and in the iienge is introduced, which is necessary for the efficient combustion of the fuel

- 7 • whereby a liquid-da ^ f separating layer is formed,

material are required to heat the liquid in the kettle to the desired temperature. The combustion gases are discharged through an exhaust pipe 29, and a stationary transverse wall JO, which is adjacent to the boiler peripheral wall 2 is arranged, lies between the fuel nozzle 23 and the exhaust pipe 29 to circulate the combustion gases to control.

Within the machine housing H is an annular expansion device FX for the working fluid for rotation therewith, which as best from Pig. 6 as can be seen, has a central bore 31 which extends coaxially through the expansion device. The expansion device FX is coaxial fixed inside the machine housing H by means of a number of radially arranged blades 32, which inside of the housing K at the same circumferential distance from one another are arranged and which at their inner and outer bands are each connected to the expansion device FX and the wall 5 of the machine housing, for example by welding as in I'ig. 4 at 33 and 34 · indicated is.

It gets to the i'ig. 3 and 6 are referred to. The expansion device FX for the working fluid consists of a single-stage, jacketed turbine, which has a rotor 35 dit a series of turbine blades 37 which are arranged on the circumference of the rotor. The turbine rotor 35 is mounted for coaxial rotation independently of the boiler B_ and the machine housing H on a shaft 38 which is arranged by means of a bearing 39 for rotation within the bore 3I of the expansion device PX . An annular row of nozzles 40 is in the expansion device FX coaxial with the turbine rotor 35 and opposite the. paddle 37 of the same arranged. An annular high pressure distributor 41 is provided in the expansion device FX and opens into the turbine nozzles 40.

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High pressure steam is fed from the boiler chamber 1 to the distributor via a number of radial openings or channels 42 and a corresponding number of radially arranged drainage pipes 43 are arranged at the same distance on the circumference of the axis in order to achieve a uniform rotation. The high-pressure steam generated in the boiler chamber 1 passes from the boiler chamber through the pipes 43 and openings 42 to the high-pressure distributor 41, from which it exits through the turbine nozzles 40 and onto the blades 37 to drive the turbine rotor 35 and its shaft 38 ^m i "fc d © ^r desired speed impacts. a seal 44, such as a non-contact labyrinth seal, is provided on the turbine shaft inside next to the bearing 39, to hold a loss of vapor pressure of the turbine along the shaft 38 as small as possible.

An annular diffuser 46 is coaxial with the turbine rotor 35 arranged in a stationary manner in order to remove the from the expansion device absorb escaping vapors, the inlet opening of the diffuser the turbines se hau fine 37 at their of facing away from the nozzles 40 sides. The one from the Exhaust steam exiting diffuser 46 reaches the machine housing H, from which it is fed to the condenser C_, as is subsequently done is described. A number of axially extending radial partitions 47 are disposed in diffuser 46 and serve with the aforementioned radial blades to control the angular velocity of the exhaust steam on the to keep the same value as the circulating boiler and the housing unit.

A refrigerant compressor or a pump P is also arranged coaxially next to the expansion device PX inside the machine housing H. The compressor P _- has an annular housing 50, which is fixedly arranged within the circumferential housing H with the aid of the radial blades 32 mentioned above, so that the compressor housing ^ O is coaxial

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rotates as a unit with the machine housing H and the boiler JB. As can best be seen in FIG. 6, this shows Compressor housing 50 has a coaxial ring-shaped chimney 51, in which a compressor rotor 52 is arranged, which is connected to the turbine shaft 38 for its drive. Coaxial to the outside of the compressor housing 50 is for example attached by Eolzen 53 an annular plate 54 which cooperates with the compressor housing 50 to a number

To form circumferentially distributed, radial inlet channels 55 to _# compressor rotor 52. The turbine shaft 38 extends / coaxially through the plate 54 - and is supported therein by a bearing 56. Fluid refrigerant entering the compressor through inlet ducts 55 is compressed by rotor 52 and then delivered through a number of radial ducts 57 and tubes 58 to an annular high pressure chamber 59 in refrigerant expansion device RX, as can be seen from FIG. 3 .

The refrigerant expansion device RX surrounds the compressor P coaxially and is mounted in such a way as to rotate with the rotating machine housing H by means of the aforementioned radial blades 32 and by means of a pair of radially extending inner and outer, axially offset, annular partition walls 60 and 61. The partition walls 60 and 61 each connect the working fluid expansion device PX and the refrigerant expansion device RX and the latter and the inner surface of the peripheral wall 5 of the rotating machine housing H, whereby the interior of the rotating machine housing H is divided and each into a cooling chamber X and a machine chamber Y _{- are} separated so that no noticeable mixing of working fluid and refrigerant occurs. Insulation, not shown, is provided in order to keep the heating of the refrigerant vapors as low as possible as they pass from the evaporator to the compressor inlet.

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As described above, the boiler B _1, the housing H _t, the condenser C_ and the evaporator E_ are arranged for coaxial rotation as a unit, wherein in accordance with the present invention a mechanical coupling between the expansion device PX and the boiler-condenser-evaporator Unit is arranged so that after the start-up during operation of the machine the unit is continuously driven by the primary power generated by the machine, liies takes place by means of an internal, closed gear with constant transmission ratio, which is arranged coaxially to the machine and inside the housing H. is provided.

In the illustrated embodiment, according to the i'ig. and FIG. 7 shows the transmission made up of a planetary gear, which has a cylindrical gear 63 which is fixedly on the turbine shaft 58 sits and is driven by this. The powered Sun gear 63 drives a number of gears, each of which is mounted in a needle bearing 64 on a stub shaft 65 which is fixed in the adjoining section of a non-inflowing Torque anchor T_ is attached, which has a coaxially arranged central hub portion 66, which is mounted on the inner end of the machine shaft 9 by means of a pair of bearings 67. As shown, the sun gear is 63 each in mesh with a larger gear 68 of each gear assembly to drive it, while a smaller Gear 69 of the gear arrangement meshes with a coaxial ring gear 70 to to drive this; the ring gear? 0 is arranged within the recess of a plate 54 of the compressor housing 50 and is held by this.

Ler torque tanker T_ has an outer circumferential end portion 72 which, in addition to the refrigerant expansion device KZ, extends radially outward, such as

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"For example, from Fig. 3 can be seen, and a radially inwardly directed web section 73 of the torque armature T ^ is formed with a number of circumferentially arranged openings 74. Its cross-sectional area is sufficient to allow a relatively free flow of the Käl.temittels within the chamber X in the Housing H. The torque _{armature T 1} is held stationary with respect to the rotating machine-condenser-evaporator unit by means of a pendulum element 75 which extends radially outward from the edge section 72 of the torque armature T_.

The pendulum element 75 is in terms of its density, its dimensions and its position is designed in such a way that it exerts the desired counterforce, which counteracts the external reaction torque of the draft in the condenser and evaporator is directed and consists according to a preferred embodiment made of steel, with an inner radius of 27 »94 cm (11.0 inches) in the embodiment according to FIG. 10, an outer one 43.18 cm (17.0 in) radius, 2.54 cm (1.0 in.) Width, 30 ° arc length, and weight 5f67 kg (12.5 pounds). The pendulum provides a counter torque which is sufficient to keep the torque anchor CD stationary hold and prevent rotation thereof against an impact of 12.6 kg-m (9 »1 foot-pounds); this Torque is required to drive the boiler-condenser-evaporator unit to be driven at 1200 revolutions per minute when both the condenser and the evaporator are pumping air.

As a result of the non-rotating torque anchor £, the Planetary gear assemblies fixedly arranged so that their axes do not rotate or do not face each other on the circumference move the machine axis. This is the output power available at the expansion device PX that is not used for the Driving the compressor rotor 52 was used by the driving force Sun gear 63 via the planetary gear arrangements directly on the driven ring gear 70 on the rotating boiler

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Cβ-7264/7370

Condenser-evaporator unit transferred, making this Unit with the constant speed of the respective gear arrangement is set in rotation.

As mentioned above, the exhaust steam exiting from the turbine diffuser 46 enters the circulating condenser C_ , where it condenses, the compressed refrigerant exiting from the compressor P also condensing in the condenser C_ in accordance with the present invention. According to the embodiment shown in FIGS. 1 and 2, the rotating capacitor C ^ comprises a coaxial arrangement of annular radial ribs 80 and axially extending heat exchange tubes 81a and 81b, which are arranged circumferentially distributed around the machine shaft 10 and with the machine housing H and the Circulate boiler B together. The ribs 80 consist of separate or independent annular disks which are held at a predetermined, equally large distance from one another by means of the heat exchange tubes 81a_ and 81b_, which extend in the longitudinal direction through the ribs 80. The fins 80 and the tubes 81a_ and 81b are made of metal of high thermal conductivity, such as. B. copper or aluminum, and the ribs are preferably connected to the heat exchange tubes by hard or soft soldering or the like. In order to achieve the greatest possible thermal conductivity between these parts. *

The heat exchange tubes 81a and 81b are balanced at the same distance from one another on the circumference of the ribs 80 around the shaft 10 arranged, as can be seen, for example, from FIG. The heat exchanger tubes serve in accordance with the present invention 81 ^ of the condenser £ for condensation of the from the diffuser 46 exiting working fluid and the alternately arranged heat exchange tubes 81b are used to condense the from the compressor P to the high pressure chamber 59 of the refrigerant expansion device RX released compressed fluid refrigerant.

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For this purpose, according to the i ^(<ig. 3, the inner ends of the tubes 81 ji in corresponding openings 82 are arranged which are provided in the attached machine housing wall 8, so that the inside of the tubes 81a. In communication with the interior of the appended machine chamber Y of the housing H, into which the exhaust vapor of the working fluid released by the diffuser 46 is released. On the other hand, the alternately arranged heat exchange tubes 81b for the compressed refrigerant vapor extend through openings 83 in the machine housing wall and their inner ends extend through the adjacent wall of the refrigerant Expansion device RX, so that the inside of the heat exchange tubes 81t is in connection with the high-pressure refrigerant chamber 59. According to FIG , which is arranged coaxially next to the outermost of the ribs 80 and which starting from the machine shaft 10 is supported by radial spokes 86 distributed around the circumference.

The inner peripheral edges of the ribs 80 form within the same has a coaxial inlet chamber 87 for the cooling fluid flowing from and between a number of circulating Ribs is released to the outside in the manner described below. The inner diameter of the ring 20 and of the ring 85 is the same as the inside diameter of the abutting group of ribs 80 to allow fluid flow to follow inside to chamber 87 is not obstructed, and one after externally widening or bell-shaped fluid inlet element 88 is fixedly arranged on the ring 20 coaxially outside the inlet end of the chamber 87. The central section the machine housing wall 8 is curved in the area of the shaft 10 and is essentially conical in shape, as in 8a is indicated to the flow of the heat exchange fluid through to streamline the chamber 87 to the ribs 80 of the condenser.

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The axial length of the capacitor C_ and the distance between adjacent ribs 80 is determined by the speed of the boiler condenser Evaporator unit and the kinematic viscosity of the cooling fluid sized so that a Taylor number in the range of about 5 to 10 and preferably 6 is obtained, and the inner and outer radius of the ribs is dimensioned so that a ratio of the inner radius to the outer radius of the Ribs 80 in the range of about 0.70 to 0.85 »and preferably about 0.77 »is obtained in order to reduce the viscosity properties of the To use cooling fluids and the shear forces exerted thereon by the rotating fins 80 to convey the cooling fluid and to accelerate radially outwardly between the ribs substantially to a speed which is an optimum total heat exchange between the fluids in the tubes 81a, and 81b_ and the fluid flowing between the ribs 80 enables. Consistent with that described in the DT-OS 2 IO7 845 Arrangement extends the outer circumferential section of both the housing wall 8 and the ring 85 radially outward beyond the ribs 80 by an amount, thereby to annular radial flange portions F_ and i ^ _ result, which increase the fluid flow to the outside between the ribs 80. Furthermore, blades can be used to increase the axial fluid flow between the flange sections F and FJ_ provided if this is desired in the respective system.

According to Fig. 3, the exhaust steam from the turbine, which comes from the Diffuser 46 is delivered into the housing chimney Y, in the Heat exchange tubes 81a of the condenser C_, in which the steam is condensed by heat exchange with a cooling fluid, which consists, for example, of ambient air in the previously described manner between the rows of ribs 80 is released to the outside. That way in the pipes 81ja formed condensate flows inwards and is transferred to the inner ends of the tubes in a η annular collecting ring 90 released and then it passes through a number of

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dialer tubes 91 in an annular boiler liquid container 92. Liquid working medium is the boiler B from Liquid container 92 is supplied via a number of radial bores 93. The liquid level i in the boiler chamber 1 is determined automatically and through a number of sensor tubes 94- showing the boiler chamber 1 and the liquid container connect, kept at a constant level; these sensor tubes operate in the US Pat. No. 3,590,786 (published on July 6, 1971).

In a similar way, the compressed refrigerant released by the compressor P passes from the high-pressure chamber 59 of the expansion device RX into the heat exchange tubes 81b of the circulating condenser C_, where the refrigerant is condensed by heat exchange with the cooling medium which, as described above, is between the rows of ribs 80 exits to the outside. The liquid refrigerant condensed in the heat exchange tubes 81b_, flows in these tubes inwards and is used for high-pressure chamber 59 of the expansion device RX returned from which it i that chamber ⁿ into an annular expansion chamber 96 flows around a radially disposed annular weir 95th

The liquid refrigerant in the chamber 96 is axially pressurized through a number of rotating expansion nozzles 97 released and then occurs through ring-shaped, non-circumferential Rows of expansion turbine blades 98, which provided in the annular peripheral edge portion 72 of the torque armature _T and opposite the circumferential Nozzles 97 according to FIGS. 3 and 10 are arranged. The expansion nozzles 97 are preferably arranged in circumferentially spaced groups, each of which is a number of Has nozzles, as can be seen for example from Fig. 5, in which the expansion nozzles 97 in two groups of each three nozzles are arranged, which are arranged diametrically and concentrically opposite the axis of rotation of the machine.

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As can be seen from FIGS. 1 and 3, this comes from the expansion show finely released liquid refrigerants in the evaporator E_, in which it is through heat exchange with a other fluid, for example ambient air, is evaporated. In the illustrated embodiment, the evaporator E has a similar structure to the condenser described above C_ and includes a coaxial series of annularly arranged radial ribs 100 and axially extending Heat exchange tubes 1O1, the circumferential side around the machine shaft 9 arranged and intended for circulation with the machine housing H, the boiler Is and the condenser £ as a unit.

The inner ends of the tubes 101 are in corresponding openings 102 attached, which in the adjacent machine housing wall 7 are provided so that the interior of the tubes 101 in connection with the adjacent inner cooling chamber X of the Machine housing H and the non-rotating expansion blades 98 is opposite. A collecting ring 99 »which with an inwardly protruding lip 99a. is provided, surrounds the inner ends of the tubes 101. The outer ends of the tubes 101 are arranged in recesses 103 which are provided in an end ring 104, which is coaxially next to the outermost ribs 100 and from the machine shaft 9 by radial spokes 105 arranged at a distance on the circumferential side will be carried.

3, the inner circumferential edges of the ribs 100 form a coaxially arranged inlet chamber 106 for the heat exchange fluid, which is discharged to the outside through and between the number of circumferential ribs 100 in the manner described above in connection with the condenser C_. The inner diameter of the ring 104 and the ring 14 resting on the outside is the same as the inner diameter of the ribs 100, so that the fluid flow into the chamber 106 is not obstructed, and an inlet element which widens outwards or is bell-shaped.

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element 107 is rigidly arranged on ring 14 coaxially thereto and outside the inlet end of chamber 106. An arched, essentially conical cap 108 surrounds the machine parts 9 'around the flow of the heat exchange fluid to make the chamber 106 to the row of ribs 100 of the evaporator E streamlined.

As in the capacitor C_, the outer circumferential portions of both the adjacent housing wall 7 and the ring 104 extend radially outward between the ribs 100 by a substantial amount in order to produce annular radial flange portions FJ ^ and F ¹¹ I ₁ , which are effective to increase the fluid flow to the outside between the ribs, while irrigation to increase the axial fluid flow between the flange sections F_ ^ and F _- ^ ¹ , if desired, can be provided in the manner described above.

As with the condenser C_, the axial length of the evaporator E_ and · the distance between adjacent ribs 100 due to the speed of the evaporator and the inner and outer Radius of the ribs 100 is determined so that the viscosity properties of the fluid and the shear forces exerted on this by the tilting 100 are used to the fluid between to convey the fins and to accelerate substantially to a speed which an optimal overall heat exchange between the fluids flowing through the ribs 100 and the refrigerant flowing in the tubes 101.

That discharged by the expansion vanes 98 condensed Refrigerant flows completely into the evaporator tubes 101 with the exception of two tubes labeled 101ji. That refrigerant entering the bore 101 is absorbed therein by heat exchange with a fluid, for example ambient air, evaporated and outwards between the row of hips 100

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"8th

delivered in the manner described above, and that evaporated refrigerant towards the tile and is from the inner ends of the tubes 101 into the adjacent cooling chamber X im Machine housing H delivered. The evaporated refrigerant in turn exits the cooling chamber X through the inlet channels 55 into the compressor F_, where it is again compressed and removed from the rotor 52 to the condenser £ and to the evaporator E in the preceding is delivered in the manner described.

The two pipes 101_a_, into which the refrigerant does not enter, are diametrically 180 ° opposite one another and the refrigerant discharged from the expansion blades 98 is on Entry into the tubes 101ει, prevented by deflection elements 110, which are axially opposite the adjacent open ends of the two tubes 101a_ according to FIGS. 3 and Yes. The two 101ji evaporation tubes are used to collect and recycle Work s fluid that migrates to the refrigerant into the chamber Y_, with the working fluid, for example, along the turbine shaft 38 migrates from the machine chamber Y to the cooling chamber X.

For this purpose, the outer ends of all the evaporator tubes 101 and the two tubes 101ja are connected by means of an annular distributor 111 which is provided in the end plate 104. In this way, working fluid that migrates into the refrigerant system does not evaporate in the pipes 101, but flows through the distributor 111 and collects in the two diametrically opposed pipes 10Ia ₁ , which are protected against the ingress of refrigerant by deflection elements 110 . Liquid working fluid, which collects in the two pipes 1O1 £, flows inwards into these and is brought by means of a pair of diametrically arranged pipes 112 to the lubricant bath 118 on the inner surface of the peripheral machine housing wall 5 next to the boiler chamber 1, where the liquid working fluid evaporates again and mixes with the turbine exhaust steam within the machine chamber Y.

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Similarly, any refrigerant that is in the working fluid enters, not in the condenser tubes 81a, for the working fluid condenses, but collects on the outer Ends of these tubes 81a. and a connecting annular Distributor 113, from which it goes to the cooling chamber X of the housing H by means of two diametrically opposed » axially extending tubes 114 is returned.

A pressure lubrication system is provided in the device using a pitot pump as shown in Figs. 3-6, 8 and 10. As can be seen from the figures, the pitot pump has a radial channel 116, which in the pendulum element 75 is arranged and which forms an L-shaped blade 117 at its outer end, the inlet end of which into an annular Lubricant bath 118 immersed, which extends circumferentially within the machine housing H and which faces a direction which is opposite to the direction of rotation of the blade. The inner end of the canal 116 is connected to a radial pipe 119, which bridges one of the Fluidö ff mangen 74- and to a radially extending one Channel 120 in the central hub portion 66 of the torque armature T. leads.

In addition to the inner end, the channel 120 divides into two branching channels 121 and 122 at an angle to one another. The channel 121 conveys lubricant to the interior of the hub portion 66 to lubricate the bearings 67 at the inner end the machine shaft 9 and the channel 122 leads to the radial Leg of a connecting part 123 in the form of one on the Head standing L, the horizontal portion of which is coaxially within the front wheel 63 of the gearbox with a constant gear ratio extends, as shown for example in FIG. The machine shaft 38 is in her Internally equipped with a coaxially extending lubricant bore 125, which radial channels 126 and 127 has, which are directed outwardly from the bore to

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To lubricate the bearings 39 and 56 of the machine shaft, as well as several gears in the gearbox with constant gear ratio.

A rotation of the machine housing H with respect to the non-rotating torque armature T_ conveys lubricant of the lubricant bath Si18 from the blade 117 inwards and through the connecting channels and pipes to the bearings 39, 56 and 67 of the transmission, as described above. Lubricant from bearing 39 enters a pair of diametrically disposed radial tubes 129 through radial channel 128 from which it returns to lubricant bath 118. Lubricant from the bearing 56 and the gearbox exits into a collecting ring 130, from which it returns to the lubricant bath 118 by means of a pair of tubes 13I arranged diametrically to one another. Similarly, lubricant also enters a collection ring I32 as the bearings 67, from which it returns to the lubricant bath 118 by means of a pair of diametrically arranged radial tubes 133. Openings 134 on the circumference of the partition wall 61 allow a flow of lubricant from the machine chamber Y_ to the cold chamber X in the machine housing H.

The liquid level of the bath 118 is regulated and kept essentially constant by a regulating tube arrangement which has a radial channel 116 'which is arranged in the pendulum element and which has an L-shaped vane 117' at its outer end, the inlet end of which in one direction shows the opposite to the rotating direction of the housing H eats and what is on the level or radius, or the desired for the surface of the lubrication splash 118th With the inner end of the channel 116 'there is an angled tube II9 ¹ in connection, the outlet end of which is directed radially outwards and opposite to an inwardly directed collecting ring 60a, which is in the circumferential section of the inner partition element 60 at the connection of the same with the outer one

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Partition wall element 61 is arranged.

Migration of working fluid to the evaporator causes the fluid level in the lubricant bath 118 to rise and cause a Rotation of the machine housing H with respect to the pendulum element 75 causes excess fluid to be skimmed off Lubricant bath 118 and pumping it inward of blade 117 'and via channel 116' to pipe 119 '' from which the fluid is discharged radially into the collecting ring 60a_. In this way the ring 60a. excess fluid supplied is fed through a radial pipe 112 'to the inner peripheral surface of the machine chamber Y adjacent to the boiler, through which the supplied working fluid is evaporated and the liquid lubricant through openings 1J4- to the cooling chamber X returns.

It is obvious that when the machine starts up, boiler B does not generate any steam pressure in order to drive the expansion device PX and thus the boiler-condenser-evaporator unit. It is therefore necessary at start-up to drive the boiler-condenser-evaporator unit independently at the desired speed in order to create and maintain a liquid-vapor boundary layer i_ in the boiler chamber 1 until the annular body of liquid in the boiler is heated to a temperature to provide the desired steam pressure to drive the turbine 35. This can take place, for example, by means of a starter motor M which drives a belt pulley 135 arranged on the machine shaft 10 via a drive belt 1J6. Means such as a clutch, not shown, may be provided to disconnect the motor M and pulley 135 when the engine reaches normal operation, or the motor may be passed through the rotating boiler-condenser-evaporator unit and the shaft continues to be driven in order to work as a generator that charges a battery, for example, which supplies the

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C R- 7264/7 370

hearing aids such as the starter motor, indicator lights and Like. Supplied with power.

A special feature of the "described according to the invention Embodiment is their structure in such a way that a separate working fluid and refrigerant can be used, without the need to provide a positive seal separating the two fluids. This is achieved by using a fluid with a vapor pressure as the working fluid, which is at the temperature in the refrigerant condenser supplies a downstream working fluid pressure that at least as high as the refrigerant pressure in the evaporator. Examples of two fluids that approximate the described Have vapor pressure relationship and that in the device can be used are 1,1,2-trichloro-i, 2,2-trifluoroethane as a fluid refrigerant and benzotrifluoride or a mixture of tetrachlorethylene and trichlorethylene as a working fluid. The pressures of the two fluids in the machine housing H are almost the same, and the temperatures of the Both fluids on the condenser tubes are the same, but the refrigerant pressure in the condenser tubes 81b_ is included the compressor outlet pressure and is therefore noticeably higher than the pressure in the condenser tubes 81a for the working fluid.

During normal operation of the rotating machine, the liquid ring body in the boiler chamber 1 to the required Temperature and the required pressure of the combustion of a fuel-air mixture in the chamber 27 is heated is, the pressure steam generated in the boiler is inwardly through the pipe 93 to a manifold 41 and then through the nozzles AO for impact against the turbines se hau fine 37 released, whereby the turbine rotor 351 the shaft 38 and the Compressor rotor 52 at the desired predetermined speed are driven. The shaft 38 drives over the foregoing described jacketed gear the revolving boiler-condenser-evaporator unit at a given speed

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compared to the speed of the shaft 38 »which is due to the constant Gear ratio of the transmission is determined. In the illustrated and described embodiment, the direction of rotation is of the boiler-condenser-evaporator unit opposite to the direction of rotation of the turbine 35 and the shaft 38.

The exhaust steam from the turbine passes through the diffuser 4-6 in the housing chamber Y and passes into the heat exchange tubes 81a, where it is condensed by the cooling fluid that flows between the Ribs 80 is released to the outside in the manner described above. The condensate flows in the pipes 81jä. after inwards into the jam 90, from which it is through pipes 91 to the Boiler liquid container 92 returned and the boiler is supplied in a controlled amount, which corresponds to the amount of evaporation of the liquid in the boiler.

The refrigerant fluid in the machine chamber X enters the Compressor P through inlet channels 55, is compressed by rotor 52 and through channels 57 and 58 of the high pressure chamber 59 supplied to the refrigerant expansion device PX. That Compressed refrigerant then reaches the heat exchange tubes 81b of the condenser C_, where it passes through the outside cooling fluid exiting between the ribs 80 is condensed in the manner described above. That condensed Refrigerant returns to the expansion device PX and enters the evaporator via nozzles 97 through the non-rotating expansion blades 98. That condensed Refrigerant fluid is evaporated in the tubes 101 and reversed then back to Kanner X to be re-compressed, condensed and evaporated.

A typical example of a germinating and cooling device with a rotary Machine, which works in a closed Rankine cycle and which a two-cycle system with two fluids according to of the present invention and designed for an output of 6.53 Pk on turbine shaft 38

309835/0545

has a boiler B_ with a diameter of the liquid level i of 86.5 cm (38.0 inches) and an axial inner length sufficient to supply the necessary heat to the boiler liquid from the combustion gases. The diameter of the boiler expansion turbine on the blades 40 is approximately 8.9 cai (3i5 inches) and the diameter of the compressor is sized to compress the refrigerant fluid from evaporator pressure to condenser pressure. The fins of the capacitor O_ have an outside diameter of 53 »34 cm (21.00 inches) and an inside diameter of 4A.2 cm (17.40 inches). The axial length of the rows of condenser fins 80 is 60.96 cm (24.00 inches) and the spacing between adjacent fins is 0.94 mm (0.037 inches) with the axes of the heat exchange tubes at a 24.74 cm (9th century) radius «74 inches) from the axis of rotation of the device. The fins of the evaporator have an outer diameter of 53 »34 cm (21.00 inches) and an inner diameter of 41.4 cm (16.30 inches). The axial length of the rows of evaporator fins is 15.24 cm (6.00 inches) and the spacing between adjacent fins is 0.81 mm (0.032 inches). The axially extending evaporator tubes are also located at a radius of 24.74 cm (9.74 inches) from the axis of rotation of the device. The boiler-condenser-evaporator unit is driven at a speed of 1200 rpm via the turbine and the gearbox with a constant transmission ratio in a direction of rotation which is opposite to the direction of rotation of the turbine rotor 35. If a mixture of tetrachlorethylene and trichlorethylene is used as the boiler working fluid and 1,1,2-trichloro-i, 2,2-trifluoroethane is used as the refrigerant fluid, the following data result for typical operation of the device:

Boiler temperature 260 ° C (5OO ⁰ l · ¹ ) "
Kesselruok 19.34 ata (£ 27 psia)
Boiler output 18.37 χ 10 ⁶ cal / h (72 900 Btu / h) turbine speed 45,000 rpm.

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Efficiency of the Hankine-Kxeise 30 7 ° condenser saturation temperature 54 ° C (13Ο ⁰ F) condenser pressure

Working group 0.19 ata (2.7 psia)
Refrigerant circuit 1.27 ata (18.0 psia)

Condenser output (boiler fluid) 14.24 χ 10 cal / h ' (56 500 Btu / h)

Condenser capacity (refrigerant) 11.69 x 10 cal / h 46 400 Btu / h)

Condenser air flow 130.83 mvmin. (4620 cfm) Evaporator Temperature 4.4 ° C (40 ° F)
Evaporator pressure 0.19 ata (2.7 psia)
Evaporator output 9.07 χ 10 ⁶ cal / h (36,000 But / h) Evaporator air flow 61.73 mViin (2180 cfm)

An alternative embodiment of a capacitor for separate Working fluid and refrigerant of a two-circuit system eats shown in FIGS. 11, 12 and 13, in which the The same reference numerals are used for parts which correspond to FIG. 3 and have been described above. In. In this alternative embodiment, the annular ribs of the capacitor described above are circumferential divided into closely spaced> outer and inner concentric annular Condenser sections CJ_ and C ^ _ each for the boiler working fluid and get the refrigerant.

The arrangement of such concentric outer and inner condenser sections CJ_ and CJ | _ creates a thermal gap between the two condenser sections so that the outer working fluid can be operated at temperatures that are much higher than those required for effective operation to achieve effective heat transfer of the inner refrigerant condenser section desired temperatures. The capacitor capacity for the working fluid can thus be increased considerably in comparison to the standard capacitor C _- , which was described above. Like in

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the system described above, which uses two fluids, the working fluid capacitor pressure should be the same like or slightly greater than the refrigerant evaporator pressure, eliminating the need for a positive To create a seal that separates the two fluids. However, with the aid of the thermally divided condenser, the Selection of a suitable refrigerant and working fluid combination considerably simplified.

Reference is made to FIG. 11, according to which the outer and inner concentric capacitor sections CJ_ and C_ ^ each have a coaxial row of closely spaced, annular tips 80 'and 80 ", which in the previously described manner consist of one metal of high thermal conductivity are made and which are radially aligned with one another in order to achieve an effective air flow between them. heat exchange tubes 81a ¹ for the boiler working fluid erstreckenßich axially through the fiippen 80 'of the external capacitor section CJ_ and heat exchange tubes 81b ¹ for the refrigerant fluid extend in similarly axially through the fins 80 'of the inner condenser section CJ ^. As previously described, the fins 80' and 80 "consist of separate or independent annular disc elements and are each equally spaced and parallel ^{by the heat exchange tubes 81a 1 and 81b_ '} held to each other, wove i the fins are preferably connected to the heat exchange tubes to achieve a

to ensure high thermal conductivity between these parts.

As shown in FIG. 12, the heat exchange tubes 81a ¹ and 81b ¹ are arranged circumferentially around the machine shaft. The tubes 81a ¹ are each connected at their opposite ends to the barrel ring 90 and the manifold 113, as previously described with respect to the tubes 81 ^, wherein, as from iig. 13 can be seen, the refrigerant heat

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Exchange tubes 81b ^{1 have} a U-shape which is elongated in the axial direction and which is closed at one end and which extends at the other end through openings 83 * in the adjacent wall 8 of the machine housing H and in the manner described with the high-pressure refrigerant chamber 59 the refrigerant expansion device BX

connected is. By using the

mentioned U-shape for the heat exchange tubes 81V, the required number of refrigerant condenser tubes can be provided while only half the number of tubes extends through the housing wall 8, so that this is not structurally is weakened.

In a manner similar to the embodiment described above, a thermally insulated partition wall 60 'is provided between the inner surface of the peripheral wall 5 of the machine housing H and the outer surface of the working fluid expansion device PX, whereby the interior of the machine housing H into the cooling and machine chamber described above X and Y is divided and separated. 'Which has a larger diameter than the heat-exchange tubes 81b' have openings 60a, 60b take insulating sleeves' of comparable diameter to which the open end portions of each pipe ^f 8lb at a distance surrounded thereof. The sleeves 6Ob _- 'extend outward from the partition wall 60' and end beyond the housing wall 8 next to the ribs C "and serve to isolate the refrigerant in enclosed sections of the pipes 81b from the higher temperature in the machine chamber Y. Apart from the Differing in the different capacitor design and the arrangement just described, the structure and operation of the embodiment of the invention according to FIGS. 11, 12 and 13 correspond to those of the embodiment according to FIGS. 1 to 10 and therefore do not need to be described again.

The capacitor design according to FIGS. 11 to I3 is for operation

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309835/0545

with a Taylor number between 5> 0 and 10.0, preferably about 6, and the ratio of the inner radius of the ribs 80 "of the inner capacitor section C ^ _ to the outer radius of the ribs 80 'in the outer capacitor section C _ ^ _ is in the range of about 0.70 to about 0.85 and preferably about 0.77 · the radial position of the bpalts between the wippen 80 'and 80 "of the outer and inner portions capacitor C' and CJ ^ depends on a number of factors, ie _w the type of working fluid and refrigerant used,. of the thermodynamic circuit and the heat transfer coefficient, of the thermal conductivities of the respective materials from which the condenser fins and heat exchange tubes are made, and must be determined in every i'all. The following equation provides a design basis for this:

A ₁ = area of the inner rib section A ₂ - area of the outer rib section q ,, = heat transfer index of the inner section q ₂ = heat transfer index of the outer section t = air temperature when entering the condenser

ty, - saturation temperature of the refrigerant in the inner condenser section

t ₂ = saturation temperature of the working fluid in the outer section of the condenser

A typical example of a heating and cooling device which works with a rotating machine in a closed Rankine cycle and which uses the subdivided condenser design according to FIGS. 11 to 13 and is designed for an output of 5.88 hb , with the turbine shaft 38 1.72 t £> are available to drive the generator motor M to generate additional electrical power, has a tank h which has a diameter i_ of the liquid level of 45.7 cm (18 inches) and an axial inner length which

- 29 -309835/0545

sufficient to transfer the required heat from the combustion gases to the boiler liquid. The diameter of the boiler expansion turbine on the blades 40 is 8.9 cm (3.5 inches) and the diameter of the compressor is designed to compress the refrigerant from evaporator pressure to condenser pressure. The ribs 80 'of the outer working fluid condenser CJ_ have an outer diameter of 23.0 cm (13 »G inches) and an inner diameter of 30» 73 cm (12.1 inches). The tips 80 "of the inner refrigerant condenser C ^ have an outside diameter of 30» 48 cm (12.0 inches) and an inside diameter of 25.4 cm (10.0 inches). The axial length of the row of condenser fins 80 'and 80 "is 24.13 cm (9.5 inches) and the distance between adjacent fins is 0.635 mm (0.028") with the axes of the heat exchange tubes at a radius from the axis of rotation of the device of 13.97 cm (5 »5 inches ) are removed for the inner capacitor section Cj ^ and 16.0 cm (6.3 inches) for the outer capacitor section C ^. The fins 100 of the evaporator E have an outer diameter of 33 »0 _C m (13» ° inches) and an inner diameter of 25.4 cm (10.0 inches). The axial length of the row of evaporator fins is 20.07 cm (7.9 inches) and the distance between adjacent fins is 0.611 mm (0.025 inches). The axially extending evaporator tubes 101 and 101a are also within a 14.73 cm (5 »8 inch) radius from the axis of rotation of the device. The boiler-condenser-evaporator unit runs at a speed of 2300 rpm. driven by the turbine via a gear with a constant transmission ratio in a direction of rotation which is opposite to the rotation of the turbine rotor 35. When using the boiler working fluid, which consists of a mixture of trichlorotrifluorobenzene isomers, according to Ub-PS 3,702,534 (issued November 14, 1972) and 1,1,2-trichloro-1,2,2-trifluoroethane as a refrigerant, the following data result for typical operation of the device:

309835/0545

Boiler temperature 327 ° C (620 ° F)

Boiler pressure 10.48 ata (149 psia)

Ke output 24.32 χ 10 ⁶ cal / h (96 500 Btu / h) turbine speed 45 000 rpm.

Efficiency of the Rahkine circuit 20% condenser saturation temperature

Working fluid circuit -15.6 ° C (4.0 ° F) Cooling circuit -7.5 ° C (18.5 ° F)

Power of the outer capacitor
(Working fluid) 20.61 χ 10 ° cal / h (81 800 Btu / h) Capacity of the inner condenser
Refrigerant 7.96 χ 10 ^b cal / h (31 600 Btu / h) condenser air flow 45.31 mVmin. (1600 cfm) Evaporator Temperature 4.4 ° C (40 ° F)
Evaporator pressure 0.19 ata (2.7 psia)
Evaporator output 6.05 χ 10 ⁶ cal / h (24,000 Btu / h) Evaporator air flow 22.65 mVmin. (800 cfm)

In the previous example, the working fluid condenser pressure (0.28 ata) is slightly higher than the evaporator pressure (0.19 ata) and this is necessary if power for a generator is to be supplied in addition to air conditioning or heating. Of the higher condenser pressure at full power allows condenser pressure fluctuations, which occur with changing generator loads and still requires that the condenser pressure is always the same as or greater than the evaporator pressure. Such an arrangement ensures that Refrigerant vapor not at the end of the working fluid condenser collects and reduces its capacity.

The embodiment described above, in which two fluids of different high molecular weights for the refrigerant and the working fluid used works more efficiently than using a single fluid as both Working fluid and refrigerant, because in a two-fluid arrangement it is possible to select a working fluid which

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309835/0545

results in a working group of the machine with higher efficiency.

However, in certain systems it may be desirable to use a single fluid and an embodiment of the invention which is used for operation with a single fluid for both machine performance and cooling is in! 'ig. shown. Apart from a few structural differences described below, the device is according to Pig. 14 in the rest in the same way as the one previously described Apparatus designed and correspondingly those components in Fig. 14 which correspond to the components of the first embodiment, are provided with the same reference numerals so that unnecessary repetition of the description is avoided.

The main differences between the embodiment according to Fig. 14 and the first embodiment consist in that 14, the interior of the machine housing into a low-pressure and high pressure canier instead of being on an im to be located substantially uniform pressure, and that all condenser heat exchange tubes for condensing the only one Fluids are used compared to the first embodiment, in which the working fluid in a group of condenser tubes condenses and the refrigerant in a second group of condenser tubes.

14 is in the embodiment with a single Fluid divides the interior of the machine housing H into two separate pressure chambers XJ_ and YV_, which is achieved by an annular, plate-like partition 140 takes place. The inner peripheral Band of partition 140 continuously surrounds the outer surface of the compressor F between the compressor inlet ducts 55 and the outlet channels 57ι as shown at 141, and is welded to the outer surface or in some other way fluid-tight connected. The outer peripheral part of the Partition 140 forms an uninterrupted, axially extending one Hand section 142, which is located on the inner surface of the

- 52 309835/0545

housing wall 8 rests and welded to this or in another Way is fluid-tightly connected, at a short radial distance outside the inner ends of the annular rows of heat exchange pipes 81c. of the capacitor C_, as in 143 is indicated. The boiler pressure steam pipes 43 and the lubricant return pipes 129 necessarily extend through the partition 140 and the gap between these tubes 43 and 129 and the partition is by welding or otherwise Manner, as indicated at 145, sealed fluid-tight.

The edge section 142 and the adjacent section of the partition wall 140 together with the adjacent inner surface of the housing wall 8 form an annular collecting chamber 146 at the inner ends of the heat exchanger tubes 81g for receiving fluid condensed therein. Since the same fluid is used for both the cooling process and the work machine, the liquid condensed in the pipes 8icj collected in the annular chamber 146 is divided, and in predetermined proportions to the refrigerant expansion ring RX ' and the boiler liquid receiver 92 supplied. Liquid condensate is fed to the expansion ring RX * by means of a pair of diametrically arranged tubes 147 which are connected at one end to the condenser chamber 146 through the peripheral edge section 142 and at the other end to the interior of the ring RX ¹ through the outer peripheral wall thereof . The pipes 147 have a predetermined flow area which is dimensioned in view of the supply of liquid condensate to the ring RX *. The ring RX ' supplies refrigerant to the expansion nozzles 97''which have a predetermined flow volume; excess liquid in the chamber 146 flows into the pipes 9 ^' through which it is returned to the boiler liquid container 92 in order to be evaporated again in boiler B. .

As described above, the partition wall 140 divides the interior of the machine housing H into two chambers X ¹ and Y_ ^, which have different pressures during operation. In relation

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on Fig. 14 the left ventricle XV_ operates with the lower one Evaporator and Compressor Inlet Pressure. On the other hand, the right chamber YJ_ works with the higher pressure of the compressor and diffuser output and capacitor G_. With it occurs in operation refrigerant vapor from the housing chamber XJ_ through the Inlet channels 55 in the compressor P, is compressed and passes through the channels 57 into the high pressure chamber YJ_, where a Mixing occurs with the turbine exhaust steam exiting the turbine through the diffuser 46. The united fluid in the chamber Y _ ^ _ enters the heat exchanger tubes eic, des Condenser C_, where it is fluid by heat exchange with a cooling condenses, which occurs between the ribs 80 of the condenser in the manner described above to the outside.

The condensate formed in the tubes 81 £ flows from the inner ends of the tubes and is collected in the annular chamber 146 from which it is divided and fed to the kettle liquid container 92 and the expansion ring EX ' in the manner previously described. The liquid flowing through the nozzles 97 'is discharged and expanded by a number of non-rotating expansion blades 98 and then conveyed into the tubes 101b of the evaporator E_, where it evaporates through heat exchange with a fluid which passes through the evaporator-condenser fins 100 to the outside . The fluid vapor formed in the evaporator tubes 101b enters these tubes and enters the low-pressure chamber X / _ of the machine housing H from the inner ends of the tubes, whereupon it is again compressed, condensed and evaporated, as already described. In the embodiment of the invention shown in Fig. 14, the outer ends of the condenser tubes 81 £, which are fastened in the ring 85 and the outer ends of the evaporator tubes 101b, which are arranged in the ring 104, do not need in connection with the first embodiment of the invention described manner to be distributed.

309835/0545

SS

An example of a fluid that can be used both is suitable as a refrigerant as well as a working fluid in the embodiment of the invention shown in FIG. 14 1,1,2-TrIChIOr-I ^, 2-trifluoroethane. This occurs during operation cold, liquid refrigerants from the expansion nozzles 97 '"and the blades 98 and partially fills all of the evaporator tubes 101b, where the flow rate of the liquid is dimensioned by the nozzles 97 'with respect to the evaporator capacity of the tubes 101b so that these tubes do not exceed are half filled with liquid. This limit value is determined by the radial height of the lip 99a of the collecting ring 99 determines which surrounds the inner ends of the evaporator tubes 101b. If there is more refrigerant through the expansion window 98 should enter the evaporator tubes 101b, excess would occur Liquid only pass over the lip 99a of the collecting ring 99 and enter the lubricant bath 118. However, the proximity of the lubricant bath 118 to the boiler chamber 1 would result in the refrigerant boiling in the bath 118, so that the refrigerant evaporate and merge with the evaporated Refrigerant would combine fluid in the housing chamber Xl.

A typical embodiment of an arrangement with a split circuit according to FIG. 14, which is designed for an output of 4.92 hp 'on the turbine shaft, has the same components that were previously described in connection with the two-circuit system, with the exception that the diameter of the boiler liquid level i_ 96.52 cm (38.0 inches), and that the turbine diameter 6.35 cm (2.5 inches) and the axial length of the evaporator fins 12,43 cm (4.5 inches ) amounts to. When using 1,1,2-ϊγιο1ι1ογ-1, 2,2-trifluoroethane as the only fluid for both the boiler working fluid and the refrigerant, the following data result for the operation of the device:

Lesselteraperatrar 188 ° C (370 ° F)
Keesel pressure 23.27 ata (331 psia)

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Boiler output 20.36 χ 10 ⁶ cal / h (80 800 But / h) O? Urbine speed 42 000 rpm.
Rankine circuit efficiency 20% Condenser saturation temperature 54 ° 0 (1 * 0 ° F) Condenser pressure 1.27 ata (18 psia)

Condenser output 25.93 x 10 ⁶ cal / h (102 900 Btu / h) condenser air flow 130.83 m ^ / min. (4620 cfni.) Evaporator Temperature 4.4 ° C (40 ° F)
Evaporator pressure 0.19 ata (2.7 psia)
Evaporation output 6.75 x 10 ⁶ cal / h (26 800 Btu / h) Evaporation pleasure flow 46.02 mvrain. (1625 cfm)

The inventive device is very suitable for Cooling or heating of the interior of buildings, houses and other structures and typical embodiments for the Summer and winter operation are shown in FIGS. 15 and 16, respectively shown.

In FIGS. 15 and 16, the device according to the invention is shown with the associated lines and valves for cooling and heating of a building. The device is preferably located next to the wall or walls of the building, to create easy access to the atmosphere outside the building, for example in the corner of the building, which is formed by the side walls 148 and 149.

In the arrangement shown, it comes from outside the building incoming air to the inlet of the circulating condenser C ^, through a horizontal line 150, which extends through the wall 148 of the building extends inward and opens at its inner end into an inlet housing 151, which has a Has condenser inlet leading opening 152. The outer The end of the line 15Ο is provided with a locking device, for example with flaps 153 »which can be opened to allow air from the outside through the conduit to the condenser or which are closed to shut off the air admission to the condenser.

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OT

A stationary housing 154 surrounds the circumferential one Capacitor G_ of the device and that supplied to capacitor C_ Air is released to the outside through the condenser fins 80, the air being heated by heat exchange with the Working fluid which condenses in the condenser tubes 81jä, is heated. An exhaust pipe 155 -for the in the housing 154-conveyed heated air leads tangentially away from this and through the housing wall 149 to the outside. The outlet end of the Line 155 is also provided with a closure device, for example with flaps 156 »around the line outlet to open or close to the outside atmosphere. A manifold 157 for conveying heated or cooled air from the device to suitable outlets 158 » which are distributed throughout the building has an inlet which is connected to the outlet line 155 at 159.

The circulating evaporator is just like the housing 154 E_ surrounded on the circumferential side by a housing 160, which absorbs the air that emerges radially outwards through the tilting of the evaporator, whereby it is expanded with the help of heat the condensed refrigerant was cooled in the evaporator tubes 101. The cooled air supplied to the housing 160 arrives into a line 161, which at one end with the Manifold 157 is connected by a side wall thereof, as shown at 162 in the drawing. One Valve means such as flap 163 eats Provided in the manifold 157 to optionally air the line 157 - either from the condenser outlet line 155 or the evaporator outlet line 161. Located For example, the flap I63 in the in ilg. 15th position shown transversely to the distribution line 157 »air from the line 161 to the line 157 and air from the Condenser exit line 155-v / ird at the entry into the line Ί57 prevented. The other end of the line 161 is with the tick line section 164a connected by a side wall thereof, as indicated at 161a, and a valve device,

- 37 -309835/0545

se

like a flap 161b is provided to selectively access refrigerated To allow air from line 161 to line 164a.!

The air distributed through the line 157, which is inside the Building exits through one or more of the outlets 158, is returned to the device through a return line 164, this line being divided into two sections 164a and 164b, with a valve, for example a flap 164c., being present is to selectively supply the returned air to branch 164a or 164b. Branch line 164a leads from the line 164 to the fresh air inlet line I50 and is with this connected on its side wall at 165. The other branch line 164b is connected to the fluid inlet chamber of the evaporator E_ and further to the air distribution line 157 »where a Valve, for example a flap 164d, is provided to optionally the flow of the recirculated air to the evaporator inlet E or to the air distribution line 157 in the desired Way to control.

According to FIG. 15 are for the purpose of cooling or air conditioning the building the fresh air inlet flaps in summer or in warm climatic zones 153 open and likewise the flaps 156 of the condenser outlet line 155i while the flap I63, as shown, is arranged such that the line 161 is opened and cooled air is supplied to the distribution line 157 while the same is sealed off from the condenser outlet line 155 from air. The flap 161b_ in the Line 161 is closed, preventing the escape of cooled air through branch line 164a into branch line 164b will. Furthermore, the flap 164d in the line 164b is closed and the flap 164 £ is arranged in the manner shown, that line 164a_ is closed and line 16 ^ b_ is open so that all returned through line 164 Air is led to the inlet of the evaporator.

When operating the in ^T ig. 15 plant shown arrives cie

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all of the heated air given off by the condenser C_ to the outside through the line 155 and does not enter the distributor line 157. On the other hand , all of the cooled air released by the evaporator E_ reaches the line via line 161 and is distributed by this to the outlets 158 distributed throughout the building. The air released into the building is returned to the device via line 164. Since the flap I64.d in the branch line 164b. is closed and the flap 164c. is compared to the branch line 164a, closed and opened with respect to the branch line 164b_, the entire returned from the line 164 air passes through the branch pipe 164b to the evaporator E ₁ where it is cooled again and circulated in the manner described by the building.

Me operation in winter or in cold climates are shown in FIG. 16, the inlet valve is closed 153 for fresh air and the like, the condenser outlet flap 156 and the flap 163 is arranged such that the line is completed 161 and the whole heated air from line enters the manifold 157. Furthermore, the flap 164c is closed with respect to the branch line 164b_ and opened with respect to the branch line 164a so that the air returning from the line 164 can enter the condenser inlet line 150. In this way , all of the air heated by the condenser £ is fed into the line 157 during operation. A portion of the heated air is distributed to the building outlets 158 and the air returned from line 164 passes through branch line 164a to condenser inlet line 150 to be reheated and recirculated in the manner described. Most of the heated air is conducted to the inlet of the evaporator via branch line 164b and cooled air from the evaporator passes through line 161 into branch line 164a.

By short-circuiting the evaporator air flow through the Condenser according to Fir. 16 the temperature and pressure of the

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CH-7264/7370

Evaporator increased and temperature and pressure of the condenser decreased. The reduced pressure increase on the refrigerant compressor in connection with a reduction in the compressor speed during winter operation, the compressor line is reduced. The operation of the compressor at low pressure ratio and low speed represents idling operation during winter.

However, in the described winter operation, the amount of heat that is not absorbed by the condenser C_ and by the the air emitted by the condenser is taken in, be slightly smaller than is normally required to heat the building, for which the performance of the cooling system is designed to properly air-condition the building, and therefore can An increased supply of heat to the boiler may be required in order to provide adequate heating in winter or in cold climates to deliver.

In the dual-circuit system working with two iluids, some pressure working fluid is passed from the Keεseidampfrohren 43 in a shunt to the turbine directly to the housing chamber Y or YJ_ in order to compensate for the increased heat load on the boiler and to reduce the power generated by the turbine 35. This shunt can, as best from i ⁿ ig. 6, can be achieved in that a number of bypass lines 170 are each connected at their outer ends to one of the boiler connection pipes 4-3, as indicated at 171, and at their inner ends via an inlet opening 172 to a common valve chamber 173 in a valve body 174 stay in contact. The valve body 174- is fastened coaxially in the housing chamber Y or YJ_ by means of a cross strut 175. An outlet from the valve chamber 173 takes place via a coaxial valve opening 176 into a small outlet chamber 177 and subsequently through a number of radial channels 178 to the housing chamber Y or Y ' . The steam pipes 17Ο are dimensioned such that they divert such a long boiler steam that is sufficient to

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power to compensate for the reduced compression load to reduce while maintaining the intended speed of the boiler-condenser-evaporator unit in winter operation .

The valve port 176 is normally through a valve element

179 closed, which in its closed position by a spring

180 is printed between the valve 179 and a locking pin 181 is arranged, which is screwed into the valve body 164. The valve element 179 has a coaxially arranged one Valve stem 182, the actuation of which moves valve element 179 against spring 180, around valve opening 176 to open what by means of a coaxial fluid-tight bellows I83 takes place via a coaxial plunger 184-. The bellows I83 lies in a chamber 185 at the inner end of the machine shaft 10. The tössel 184 extends completely through the shaft 10 out the end thereof and through a coaxial stationary hub member 186 and a magnet coil attached to the end thereof 187, as best seen in FIG. The outer end of the machine shaft 10 is in a stationary hub element 186 is supported by means of bearings 188, and the hub element 186 is held in its stationary position by a pin 189, which axially at the front of one of the radial is spokes 19 and is fastened in a stationary radial arm 190 on the hub element 186 according to FIG.

The magnetic coil 187 has the usual winding 187a, the outer end of the plunger 184 forming the core 187b of the magnetic coil, as can be seen from FIG. 9. When the solenoid 187 is excited, the ktössel 184 in the arrangements of the above. 6 and 9 moved to the left, whereby the valve opening 176 is opened and part of the boiler steam in the pipes 43 passes through the surrounding pipes 170 and the radial channels 178 in the bypass to the turbine power to the chamber Ί_ or YJ_ . The excitation of the solenoid can, if desired, by a hand-operated container or automatically, for example by a

- 41 -

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temperature-sensitive thermostat switch. In order to the majority of that is contained in the working fluid in winter Heat is given off by the condenser to the air circulating in the building and only a small proportion of this energy is branched off by the turbine to drive the condenser and evaporator.

On the other hand, for winter and sin-off operation with a single fluid (split circuit), the bypass valve arrangement for a two-fluid system is not used, instead a valve arrangement is used to restrict the flow of condensate from the collection chamber 164 through the tube 147 to the refrigerant expansion device RX ' , so that during such an operation of the expansion device BX ^1, only a condensate portion is returned which is adapted to the flow of the refrigerant through the compressor and which is necessary for the refrigerant in the evaporator tubes 101b. essentially at the level determined by the "overflow lip 99§" of the collector ring 99. This restricted refrigerant flow reduces the load on the compressor and limits the consumption of boiler fuel when the device is not used for cooling.

According to the present invention, the flow of the condensate to the expansion device RX ' is restricted by a pair of diametrically arranged axially arranged in the expansion ring between the chamber located therein and the tubes 147

extending valve chambers 193 is provided, in which ^ An axially movable valve element 194 is arranged in each case, which for example in Pig. 14A is shown. In the embodiment shown, each of the valves 194 is through a cable 195 »starting from a common actuating element 196 actuated, which is arranged coaxially in a housing 197 and is normally under liinffektunc: for example a spring 198 according to FIG. 14B in one position

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^ indet which corresponds to the opening position of the valves 194. the The actuation element 196 is actuated with the aid of a coaxially arranged btabs 182 'and one not shown otössels, which in the same way as the valve stem 182 and the previously described ütössel 184 which in fig. 6 and 9 can be actuated.

In operation, when the tab 182 'is moved to the left according to FIG. 143, the actuating element 196 is correspondingly displaced, whereby the additional cables 195 are actuated and the valves 194 are actuated in the closing direction, thereby reducing the flow of condensate to the expansion device RX' . It should be noted that the valves 194 are not moved into their fully closed position, in which the condensate flow to the expansion device RX ^{1 is} completely shut off, but that they reach a partially closed limit position in which the valves 194 are open to the extent that that they allow a sufficient condensate flow to the expansion device HX ¹ , which maintains the desired condensate level in the evaporator tube 1O1b_. In most systems, the reduction in the condensate flow to the expansion device HX ' through the valves 194 is about 10% or less of the condensate flow to the expansion device when the valves 194 are fully open.

If the ambient temperature in winter is higher than the evaporator temperature, it is possible to use the device as a heat pump to operate. With this operating mode, effective space heating is achieved by removing the heat not used by the cooling circuit added to the heat not consumed in the Rankine working group will. The arrangement of the air lines is similar to that according to FIG. 16 with the exception that outside air to the evaporator must be approved and directed by it.

The present invention is not directed to the use of a

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3 0 9 8 3 b / 0 Γ> U 5

turbine-like Kaltemi ttel expansion device of the type described, designed with nozzles and blades, and although in such expansion devices the expansion is isentropic and the maximum cooling effect for the one used Therraodynamic circuit enables valve or Capillary expansion devices are used in which the expansion takes place isenthalpically, with only there is a slight reduction in the cooling effect.

An embodiment of the invention which includes capillary tubes operating refrigerant expansion device is used, is shown in FIG. 17. With the exception of the following structural differences described is the device according to FIG. 17 is identical and corresponding to the device according to FIG. 3 Components in FIG. 17 which correspond to those in FIG. 3 have been given the same reference numerals to avoid unnecessary To avoid repetition of the description thereof.

According to FIG. 17, an annular refrigerant expansion chamber HX 'is arranged coaxially within the housing H and thus revolves in the manner described. Condensed refrigerant passes from the condenser tubes 81b_ to the expansion chamber RX ' and is discharged from the latter via a number of radial tubes 199 and then flows through a number of capillary tubes 200, from which the refrigerant flows into the adjoining tubes 101 of the evaporator E_ where it is vaporized in the manner described. Two or more capillary tubes 200 are used and are equidistantly spaced about the axis of rotation of the housing H. As can be seen, each capillary tube 200 is connected at its inlet end to one of the radial tubes 199 and extends radially outward to the housing wall 5 »through an opening 134 in the deflector plate 61, outside past the fender element 75 * of the torque armature TJ_ and then radially inward to the next evaporator tube 101 of the evaporator E_, the outlet end of the capillary tube directed axially into the evaporator tube 101

_ 44 -30983b / Ü545

fs

is to deliver expanded refrigerant to this. Since the temperature of the lubricant 118 is usually higher than that Temperature of the refrigerant in the capillary tubes 200, the sections of the latter that pass through the lubricant bath are guided, preferably thermally insulated from the lubricant, for example by means of a circumferential side arranged sleeve 201, which is closed at its opposite ends and which is filled with an insulating material 202 is.

The length and the inner diameter of the capillary tubes 200 are matched to one another and to the number of tubes used, in order to supply an amount of expanded refrigerant to the evaporator E_ which is necessary to achieve the desired Amount of cold is required. This coordination is critical and can be determined for each system by a specialist in refrigeration systems will.

In the embodiment according to FIG. 17, the torque armature Tj_ differs from the armature 50 described above, in that the circumferential hand section 72 with its expansion blades 98 of the armature T is omitted, so that the in Fig. 17 illustrated anchor TJ_ a central hub portion 66 · and a pendulum element 75 'on v / ei st and designed such that a sufficient counter-torque is supplied to the Anchor QV. to hold stationary and a rotation of the same against to prevent the counter-torque generated by the gearbox.

As in the previously described embodiments, the arrangement according to FIG. 17 also has a pressure lubrication system which uses a pitot pump which has a radial channel 116 in the pendulum element 75 ', on the outer side of which an L-shaped blade 117' is arranged, the inlet end of which is in the lubricant bath 118 is immersed and which faces away from the direction of rotation of the housing, so that a rotation of the housing with respect to the blade 117 ^{1 is} effective in order to transfer lubricant from the bath 118 via branch lines 121 'and 122' to the bearings and

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to the gearbox in the manner described above pump.

The operation of the embodiment of the invention according to i'ig. 17th is essentially the same as previously described and need not be repeated.

From the foregoing description it will be apparent that the present invention provides a new heating and cooling device with one with a closed fiankine circle working machine is created, which has a compact uniform design and which completely assembled and hermetically sealed and manufactured with the desired working fluid and refrigerant and can be shipped. The device works with isentropic expansion of the refrigerant, whereby the cooling and heating fluids are increased independently of other energy sources, the device having a quiet operation and has good efficiency.

309835/0545

Claims (20)

CH-726V737O Claims Heating and cooling device with rotary drive, marked a rotating engine through a cylindrical housing which is mounted for rotation on its axis in the housing, which has a coaxially arranged »drive element actuated by this, a refrigerant compressor, which is rotatably arranged coaxially in the housing and through the drive element with a predetermined first speed is driven to compress refrigerant vapor in the housing, a condenser assembly that is arranged coaxially next to one side of the housing and revolves with the housing as a unit in order to to condense refrigerant coming from the compressor, a refrigerant expansion device, which is arranged in the housing is »to expand condensed refrigerant in the condenser device, a device for supply from condensed refrigerant to refrigerant expansion device, one coaxially next to the other Evaporator arranged on the housing side, which rotates with the housing as a unit and from the expansion device Absorbs refrigerant and evaporates, a device for returning evaporated refrigerant from the evaporator to the Housing, and a gear arrangement arranged in the housing, which acts between the drive element and the housing to make the housing, the condenser and the evaporator as a unit to set in rotation with a predetermined second speed, which is considerably lower than the first-mentioned speed of the drive element and compressor. 2. Apparatus according to claim 1, characterized in that the condenser and the evaporator each have a number of have annular ribs which are axially spaced from one another and which form a fluid chamber, which on the outer At the end of which has an i'lui dein step, and through a - 47 - 30983b / 0 545 • Number of heat exchanger tubes running lengthways respectively through the fins of the condenser and evaporator extend to condense the refrigerant therein and to evaporate as a result of the heat exchange with the i'luid, which is outside the chamber by tilting flows. 3. Device according to claim 1 or 2, characterized in that that the gear arrangement for rotating the housing, the condenser and the evaporator with a second predetermined Speed is determined, which on the axial distance and the radius ratio of the capacitor and Evaporator fins is turned off so that the fluid through Vißcoeitäts-bcherkrrafts between the fins of the condenser and evaporator and promoted to the outside at a speed is accelerated, which ensures an optimal overall heat exchange between the i'luid and the refrigerant in the heat exchange pipes ?! of the condenser and evaporator. 4. Device according to one of claims 1 to 3 »characterized in that the cylindrical housing has an annular vessel in which an annular body of boiler fluid is maintained on the inner circumference of the housing during operation, a liquid-vapor boundary layer in a predetermined radial Distance outside the axis of rotation of the housing is present, and a device is provided to heat the fluid body in the boiler and to generate a steam pressure therein, and furthermore the ^um / ^au KrSr1; machine has a boiler steam expansion device to work from the boiler steam to drive the rotatable drive element, and by a condenser arrangement which is arranged coaxially next to a fcieite of the housing and rotates with this as a unit, wherein the condenser arrangement is designed in such a way to the boiler steam from the KeEseldarapf-üorpan- - 48 309835/0545 HS sion device to condense, and by a device for returning condensed boiler steam to the boiler. 5- device according to claim 4, characterized in that the boiler steam expansion device with a turbine a number of nozzles disposed in the housing and rotatable therewith and by a driven rotor and a shaft rotatable coaxially in the housing independently of the rotation of the housing. 6. Device according to one of claims 1 to 5, characterized in that that the refrigerant expansion device has annular nozzles and an annular row of expansion blades which are axially aligned with the nozzles lying, with the nozzles and the rows of expansion vanes are rotatable relative to one another at the speed of the housing. 7. Device according to one of claims 1 to 6, characterized in that that the gear arrangement between the drive element and the housing is a jacketed gear having a constant transmission ratio, which is arranged coaxially within the housing. 8. Apparatus according to claim 7> characterized by a Means cooperating with the jacketed gearbox for generating a counter-torque, which is the reaction torque counteracts that is generated by the gearbox when it is connected to the housing-condenser-evaporator unit the specified speed. 9. Apparatus according to claim 8, characterized in that the device for generating a counter torque a Pendelelenent, which is at least one of the transmission gears is connected and which has a - 49 -309835/0545 SO given density and dimensions, un the gear wheel to be defined circumferentially opposite the housing axis. 10. Device according to one of claims 7 to 9j characterized in that an annular array of non-rotatable expansion vanes is arranged in the shuttle and the refrigerant expansion nozzles in axial direction opposite. 11. Device according to one of claims 1 to 10, characterized by two different fluids for the boiler and the refrigerant, with a partition wall in the housing, which divides the interior of the housing into a chamber for refrigerant fluid and a chamber for boiler fluid divided, wherein the first-mentioned chamber is located next to the evaporator and the inlet to the refrigerant compressor and with this is connected, while the other chamber for the boiler expansion steam next to a section of the condenser lies and is connected to this in order to condense the exhaust steam contained therein, and by a device, to compressed refrigerant fluid from the compressor to a other section of the condenser to condense the refrigerant contained therein. 12. Device according to one of claims 1 to 10, characterized in that a single fluid as the boiler i'luid and refrigerant fluid is used, and that a partition is present in the housing, which the housing interior into a low-pressure refrigerant chamber, which is next to the evaporator and the inlet to the refrigerant compressor is arranged and is in communication therewith, and a Cooking pressure chamber for the boiler expansionEabdampf and that divided by the compressor released compressed refrigerant, which is arranged next to the condenser and with - 50 - 309835/0545 CH-7264/7370 nasty is related to the boiler exhaust steam and the condense the compressed refrigerant contained therein. 13. Device according to one of claims 1 to 11, characterized in that the capacitor arrangement is separate from ser and inner concentrically arranged capacitor sections has, each for the ExpansionsejLnriphtungsabdampf and the refrigerant vapor are determined ujid the coaxially next to one side of the housing and of the boiler are arranged to circulate with the same, wherein 0 the condenser section a number of in the axial Having spaced annular sibs, the at a distance from the ribs of the other section in order to create a thermal gap therebetween a number of heat exchanger tubes running axially through the hips of the outer condenser section extend, around the expansion device exhaust gases located therein to condense, and through a number of heat exchanger tube s that extend axially through the ribs of the inner capacitor section extend to condense refrigerant vapor contained therein, the exhaust vapor of expansion device and the refrigerant vapor in the heat exchanger tubes is condensed by means of heat exchange with a cooling fluid which is located between the ribs of said Sections flows outwards. 14. The device according to claim 13 »characterized in that the ribs of the outer and inner capacitor sections are arranged in radial alignment with one another and that the axial distance between adjacent hips of each section to the speed of the same and turned off the kinematic viscosity of the cooling fluid and has a Taylor number at which the cooling fluid is used in the ratio of the inner radius and outer radius of the ribs by viscosity ocher forces spirally between the tilting to the outside and essentially on - 51 -30983b / ü545 CÄ-726V737O a speed is accelerated, which an optimal heat exchange between the cooling fluid and the vapors in the heat exchanger tubes for condensation of these vapors enables. 15 · Device according to one of claims 1 to 11, characterized by a bypass device through which a part of the pressure steam from the boiler to the boiler steam expansion device around is fed directly to the capacitor. 16. The device according to claim 15 * characterized by a Valve device, which is selectively operable to the flow of boiler steam through the bypass device to control. 17 · Device according to one of claims 1 to 16, characterized in that that the device for supplying condensed refrigerant to the refrigerant expansion device a device which is operable to increase the amount of the refrigerant expansion device supplied to restrict condensed refrigerant to a predetermined limit. 18. The device according to claim 17 »characterized in that the device for restricting the supply of condensed refrigerant to the expansion means is normally one has opened Venti! device, the optional can be actuated in a predetermined partially closed position. 19 · Device according to one of claims 1 to 18, characterized in that that the refrigerant expansion device has a number of capillary tubes which are within the Housing circumferentially equidistant from one another are arranged and rotatable with the housing, wherein the - 52 309835/0545 Length of the capillary tubes based on their flow cross-section and the number of tubes is adjusted in such a way that aa £ the evaporator an amount of expanded refrigerant is supplied to provide the specified cooling capacity, 20. Cooling and heating device according to one of claims 1 to 19 »characterized by a fluid inlet line which is connected to the inlet to the condenser fluid chamber, through a housing which forms a chamber that surrounds the condenser, for heated, through the condenser fins to receive externally released fluid through a discharge line connected to the condenser chamber. for receiving heated fluid therefrom, through a fluid distribution line which is connected to the drain line is to direct heated fluid from the vent line to a remote zone and through a return line from this zone, which opens into a first branch line connected to the air inlet line to the condenser chamber and which also opens into a second branch line which connects to the fluid inlet chamber of the evaporator and connected to the air distribution duct by a housing defining a chamber containing the evaporator uraschlosst to get out of this through the evaporator fins to receive outward escaping cooling fluid, through a line for the cool fluid, which is connected to the evaporator chamber is connected to receive from this cool fluid, the line for the cool fluid also with the first branch return and is connected to the manifold, through a valve device, which is optional can be actuated to control the fluid flow in each case from the drain line and to control the line for the cool fluid to the distribution line, and by valve means ;, which is selectively operable to control the fluid flow of the Return line to the first and second branch lines and between the latter and the line for the cool Control fluid and the fluid distribution line. - 53 309835/0545 SH ^X Blank page