US3260050A

US3260050A - Rotary vapor generator

Info

Publication number: US3260050A
Application number: US402993A
Authority: US
Inventors: James H Anderson
Original assignee: Individual
Current assignee: Individual
Priority date: 1964-10-12
Filing date: 1964-10-12
Publication date: 1966-07-12
Anticipated expiration: 1983-07-12

Description

July 12, 1966 J. H. ANDERSON 3,260,050

ROTARY VAPOR GENERATOR Filed Oct. 12, 1964 4 Sheets-Sheet l INVENTOR. JAMES H. ANDERSON BYKM WJLQW iv M A TTORNE Ys.

July 12, 1966 J. H. ANDERSON ROTARY VAPOR GENERATOR 4 Sheets-Sheet 2 Filed Oct. 12, 1964 FIG. 2

INVENTOR JAMES H ANDERSON BY/ flh /L.u+

. nlllikllllllllll ATTORNEYS,

July 12, 1966 J. H. ANDERSON 3,260,050

ROTARY VAPOR GENERATOR Filed Oct. 12, 1964 4 Sheets-Sheet 3 FIG. 5

' INVENTOR.

JAMES H. ANDERSON Y a B 654 ATTORNEYS J. H. ANDERSON ROTARY VAPOR GENERATOR July 12, 1 966 4 Sheets-Sheet 4 Filed Oct. 12, 1964 INVENTOR.

JAMES H. ANDERSON BY j M 2 m A TTORNEY'.

United States Patent 3,260,050 ROTARY VAPOR GENERATOR James H. Anderson, 1615 Hillock Lane, York, Pa. Filed Oct. 12, 1964, Ser. No. 402,993 19 Claims. (Cl. 60-39.18)

This invention relates generally to vapor generators and more particularly to vapor generators having a rotating vapor tube system therein.

Although the vapor generator of this invention may be used with various types of boiling liquids for many suitable purposes, it is specifically intended that this boiler be incorporated in the automotive power plant system disclosed in applicants co-pending application, Serial No. 373,661, filed June 9, 1964. As disclosed in that application, the rotary or rotating vapor tube boiler is particularly suitable for use with a closed cycle halocarbon vapor system acting as a power source for motor vehicles. The rotary feature enables the provision of a lightweight, minimum size boiler in a vehicle, the boiler being particularly suited for utilizing a halocarbon as the boiling liquid since the rotary vapor tube system diminishes the likelihood of hot spots in the vapor tubes thereof. Such hot spots degenerate the halocarbons making them unfeasible for use in the closed circuit system contemplated in the abovementioned co-pending application.

It is an object of this invention to provide an improved rotary vapor generator particularly adapted for incorporation in a vehicular prime mover system.

It is another object of this invention to provide a vapor generator which is light in weight and of minimum size.

It is a further object of this invention to provide a highly efficient rotary vapor generator incorporating a preheater, heater and superheater in the same basic structure.

It is still another object of this invention to provide a rotary vapor generator which requires a minimum percentage of high temperature material in the structure thereof by providing a burner chamber therefor which is fully shielded by liquid containing structure.

It is still a further object of this invention to provide a vapor generator which is particularly adapted to work with halocarbons by incorporating a rotating vapor tube structure therein to minimize the probability of vapor pockets and attendant halocarbon degenerating hot spots in the vapor tube structure thereof.

It is yet another object of this invention to provide a small compact vapor generator particularly adapted for use in prime mover systems by obtaining a high heat transfer rate between the vapor tubes of the generator and the heating gases through the incorporation of a rotary vapor tube structure therein.

It is yet a further object of this invention to provide a vapor generator which may be economically perpetually maintained at operating pressure by enclosing the vapor generator structure in a low heat transfer insulation medium and by providing internal and insulated valving to avoid leakage of the vapor phase from the generator during shut-down periods thereof.

These and other objects of the invention will be apparent to those skilled in the art when reference is made to the following detailed description when viewed in light of the accompanying drawings wherein like numerals indicate like parts throughout the figures thereof and where- FIGURE 1 is a schematic representation of a portion of a system incorporating a boiler in accordance with the invention;

FIGURE 2 is an enlarged elevational view in section and partly broken away of a vapor generator in accordance with the invention;

3,250,050 Patented July 12, 1966 FIGURE 3 is an enlarged fragmentary plan view, partly in section, of a portion of the structure of FIGURE 2;

FIGURE 4 is an enlarged fragmentary view in section of another portion of the structure of FIGURE 2;

FIGURE 5 is an enlarged fragmentary elevational view in section of yet another portion of the structure of FIG- URE 2 showing the bearing and seal portion thereof;

FIGURE 6 is an elevational fragmentary view in section of still another portion of the structure of FIGURE 2;

FIGURE 7 is a sectional view of the structure view of FIGURE 6 taken along the lines 7-7 thereof;

FIGURE 8 is a fragmentary elevational view in section of still another portion of the structure of FIGURE 2 showing details of a fluid control mechanism therefore;

FIGURE 9 is a fragmentary elevational view in section of a portion of the insulating wall of the boiler of FIG- URE 2;

FIGURE 10 is a sectional view taken along the lines 10-10 of FIGURE 8;

FIGURE 11 is a view similar to FIGURE 1 showing a variation in the supply system of a boiler in accordance with the invention.

Referring now to FIGURE 1 of the drawings, a boiler, illustrated generally at 10, is shown incorporated in a power plant system. The boiling fluid of the system is supplied through a fluid intake line 12 and is exhausted, in a vapor state, through an output line 14 connected to a standpipe 15 which is, in turn, centrally disposed in the boiler. The vapor from the output line 14 is then conducted to a turbine 16 or any other motor which can utilize vapor for converting the thermal-pressure energy thereof into mechanical or electrical energy. Fuel is supplied to the boiler system through the fuel input line 17 and exhaust is expelled therefrom through an exhaust line 18. The boiler, being of the rotary or rotating vapor tube type, requires power to rotate the vapor tube structure thereof. This power is supplied at least partially by a motor 20 driving a vapor tube pulley 22 through a drive belt 24. For a more detailed description of a system in which the boiler may be used, reference is again made to the aforementioned co-pending application, Serial No. 373,661.

Turning now to FIGURE 2 of the drawings, an enlarged, detailed view of the boiler of FIGURE 1 is shown in section to enable the description and clear illustration of the internal components thereof. An annular flange 26 comprises the main outer support for the boiler system. An inner support plate 28 is bonded to the flange 26 through a heat insulating ring 30 disposed therebetween. The plate 28 supports a bearing base and rotor support 32 through which the fluid input line 12 and the standpipe 15 pass. A ball bearing housing 34 is mounted on the support 32 and rotatably supports a boiler rotor 36 and a vapor tube support 39 through ball bearings 38. A vapor pressure dome 40 is centrally mounted on the support disc 39 and is connected, at the top thereof, to the vapor tube pulley 22 through a flexible splined shaft 42. Through the aforedescribed structure, the rotative power from the motor 20 (FIGURE 1) is supplied to the support disc 39 and the rotor 36.

A double wall insulating shell shown generally at 44 is mounted on the flange 26 and support plate 28 and comprises an inner wall 46 and an outer corrugated wall 48 straddling the insulation 30 and configured to completely enclose the boiler structure therein. The space between the walls of the shells is preferably evacuated and sealed to provide a low heat transfer rate between the inner and outer surface thereof. In lieu of the evacuated space or in addition thereto, a filler having low heat transfer properties 49 (FIGURE .9) may be disposed between the walls 46 and 43. This filler may be any suitable material such as glass fiber, iperlite, Styrofoam or the like. In addition to the evacuated shell 44, a base member 50 is attached beneath the main flange 26 and the support plate 28 to define a space beneath these members, the space being evacuated, sealed and/ or filled in the manner of the walls of the shell to provide minimum heat transfer between the support plate 28 and the atmosphere. An annular reinforcing flange 52 is disposed on the top of the shell 44 proximate the center thereof to provide support for the shaft 42 through a ball bearing housing and assembly 54. The top of the shell 44 is configured, at the point where the shaft 42 is disposed therethrough, to form a depending annular chamber with an annular base disposed proximate the bottom portion of the shaft 42. The configuration of the shell at this point provides isolation of the bearing housing and assembly from the interior of the boiler to prevent overheating thereof as well as heat transfer to the atmosphere therethrough. A bearing cooling and lubricating fluid is supplied to the bearing housing 54 through a port 56 in the top end of the shaft 42 and is exhausted from the housing through a port 58 disposed beneath a pulley 22. This fluid may be diverted from the boiler working fluid as is described in more detail in applications above-mentioned co-pending application, Serial No. 373,661.

Referring again to the vapor tube support 39, the support is provided with an upstanding wall 60 around the outer periphery thereof forming, with the support, a general ly tub-shaped structure as shown. A continuous set of vapor tube coils are helically wound in the manner of a multiple thread screw around the outside of the wall 60 to provide an outer bank of vapor tubes 62. The tubes are then helically wound down the inner surface of the wall 60 to provide an inner bank of vapor tubes 64. A plurality of U-shaped superheater coils 66 are mounted in an annular configuration between the wall 60 and the vapor dome 40. The superheater coils are mechanically supported by a plurality of annular fins 68 in such a manner that an inner concentrically disposed foraminous tub is formed within the wall 60.

Referring again to the inlet line 12, an inlet fluid distribution line 70 is communicative therewith and conmeets the inlet line to a preheater inlet line 72. The line 72, drilled through a conical annular preheat tube supsort 73, is connected to a continuous coil of tubing 74 which is helically wound to form a cylinder proximate lo the inner wall 46 of the shell 44. The coil 74 thereby :orms a preheat she'll spaced from the inner wall 46 erminating in a connection with a preheat fluid collector nanifold 76 at the top thereof. The manifold, in turn, s connected to the preheat fluid discharge line 78 which s routed down the outside of the shell formed by the rreheat coil 74 and through the connector 80 to the aniulair space 82 situated within the bearing base 32. The tandpipe 15 is coaxially supported within the annular pace 82 in spaced relation to the walls thereof by ribs i4 so that fluid in this space completely surrounds the tandpipe. The annular space 82 is communicative, lroximate the upper end thereof, with radially extending 'apor tube feed lines 86 radially disposed in the vapor ube support 39. Each of the feed lines 86 terminates 1 communication with an individual coil in the outer ank of vapor tubes 62 at the outer ends thereof. As has een set forth above, the inner bank of vapor tubes 64 onstitute continuations of a set of continuous vapor tubes I-hich cross over the wall 60 from the outer bank of tubes 2. The tubes of the inner bank terminate in a connecon to superheater feed conduit 88, disposed in the vapor lbe support 39 above the vapor tube feed lines 86. The iperheater feed conduits communicate with the supereater coils 66, with communication being first made to re innermost leg thereof and exhaust being made from it; outermost leg, The outermost leg of the superheater coil communicates, at the bottom end thereof, with the vapor dome feed line 90.

A vapor outlet valve, shown generally at 92 is centrally disposed on the top end of the standpipe 15. This valve consists of a cylinder 94 containing a piston 96 which has a valving member 98 formed integrally therewith. The valving member cooperates with a valve .seat 100, mounted on the standpipe 15 to control communication between the vapor dome 40 and the standpipe. The upper end of the cylinder 94 is partially sealed by a concave plate 102 to enable a certain amount of fluid leakage from the interior of the vapor dome 40 into the cylinder. A pilot line 104 communicates with the enclosed space formed between the plate 102 and the piston 86 for purposes to be described below.

Referring now to FIGURE 3 of the drawings, the disposition and communication of a portion of the various feed lines described above is shown in plan form. One of the vapor tube feed lines 86 is shown emanating from the annular space 82 for connection with one of the coils of the outer bank of vapor tubes 62 mounted on the outer periphery of the wall 60. Return from the coil in the inner bank of vapor tubes 64 is accomplished through the superheater feed line 88 which communicates with the innermost leg of the superheater coil 66. The output from the outermost leg of the coil 66 is discharged into the vapor dome feed line which communicates with the steam dome 40.

Referring to FIGURE 4, details of the superheater coils 66 are shown in plan form. As can be seen by reference to this figure, the superheater coils are preferably elliptical in cross sectional shape with the major axis thereof oriented in a direction angled outwardly and toward the direction of rotation of the boiler rotor as indicated by the solid arrow in that figure.

-In the operation of the device as thus far described and again referring to FIGURE 2 of the drawings, fuel is supplied to the boiler through the fuel input line 17 and ignited by suitable means (not shown) so that a hot flame is injected into the lower portion of the boiler. The hot gases, rising in the direction shown by the broken arrows, pass between the preheater coils 74 and the outer bank of vapor tube coils 62, over the top of the wall 60 into the space formed therein. From this point the gases pass over the inner bank of vapor tubes 64 and through the structure formed by the superheater coils 66 and the fins 68. The resultant gases, with most of the energy removed therefrom by passage through the aforementioned structures, are then exhausted outwardly along the inner wall 46 passing between the inner wall and the preheater coils to the exhaust line 18. An annular seal 67, provided around the upper portion of the structure formed by the superheater tubes 66 and the tins 68, is in close proximity with the preheater collector manifold around the inner periphery thereof and serves to direct all of the exhaust gases from the superheater coils directly to the boiler exhaust. Circulation of the gases may be augmented by furnishing a series of fan blades 108 on the base of the vapor tube support 39. These blades rotate with the boiler rotor and are disposed to create upward currents between the wall 60 and the preheater coil 74.

The fluid circuit Fluid from the intake line 12 is transmitted to the preheater coils 74 through the distribution line 70 and the preheater inlet line 72. The fluid is then circulated through the preheater coils 74 picking up energy from the hot inlet gases rising between the preheater coil and the outer bank of vapor tube coils 62. The preheated fluid is then gathered in the preheater collector manifold 76 and passed through the preheater discharge 78 to the annular chamber 82. With the boiler rotor 36 and vapor tube support 39 suitably driven by the motor 20 (FIG- URE 1), the fluid in the chamber 82, under the influence of the centrifugal force generated by the rotating struc-.

ture, is passed through the vapor tube feed lines 86 to the outer bank of vapor tubes 62. Fluid is then circulated through the outer bank of the vapor tubes 62 where it is heated by the incoming gases rising between the preheater tubes 74 and the outer tube bank 62. Since centrifugal force is greatest at this point, the pressure acting on the fluid is at its highest value and, even though vapor may exist in isolated pockets in the fluid, the more .dense liquid phase of the fluid is kept at the outer surface of the bank with the less dense vapor being forced to the inner surface of the tubing so that the liquid is always disposed next to the hottest part of the combustion chamber formed between the tubes. Local pockets of vapor which could cause hot spots are thereby prevented by the rotating rotary structure of the boiler. The peripheral speed of the boiler rotor 36 is also greatest at this point thereby providing the highest heat transfer rates between the hot gases and the surface of the vapor tubes since heat transfer is proportional to the velocity of the gas over the surface to which heat is being transferred. The fluid is then passed over the top of the wall 60 and down the inner bank of vapor tubes 64 where, because of the lower pressure in this area and due to the incre-ased'fluid temperature, the liquid is transformed into vapor. The vapor then enters the superheater feed conduits 88 and is transferred to the super-heater coils 66. The fluid circulating in these coils is then superheated by the hot gases passing through the coils 66 and tins 68. As pointed out above, the fluid enters the inner leg of the superheater coils first and is exhausted from the outer leg so that a counterflow heat exchange efifect is produeed increasing the efficiency of heat transfer between the combustion gases and the vapor in the tubes. This counterflow is achieved by passing the cooler input vapors through the cooler exhaust gases first and then exposing the warmer output vapors to the hotter input gases thereby providing a maximum temperature differential and, therefore, the most efiicient heat exchange vbetween the gases and the vapor. From the superheater coils fluid is then transferred to the vapor dome 40 through the vapor dome feed conduits 90 where it is collected in the high pressure reservoir for-med thereby.

The valve 92, when initially disposed in a closed condition as shown, is held in the closed condition by high pressure vapor which leaks through the seal for the plate 102 and exerts force between the plate and the piston 96 to maintain the piston and the valving member 98 biased against the valve seat 100. When vapor is required from the boiler, a bleed valve 105 disposed outside of the boiler area in the pilot line 104, is opened to exhaust the high pressure vapor from between the plate 102 and the piston 96. The fluid pressure of the vapor in the dome, acting on the outer transverse surfaces of the piston 96, forces the piston upwardly thereby lifting the valving member 98 from the valve seat 100 and allowing the high pressure, high temperature vapor to be exhausted through the output line 14. Referring again to the superheater tubes 66 and particularly to the view thereof shown in FIGURE 4, the elliptical configuration of these tubes and their disposition with respect to the incoming gas offers a minimum amount of resistance to the flow of the combustion gas therethrough and, in combination with the rotation of the structure as a whole, can be designed to further induce the gas flow therethrough.

Although two circular rows of superheater tubes are shown, it should be understood that more than this number could be incorporated in the superheater structure if necessary. The particular shape of these vapor tubes shown, although preferred for the reasons given above, could also be obviously varied without altering the basic operation of the invention.

The helical arrangement of the vapor tubes in the

banks

62 and 64, as before described, is like the configuration of a multiple thread screw. Each of the tubes may have more than one turn around the boiler rotor depending on 6 the tube size, fluid flow velocity, etc. The total cross sectional area of .the tube must be great enough to allow moderate fluid velocity through the tubes as can be determined by proper design thereof.

It is particularly important and preferred that the valve 92 be located inside the vapor storage space and not outside of the boiler on the line 14 since, if so situated, the valve would not be well insulated and would, therefore, cool to a temperature lower than that of the vapor dome on shut-down. The vapor .trapped in the valve at shutdown would eventually condense into liquid in the outlet line causing not only a heat loss but would throw a slug of liquid through the power system when the valve ultimately is opened.

It should be also obvious that the areas of the piston and valve seat can be adjusted through standard design techniques and that springs could also be incorporated in the valve structure to alter or balance the force acting on the valve as desired.

Since a fluid in the vapor state has a higher specific volume than fluid in the liquid state, a larger flow rate will be induced in the inwardly flowing vapor conduits 90, than in the outwardly flowing liquid in the conduits 86. This situation can create an appreciable discharge velocity through the conduits 90, and this velocity may be utilized to help provide motive force for the rotor 36, thereby reducing the power requirements for rotation of the rotary stmcture through the shaft 42. Turning now to FIGURES 6 and 7 of the drawings, a device for so utilizing this increased vapor discharge velocity is shown. Generally speaking, the invention consists of means to deflect the exhaust flow, into the vapor dome 40, in a direction opposite to the direction of rotation of the boiler rotor thereby utilizing the jet reaction force of the exhausting vapor to aid in the rotation of the boiler rotor. This is achieved by providing a ring of exhaust nozzles 112 around the inner periphery of the boiler rotor 36 adjacent each of the vapor dome feed conduits 90, the exhaust nozzles being formed to deflect the exhaust from these conduits in a direction opposite the rotative direction of the rotor indicated by the arrow.

Since both the rotor 36 and the stationary bearing base and the rotor support contain fluid, a seal must be provided to retain the liquid within the structure at the joint between the relatively rotating parts. Turning now to FIGURE 5, an enlarged detail of the main rotor seal is shown generally at 114. This seal incorporates principles more fully disclosed in the applicants co-pending application, Serial No. 403,234, filed October 12, 1964, and generally includes rotating metallic seal face 116 mounted on the boiler rotor in close, lapped mechanical rubbing contact with a stationary graphite seal face 118 mounted on the bearing base and rotor support 32. The seal 118 is held against the seal 116 by a coil spring 120 and both seals are slightly free to align themselves against each other by a loose mounting .to their supporting structure and flexible packing rings 122 and 124 providing sealing contact between the seal member and the supporting structure. The contact portion of the rubbing seal face is at approximately the same diameter as .the cylindrical surfaces on which the seal rings are mounted so that unbalanced pressure from inside the seal faces produce very little vertical or axial force on the rings. A chamber 126 is provided around the

seals

116 and 118 and is further pressurized with a lubricant through conduit 128 from a pressure source (not shown), the pressure thereof being kept approximately equal to the pressure of the fluid in the space 82 so that the tendency of the fluid :to leak across the sealing faces under the influence of differential pressure is minimized.

The lubricant is sealed in the chamber 126 by a secondary seal which is composed of a graphite sealing ring 130 rotating against a stationary spring biased seal face 132. A chamber 134 is provided around .these latter-mentioned sealing members and is isolated by a packing seal 136.

This chamber is at approximately atmospheric pressure but is kept full of liquid by the packing seal 136. As the lubricant tends to leak from the high pressure area of the chamber 126 into the low pressure 134, the lubricant collects in the chamber 134 and overflows through a passage 138 into the area of the ball bearings 38 and from there may be drained out to a lubricant sump (not shown). It should be obvious that additional lubricant for cooling and lubricating the bearings could be supplied from pumps (not shown) to .the chamber 134 if additional cooling is required in the ball bearing area. A heat shield 140 is disposed on the outside of the bearing housing to reduce the heat transfer from the combustion space inside of the boiler into the bearing housing 34.

It is important to keep the seal rubbing speed and the diameter of the seal faces 116 and 118 as small as possible to minimize wear. To produce the minimum diameter in the seals, the standpipe is formed in the shape of a venturi as shown with the throat of the venturi being near the position of the seals with the diffuser toward the larger diameter at the base of the standpipe. This provides a relatively small diameter and high velocity vapor flow at the throat of the venturi proximate the seals, however, the vapor kinetic energy is largely recovered and converted into pressure by the expansion into the diffuser toward the outlet of the standpipe.

By utilizing the centrifugal force, the conduits 86 can serve as a partial boiler feed pump to increase the pressure of the fluid therein to a higher value. The tubes may be modified so that the passages in themselves do not generate any substantial pressure increase by alternately connecting conduits 88 (FIGURE l) and 86. If, however, it is desired to utilize the conduits 86 as partial feed pumps, then the interior of the vapor dome 40 (FIGURE 2) must be sealed from the annular space 82 since a pressure differential will exist therebetween. In FIGURE 5, this seal is shown generally at 142 and comprises close fitting sealing rings 144, 145, 146 and 147 which are mounted on the rotor 36 and run with a close clearance around the standpipe 15.

Referring again to FIGURE 2, a safety pressure release device 148 is disposed in the annulus between the bearing base and rotor support 32 and the standpipe 15. This device is required on high pressure boilers and comprises a breakable disc of carbon or other suitable brittle material. The disc is supported at the outer periphery thereof by suitably

soft gaskets

150 and 152 and is sealed against the standpipe wall by an O ring 154 or other suitable packing material.

In case of an overpressure condition in the boiler, the disc will fracture and release the boiler fluid downward, thereby serving as an emergency pressure release. Under the normal conditions the disc is beneath the fluid in the liquid state and is not subject to the higher superheat temperature except at the surface of the output line 14. The disc furthermore, is not subjected to the full pressure of the fluid in normal operation because of the centrifugal force on the liquid, but in the event of overheating with the attendant overpressure in the boiler, the vapor will tend to reverse flow and fail the disc. The location of the disc also provides for easy replacement thereof in the event of overheating of the boiler or premature fatigue failure. It should be noted that the disc is under full fluid pressure when the boiler is shut down and not rotating, thereby providing for safety release at the most dangerous time when overpressure is likely to occur since overheating is most likely through control malfunction when no one is normally in attendance.

It should be noted that, in general, the boiler provides gas-to-fluid contact in such a manner that the hottest exhaust gas generally gives up heat to the coolest vapor passages, thereby providing the greatest temperature differential and the greatest possible heat transfer from the exhaust gases. The arrangement and configuration of the vapor tubes also provides insulation for the boiler inner wall 46 so that high temperature materials are not required for this portion of the boiler structure.

As an alternate to having fan blades 1118 on the rotor 36, an external fan 183 (FIGURE 11) can be used to force air through the combustion space. Guide fins could be placed on the preheat inlet line 72 to guide the combustion gases radially outwardly. This variation would use less power since less power is required to move the cool air than the hot combustion gases and the relative velocity of the rotating vapor tubes with respect to the gas would, therefore, be higher. If an external fan is used, it is also possible to form the fan blades 108 in a configuration so that they would act as turbine blades and utilizing the action of the flow through the blades to turn the rotor. This would, in effect, produce a simple combustion gas turbine which would make it possible to turn the rotor with a minimum requirement for external power.

Referring to FIGURE 8 and FIGURE 11, an arrangement is shown incorporating the above-referred to external fan, turbine blades 108a and also incorporating turbine nozzles 184 mounted on the disc 73 which encloses the preheat inlet lines 72. This arrangement directs the incoming flow of gas against the turbine blades 108a. In effect, with this arrangement, the rotor 39 becomes a gas turbine with sufiicient power to overcome friction and whatever boiler feed pumping power required by the rotor. By utilizing this arrangement, the motor for turning the rotor can be comparatively small and need only be used at startup and possibly at idling conditions.

The space defined by the outer wall 48 and the inner wall 46 is preferably evacuated and/or filled with an insulation material thereby providing an extremely effec tive heat transfer barrier around the entire boiler structure. Little heat loss, therefore, occurs in the boiler and, as described in greater detail in the aforementioned copending application, Serial No. 373,661, allows the boiler to be shut down for long periods of time while maintaining operating pressure with a minimal expenditure of fuel.

It should be noted that, as shown in FIGURE 2, the gas inlet and exhaust outlet openings are disposed toward the lower portion of the boiler. This provides a benefit in that, since the hotter air and gas normally tends to rise to the top of the confine, the heat losses through these openings when the boiler is in a period of extended shutdown will be kept to a minimum. It is also contemplated that valves may be inserted in the exhaust and/or intake lines outside of the boiler to provide reduced heat loss. This system is more completely described in the aforementioned co-pending application, Serial No. 373,661.

The outer wall 48 is subjected to compressive stress and is, therefore, preferably formed with integral corrugations to resist collapse of the wall under the force imposed by the vacuum. The outer wall 48 is kept concentric with the inner wall 46 preferably by utilizing a low heat transfer type of spacing support therebetween. A support ideally adapted for this use is described in detail in applicants co-pending application, Serial No. 374,448, filed June 11, 1964.

In a rotary boiler such as that described above, and particularly in a rotary boiler utilizing halocarbon as a boiling liquid, the maintenance of the proper amount of liquid in the boiler during operation thereof constitutes an important problem. It is very important to keep the boiling fluid in its liquid form on the outer periphery of the rotating section and particularly in the outer portion of the outer bank of vapor tubes 62 because this structure is closest to the hottest part of the combustion zone. It is also important to restrict the fluid in the superheater section to the vapor phase in order to raise the temperature thereof high enough to obtain the proper thermodynamic cycle efficiency. The line of demarkation between the liquid and the vapor phase should, therefore,

-or decreased liquid'flow to the boiler as required.

.sulation ring 178.

be near the outer periphery of the rotor 36, between the superheater tubes 66 and the outer bank of vapor tubes 62. Referring now to FIGURE 8 of the drawings, a device for providing a proper control for the fluid flow to the'boiler and, therefore, the position of the vapor-liquid phase interface is shown. The flow of liquid into the boiler can be easily cont-rolled by a throttle valve at the feed pump and any type of servo motor could operate the valve in response to a suitable signal from a sensing device in the boiler. The main difficulty in the control of the phase interface line is the problem of continually Sensing the location of the line. It is, therefore, necessary to provide a device which signals a servo motor or the like-to operate the throttle valve and provide increased In the device of FIGURE 8, a channel 156is provided radially in the boiler rotor 36between adjacent vapor tube feed lines 86 (FIGURE 2) and is in communication with the inner bank of the vapor tubes 64 through a sensing bore 158. A mass bob 160 is suspended in the channel 156 by a cable or rod 162 which, in turn, is connected to a spring 164 mounted on a support 166 situated on the rotor 36. A contact 168 is disposed on the free end of the spring 164 and co-acts' with a similar contact 170 mounted on an annular slip ring 172. The slip ring 172 is supported on the rotor 39 by a suitable insulation ring 174 and is contacted by a carbon brush 176, mounted on the valve seat 100 and insulated therefrom by an in- The brush is connected to a feed pump valve servo motor 179 by an insulated electrical conductor 180 disposed through the wall of the valve seat 100, enclosed by a thermally insulated tube 182 to the exterior of the boiler.

In operation, the sensing device functions as follows: When the boiler is in operation and the rotor 36 is rotating, the liquid-vapor interface of the fluid in the vapor tubes takes a position of equilibrium, with respect to the fluid in the centrifugal force field, in the channel 156 through the agency of the sensing bore 158. When the boiler is at a proper rotative speed, the mass bob 160 is suspended concentrically within the channel 156 and exerts a force on the spring 164 through the cable 162. The force exerted by the mass bob is proportional to the square of the rotational velocity of the rotary portion of the boiler times the mass of the bob less the mass of the fluid 'which the bob displaces. Since the density of liquid is greater than that of vapor, the force will be less when the mass is immersed in liquid than when it is immersed in vapor. For example, if the density of the material of the mass bob 160 is equal to that of the liquid, then the force on the cable would be substantially zero if the mass is fully immersed in the liquid. As the line of demarcation or interface between the liquid and the gas moves along the length of the mass bob 160, the force on the cable 162 will change and this change can be utilized to deflect the spring. When the liquid in the channel 156 is reduced to a certain extent, the effective mass of the mass bob 160 acting on the spring 164 is increased to a degree suflicient, under the influence of centrifugal force, to deflect the spring 164, thereby breaking the electrical circuit between the contacts 168 and 170. This break in the circuit is sent as a signal to the control operating a valve 181 at the feed pump through the slip ring 172, brush 176, and conductor 180 to open the-valve and provide an'increasedamount of liquid to the boiler. When the amount of liquid in the boiler is suflicient to maintain the desired vapor-liquid phase distribution, the volume of fluid in 1 the channel 156 is increased to the point that the eflective mass of the bob acting on the spring is overcome by the force of the spring and the contacts close completing the trical transducers that could be utilized to transmit the signal indicating the sensed liquid-vapor phase line. Other devices such, for example, as variable resistance rheostats operated by the movement of the spring 164, variable inductance devices comprising a magnetic membrane inside a coil, variable capacitance devices or the like could obviously be used.

The slip ring and brush structure described could also be replaced with a small coil on the valve seat proximate a magnetic material mounted on the spring 164 so that, as the magnetic material passes the coil on each revolution of the rotor, the inductance of the coil would be affected to a greater or lesser degree depending on the proximity of the magnetic piece 164 to the coil, which, in turn, would be controlled by the deflection of the spring 164, thereby providing a signal for the amount of deflection of that spring. The change in force acting on the spring can be translated into a changing electrical signal by utilizing a transducer to sense the change in force. In the simplified case shown in FIGURE 8, the transducer is in the form of the switch shown which consists of the pair of contacts 168 and 170. The contact 168 is grounded to the boiler and frame of the apparatus through the boiler structure, ball bearings, etc. while the contact 170 is suitably insulated from the supporting structure.

As a further alternative, the sensing device for the vapor-liquid interface could take the form of a temperature sensitive device suspended in the channel 156. If the device were submerged in liquid, then the temperature would be at or below the saturation temperature for the fluid whereas if the sensing device were primarily in vapor, the temperature would be closer to the superheat temperature for that vapor. The temperature sensitive device could be a thermistor, which has a sharp change in resistance under the influence of a small change in temperature, which 'would change the current in a circuit in the same manner as was accomplished by the variable resistance transducer actuated by a change of force as described above.

It is intended that an automatic control to monitor the fuel supply to the boiler will be incorporated with the boiler system to provide continuing control of the supply of heat to the boil as heat is taken therefrom. This control could be operated in various manners, such, for example, as temperature sensitive probes in the vapor system to signal the control for increased heat when the temperature level of the vapor diminishes or increases to a certain value.

Although the geometry and dimensions of the boiler system will depend on the power requirements placed thereupon, a boiler of the type described, suitable for .powering the automotive vehicle of the above-referred to co-pending application Serial No. 373,661, could reasonably be on the order of 24 inches in height by 24 inches in diameter. The vapor pressure anticipated in the system is in the neighborhood of 300 to 400 lbs. per square inch maximum with a vapor temperature in the neighborhood of 400 F. The maximum temperature at the hottest parts of the burner section of the boiler is not anticipated to be greatly in excess of 500 F. In the system described as intended to be used in the automotive power plant, the rotating velocities for the boiler rotor and rotating elements are not predicted to be greatly in excess of 2000 r.p.m.

Although many fluids could be used as the boiling liquid in the above system, it is specifically contemplated that a suitable halogenated hydrocarbon such as one of the fluorocarbons will be utilized since they are particularly suitable for use in this system. A preferred compound of this type is octafluorocyclobutane (C 1 which has boiling point of 21.1 F. at standard atmospheric pressure and is commercially available under the trademark name of Freon-C318. This fluid has, in relation to water, a higher vapor pressure, lower specific volume at atmospheric pressure and standard temperature, higher molecular weight, lower latent heat of vaporization and a lower energy drop per pound of fluid passing through an expansion cycle. This fluid although initially expensive, is particularly suitable for the use contemplated since it allows the use of a small volume of fluid because of the high energy delivery capability. A fluid capacity of 2 gallons is deemed feasible for the system described when applied to an average automotive power plant.

A particular advantage realized by the boiler embodying this invention lies in the type of fuel usable in its operation. Any type of reasonably light hydrocarbon fuel may be used interchangeably and the boiler will operate efliciently on propane, butane, kerosenes, low octane, or high octane gasoline, diesel oil, etc. The combustion in the boiler is efficient and relatively complete thereby substantially eliminating discharge of unburned residue such as carbon monoxide in the exhaust gases.

What has been set forth above is primarily intended as exemplary to enable those skilled in the art in the practice of the invention. It should, therefore, be understood that, within the scope of the appended claims, the invention may be practiced otherwise than as specifically set forth.

What is, therefore, claimed as new and desired to be protected by Letters Patent of the United States is:

1. A vapor generator comprising:

a vapor generator enclosure having vaporizable fluid therein, a vapor exhaust standpipe disposed in said enclosure, means to control fluid communication between said enclosure and said standpipe, means to heat said enclosure to provide vaporization of the fluid therein, a rotating support in said enclosure coaxially disposed intermediate the ends of said standpipe, a vapor dome mounted on said rotating support to enclose the upper end of said standpipe, a fluid heat exchange and transmitting tube assembly disposed on said rotating support, means to transmit vapor from said assembly to said vapor dome for storage therein, a preheater tube assembly fixedly mounted around the walls of said enclosure adjacent said rotating support and fluid tube assembly, means to supply liquid to said preheater tube assembly for preheating therein and means to transmit preheated liquid therefrom to the fluid tube assembly disposed on said rotating support, and means to control the quantity of liquid and heat supplied to said generator.

2. A vapor generator for vapor powered prime movers comprising:

a generator support;

a vertical vapor exhaust standpipe coaxially disposed through said support, means to control communication into the upper end of said standpipe;

an enclosure mounted on said support to enclose the upper surface thereof;

a rotating support mounted in said enclosure coaxially around said standpipe, means to rotate said rotating support;

a vapor dome coaxially mounted on said rotating support to enclose the upper end of said standpipe;

an annular stationary preheater support disposed around the periphery of said rotating support;

and a fluid system comprising:

(a) a fixed preheater tube system including a helical coil forming a vertical tubular structure mounted on said preheater support, means to supply fluid to said preheater coil for preheating therein;

(b) an annular reservoir disposed around said standpipe, means to supply fluid from said preheater coil to said reservoir;

() a plurality of helically wound vapor tube coils configured to form a vertical tubular structure mounted around the periphery of said rotating support to rotate therewith, means 'to supply fluid from said reservoir to said vapor tubes for vaporization therein;

((1) a plurality of superheater tubes disposed on said rotating support intermediate said vapor tubes and said vapor dome, means to supply vapor from said vapor tubes to said superheater tubes for superheating therein, and means to transmit superheated vapor from said superheater tubes to said vapor dome for collection therein;

gas inlet and exhaust conduits through the walls of said enclosure, and means to supply heat through said inlet to said enclosure for circulation between said preheater tubes and said vapor tubes, means to direct said gas inward over the top of said vapor tubes and through said superheater tubes, and means to exhaust said gas between said preheater tubes and the walls of said enclosure to said exhaust.

3. A vapor generator comprising:

a base support;

a casing mounted on said support to form an enclosure therefor;

a vapor exhaust standpipe coaxially disposed through said support and extending into said enclosure, means disposed at the upper end of said standpipe to control communication therewith;

an annular wall concentrically disposed around a portion of said standpipe, said Wall with said standpipe defining a fluid reservoir therebetween;

means to supply heated gas to and exhaust spent gas from said enclosure;

a rotating support in said enclosure coaxially disposed intermediate the ends of said standpipe adjacent said reservoir, means to rotate said rotating support;

sealing means between the annular wall defining said reservoir and said rotating support;

a vapor dome coaxially mounted on said rotating support, said dome enclosing the upper end of said standa vapor tube assembly disposed on said rotating support proximate the periphery thereof, means to transmit liquid from said reservoir to said vapor tube assembly for vaporization therein;

a superheater tube assembly disposed on said rotating support intermediate said vapor tube assembly and said vapor dome, means to transmit vapor from said vapor tube assembly to said superheater assembly for superheating therein, and means to transmit superheated vapor from said superheater assembly to said vapor dome for storage therein;

an annular preheater support fixed with respect to said base support and disposed around and proximate the periphery of said rotating support;

a preheater tube assembly disposed on said preheater support including means to supply liquid thereto for preheating therein, and means to transmit preheated liquid from said preheater tube assembly to said reservoir for collection therein;

and means to control the quantity of liquid supplied to said preheater tube assembly, said means being actuated by the location of the vapor-liquid interface between said vapor tube assembly and said superheater tube assembly.

4. A vapor generator comprising:

a bas support;

a casing mounted on said support to form an enclosure therefor;

a vapor exhaust standpipe coaxially disposed in spaced relationship through said base support, means disposed at the upper end of said standpipe to control communication therewith;

an annular wall concentrically disposed around a portion of said standpipe, said wall with said enclosure defining a fluid reservoir therebetween;

a fiangeable safety disc disposed in sealing relationship between said "base support and said standpipe to form the lower portion of said reservoir, said disc being configured to fail and provide safety release of vapor in said reservoir upon overpressure therein;

' means to supply heated gas to and exhaust spent gas from said enclosure;

a rotating support in said enclosure coaxially disposed intermediate the ends of said standpipe adjacent said I reservoir, means to rotate said rotating support; sealing means between the annular wall defining said reservoir and said rotating support;

a vapor dome coaxially mounted on said rotating support, said dome enclosing the upper end of said standp r a vapor tube assembly disposed on said rotating support proximat the periphery thereof, means to transmit liquid from said reservoir to said vapor tube assembly for vaporization therein;

a superheater tube assembly disposed on said rotating support intermediate said vapor tube assembly and 'said vapor dome, means to transmit vapor from said vapor tube assembly to said superheater assembly for superheating therein, and means to transmit superheated vapor from said superheater assembly to said vapor dome for storage therein, said superheater tubes being elliptical in cross section, the major axis of said superheater being angled outwardly in the direction of rotation of said rotating support to provide miniinumresistance thereof to the flow of gas therethrough;

a preheater tube assembly disposed on said preheater support including means to supply liquid thereto for preheating therein, and means to transmit preheated liquid from said preheater tube assembly to said reservoir for collection therein; 1

5. A generator in accordance with claim 4 wherein said base support includes upper and lower spaced surfaces having thermal insulation therebetween, and wherein said casing includes spaced outer and inner walls thereto having thermal insulation therebetween.

6. A vapor generator in accordance with claim 5 wherein said thermal insulation includes a material of low thermal conductivity between said surfaces and between said walls.

7. A vapor generator in accordance with claim 6 wherein said thermal insulation further includes a vacuum between said surfaces and between said walls.

8. A vapor generator in accordance with claim 5 wherein said thermal insulation includes a vacuum between said surfaces and between said walls.

9. A generator in accordance with claim 4 wherein said sealing means comprises an annular non-rotating shoulder having a transverse surface thereto coaxially mounted on said annular wall, said shoulder having a cylindrical sealing surface therearound, an annular nonrotating sealing member slidably and sealably mounted .on said sealing surface, a rotating shoulder mounted on shoulder, an annular rotating sealing member slidably and sealably mounted around said rotating shoulder cylindrical sealing surface in abutting sealing relationship to said non-rotating member, the abutting faces of said members being substantially equal in area and diameter to the transverse surfaces of said shoulders, said annular wall having a bore coaxially disposed therein defining a chamber around said shoulders and said sealing members, annular bearings coaxially disposed around said annular wall to rotatably support said rotating support, means to provide communication between said bearings and said chamber, means to supply lubricant under pressure to said bearings and said chamber, and means to substantially equalize the pressure between the lubricant in said chamber and the fluid in said reservoir to minimize pressure differentials across the sealing faces of said sealing members and means to bias said sealing members in sealing relation to one another.

10. A vapor generator in accordance with claim 4 wherein said means to rotate said rotating support comprises at least a shaft coaxially mounted on said rotating support and extending through said enclosure, a motor associated with said shaft to provide rotation thereof, and motor control means to control the operation of said motor.

11. A vapor generator in accordance with claim 10 wherein said means to rotate said rotary support further comprises turbine blades mounted thereon, said blades being disposed to be rotated by the heated gases supplied to said enclosure to provide a portion of the energy for rotation of said rotating support. 7

12. A generator in accordance with claim 10 wherein said means to rotate said rotary support further comprises a gas compressor associated with said means to supply heated gas to said enclosure, said compressor being disposed to provide pressurization of said gas prior to heating thereof, turbine nozzles mounted on said preheater tube support adjacent said rotating support, turbine blades mounted on said rotating support adjacent said nozzles,

said blades and said nozzles extracting energy from the pressurized heated gas supplied to said enclosure to provide rotative power for said rotating support.

13. A vapor generator in accordance with claim 10 wherein said means to rotate said rotating support further comprises flow nozzles disposed on said means to transrnit superheater vapor, said nozzles being configured to deflect said vapor into said vapor dome in a direction opposite the direction of rotation of said rotating support, whereby reaction from the deflected vapor flow through said nozzles provides a portion of the energy for rotation of said rotating support.

14. A vapor generator in accordance with claim 4 wherein said means to control communication with said standpipe comprises:

a valve seat concentrically disposed at the top ofsaid standpipe;

a valving member movable with respect to said seat between a closed position engaging said seat blocking communication with said standpipe and an open position spaced from said seat and providing comrnunication between said dome and said standpipe;

a cylinder coaxially disposed over said valve seat, said cylinder having a closed end and open end thereto, said open end being disposed adjacent said valve seat;

a follower piston associated with said valviug member movable therewith, said piston having transverse areas on either side thereof, said piston being slidably mounted in said cylinder and having a transverse area thereof exposed to the interior of said dome, said piston further having a transverse area exposed to the interior of said cylinder greater than the transverse area thereof exposed to the interior of said dome, partial sealing means between said dome and said cylinder to provide a control leakage between the interior of said dome and said cylinder;

bleed means including a bleed valve disposed on the exterior of said enclosure and communicative with the interior of said cylinder to provide remote control of bleeding from the interior of said cylinder;

whereby closure of said bleed valve provides actuation of said piston and said valving member to said closed position under the influence of differential pressure for acting on said piston resulting from the pressure buildup in said cylinder through leakage thereto from said dome, and whereby opening of said bleed valve will provide actuation of said valving member to said open position under the influence of a differential pressure acting on said piston resultmg from the drop in pressure in said cylinder through the loss of pressure therefrom through said bleed valve.

15. A vapor generator in accordance with claim 4 wherein said means to control the quantity of liquid supplied to said preheater tube assembly comprises sensing means to signal the liquid-vapor interface between the vapor tubes and superheater tubes of said vapor generator, a vapor feed valve to control the supply of liquid to said preheater tube assembly, operating means to operate said valve, and means to transmit the signal from said sensing means to said operating means to vary the quantity of fluid supplied to said vapor generator as determined by the location of said interface therein.

16. A vapor generator in accordance with claim 4 wherein said rotating support has at least one radially disposed bore defining a chamber therein, said chamber being communicative with said vapor tube assembly, and wherein said sensing means comprises a mass bob axially disposed in said chamber in spaced relationship to the walls thereof, an electrical transducer, means connecting said mass bob to said transducer to provide a signal of the force acting on said bob, said bob being disposed to intersect the vapor-liquid interface between the vapor tubes and superheater tubes in said vapor generator to thereby signal the location said interface through said transducer as a function of the relative mass of said bob when said rotating support is rotating.

17. A vapor generator comprising:

an annular base support including upper and lower spaced surfaces, thermal insulation between said surfaces;

a casing mounted on said support to form an enclosure thereon, said casing including spaced outer and inner walls thereto, thermal insulation between said walls;

a vapor exhaust standpipe coaxially disposed in spaced relation through said support and extending into said enclosure, said standpipe having a reduced Venturi portion thereto disposed intermediate the ends thereof, means disposed at the upper end of said standpipe to control communication therewith;

an annular wall concentrically disposed around a portion of said standpipe, subjacent said reduced portion, said wall with said enclosure defining a fluid reservoir therebetween;

a safety release including a flangeable safety disc disposed in sealing relationship between said base sup port and said standpipe, said disc being configured to fail and provide safety release of vapor in said reservoir upon over pressure therein;

means to supply heated gas to and exhaust spent gas from saidenclosure;

a rotating support in said enclosure coaxially disposed intermediate the ends of said standpipe adjacent said reservoir, means to rotate said support;

sealing means between the annular wall defining said reservoir and said rotating support, said sealing means being disposed adjacent the reduced portion of said standpipe;

a plurality of helically wound vapor tube coils mounted around the periphery of said rotary support, said coils being configured when wound to form a vertical tubular structure extending upwardly from said .rotary support an annular vapor tube support mounted on said rotary support, said vapor tube support being coextensive with and adapted to support the tubular structure formed by said vapor tubes, said rotary support having radially disposed bores therethrough connecting individual ones of said vapor tube coils to said reservoir to transmit fluid from said reservoir thereto;

a plurality of superheater tubes disposed on said rotary support intermediate said vapor tubes and said vapor dome, each of said superheater tubes com-prising an inverted U-shaped coil having outer and inner legs thereto and extending upwardly perpendicular to said rotary support, said superheater tubes being disposed in spaced relationship on a radius around said rotating support to form an upstanding annular structure thereon, a plurality of annular discs in coincidence with the annular structure formed by superheater tubes and disposed in spaced vertical relationship along the legs thereof, said discs engaging each of said superheater tubes to provide structural support and heat exchange fins therefore, said rotating support further having radial-1y disposed bores therein connecting each of said vapor tubes to an inner leg of said superheater tube for transmission of fluid from said vapor tubes to said superheater tubes and a plurality of radially disposed bores therein connecting the outer leg of each of said superheater tubes to said vapor dome for transmission of fluid from said superheater tubes to said vapor dome;

an annular frusto-conical preheater support member mounted on said casing and disposed around the periphery and proximate the lower face of said rotating support;

a preheater tube assembly disposed on said preheater support, said preheater tube assembly comprising a helical coil wound thereon to form a vertical tubular structure extending upwardly therefrom, said preheater tube assembly peripherally enclosing the tubular structure formed by said vapor tubes, means to supply fluid to said preheater coil for preheating therein, and means connecting said preheater tube assembly to said reservoir for transmitting the preheated fluid from said preheater tube assembly to said reservoir;

18. A vapor generator in accordance withclaim 17 wherein said means to control communication with said standpipe comprises:

a valve seat concentrically disposed at the top of said standpipe;

a valving member movable with respect to said seat between a closed position engaging said seat blocking communication with said standpipe and an open position spaced from said seat and providing communication between said dome and said standpipe;

a follower piston associated with said valving member and movable therewith, said piston having transverse areas on either side thereof, said piston being slidably mounted in said cylinder and having a transverse area thereof exposed to the interior of said dome, said piston further having a transverse area exposed to the interior of said cylinder greater than the transverse area thereof exposed to the interior of said dome, partial sealing means between said dome and said cylinder to provide a control leakage between the interior of said dome and said cylinder;

bleed means including a bleed valve disposed on the exterior of said enclosure and communicative with the interior of said cylinder to provide remote control of bleeding from the interior of said cylinder; whereby closure of said bleed valve provides actuation of said piston and said valving member to said closed position under the influence of differential pressure for acting on said piston resulting from the pressure buildup in said cylinder through leakage thereto from said dome, and whereby opening of said bleed valve will provide actuation of said valving member to said open position under the influence of a diflerential pressure acting on said piston resulting from the drop in pressure in said cylinder through the loss of pressure therefrom through said bleed valve. 19. A vapor generator in accordance with claim 17 wherein said sealing means comprises an annular nonrotating shoulder having a transverse surface thereto coaxially mounted on said annular wall, said shoulder having a cylindrical sealing surface therearound, an annular non-rotating sealing member slidably and sealably mounted on said sealing surface, a rotating shoulder mounted on said rotating support in opposed coaxial spaced relationship to said non-rotating shoulder, said rotating shoulder having a cylindrical sealing surface therearound and a transverse surface thereto substantially equal in area and diameter to the transverse surface of said non-rotating shoulder, an annular rotating sealing member slidably and sealably mounted around said rotating shoulder cylindrical sealing surface in abutting sealing relationship to said non-rotating member, the abutting faces of said members being substantially equal in area and diameter to the transverse surfaces of said shoulders, said annular wall having a bore coaxially disposed therein defining a chamber around said shoulders and said sealing members, annular bearings coaxially disposed around said annular wall to rotatably support said rotating support, means to provide communication between said bearings and said chamber, means to supply lubricant under pressure to said bearings and said chamber, and means to substantially equalize the pressure between the lubricant in said chamber and the fluid in said reservoir to minimize pressure differentials across the sealing faces of said sealing members, and means to bias said sealing members in sealing relation to one another.

References Cited by the Examiner UNITED STATES PATENTS 3/1905 Brown 12211 4/1939 Vorkauf 39.18

Claims

1. A VAPOR GENERATOR COMPRISING: A VAPOR GENERATOR ENCLOSURE HAVING VAPORIZABLE FLUID THEREIN, A VAPOR EXHAUST STANDPIPE DISPOSED IN SAID ENCLOSURE, MEANS TO CONTROL FLUID COMMUNICATION BETWEEN SAID ENCLOSURE AND SAID STANDPIPE, MEANS TO HEAT SAID ENCLOSURE TO PROVIDE VAPORIZATION OF THE FLUID THEREIN, A ROTATING SUPPORT IN SAID ENCLOSURE COAXIALLY DISPOSED INTERMDIATE THE ENDS OF SAID STANDPIPE, A VAPOR DOME MOUNTED ON SAID ROTATING SUPPORT TO ENCLOSE THE UPPER END OF SAID STANDPIPE, A FLUID HEAT EXCHANGE AND TRANSMITTING TUBE ASSEMBLY DISPOSED ON SAID ROTATING SUPPORT, MEAN TO TRANSMIT VAPOR FROM SAID ASSEMBLY TO SAID VAPOR DOME FOR STORAGE THEREIN A PREHEATER TUBE ASSEMBLY FIXEDLY MOUNTED AROUND THE WALLS OF SAID ENCLOSURE ADJACENT SAID ROTATING SUPPORT AND FLUID TUBE ASSEMBLY, MEANS TO SUPPLY LIQUID TO SAID PREHEATER TUBE ASSEMBLY FOR PREHEATING THEREIN AND MEANS TO TRANSMIT PREHEATED LIQUID THEREFROM TO THE FLUID TUBE ASSEMBLY DISPOSED ON SAID ROTATING SUPPORT, AND MEANS TO CONTROL THE QUANTITY OF LIQUID AND HEAT SUPPLIED TO SAID GENERATOR.