US3863454A

US3863454A - Rotary heat engine powered two fluid cooling and heating apparatus

Info

Publication number: US3863454A
Application number: US386630A
Authority: US
Inventors: William A Doerner
Original assignee: EI Du Pont de Nemours and Co
Current assignee: EIDP Inc
Priority date: 1972-02-22
Filing date: 1973-08-08
Publication date: 1975-02-04
Anticipated expiration: 1992-02-04

Abstract

Rotary closed Rankine cycle cooling and heating apparatus utilizing separate engine power fluid and refrigerant fluid. The apparatus includes a rotary boiler, power fluid expander and condenser coupled with a refrigerant compressor, refrigerant expander and refrigerant evaporator. The components are disposed on a common axis with the condenser and evaporator axially spaced and the boiler, power fluid expander, refrigerant compressor and expander compactly arranged in a housing between the condenser and evaporator. The housing, condenser and evaporator are mounted for coaxial rotation together as a unit. The power fluid expander is driven at a predetermined speed by pressure power fluid generated in the boiler and in turn drives the refrigerant fluid compressor. The refrigerant expander is of the capillary type constructed and arranged with respect to the evaporator to automatically control the capacity balance of the refrigerant system. The entire unit is hermetically sealed and the Rankine cycle power system is adapted and designed for use with high molecular weight fluids. In one disclosed embodiment of the invention the rotary housing-condenser-evaporator unit is rotationally driven at constant speed by the power fluid expander through an internal occluded fixed-ratio gear train and torque anchor, and in another disclosed embodiment, the housingcondenser-evaporator unit is rotationally driven at constant speed by an external motor and the power fluid expander drives an internal alternator that provides electric current for the external drive motor and other electrical equipment.

Description

United States Patent Doerner 1 Feb. 4, 1975 ROTARY HEAT ENGINE POWERED TWO FLUID COOLING AND HEATING APPARATUS [75] Inventor: William A. Doerner, Wilmington,

Del.

[73] Assignee: E. I. du Pont de Nemours and Company, Wilmington, Del.

[22] Filed: Aug. 8, 1973 [21] Appl. No.: 386,630

Related US. Application Data [63] Continuation-impart of Ser. No. 316,851, Jan. 2, 1973, which is a.continuation-in-part of Ser. No. 227,902, Feb. 22, 1972, abandoned.

Primary ExaminerMartin P. Schwadron Assistant Examiner-Allen M. Ostrager Attorney, Agent, or Firm-Howson and Howson [57] ABSTRACT Rotary closed Rankine cycle cooling and heating apparatus utilizing separate engine power fluid and refrigerant fluid. The apparatus includes a rotary boiler, power fluid expander and condenser coupled with a refrigerant compressor, refrigerant expander and refrigerant evaporator. The components are disposed on a common axis with the condenser and evaporator axially spaced and the boiler, power fluid expander, refrigerant compressor and expander compactly arranged in a housing between the condenser and evaporator. The housing, condenser and evaporator are mounted for coaxial rotation together as a unit. The power fluid expander is driven at a predetermined speed by pressure power fluid generated in the boiler and in turn drives the refrigerant fluid compressor. The refrigerant expander is of the capillary type constructed and arranged with respect to the evaporator to automatically control the capacity balance of the refrigerant system. The entire unit is hermetically sealed and the Rankine cycle power system is adapted and designed for use with high molecular weight fluids. In one disclosed embodiment of the invention the rotary housing-condenser-evaporator unit is rotationally driven at constant speed by the power fluid expander through an internal occluded fixed-ratio gear train and torque anchor, and in another disclosed embodiment, the housing-condenser-evaporator unit is rotationally driven at constant speed by an external motor and the power fluid expander drives an internal alternator that provides electric current for the external drive motor and other electrical equipment.

31 Claims, 11 Drawing Figures PATENTEB FEB 4I975 sum 2 or s PATENTED FEB 41975 SHEET l 0F 6 ROTARY HEAT ENGINE POWERED TWO FLUID COOLING AND HEATING APPARATUS This application is a continuation-in-part of my application Ser. No. 316,851, filed Jan. 2, 1973 which is a continuation-in-part of my earlier application Ser. No. 227,902, filed Feb. 22, l972, now abandoned.

This invention relates to rotary engine powered cooling and heating apparatus, and more particularly to closed Rankine cycle engine powered cooling and heating apparatus utilizing separate engine power fluid and refrigerant fluid and having a condenser for the power and refrigerant fluids and an evaporator for the refrigerant fluid coupled to the engine for rotation therewith as a unit.

An object of the present invention is to provide a rotary closed Rankine cycle engine powered cooling and heating apparatus that is of compact, unitary construction and both quiet and efficient in operation, and which is readily adapted to generate auxiliary electrical power.

Another object of the invention is to provide a rotary engine powered cooling and heating apparatus having the features described that is hermetically sealed and does not require high speed seals for separating portions of the apparatus operating with different power and refrigerant fluids at different pressures.

Another object of the invention is to provide a rotary engine powered cooling and heating apparatus of the character set forth that is operable to function either as a space cooler or heater as desired and the rotary condenser and evaporator function also as blowers for circulating the cooling or heating fluid independently of other power sources.

Still another object of the invention is to provide cooling and heating apparatus as set forth employing a novel arrangement of capillary expander for the refrigerant fluid whereby the capacity balance of the system is automatically controlled.

A further object of the invention is to provide a cooling and heating apparatus embodying the features set forth that can be manufactured and shipped fully assembled, hermetically sealed and charged with the refrigerant fluid and the power fluid.

These and other objects of the invention and the various features and details of the construction and operation thereof are hereinafter set forth and described with reference to the accompanying drawings, in which:

FIG. 1 is a typical sectional view diametrically through one embodiment of a rotary heat engine powered apparatus according to the present invention;

FIG. 2 is a transverse sectional view on line 2-2, FIG. 1;

FIG. 3 is an enlarged fragmentary vertical sectional view diametrically through the rotary heat engine;

FlG. 4 is a schematic view of the fixed-ratio gear train on line 44, FIG. 3;

FIG. 5 is an end elevational view in reduced scale of the torque anchor and pendulum shown in FIG. 3;

FIG. 6 is a view similar to FIGS. 1 and 3 showing another embodiment of the present invention;

FIG. 7 is a fragmentary view partially in section on lines 77, FIG. 6;

FIG. 8 is an end elevational view of the disclosure in FIG. 7;

FIG. 9 is a schematic diagram of an alternator circuit for the embodiment of the invention shown in FIG. 6;

FIG. 10 is a perspective view showing the apparatus of the present invention with associated duct work and valving arranged for cooling or air conditioning a building in the summertime or other warm temperature climate; and

FIG. I1 is a view similar to FlG. 10 showing the duct valving arranged for heating a building in the winter time or other cool temperature climate.

A two fluid rotary engine powered cooling and heating apparatus according to the present invention comprises a rotary closed Rankine cycle engine including a rotary housing H containing a power fluid boiler B, power fluid expander PX and a refrigerant compressor P. A condenser C having separate portions C and C" for condensing the power fluid and refrigerant fluid is mounted coaxially at one side of the engine housing, and a refrigerant evaporator E is coaxially mounted at the opposite side of the engine housing. The power fluid expander PX is driven at a predetermined speed by the pressure power fluid generated in the boiler B and in turn drives the refrigerant compressor P. The housing-condenser-evaporator unit is rotationally driven at a predetermined lesser speed. Refrigerant condensed in the condenser is delivered to the evapora tor through a capillary expander in which the capacity balance of the expander is controlled and determined automatically by the pressure drop across the expander. The entire housing unit is hermetically sealed and the closed Rankine cycle power engine is adapted and designed for use with high molecular weight fluids and different high molecular weight fluids may be employed for the boiler power fluid and for the refrigerant fluid.

Referring to the drawings, in the embodiment of the invention shown in FIGS. 1-4 of the drawings, and with reference particularly to FIG. 1 thereof, the rotary engine housing H comprises a central generally cylindrical portion 1 and opposite

end housing portions

2 and 3, respectively.

The central housing portion 1 includes an annular boiler compartment B and a lubricant sump compartment S, the latter being of slightly larger diameter than the boiler compartment B and being axially spaced therefrom by an intermediate cylindrical portion 4 of less diameter than the boiler B which has formed therein an annular vaporizing chamber 5 that is heated by thermal conduction from the boiler B. The boiler chamber B is defined by an outer continuous circumferentially extending wall 6, side walls 7 and 8 and an inner continuous wall 9. The sump compartment S is defined by an outer continuous circumferentially extending wall portion 10 and

side walls

11 and 12, respectively. Preferably, the outer circumferential wall 6 of the boiler is provided with circumferential fins 13, as shown, to increase the heat transfer from the combustion gases and, alternatively, the boiler chamber wall 6 may be configurated or contoured to provide an expander or extended thermal conductive surface area in accordance with the invention disclosed in US. Pat. No. 3,690,302, issued Sept. 12, 1972. The outer circumferential wall 10 of the sump compartment S is also provided with circumferential fins 14 to increase the heat transfer to the surrounding air from said wall 10 and thereby tend to cool lubricant in the sump S.

The engine housing H embodying the construction described is mounted for rotation about its axis by means of shafts l5 and 16 secured to and extending coaxially outward endwise from the

housing end portions

2 and 3, respectively. The outer end of the shaft is journalled by means of a bearing 17 in a stationary hub 18 that is fixedly supported by means of radial spokes 19 from a circumscribing concentric ring 20 that in turn is fixedly supported by a standard 21 from a fixed base or support 22 of the machine. In similar manner. the outer end of the shaft 16 is rotatably journalled by means ofa bearing 23 in a stationary hub 24 that is supported by means of radial spokes 25 within a circumscribing concentric ring 26 that in turn is fixedly supported by a standard 27 from the fixed base 22 of the machine. From the foregoing, it will be apparent that the engine housing H including the central portion 1 containing the annular boiler B and refrigerant sump S, together with the

end housing portions

2 and 3 and the

shafts

15 and 16, constitute a unitary structure that is rotatably mounted by means of the

bearings

17 and 23 for coaxial rotation as a unit about the engine axis.

The rotary boiler is adapted to be driven about its axis at a predetermined speed of rotation calculated to create the centrifugal force necessary to dispose and maintain the selected boiler power liquid therein uniformly distributed circumferentially about and in contact with the inner surface of the outer peripheral wall 6 of the boiler with a liquid/vapor interface, designated i in FIG. 1, that is highly stable and essentially cylindrical and concentric with the axis of rotation of the boiler. Essentially the liquid/vapor interface 1' is disposed at a predetermined radius from the rotation axis of the boiler to provide high boiling heat fluxes in excess of those obtainable at ambient gravity.

Referring to FIGS. 1 and 2, the annular body ofliquid in the boiler may be heated to the required boiling temperature to vaporize the same, for example, by the combustion of a suitable fuel-air mixture in a stationary combustion box 30 that circumscribes the rotatable boiler chamber B. Fuel for combustion is discharged into the combustion box 30 from a nozzle 31 at the required rate and pressure, and air for mixture with the fuel is discharged into the combustion box through a plurality of ports 32 in the peripheral wall 33. A hood structure 34 defines a plenum chamber 35 into which the air is supplied through a duct 36 at the pressure and volume required for efficient combustion of the fuel to heat the liquid in the boiler casing to the desired temperature. The residual combustion gases are discharged through an exhaust duct 37, and a stationary transverse baffle 38 configurated for complementary interfitting cooperation with the configuration of the boiler peripheral wall 6, is mounted intermediate the fuel nozzle 31 and exhaust duct 37 to control recirculation of the combustion gases.

Coaxially mounted within the engine housing H for rotation with the latter is an annular power fluid expander PX having a central bore 40 extending coaxially therethrough as best shown in FIG. 3. The expander PX is fixedly supported within the engine housing H by an annular support ring 41 that is in turn supported coaxially within the engine housing by an integral radially extending partition portion 42 that terminates at its outer periphery in an axially extending flange portion 43 connected to the inner surface of the adjacent wall of the housing and forming therewith an annular collector ring 44 for the power fluid condensate that is condensed in the condenser. The expander support ring 41 and its radial partition portion 42 thus form with the adjacent end portion 3 of the housing H interiorly of the latter an engine power fluid compartment X that is substantially closed from the remainder of the interior of the engine housing H. However, since there are no contacting shaft seals some migration of fluid along the turbine shaft is possible and means, hereinafter described, are provided for separating refrigerant fluid and power fluid in the event that admixture thereof should occur.

The power fluid expander PX is in the form of a single stage shrouded turbine comprising a rotor 45 having a series of turbine blades 46 arranged peripherally thereabout. The turbine rotor 45 is fixedly mounted on a shaft 48 for coaxial rotation independently of the rotary housing-condenser-evaporator unit. The shaft 48 is rotatably mounted within the bore 40 of the expander PX. An annular series of nozzles 50 is provided within the power fluid expander PX coaxially adjacent the turbine rotor 45 and in confronting relation to the blades 46 thereof. An annular high pressure manifold 51 is provided in the expander PX and opens to the turbine nozzles 50.

High pressure vapor is supplied from the boiler chamber B to the manifold 51 through a plurality of radial ports or passages 52 and a corresponding plurality of radially disposed vapor tubes 53 arranged in equally spaced relation circumferentially of the axis to insure rotational balance. Thus the high pressure vapor generated in the boiler chamber B passes from the latter through the tubes 53 and passages 52 to the high pressure manifold 51 from which it is discharged through the turbine nozzles 50 and impinges upon the blades 46 to drive the turbine rotor 45 and its shaft 48 at the desired speed of rotation.

An annular diffuser 55 is provided in the ring 41 coaxially adjacent the turbine rotor 45 to receive the exhaust vapor from the expander, and the inlet opening thereto is disposed in confronting relation to the turbine blades 46 at opposite sides thereof from the nozzles 50. Exhaust vapor is discharged from the diffuser 55 into the engine power fluid compartment X of the housing H from which it passes into the condenser C as hereinafter described. A plurality of axially extending radial partitions 56 are provided in the diffuser 55 and these, together with the radial vanes 57 in the compartment X, function to maintain the angular velocity of the exhaust vapor the same as that of the rotating housing-condenser-evaporator unit.

Also mounted within the engine housing H coaxially adjacent the power fluid expander PX is a refrigerant compressor or pump P. The compressor P comprises an annular housing structure 60 that is fixedly supported within the engine housing H by means of an axially extending annular support sleeve 61 having integrally therewith a radially extending circumferential partition portion 62 that is connected at its periphery to the internal surface of the central cylindrical portion 1 of the housing H. The partition 62 is spaced axially from the partition 42 and subdivides the remainder of the engine housing H, other than the fluid compartment X, into a refrigerant compartment Y and an intermediate compartment Z that is evacuated to provide thermal insulation between the higher temperature power fluid compartment X and the lower temperature refrigerant fluid compartment Y. By the construction described, it will be apparent that the compressor housing 60 rotates coaxially as a unit with the rotary housing-condenserevaporator unit.

As shown in FIG. 3 of the drawings, the compressor housing structure 60 defines interiorly thereof a coaxial annular chamber 64 having radial openings 65 thereto from the refrigerant fluid compartment Y of the housing H. Mounted in the chamber 64 of the pump P is a compressor rotor 66 that is keyed to the engine shaft 48 to be driven thereby. The turbine shaft 48 extends coaxially through the compressor housing structure 60 and is journalled therein by bearings 68 and 69, respectively. Refrigerant vapor in the compartment Y of the housing entering the compressor or pump P through passages 65 is compressed by the rotor 66 and then discharged through a plurality of radial passages 70 to an annular manifold 71 and thence through a plurality of radial passages 72 to an annular refrigerant manifold 73. The manifold 73 circumscribes the compressor or pump P and is mounted to rotate with the latter and the housing-condenser-evaporator unit by means of a plurality of radial vanes 74 that are secured between the manifold 73 and adjacent surface of the radial partition 62, for example by welding.

In the embodiment of the invention shown in FIGS. 1-3 of the drawings, the housing-condenser-evaporator unit is rotationally driven by a mechanical coupling provided between the expander PX and the housing H so that during operation of the engine, after start-up, the unit is rotationally driven continuously by the primary power output generated by the engine. This is accomplished by means of an internal occluded fixedratio gear train arranged coaxially interiorly of the housing H, for example similar to that shown and described in the copending application of Max F. Bechtold Ser. No. 206,779, filed Dec. 10, 1971, now US. Pat. 3,769,796.

As shown, the fixed-ratio gear train is in the form of a planetary gear system comprising a sun gear 76 fixedly mounted on and driven by the turbine shaft 48. The driven sun gear 76 drives a plurality of compound planet gears 77 each secured on a stub shaft 78 that is journalled by means of bearings 79 and 80 in an anchor plate member 81 and planet gear carrier ring 82, respectively. Carrier ring 82 is rotationally mounted by means of bearings 83 and 84 on the coaxially extending hub portion 60a of the compressor housing structure 60. As shown, the sun gear 76 is meshed with and rotationally drives the larger diameter gear 77a of each compound planet gear 77, and the smaller diameter gear 77b of each compound gear is meshed with and drives a coaxial annular ring gear 86 recessed within and carried by the compressor housing structure 60. The anchor plate member 81 and the gear carrier ring 82 are connected to a non-rotating torque anchor member T having a coaxially disposed central hub portion 87 that is journalled on the inner end of the engine housing shaft by means of

bearings

88 and 89.

The torque anchor T includes an inner circumferential cup-shaped portion 90 formed integral with the hub portion 87 and coaxially disposed adjacent the fixedratio gear train just described. The compound gear carrier ring 82 is connected to the non-rotating torque anchor T by a plurality of circumferential equally spaced connector rods 91 each having its inner end fixedly mounted in the carrier ring 82 and its outer end portion extending through the anchor plate 81 and into an aligned opening 93 in the cup portion 90 of the torque anchor T, each of said connector rods 91 being secured in the anchor plate 81 by means of a nut 94 threaded thereon. The torque anchor T is held stationary with respect to the rotary housing-condenser-evaporator unit by means of a pendulum element 95 that projects radially outward from the rim of the cup-shaped portion of the torque anchor T.

The pendulum 95 is of predetermined density. dimensions and location to generate the desired counterforce to oppose the external reaction torque of the air drag in the condenser and evaporator and, as a typical example, a pendulum element 95 made of steel in the configuration shown in H6. 5 of the drawings having an inner radius of 7.0 inches, an outer radius of l0.0 inches, a width of 0.75 inch, an arc length of and weighing 8.5 pounds, will provide a countertorque force sufficient to hold the torque anchor T stationary and prevent rotation thereof against a reaction of 3.9 ft. lbs. which is the torque required to rotate the boiler-c0ndenser-evaporator unit at 2,400 rpm. when both the condenser and evaporator are pumping air.

By reason of the non-rotating torque anchor T the compound planetary gears are fixedly positioned so that their axes do not rotate or move circumferentially relative to or about the engine axis. Thus, the balance of the power output of the engine expander PX not used to drive the compressor rotor 66 is transmitted from the driving sun gear 76 through the compound planetary gears directly to the driven ring gear 86 on the rotary boiler-condenser-evaporator unit thereby rotationally driving said unit at the fixedspeed of the particular gear train.

As previously stated, exhaust vapor discharged from the turbine diffuser 55 into the engine compartment X of the housing H enters the condenser C where it is condensed, and, in accordance with the present invention, the compressed refrigerant discharged from the compressor P to the manifold 73 is also condensed in the condenser C.

The condenser construction shown comprises closely radially spaced outer and inner concentrically arranged annular condenser sections C and C" for the engine power fluid and the refrigerant fluid, respectively. By providing such concentric outer and inner condenser sections C and C a thermal break or gap is provided between the two condenser sections so that the outer power fluid condenser section can be operated at much higher temperatures for more efficient heat transfer than the substantially lower temperatures desired for efficient operation of the inner refrigerant condenser section.

Referring to the drawings, the outer and inner concentric condenser sections C' and C" each comprises a coaxial array of closely spaced annular fins 96' and 96" fabricated of metal having high thermal conductivity as previously described, and disposed in radial alignment with respect to each other for efficient air flow therebetween. Heat exchange tubes 97 for the boiler power fluid extend longitudinally through the fins 96' of the outer condenser section C and heat exchange tubes 97" for the refrigerant fluid extend in similar manner longitudinally through the fins 96" of the inner condenser section C. As previously described, the fins 96' and 96" consist of separate or independent annular disk elements and are supported and secured in predetermined equally spaced parallel relation with respect to one another by the heat exchange tubes 97' and 97",

respectively, the fins preferably being bonded to the heat exchange tubes to provide maximum thermal conductivity therebetween.

The inner end portions of the heat exchange tubes 97' of the outer power fluid condenser section C extend through the adjacent wall of the housing H and the tubes are in open communication with the condensate collector ring 44 and at their outer ends are connected to a common manifold 99 formed in an annular outer end ring 100 that is supported from the engine end housing portion 3 by a plurality of circumferentially equally spaced radial spokes 101. Power fluid condensed in the heat exchange tubes 97' of the condenser collects in the collector ring 44 and is returned through a plurality of circumferentially equally spaced radial tubes 102 to the boiler B where the power fluid condensate is again vaporized and the power cycle repeated.

With respect to the refrigerant condenser tubes 97", all but a predetermined small number, for example three, of said tubes 97" are closed at their inner ends by an annular plate 103 to which the inner ends of said tubes are secured, and the outer ends of all of the condenser tubes 97 are connected to a common manifold 104 also formed in the condenser end ring 100. The predetermined small number of the heat exchange tubes 97 that are not closed at their inner ends by the annular plate 103 are of longer length than the remainder of the heat exchange tubes 97 and extend through openings 106 in the plate 103 and through

larger openings

108 and 110 in the housing end portion 3 and radial wall portion 42 of the power fluid expander support ring 41, respectively, as more clearly shown in FIG. 3 of the drawings, and are connected at their inner ends to the annular refrigerant manifold 73 previously described. The

openings

108 and 110, just mentioned, are larger in diameter than the refrigerant heat exchange tubes 97" extending therethrough in order to accommodate insulating sleeves 112 of comparable diameter that concentrically circumscribe the portions of the heat exchange tubes 97" that pass through the power fluid compartment X in the engine housing H. The sleeves 112 are circumferentially spaced from the heat exchange tubes 97" and function to insulate the cooler refrigerant in the enclosed portions of the tubes 97" from the surrounding high temperature power fluid in the housing compartment X.

Liquid refrigerant condensed in the heat exchange tubes 97" flows outwardly endwise therein to the manifold 104 in the end ring 100 and thence inwardly through the aforesaid small number of said tubes to the annular refrigerant manifold 73 from which it is conducted by a small number of circumferentially arranged equally spaced capillary expander tubes 114 which deliver the low temperature mixture of refrigerant liquid and vapor to an annular inlet manifold ring 116 of the evaporator E. As shown in FIG. 3, a portion of each of the capillary expander tubes 114 passes through the vaporizing chamber of the central portion 1 of the engine housing H and is thermally insulated therefrom by a spaced circumscribing sleeve 118. Each capillary tube then extends radially to a point adjacent the periphery of the lubricant sump portion of the housing and thence axially through the peripheral wall of the latter and thence radially inward and into the refrigerant compartment Y of the housing with its end terminating in the evaporator inlet manifold 116.

The evaporator E comprises a coaxial array of closely spaced annular radial fins 120 and a plurality of heat exchange tubes 122 extending longitudinally through said fins arranged circumferentially in equally spaced relation about the engine shaft 15. The inner ends of the evaporator heat exchange tubes 122 extend through the radial wall portion of the housing end portion 2 and are connected to the refrigerant inlet manifold 116 as shown. The outer ends of the tubes 122 are mounted in recesses in an annular end ring 124 and connected to an annular manifold 126 provided therein. The end ring 124 is disposed coaxially adjacent the outermost of the evaporator fins 120 and supported from the engine housing end portion 2 by a plurality of circumferentially arranged equally spaced spokes 128. By the construction described, the evaporator E is fixedly mounted with respect to the engine housing H for rotation therewith and with the condenser C as a unit. The low temperature refrigerant delivered to the manifold 116 enters the evaporated heat exchange tubes 122 where it is evaporated and returned to the refrigerant manifold 116. The evaporator inlet mani fold 116 is in open communication inwardly thereof with the interior of the housng refrigerant compartment Y and hence evaporated refrigerant returned from the tubes 122 to the manifold 116 is delivered to the compartment Y of the engine housing and thence to the compressor P where it is again compressed to repeat the refrigerant cycle.

A feature of the invention resides in the construction and arrangement of the capillary expanders 114 and the evaporator E whereby the refrigerant flow rate in the capillary expander tubes 114 is automatically adjusted according to the refrigerant flow rate through the compressor P to thereby maintain the capacity balance of the refrigerant system. In this connection, it is desirable that the radial distance of the liquid level in the evaporator tubes 122 from the engine axis be greater than the radial distance of the refrigerant condenser tubes 97" from the engine axis so that the flow rate of refrigerant through the capillary expander tubes 114 is controlled by the pressure drop across the capillary expander tubes 114. This pressure drop is deter mined not only by the difference between the pressure of the vapor at the refrigerant manifold 73 and that of the vapor at the evaporator inlet manifold 116, but also by the difference in liquid level between the level r in the radially extending inlet portions of the expander tubes 114 adjacent the refrigerant manifold 73 and the level in the evaporator tubes 122.

Thus, when the compressor P delivers refrigerant at a high flow rate, the liquid lever r in the expander tubes 114 will move radially inward therein to provide the additional pressure necessary to drive the refrigerant through the capillary expander tubes 114 at the proper matching flow rate in relation to the delivery flow rate of the compressor P. Due to the amplifying effect of the centrifugal force created by rotation of the housing-condenser-evaporator unit, small variations in the liquid level r will compensate for wide variations in the flow rate of the refrigerant and the described arrangement of capillary expander and evaporator is 0perable to provide a capacity balanced system for any refrigerant flow rate from the designed flow rate of the particular apparatus to zero flow of the refrigerant,

The annular fins of the condenser C and evaporator E define interiorly thereof

coaxial inlet chambers

130 and 132, respectively, for a cooling fluid to be discharged outwardly by and between the rotating tins of the condenser and evaporator as hereinafter set forth. The inner diameters of the outer condenser end ring 100 and adjacent engine support ring 26 and the outer end ring 124 of the evaporator and the adjacent engine support ring 20 are the same as the inner diameters of the condenser fins 96" and evaporator fins 12, respectively, so as not to restrict the flow of fluid inwardly of the

chambers

130 and 132. Outwardly flared or bellshaped

fluid intake members

134 and 136 are fixedly mounted on the engine support rings 26 and 20, respectively, in coaxial relation outwardly adjacent the inlet ends of the

chambers

130 and 132.

The axial spacing between the adjacent annular fins 96' and 96" of the condenser sections C and C" and the relationship of the inner radius of the inner fins 96' to the outer radius of the outer fins 96' may vary between predetermined ranges or limits for any given range of speeds of rotation (r.p.m.) of the condenser, and are determined so as to utilize the viscous properties of the condenser cooling fluid and evaporator heat exchange fluid and the shear forces exerted thereon by the rotating fins to convey and accelerate the fluid radially outward between the fins of the condenser C and the evaporator E substantially to the velocity providing optimum total heat exchange between the fluids in the heat exchange tubes and the fluid passing outwardly between said fins.

The nature of the flow for rotational shear force devices is completely described by the Taylor number, N where:

d distance between fins w angular velocity (radians per sec.)

v kinematic viscosity We have found that most efficient pumping occurs when N 3.25. However, efficient fluid pumping does not lead to an efficient heat exchanger. Efficient pumping occurs when the energy transfer to the fluid is maximized. Efflcient heat exchange depends upon both the fin area and the difference between the speed of the tins and the velocity of the fluid flowing between them. Thus, for heat transfer, the Taylor number is not adequate by itself to completely describe an optimum configuration. We have found that for various combinations of inner radius (Ri) of the inner fins 96'' and the outer radius (R) of the outer fins 96' the Taylor number for efficient heat exchanger will always be greater than 4.5. The precise values of Taylor number and the ratio of the inner to outer radii of the fins depend upon the thermodynamic and transport properties of the fluids exchanging heat and whether the heat transfer mechanism for the fluid in the heat exchange tubes is boiling, condensing or convective.

For heat transfer to or from air on the fin side to or from a boiling or condensing fluid within the tubes, it has been determined that the Taylor number for an efficient heat exchanger is within the range of from 5.0 to 10.0 and the inner to outer radii ratio of the fins is within the range of from 0.70 to 0.85. For optimum results the Taylor number will be in the neighborhood of about 6.0 and the tin radii ratio will be in the neighborhood of about 0.77, and these values constitute good starting points for the design of an efficient heat exchanger according to the present invention. The particular optimum design and operating conditions for any given heat exchanger for installation can be determined by a person skilled in the art. It has been determined that the values of Taylor number and fin radii ratio for other gaseous fluids are essentially the same as the values stated for air.

The axial spacing between the fins of the evaporator E and the inner and outer radii ratio thereof is similarly determined with relation to the rotational speed of the unit and kinematic vicosity ofthe evaporator heat exchange fluid, such as air. to provide a Taylor number and fin radii ratio the same as previously described for the condenser C.

The location radially of the split or division between the fins 96' and 96" of the outer and inner condenser sections C and C is also important and depends upon a number of factors such as the power and refrigerant fluids employed, their thermodynamic cycles and heat transfer coefficients, the heat transfer properties of the particular materials of which the condenser fins and heat exchange tubes are fabricated, and must be determined for each case. The follow equation provides a good design starting point:

2 12 '1 iii/ r (11 2 o) Where A inner section fln area A outer section fin area q, inner section heat transfer rate outer section heat transfer rate t temperature of the air entering the condenser t saturation temperature of the refrigerant fluid in the inner section of the condenser t saturation temperature of the power fluid in the outer section of the condenser Incorporated in the apparatus is a forced-feed lubrication system utilizing a Pitot pump of the type described and claimed in my copending application Ser. No. 231,232, filed Mar. 2, I972, now U.S. Pat. No. 3,744,246. As shown, the Pitot pump comprises a tube that extends radially outward through the pendulum 95 and has at its outer end an L-shaped scoop portion 141, the inlet end of which is immersed in an annular bath of lubricant 142 extending circumferentially interiorly of the lubricant sump portion S of the engine housing H and facing in the direction opposite the direction of rotation thereof. From the pendulum 95 the tube 140 extends inwardly and has its inner end extending into the torque anchor hub portion 87 and connected to the axially extending lubricant passage 144 provided therein. From passage 144 lubricant is conducted through an S-shaped tube section 146 to a lubricant passage 148 formed coaxially in the turbine shaft 48 and having radial ports 149a, 150 communicating with the turbine shaft bearings 69 and 68 to supply lubricant thereto. Lubricant supplied to the bearing 68 drains through a passage 152 and returns to the lubricant bath 142 in the sump S, and lubricant supplied to the shaft bearing 69 drains in part back through radial port 149 to bearing 84. Lubricant overflow from hearing 84 and from bearing 69 drains back through the fixed-ratio gear train and similarly is returned to the lubricant bath 142 from which the lubricant is recirculated by the Pitot pump by reason of the rotation of the engine housing l-l relative to the non-rotating torque anchor T and its pendulum portion 95.

Any refrigerant vapor and other non-condensable gases that may migrate into the power fluid system of the engine will flow through the condenser tubes 97 and collect in the manifold 99 from which they are returned through a plurality of circumferentially equally spaced longitudinally extending tubes 154 to the refrigerant compartment Y of the engine. Similarly, since the volatility of the power fluid is much less than that of the refrigerant, any power fluid which may migrate into the refrigerant system will collect in the evaporator manifold 126 at the outer end of the heat exchange tubes I22 and overflow, as a power fluid rich mixture, into a plurality of circumferentially equally spaced radial weir tubes 156 and thence through a corresponding plurality of longitudinally extending tubes 158 to the refrigerant compartment Y of the engine. The migratory power fluid mixes with the lubricant in bath 142 while the liquid refrigerant tends to vaporize due to the elevated temperature of the bath 142 as compared to the evaporator. Migratory power fluid that collects in the lubricant bath 142 in the sump S raises the lubricant liquid level of the bath 142 and the excess power fluidlubricant mixture is removed therefrom by a radial tube 160 mounted in the pendulum 95 and having at its outer end an L-shaped scoop portion the inlet end of which faces opposite the direction of rotation of the engine housing H and disposed at the surface level of the lubricant bath 142. Power fluid-lubricant mixture picked up by the tube 160 is discharged from the inner end of said tube into an annular collector ring 163 from which it is conducted by a tube 164 to the annular vaporizing chamber previously described, wherein the power fluid is vaporized and returned by a plurality of circumferentially equally spaced tubes 166 to the power fluid compartment X of the housing H. The lubricant residue is not vaporized in chamber 5 and drains therefrom and is returned by a tube 168 to the lubricant bath 142 in the sump S.

In operation of the embodiment of the engine shown in FIGS. 1-5 of the drawings, it will be apparent at start-up that there will be no pressure vapor generated by the boiler B to drive the expander PX and in turn the housing-condenser-evaporator unit. Consequently, at start-up it is necessary to independently drive the housing-condenser-evaporator unit at the designed predetermined speed of rotation to establish and maintain the liquid/vapor interface i in the boiler chamber until the annular body of the power fluid liquid therein is heated to the temperature required to produce the desired pressure vapor to drive the engine rotor 45 and its shaft 48. This may be accomplished, for example, by means of a starter motor M driving a pulley 170 fixed on the evaporator end ring 124 through a belt 172. Means such as a clutch (not shown) can be provided for breaking the drive between motor M and pulley 170 when the engine attains normal operation, or the motor M can continue to be driven by the rotating housing-condenser-evaporator unit to function as a generator operable, for example, to provide electric power for external equipment and accessories such as batteries for the starter motor M, lights and the like.

In normal operation of the rotary engine shown in FIGS. 1-5 of the drawings, with the annular body of liquid in the boiler chamber heated to the required temperature and pressure by combustion of fuel-air mixture in the chamber 30, the pressure generated in the boiler is discharged inwardly through tubes 53 to the manifold 51 and thence through nozzles 50 into impinging contact against the turbine blades 46 thereby driving the engine rotor 45, shaft 48, compressor rotor 66 and the sun gear 76 at the desired predetermined speed of rotation. The sun-gear 76 through the fixedratio gear train previously described drives the rotary housing-condenser-evaporator unit at a predetermined substantially slower speed of rotation relative to the shaft 48 determined by the fixed-ratio of the gear train. In the embodiment of the invention shown in FIGS. l-S of the drawings, the direction of rotation of the housing-condenser-evaporator unit is opposite the direction of rotation of the turbine rotor 45 and shaft 48.

The exhaust vapor from the power fluid turbine discharges through the diffuser 55 into the-compartment X of the engine housing and enters the heat exchange tubes 97' of the outer condenser section C where it is condensed by the cooling fluid discharged outwardly between the fins 96', as previously described. The power fluid condensate flows inwardly in the tubes 97' to the collector ring 43 from which it is returned through tubes 102 to the boiler B at a controlled rate equal to the rate of vaporization of the power fluid in the boiler.

Refrigerant fluid in the housing compartment Y enters the compressor P through inlet passages 65, is compressed by the rotor 66 and discharged through diffuser passages 70, manifold 71 and passages 72 to the annular refrigerant manifold 73. From the manifold 73 the compressed refrigerant is delivered to the inner refrigerant condenser section C" through the small number of the heat exchange tubes 97" that is connected to said manifold 73 and is distributed by the manifold 104 into all of the refrigerant condenser heat exchange tubes 97" where it is condensed by the cooling fluid discharged outwardly between the fins 96", as previously described. The condensed refrigerant is returned to the refrigerant manifold 73 through the small number of heat exchange tubes 97" connected thereto and is delivered through the capillary expander 114 to the .evaporator inlet manifold 116 and thence into the evaporator heat exchange tubes 122 wherein it is evaporated by heat exchange with the fluid discharged outwardly between the evaporator fins 120, as previously described. Refrigerant fluid vaporized in the evaporator tubes 122 flows inwardly therein to the manifold 116 and thence into the refrigerant compartment Y of the engine housing to be again compressed, condensed and evaporated, as previously described.

A typical example of closed Rankine cycle rotary engine powered heating and cooling apparatus embodying the construction shown in FIGS. 1-5 and designed for an output of 8.77 hp at the turbine shaft 48, comprises a boiler B having a liquid level 1' diameter of 9.0 inches and an axial internal length sufficient to provide the heat input required to the boiler liquid from the combustion gases. The diameter of the boiler expander turbine at the blades 46 is of the order of 3.1 inches and the diameter of the compressor is of the order of 3.5 inches. The fins 96 of the outer power fluid condenser C have an outer diameter of 13.1 inches and an inner diameter of 12.1 inches. The fins 96" of the inner refrigerant condenser C have an outer diameter of 12.0 inches and an inner diameter of 10.0 inches. The axial length of the series of condenser fins 96' and 96 is l0.0 inches and the spacing between adjacent fins is 0.028 inches with the axes of the heat exchange tubes disposed at a radius from the rotation axis of the apparatus of 5.5 inches for the inner condenser section C" and 6.3 inches for the outer condenser section C. The fins 120 of the evaporator E have an outer diameter of 14.0 inches and an inner diameter of 11.0 inches. The axial length of the series of evaporator fins is 5.6 inches and the spacing between adjacent fins is 0.025 inches. The axially extending evaporator tubes 122 are also disposed at a radius of 6.25 inches from the rotational axis of the apparatus. The housing-condenserevaporator assembly is rotationally driven at a speed of 2,400 rpm. by the turbine through fixed-ratio gear train in the direction opposite to rotation of the turbine rotor 45. Using as the boiler power fluid a mixture of trichlorodifluorobenzene isomers, as disclosed in patent application Ser. No. 172,513, filed Aug. 17, 1971 by Max F. Bechtold and Charles W. Tullock, now Patent No. 3,774,393 and 1,1,2-trichloro-1,2,2-trifluoroethane as the refrigerant fluid, the specifications of a typical operation of the designed apparatus are as follows:

Evaporator pressure (psia) 2 7 Evaporator load (Btu/hr) 24,000: Evaporator air flow (cfm) 800. Available surplus power (watts) 850.

In the foregoing example the power fluid condenser pressure (4.0 psia) is somewhat higher than the evaporator pressure (2.7 psia), and this is necessary when power for a generator is to be supplied in addition to air-conditioning or heating. The higher full power condenser pressure insures sufflcient turbine nozzle expansion ratio in spite of the power variations which occur with varying generator load. Such an arrangement insures that the refrigerant vapor in the end of the power fluid condenser does not decrease the capacity of the power fluid condenser.

The present invenion is not limited to use of an internal gear train as previously described to rotationally drive the housing-condenser-evaporator unit directly from the internal power fluid expander, and in many installations it may be advantageous to rotationally drive the housing-condenser-evaporator unit continuously by means of an electric motor mounted externally of the unit and supplied with electric current generated by an alternator mounted internally of the rotary engine housing coaxially thereof and driven by the internal power fluid expander. In addition to supplying electric power to the unit drive motor, the alternator may also supply electric power for appliances, lighting and other electrical equipment.

One embodiment of such an arrangement is shown in FIGS. 6, 7, 8 and 9 of the drawings and, except for the differences hereinafter set forth, is generally similar in construction and operation to the embodiments of the invention previously described. Referring to FIG. 6 of the drawings, the rotary boiler B is formed integral within the coaxial engine housing H. The engine housing H comprises a central cylindrical portion 1 and axially spaced

end housing portions

2 and 3 at respectively opposite sides thereof. The engine housing H and boiler B are mounted for rotation about their common axis by means of

shaft members

15 and 16 extending coaxially outward from the

opposite housing portions

2 and 3, respectively. The outer end of the shafts 15 is journalled by means of a bearing 17' in a stationary hub 18 fixedly supported by means of radial spokes 19 from a circumscribing concentric ring 20 that is fixedly supported from a fixed base or support (not shown) of the machine in a manner similar to that shown in FIG. 1. In similar manner the outer end of the other shaft 16' is rotatably journalled by means of a bearing (not shown) mounted in a stationary hub 24 that is supported by means of radial spokes 25 within a circumscribing concentric ring 26 that is in turn fixedly supported from the fixed base of the machine. From the foregoing it will be apparent that the cylindrical boiler B and engine housing H together with the aforesaid shafts l5 and 16 constitute a unitary structure that is rotatably mounted for coaxial rotation as a unit about the engine axis.

As in the embodiment previously described, the rotary boiler B is adapted to be driven about its axis at a predetermined speed of rotation calculated to create the centrifugal force necessary to dispose and maintain the selected boiler liquid therein uniformly distributed circumferentially about and in contact with the inner surface of the outer peripheral wall of the boiler with a liquid/vapor interface, designated i. The annular body of liquid in the boiler may be heated to the required boiling temperature by combustion of a suitable fuel-air mixture in a stationary combustion box 30' constructed and arranged as previously described and shown in FIG. 2 of the drawings.

Coaxially mounted within the engine housing H for rotation with the latter is an annular power fluid expander PX having a central bore 40 extending coaxially therethrough. The expander PX is fixed supported coaxially within the rotatable engine housing H by means of annnular ring 41 having a radially extending circumferential wall portion 42 that terminates at its periphery in an annular collector ring 43. The ring 43 is in sealing engagement with the internal wall surface of the housing end portion 3 and forms therewith a closed power fluid compartment X within the engine housing H so that the power fluid is effectively segregated from the refrigerant fluid and there is no substantial intermixing thereof.

The expander PX shown is in the form of a single stage shrouded turbine comprising a rotor 45 having a series of turbine blades 46 arranged peripherally thereabout. The turbine rotor 45 is keyed on a shaft 48 for coaxial rotation therewith independently of the boiler B and engine housing H. The shaft 48 is rotatably mounted in the bore 40 of the expander PX by means of a bearing mounted in an annular internal housing 182 having a coaxially extending cylindrical casing portion 184 for an alternator A hereinafter described. The housing member 182 is mounted in the rotary housing H for rotation therewith by means of an annular support ring 186 having an angularly extending circumferential web portion 188 that terminates in an annular refrigerant manifold 190. The support ring 186 is secured coaxially within the engine housing H by means of

struts

192 and 194 secured at opposite sides of the web portion of the ring for example, by welding.

An annular series of nozzles 50 is provided in the expander PX in confronting relation to the blades 46 of the turbine rotor 45 and an annular manifold 51 opens to the turbine nozzles 50. High pressure vapor is supplied from the boiler B to the manifold 51 through a plurality of radial passages 52 in the expander and a corresponding plurality of radially disposed vapor tubes 53 arranged in equally spaced relation circumferentially of the engine axis to insure rotational balance. Thus, high pressure vapor supplied to manifold 51 is discharged through the turbine nozzles 50 and impinges upon the blades 46 to drive the turbine rotor 45 and its shaft 48 at the desired speed of rotation.

An annular diffuser 55 mounted coaxially within the expander support ring 41 receives the exhaust vapor from the turbine and discharges said vapor into the power fluid compartment X of the engine housing H from which it passes into the condenser C which, in the illustrated embodiment is constructed and operable substantially as previously described and shown in FIGS. 1-3 of the drawings. A plurality of radial partitions 56 and vanes 57' is provided to maintain the angular velocity of the exhaust power fluid vapor the same as that of the rotating housing unit H. Power fluid vapor condensed in the condenser collects in the collector ring 43 and is returned through a plurality of circumferentially equally spaced radial tubes 102 to the boiler B where the condensate is again vaporized and the power cycle repeated.

As shown, the turbine shaft 48 extends coaxially an appreciable length outwardly from the turbine rotor 45 and has its outer end portion rotatably supported in a bearing 196 mounted in the annular housing 198 of a compressor or pump P disposed coaxially of the turbine shaft 48. The peripheral surface of the compressor housing 198 is in sealing engagement with a shoulder 200 provided interiorly of the engine housing portion 2 and forms with the latter an enclosed refrigerant compartment Y in the engine housing H. Between the power fluid compartment X and refrigerant compartment Y, the housing H defines internally thereof a sealed intermediate compartment Z which is evacuated to thermally separate the two compartments X and Y from each other and minimize heat exchange between the high temperature power fluid and the substantially lower temperature refrigerant fluid.

In the embodiment illustrated, the alternator A is of the known inductor alternator type, such as Rice, Lundell or homopolar. The alternator is enclosed within a casing 202 mounted coaxially of the engine within the cylindrical casing portion 184 of the housing member 182 and the alternator armature 204 is integral with the turbine shaft 48' and rotationally driven by the turbine rotor 45. The

alternator field windings

206, 2060 and 235 and the alternator casing 202 are fixedly secured to the housing 182 and the outwardly adjacent compressor housing 198 so that the latter as well as the armature casing and field windings rotate as a unit with the engine housing H and relative to the alternator armature 204 driven by the turbine rotor 45.

The compressor housing 198 has an internal coaxial rotor chamber 208 therein having a coaxial inlet 210 thereto that is in open communication with the interior of the refrigerant compartment Y. A compressor rotor 212 is rotatably mounted in the compressor housing 198 and keyed to the turbine shaft 48 to be rotationally driven thereby. By this construction vaporized refrigerant in the compartment Y enters the compressor housing 198 through the inlet 210 and is compressed by the rotor 212 from which it is discharged through a plurality of radial diffuser-passages 214 formed in the housing 198 to an annular manifold 216 therein. From the manifold 216 the compressed refrigerant flows through a plurality of circumferentially equally spaced passages 218 to the annular refrigerant manifold 190 and thence into the condenser C where it is condensed.

As previously stated the condenser is constructed as previously described and shown in FIGS. 1-3 of the drawings, and comprises concentric outer power fluid and inner refrigerant fluid condenser sections C and C" each comprising a coaxial array of spaced

annular fins

96 and 96" having a plurality of

heat exchange tubes

97 and 97", respectively, extending longitudinally therethrough and arranged in equally spaced relation circumferentially about the engine axis, as previously described. The heat exchange tubes 97 of the outer power fluid condenser section C are connected at their inner ends to the collector ring 44 and at their outer ends are connected to a common manifold 99 formed in an annular end ring 100 that is supported from the engine housing portion 3' by a plurality of circumferentially equally spaced radial spokes 101.

As in the previous embodiment, all but a predetermined small number of the refrigerant condenser tubes 97" are closed at their inner ends by an annular plate 103 to which the inner ends of the tubes are secured, and the outer ends of all of the refrigerant condenser tubes 97" are connected to a common manifold 104 also formed in the condenser and ring 100. The predetermined small number of the heat exchange tubes 97 that are not closed at their inner end portions extend through openings 106 in the plate 103' and through

larger openings

108 and 110 in the engine housing portion 3 and wall portion 42 of the ring 41, respectively, and are connected at their inner ends to the refrigerant manifold 190 previously described. The openings 108 and 110' are larger in diameter than the refrigerant heat exchange tubes 97 extending therethrough in order to accommodate insulating sleeves 112 of comparable diameter that concentrically circumscribe the portions of the heat exchange tubes 97 that pass within the power fluid compartment X. The sleeves 112 are circumferentially spaced from the heat exchange tubes 97" and function to insulate the refrigerant in the enclosed portions of the tubes 97" from the high temperature power fluid in the compartment X of the housing H.

As in the previous embodiment, liquid refrigerant condensed in the heat exchange tubes 97" flows outwardly therein to the manifold 104 in end ring 100 and thence inwardly through the predetermined small number of said tubes to the refrigerant manifold 190 from which it is conducted by a small number of circumferentially arranged equally spaced capillary expander tubes 114 that deliver the low temperature mixture of refrigerant liquid and vapor to an annular inlet manifold 116 of the evaporator E.

The evaporator E, constructed and operable substantially as previously described and shown, comprises a coaxial array of annular radial fins 120 and longitudinally extending heat exchange tubes 122 circumferentially arranged in equally spaced relation about the engine shaft 15 and mounted for rotation with the engine erant inlet manifold 116 as shown. The outer ends of the tubes [22' are mounted in recesses in an annular end ring I24 and connected to an annular outlet manifold l26 provided therein. The end ring 124 is disposed coaxially adjacent the outermost of the fins 120 and supported from the end housing portion 2' by a plurality of circumferentially arranged equally spaced tubes 220. The outer ends of the tubes 220 are connected to the annular manifold I26 and the inner ends of said tubes 220 are connected to the interior of the refrigeration compartment Y of the engine housing H. The low temperature refrigerant delivered to the manifold 126' enters the evaporator heat exchange tubes 122 where it is evaporated. The evaporated refrigerant collects in the manifold 126 and is returned through the tubes 220 to the refrigerant compartment Y and the compressor P to repeat the cycle.

As previously stated, the housing-condenserevaporator unit is rotatably driven at a predetermined constant speed of rotation, and in the illustrated embodiment of the invention, this is accomplished by means of an external constant speed motor M driving a pulley 170 secured on the evaporator end ring 124, through a belt 172.

The spacing between the adjacent

annular fins

96 and 96" of the condenser sections C and C and the spacing of the evaporaton fins 120 is determined with relation to the rotational speed at which the housing-condenser-evaporator unit is driven and to the kinematic viscosity of the cooling fluid, such as air, to provide a Taylor number in the range of about 5 to 10, preferably about 6, and the outer radius of the fins 97 and the inner radius of the fins 97" are determined to provide a ratio of inner to outer radii of the fins in the range of 0.70 to 0.85, preferably about 0.77, as previously described, whereby the viscous properties of the fluid and the shear forces exerted thereon by the rotating fins are utilized as previously described to convey and accelerate the fluid radially outward between said fins substantially to the velocity providing optimum total heat exchange between the fluids in the heat exchange tubes and the fluid passing outwardly between the fins.

Any refrigerant vapor and other non-condensable gases that may migrate into the power fluid system of the engine will flow through the condenser tubes 97 and collect in the manifold 99 from which they are returned through a pair of diametrically arranged tubes 154' to the inlet manifold 116 of the refrigerant evaporator E. Similarly, since the volatility of the power fluid is much less than that of the refrigerant, any power fluid which may migrate into the refrigerant system will collect in the evaporator outlet manifold 126 and overflow into a pair of diametrically arranged radial weir tubes 156 and thence through a corresponding pair of longitudinally extending tubes 158 to an annular vaporizing chamber 5 provided inwardly adjacent the boiler B and heated thereby. Power fluid liquid returned to the chamber 5 is vaporized therein and passes inwardly through a plurality of equally spaced radial tubes 166 to the collector ring 44 and power fluid compartment X of the engine. Each of the tubes I58 extends l80 circumferentially about the housing H and a liquid trap 222 is provided in each tube 158 to prevent the refrigerant from flooding into the power fluid condenser on shut down of the engine.

In the embodiment of the invention illustrated in FIG. 6, provision is made for cooling the alternator A by the circulation of ambient air in contact with the outer cylindrical wall surface of the alternator casing 202. As shown in FIGS. 6, 7 and 8 of the drawings. a plurality of circumferentially equally spaced U-shapcd groove passages 224 is formed in the internal surface of the casing portion I84 of the alternator housing 182. The passages 224 are open to the external surface of the alternator casing 202 so that air flowing through said passages 224 is in contact with the outer surface of the alternator casing thus cooling the alternator A.

Cooling air enters the passages 224 through a corresponding plurality of axially extending inlet tubes 226 that are open to the condenser air inlet chamber and the portions of said tubes 226 that pass through the power fluid compartment X of the engine are shielded from the high temperature therein by means of sleeves 228 that circumscribe the said tubes in spaced relation thereto. Cooling air is exhausted from the passages 224 through radially extending outlet tubes 230 having their outer ends opening to the ambient atmosphere exteriorly of the rotary engine. The discharge ends of the outlet tubes 230 are radially spaced from the engine rotation axis a distance sufficiently greater than the openings to the inlet tubes 226 so that rotation of the engine causes a pumping action that operates to draw ambient air inwardly of the tubes 226, through passages 224 and discharge same outwardly through the tubes 230.

The alternator A generates alternating current which is conducted from the engine housing H through a conventional slip-ring arrangement comprising a plurality of rotating contacts 232 carried by the outer end portion of the engine shaft 15 and having electrical contact with the corresponding number of circumscribing ring contacts 234 fixedly mounted in the stationary hub 18 of the engine as shown in HO. 6. A typical alternator electrical circuit is illustrated schematically in FIG. 9 of the drawings.

Referring to FIG. 9 of the drawings, three phase alternating current generated by the alternator A is conducted from the alternator stator windings 235 through conductors 236 to three of the rotating contacts 232 and thence through the corresponding stationary ring contacts 234 and conductors 238 to a transformer 240. Conductors 242 conduct the current from the transformer 240 to a rectifier 244 which converts the alternating current generated by the alternator A to direct current. The direct current from the rectifier 244 is conducted by a pair of conductors 246 to the line conductors 248 of a service circuit that includes the main load terminals 250, the engine drive motor M and a storage battery 252 for the latter. The input terminals of a voltage regulator 254 are connected by a pair of conductors 256 to the aforesaid conductors 246 and the output terminals of the regulator 254 are connected by conductors 258 to the remaining two ring terminals 234 whereby current for field coils 206 and 206a for armature magnetization is supplied through the corresponding rotary contacts 232 and conductors 260.

In operation of the engine, it will be apparent at startup that there will be no pressure vapor generated by the boiler B to drive the expander PX, alternator A and refrigerant compressor P, and consequently, the rotary housing-condenser-evaporator unit is rotationally driven at the designed predetermined speed of rotation by the external motor M energized solely by the battery 252 until the liquid in the boiler is heated and produces the required power fluid pressure vapor to drive the alternator A, and generate the electrical current required for operation of the electrical system as described.

A typical example of closed Rankine cycle rotary cngine powered heating and cooling apparatus embodying the construction shown in FIGS. 6-9 of the drawings and designed for an output of 8.77 hp at the turbine shaft 48 with 1.34 hp available for driving motor generator M to produce electrical power, comprises a boiler B having a liquid level 1" diameter of 9.0 inches and an axial internal length of 4.2 inches to provide the heat input from the combustion box 30 required to the boiler liquid. The remaining dimensional data for the embodiment of the apparatus shown in said FIGS. 6-9 and the specifications of a typical operation thereof are the same as previously set forth for the embodiment of the apparatus shown in FIGS. 1-5 of the drawings, except that the surplus power available at the load terminals 250 is 750 watts.

Apparatus embodying the present invention is wellsuited for cooling or heating the interior of buildings, homes and other enclosed structures, and typical arrangements thereof for summer and winter operations are shown in FIGS. 10 and 11, respectively, of the drawings.

Referring to FIGS. 10 and 11, apparatus embodying the invention is shown with associated ducts and valves arranged for cooling and heating a building, respectively. Preferably, the apparatus is located adjacent a wall or walls of the building for convenient access to the atmosphere outside the building such as, for example, adjacent the corner of two

side walls

264 and 266 of a building, as shown.

In the arrangement shown, air from outside the building is supplied to the inlet of the rotary condenser C of the apparatus through a horizontal duct 268 that extends inwardly through the building wall 264 and connects at its inner end to an inlet housing 270 having an opening 272 to the condenser inlet. The outer end of the duct 268 is provided with suitable valve closure means such as shutters 274 which may be opened, as shown, to admit outside air through the duct to the condenser, or closed to prevent the admission of outside air to the condenser.

A stationary housing or plenum chamber 276 circumferentially encloses the rotary condenser C of the apparatus and air admitted to the condenser C is discharged outwardly through the condenser flns 96' and 96" where it is heated by heat exchange with the hot power fluid being condensed in the condenser tubes 97. An exhaust duct 278 for the heated air discharged into the plenum chamber 276 leads tangentially therefrom and then outwardly through the building wall 266 to the exterior of the building. The outlet end of the duct 278 is also provided with suitable valve closure means, such as shutters 280, for opening or closing the duct inlet to the outside atmosphere. A distribution duct 282, for conveying heated or cooled air from the apparatus to suitable outlets 284 appropriately located throughout the building, has an inlet thereto connected at 286 to the exhaust duct 278.

Similar to the condenser plenum chamber 276, the rotary evaporator is also circumferentially enclosed within a stationary housing or plenum chamber 288 to receive the air discharged radially outward through the fins of the evaporator during which it has been cooled by heat exchange with the condensed refrigerant in the evaporator tubes. The cooled air discharged to the plenum chamber 288 is delivered to a duct 290 that is connected at one end thereof to the distribution duct 282 through a side wall thereof as indicated at 292. Valve means, such as a shutter 294, is provided in the distribution duct 282 for selectively admitting air to the duct 282 from either the condenser exhaust duct 278 or the evaporator exhaust duct 290. For example, with the shutter 294 in the position shown in FIG. 10 disposed crosswise of the distribution duct 282, air is admitted from duct 290 to duct 282 and air from the condenser exhaust duct 278 is prevented from entering the duct 282. The other end of the duct 290 is connected to the return duct branch 296 through a side wall thereof, as indicated at 290a, and valve means, such as shutter 290b, is provided for selectively admitting the cooled air from duct 290 to duct 296.

Air distributed by the duct 282 and discharged throughout the interior of the building through one or more of the outlets 284 is returned to the apparatus by a return duct 298 that divides into two

branches

296 and 300, respectively, a valve, such as shutter 302 being provided for selectively admitting returning air to branch

ducts

296 and 300 as desired. The branch duct 296 leads from the duct 298 and is connected into the fresh air inlet duct 268 through a side wall thereof as indicated at 304. The other branch duct 300 is connected to the fluid inlet chamber of the evaporator and also to the air distribution duct 282, a valve, such as shutter 306, being provided for selectively controlling the flow of air to the evaporator inlet or the air distribution duct 282 as desired.

Referring to FIG. 10 of the drawings, for cooling or air-conditioning the building in summer or other warm climate, the fresh air inlet shutters 274 are open as are the shutters 280 of the condenser exhaust duct 278, and the shutter 294 is positioned, as shown, to open the duct 290 and admit cooled air to the distribution duct 282 and close the latter to air from the condenser exhaust duct 278. Shutter 290b in duct 290 is closed thereby preventing discharge of cooled air through branch duct 296 into the branch duct 300. Also, shutter 306 in duct 300 is closed and shutter 302 is positioned, as shown, to close duct 296 and open duct 300 so that all air returning through duct 298 is conducted to the inlet of the evaporator.

In operation of the arrangement shown in FIG. 10, all of the heated air discharged from the condenser C is exhausted through duct 278 to the outside atmosphere and does not enter the distribution duct 282. On the other hand, all of the cooled air discharged from the evaporator is delivered by duct 290 to the duct 282 and distributed thereby to the outlets 284 located throughout the building. The air discharged into the building is returned to the apparatus through the duct 298. Since the shutter 306 in branch duct 300 is closed, and shutter 302 is closed to branch duct 296 and open to branch duct 300, all of the air returned by the duct 298 is delivered by branch duct 300 to the evaporator where it is again cooled and recirculated through the building as described.

For winter or other cold climate operation as shown in FIG. 11, the fresh air inlet shutters 274 are closed as are the condenser external exhaust shutters 280, and the shutter 294 is positioned to close the duct 290 and allow all of the heated air from the duct 278 to enter the distribution duct 282. Also, the shutter 302 is closed to branch duct 300 and opened to branch duct 296 to admit return air from duct 298 into the condenser inlet duct 272. Thus, in operation. all of the heated air from the condenser C is discharged into the duct 282. A portion of the heated air is distributed to the building outlets 284 and the air returned by the duct 298 is delivered by branch duct 296 to the condenser inlet duct 270 to be again heated and recirculated as described. The balance of the heated air is con-- ducted through branch duct 300 to the inlet of the evaporator and the cooled air from the evaporator is discharged through duct 290 into the branch duct 296.

By short-circuiting the evaporator air flow through the condenser as shown in FIG. 11, the evaporator temperature and pressure are raised and the condenser temperature and pressure are lowered. The reduced pressure rise across the refrigerant compressor combined with a decrease in compressor and housing-condenser-evaporator speed during winter operation reduces the turbine work load. The low pressure ratio, low speed compressor operation serves as an idle condition for the compressor during winter operation.

Whenever the winter ambient air temperature is greater than the evaporator temperature, it is possible to operate the apparatus as a heat pump. In this mode of operation efficient space heating results from the addition of the heat rejected by the refrigeration cycle to the heat rejected by the Rankine power cycle. The air duct arrangement will be similar to that shown in FIG. 11 except that provision is made for outside air to be admitted and caused to flow through the evaporator.

From the foregoing it will be observed that the present invention provides novel closed cycle Rankine engine powered cooling, heating and power generation apparatus that is of compact unitary construction and can be manufactured and shipped fully assembled, hermetically sealed and charged with the desired power and refrigerant fluids. The apparatus provides isenthalpic expansion of the refrigerant fluid with automatic control of the capacity balance of the refrigerant system, automatic separation of the refrigerant and power fluids in an efficient two fluid system without the use of high speed shaft seals, and the rotary condenser and evaporator function also as blowers for circulating the cooling and heating fluids independently of other power sources thereby providing an apparatus that is quiet and efficient in operation. The apparatus is unique in accomplishing its many functions without the use of valves for controlling the flow of refrigerant fluid or power fluid thereby leading to a more simple and reliable apparatus.

While certain embodiments of the invention have been illustrated and described, it is not intended to limit the invention to such embodiments, and it is contemplated that changes and modifications may be made and incorporated as desired or required within the scope of the following claims.

I claim:

1. Rotary closed Rankine cycle engine powered cooling and heating apparatus utilizing different engine power fluid and refrigerant fluid comprising.

a cylindrical housing mounted for rotation about the axis thereof including an internal power fluid boiler,

means for heating the power fluid in said boiler to generate pressure power fluid vapor therein,

a power fluid expander in said housing including a coaxial driving member rotatably driven at a first predetermined speed by the power fluid vapor generated in the boiler,

means subdividing the interior of said rotatable housing to provide a power fluid compartment for receiving the power fluid from said expander and a refrigerant fluid compartment,

a compressor rotatably mounted coaxially in the housing and rotationally driven by the expander driving member for compressing refrigerant fluid from said refrigerant fluid compartment.

a condenser mounted coaxially adjacent one side of the housing and rotatable therewith comprising a plurality of axially spaced annular fins having heat exchange tubes extending longitudinally therethrough,

a predetermined number of said condenser heat exchange tubes being in communication with the power fluid compartment of the housing for receiving and condensing therein the power fluid vapor from said power fluid expander,

means for conducting compressed refrigerant fluid from the compressor to the remainder of said condenser heat exchange tubes for condensing said compressed refrigerant fluid therein,

refrigerant expander means in said housing for expanding the refrigerant fluid condensed in said condenser,

means for supplying condensed refrigerant fluid from said condenser to said refrigerant expander,

an evaporator mounted coaxially adjacent the other side of the housing from said condenser and rotatable therewith comprising a plurality of axially spaced annular fins having heat exchange tubes extending longitudinally therethrough and arranged to receive and vaporize therein refrigerant fluid from the refrigerant expander,

means for returning vaporized refrigerant from said evaporator to said refrigerant compartment of the housing,

and means operable to rotationally drive the housing, condenser and evaporator as a unit at a second pre determined speed substantially slower than said first predetermined speed and operable to cause a gaseous heat exchange fluid to be conveyed and accelerated by viscosity shear forces outwardly between the fins of the condenser and evaporator to the velocity providing optimum heat exchange between said gaseous fluid and the fluids in the heat exchange tubes of the condenser and evaporator.

2. Apparatus as claimed in claim 1 wherein the refrigerant expander comprises a plurality of capillary tubes equally spaced circumferentially of the housing and rotatable therewith, the length of said capillary tubes being correlated to the internal flow area thereof and to the number of said tubes to supply the amount of expanded refrigerant to the evaporator required to provide the designed refrigeration capacity of the apparatus.

3. Apparatus as claimed in claim 2 wherein the liquid level of refrigerant in the heat exchange tubes of the evaporator is disposed at a greater radial distance from the rotation axis of the housing than the refrigerant heat exchange tubes of the condenser, and the capillary expander tubes are operable in response to the pressure drop across said expander tubes between the refrigerant condenser and evaporator to automatically establish and maintain capacity balance in the refrigerant fluid system.

4. Apparatus as claimed in claim 1 comprising means for returning to the refrigerant fluid compartment of the housing refrigerant vapor that migrates into the power fluid system and collects in the power fluid condenser tubes.

5. Apparatus as claimed in claim 1 comprising means for returning to the power fluid compartment of the housing power fluid that migrates into the refrigerant fluid system and collects in the evaporator.

6. Apparatus as claimed in claim 5 wherein the rotary housing includes an annular vaporizing chamber and means is provided for delivering to said vaporizing chamber power fluid that migrates into the refrigerant fluid system and collects in the evaporator, said vaporizing chamber being heated by the boiler to vaporize the power fluid delivered thereto, and means for returning vaporized power fluid from said vaporizing chamber to the power fluid compartment of the housing.

7. Apparatus as claimed in claim 1 wherein the means for rotationally driving the housing, condenser and evaporator as a unit comprises an occluded fixedratio gear train mounted coaxially within the housing and connected between the power fluid expander driving member and said housing, and torque anchor means cooperable with the occluded gear train opposing the reaction torque generated thereby so that the full power output of the power fluid expander is transmitted directly to the compressor and rotary housing.

8. Apparatus as claimed in claim 1 wherein the means for rotationally driving the housing, condenser and evaporator as a unit comprises rotary power means mounted externally of the said unit and having a driving connection thereto.

9. Apparatus as claimed in claim 1 comprising an alternator mounted coaxially in the housing having the armature thereof driven by the rotatable driving member of the power fluid expander and operable to generate an electric current, and means for conducting the electric current generated by said alternator to a load located exteriorly of the rotary housing-condenserevaporator unit.

10. Apparatus as claimed in claim 1 wherein the means for rotationally driving the housing, condenser and evaporator as a unit comprises a constant speed electric motor mounted externally of said unit and having a driving connection thereto, an alternator is mounted coaxially in the housing having the armature thereof driven by the rotatable driving member of the power fluid expander and operable to generate an electric current, and means is provided for conducting the electric current generated by said alternator externally ofthe rotary housing-condenser-evaporator unit to said electric motor.

ll. Apparatus as claimed in claim 1 wherein the condenser means comprises separate outer and inner concentrically disposed condenser sections respectively for the expander exhaust power fluid and compressed refrigerant fluid mounted coaxially adjacent one side of the housing and rotatable therewith, each condenser section comprising a plurality of axially spaced annular fins radially spaced from the fins of the other section to provide a thermal gap therebetween, a plurality of heat 5 exchange tubes extending longitudinally through the fins of said outer condenser section for condensing the expander exhaust fluid therein, and a plurality of heat exchange tubes extending longitudinally through the fins of the inner condenser section for condensing refrigerant fluid therein. the expander exhaust and refrigerant fluids in said heat exchange tubes being condensed by heat exchange with a cooling fluid passing radially outward between the tins of said sections.

12. Apparatus as claimed in claim 11 wherein the fins of the outer and inner condenser sections are disposed in radial alignment with one another and the axial spacing between adjacent fins of each section is correlated to the speed of rotation thereof and the kinematic viscosity of the cooling fluid to provide a Taylor number operable at the ratio of the inner radius of the inner section fins to the outer radius of the outer section fins to convey and accelerate said cooling fluid by viscosity shear forces spirally outward between the fins substantially to the velocity providing optimum heat exchange between the cooling fluid and the fluids in said heat exchange tubes to condense said fluids.

13. Apparatus as claimed in claim 9 comprising means for circulating a cooling fluid within the rotary housing in heat exchange relation with the alternator to cool the same.

14. Apparatus as claimed in claim 9 comprising means for circulating air from the ambient atmosphere surrounding the rotary housing interiorly of said housing in heat exchange relation with the alternator to cool the same.

15. Apparatus as claimed in claim 7 wherein the rotary housing includes a sump compartment for containing an annular bath of lubricant and the torque anchor means is non-rotatable with the housing and includes pump means operable to pump lubricant inwardly from said annular bath to the expander driving member to lubricate same.

16. Apparatus as claimed in claim 15 comprising means for delivering to the lubricant bath in the sump compartment power fluid that migrates into the refrigerant fluid system and collects in the evaporator, and means for returning said power fluid from the lubricant bath to the power fluid compartment of the housing.

17. Apparatus as claimed in claim 16 wherein the means for returning power fluid from the lubricant bath to the power fluid compartment of the housing includes an annular vaporizing chamber in said housing, means for delivering power fluid from the lubricant bath to said vaporizing chamber, said vaporizing chamber being heated by the boiler to vaporize the power fluid delivered thereto, and means for returning the vaporized power fluid from the vaporizing chamber to the power fluid compartment of the housing.

18. Cooling and heating apparatus as claimed in claim 1 comprising a fluid inlet duct connected to the inlet to the condenser fluid chamber, a housing defining a plenum chamber enclosing the condenser for receiving heated fluid discharged outwardly through the condenser flns, an exhaust duct connected to the condenser plenum chamber to receive heated fluid therefrom, a fluid distribution duct connected to said exhaust duct for conducting heated fluid therefrom to a remote zone, a return duct from said zone terminating in a first branch duct connected to said air inlet duct to the condenser chamber and a second branch duct connected to the fluid inlet chamber of the evaporator and to said air distribution duct, a housing defining a plenum chamber enclosing the evaporator for receiving therefrom cool fluid discharged outwardly through the evaporator fins, a cool fluid duct connected to said evaporator plenum chamber for receiving cool fluid therefrom. said cool fluid duct also being connected to said first return branch duct and to said distribution duct, valve means selectively operable for controlling the flow of fluid respectively from said exhaust duct and said cool fluid duct to the distribution duct, and valve means selectively operable for controlling fluid flow from said return duct to the said first and second branch ducts and between the latter and said cool fluid duct and fluid distribution duct.

19. Apparatus as claimed in claim 3 comprising means for returning to the refrigerant fluid compartment of the housing refrigerant vapor that migrates into the power fluid system and collects in the power fluid condenser tubes.

20. Apparatus as claimed in claim 3 comprising means for returning to the power fluid compartment of the housing power fluid that migrates into the refrigerant fluid system and collects in the evaporator.

21. Apparatus as claimed in claim 3 wherein the rotary housing includes an annular vaporizing chamber and means is provided for delivering to said vaporizing chamber power fluid that migrates into the refrigerant fluid system and collects in the evaporator, said vaporizing chamber being heated by the boiler to vaporize the power fluid delivered thereto, and means for returning vaporized power fluid from said vaporizing chamber to the power fluid compartment of the housing.

22. Apparatus as claimed in claim 3 wherein the means for rotationally driving the housing, condenser and evaporator as a unit comprises an occluded fixedratio gear train mounted coaxially within the housing and connected between the power fluid expander driving member and said housing, and torque anchor means cooperable with the occluded gear train opposing the reaction torque generated thereby so that the full power output of the power fluid expander is trans mitted directly to the compressor and rotary housing.

23. Apparatus as claimed in claim 3 wherein the means for rotationally driving the housing, condenser and evaporator as a unit comprises a rotary power means mounted externally of the said unit and having a driving connection thereto.

24. Apparatus as claimed in claim 3 wherein the means for rotationally driving the housing, condenser and evaporator as a unit comprises a constant speed electric motor mounted externally of said unit and having a driving connection thereto, an alternator is mounted coaxially in the housing having the armature thereof driven by the rotatable driving member of the power fluid expander and operable to generate an electric current, and means is provided for conducting the electric current generated by said alternator externally of the rotary housing-condenser-evaporator unit to said electric power.

25. Apparatus as claimed in claim 24 comprising means for circulating air from the ambient atmosphere surrounding the rotary housing interiorly of said housing in heat exchange relation with the alternator to cool the same.

26. Cooling and heating apparatus as claimed in claim 3 comprising a fluid inlet duct connected to the inlet to the condenser fluid chamber, a housing defining a plenum chamber enclosing the condenser for receiving heated fluid discharged outwardly through the condenser fins, an exhaust duct connected to the condenser plenum chamber to receive heated fluid therefrom, a fluid distribution duct connected to said exhaust duct for conducting heated fluid therefrom to a remote zone, a return duct from said zone terminating in a first branch duct connected to said air inlet duct to the condenser chamber and a second branch duct connected to the fluid inlet chamber of the evaporator and to said air distribution duct, a housing defining a plenum chamber enclosing the evaporator for receiving therefrom cool fluid discharged outwardly through the evaporator fins, a cool fluid duct connected to said evaporator plenum chamber for receiving cool fluid therefrom, said cool fluid duct also being connected to said first return branch duct and to said distribution duct, valve means selectively operable for controlling the flow of fluid respectively from said exhaust duct and said cool fluid duct to the distribution duct, and valve means selectively operable for controlling fluid flow from said return duct to the said first and second branch ducts and between the latter and said cool fluid duct and fluid distribution duct.

27. Apparatus as claimed in claim 3 wherein the con denser means comprises separate outer and inner concentrically disposed condenser sections respectively for the expander exhaust power fluid and compressed refrigerant fluid mounted coaxially adjacent one side of the housing and rotatable therewith, each condenser section comprising a plurality of axially spaced annular fins radially spaced from the fins of the other section to provide a thermal gap therebetween, a plurality of heat exchange tubes extending longitudinally through the fins of said outer condenser section for condensing the expander exhaust fluid therein, and a plurality of heat exchange tubes extending longitudinally through the fins of the inner condenser section for condensing refrigerant fluid therein, the expander exhaust and refrigerant fluids in said heat exchange tubes being condensed by heat exchange with a cooling fluid passing radially outward between the fins of said sections.

28. Apparatus as claimed in claim 22 wherein the condenser means comprises separate outer and inner concentrically disposed condenser sections respectively for the expander exhaust power fluid and compressed refrigerant fluid mounted coaxially adjacent one side of the housing and rotatable therewith, each condenser section comprising a plurality of axially spaced annular fins radially spaced from the fins of the other section to provide a thermal gap therebetween, a plurality of heat exchange tubes extending longitudinally through the fins of said outer condenser section for condensing the expander exhaust fluid therein, and a plurality of heat exchange tubes extending longitudinally through the fins of the inner condenser section for condensing refrigerant fluid therein, the expander exhaust and refrigerant fluids in said heat exchange tubes being condensed by heat exchange with a cooling fluid passing radially outward between the fins of said sections.

Claims

1. Rotary Rankine cycle engine powered cooling and heating apparatus utilizing different engine power fluid and refrigerant fluid comprising, a cylindrical housing mounted for rotation about the axis thereof including an internal power fluid boiler, means for heating the power fluid in said boiler to generate pressure power fluid vapor therein, a power fluid expander in said housing including a coaxial driving member rotatably driven at a first predetermined speed by the power fluid vapor generated in the boiler, means subdividing the interior of said rotatable housing to provide a power fluid compartment for receiving the power fluid from said expander and a refrigerant fluid compartment, a compressor rotatably mounted coaxially in the housing and rotationally driven by the expander driving member for compressing refrigerant fluid from said refrigerant fluid compartment, a condenser mounted coaxially adjacent one side of the housing and rotatable therewith comprising a plurality of axially spaced annular fins having heat exchange tubes extending longitudinally therethrough, a predetermined number of said condenser heat exchange tubes being in communication with the power fluid compartment of the housing for receiving and condensing therein the power fluid vapor from said power fluid expander, means for conducting compressed refrigerant fluid from the compressor to the remainder of said condenser heat exchange tubes for condensing said compressed refrigerant fluid therein, refrigerant expander means in said housing for expanding the refrigerant fluid condensed in said condenser, means for supplying condensed refrigerant fluid from said condenser to said refrigerant expander, an evaporator mounted coaxially adjacent the other side of the housing from said condenser and rotatable therewith comprising a plurality of axially spaced annular fins having heat exchange tubes extending longitudinally therethrough and arranged to receive and vaporize therein refrigerant fluid from the refrigerant expander, means for returning vaporized refrigerant from said evaporator to said refrigerant compartment of the housing, and means operable to rotationally drive the housing, condenser and evaporator as a unit at a second predetermined speed substantially slower than said first predetermined speed and operable to cause a gaseous heat exchange fluid to be conveyed and accelerated by viscosity shear forces outwardly between the fins of the condenser and evaporator to the velocity providing optimum heat exchange between said gaseous fluid and the fluids in the heat exchange tubes of the condenser and evaporator.

7. Apparatus as claimed in claim 1 wherein the means for rotationally driving the housing, condenser and evaporator as a unit comprises an occluded fixed-ratio gear train mounted coaxially within the housing and connected between the power fluid expander driving member and said housing, and torque anchor means cooperable with the occluded gear train opposing the reaction torque generated thereby so that the full power output of the power fluid expander is transmitted directly to the compressor and rotary housing.

9. Apparatus as claimed in claim 1 comprising an alternator mounted coaxially in the housing having the armature thereof driven by the rotatable driving member of the power fluid expander and operable to generate an electric current, and means for conducting the electric current generated by said alternator to a load located exteriorly of the rotary housing-condenser-evaporator unit.

10. Apparatus as claimed in claim 1 wherein the means for rotationally driving the housing, condenser and evaporator as a unit comprises a constant speed electric motor mounted externally of said unit and having a driving connection thereto, an alternator is mounted coaxially in the housing having the armature thereof driven by the rotatable driving member of the power fluid expander and operable to generate an electric current, and means is provided for conducting the electric current generated by said alternator externally of the rotary housing-condenser-evaporator unit to said electric motor.

11. Apparatus as claimed in claim 1 wherein the condenser means comprises separate outer and inner concentrically disposed condenser sections respectively for the expander exhaust power fluid and compressed refrigerant fluid mounted coaxially adjacent one side of the housing and rotatable thereWith, each condenser section comprising a plurality of axially spaced annular fins radially spaced from the fins of the other section to provide a thermal gap therebetween, a plurality of heat exchange tubes extending longitudinally through the fins of said outer condenser section for condensing the expander exhaust fluid therein, and a plurality of heat exchange tubes extending longitudinally through the fins of the inner condenser section for condensing refrigerant fluid therein, the expander exhaust and refrigerant fluids in said heat exchange tubes being condensed by heat exchange with a cooling fluid passing radially outward between the fins of said sections.

18. Cooling and heating apparatus as claimed in claim 1 comprising a fluid inlet duct connected to the inlet to the condenser fluid chamber, a housing defining a plenum chamber enclosing the condenser for receiving heated fluid discharged outwardly through the condenser fins, an exhaust duct connected to the condenser plenum chamber to receive heated fluid therefrom, a fluid distribution duct connected to said exhaust duct for conducting heated fluid therefrom to a remote zone, a return duct from said zone terminating in a first branch duct connected to said air inlet duct to the condenser chamber and a second branch duct connected to the fluid inlet chamber of the evaporator and to said air distribution duct, a housing defining a plenum chamber enclosing the evaporator for receiving therefrom cool fluid discharged outwardly through the evaporator fins, a cool fluid duct connected to said evaporator plenum chamber for receiving cool fluid therefrom, said cool fluid duct also being connected to said first return branch duct and to said distribution duct, valve means selectIvely operable for controlling the flow of fluid respectively from said exhaust duct and said cool fluid duct to the distribution duct, and valve means selectively operable for controlling fluid flow from said return duct to the said first and second branch ducts and between the latter and said cool fluid duct and fluid distribution duct.

22. Apparatus as claimed in claim 3 wherein the means for rotationally driving the housing, condenser and evaporator as a unit comprises an occluded fixed-ratio gear train mounted coaxially within the housing and connected between the power fluid expander driving member and said housing, and torque anchor means cooperable with the occluded gear train opposing the reaction torque generated thereby so that the full power output of the power fluid expander is transmitted directly to the compressor and rotary housing.

27. Apparatus as claimed in claim 3 wherein the condenser means comprises separate outer and inner concentrically disposed condenser sections respectively for the expander exhaust power fluid and compressed refrigerant fluid mounted coaxially adjacent one side of the housing and rotatable therewith, each condenser section comprising a plurality of axially spaced annular fins radially spaced from the fins of the other section to provide a thermal gap therebetween, a plurality of heat exchange tubes extending longitudinally through the fins of said outer condenser section for condensing the expander exhaust fluid therein, and a plurality of heat exchange tubes extending longitudinally through the fins of the inner condenser section for condensing refrigerant fluid therein, the expander exhaust and refrigerant fluids in said heat exchange tubes being condensed by heat exchange with a cooling fluid passing radially outward between the fins of said sections.

29. Apparatus as claimed in claim 24 wherein the condenser means comprises separate outer and inner concentrically disposed condenser sections respectively for the expander exhaust power fluid and compressed refrigerant fluid mounted coaxially adjacent one side of the housing and rotatable therewith, each condenser section comprising a plurality of axially spaced annular fins radially spaced from the fins of the other section to provide a thermal gap therebetween, a plurality of heat exchange tubes extending longitudinally through the fins of said outer condenser section for condensing the expander exhaust fluid therein, and a plurality of heat exchange tubes extending longitudinally through the fins of the inner condenser section for condensing refrigerant fluid therein, the expander exhaust and refrigerant fluids in said heat exchange tubes being condensed by heat exchange with a cooling fluid passing radially outward between the fins of said sections.

30. Cooling and heating apparatus as claimed in claim 28 comprising a fluid inlet duct connected to the inlet to the condenser fluid chamber, a housing defining a plenum chamber enclosing the condenser for receiving heated fluid discharged outwardly through the condenser fins, an exhaust duct connected to the condenser plenum chamber to receive heated fluid therefrom, a fluid distribution duct connected to said exhaust duct for conducting heated fluid therefrom to a remote zone, a return duct from said zone terminating in a first branch duct connected to said air inlet duct to the condenser chamber and a second branch duct connected to the fluid inlet chamber of the evaporator and to said air distribution duct, a housing defining a plenum chamber enclosing the evaporator for receiving therefrom cool fluid discharged outwardly through the evaporator fins, a cool fluid duct connected to saId evaporator plenum chamber for receiving cool fluid therefrom, said cool fluid duct also being connected to said first return branch duct and to said distribution duct, valve means selectively operable for controlling the flow of fluid respectively from said exhaust duct and said cool fluid duct to the distribution duct, and valve means selectively operable for controlling fluid flow from said return duct to the said first and second branch ducts and between the latter and said cool fluid duct and fluid distribution duct.

31. Cooling and heating apparatus as claimed in claim 29 comprising a fluid inlet duct connected to the inlet to the condenser fluid chamber, a housing defining a plenum chamber enclosing the condenser for receiving heated fluid discharged outwardly through the condenser fins, an exhaust duct connected to the condenser plenum chamber to receive heated fluid therefrom, a fluid distribution duct connected to said exhaust duct for conducting heated fluid therefrom to a remote zone, a return duct from said zone terminating in a first branch duct connected to said air inlet duct to the condenser chamber and a second branch duct connected to the fluid inlet chamber of the evaporator and to said air distribution duct, a housing defining a plenum chamber enclosing the evaporator for receiving therefrom cool fluid discharged outwardly through the evaporator fins, a cool fluid duct connected to said evaporator plenum chamber for receiving cool fluid therefrom, said cool fluid duct also being connected to said first return branch duct and to said distribution duct, valve means selectively operable for controlling the flow of fluid respectively from said exhaust duct and said cool fluid duct to the distribution duct, and valve means selectively operable for controlling fluid flow from said return duct to the said first and second branch ducts and between the latter and said cool fluid duct and fluid distribution duct.