Cooling configuration for a cold gas turbine generator assembly

Abstract

A turbine generator assembly includes a turbine drivably connected to an electrical generator. The turbine includes a propellant input and a spent propellant exhaust. The spent propellant exhaust is connected to an exhaust flow path. An electrical component is connected to an output of the electrical generator such that the electrical component is powered by the electrical generator. A first heat exchanger including a cooling fluid inlet is connected to the exhaust flow path and a cooled feature is configured to be cooled by fluid received through the cooling fluid inlet. The cooled feature is at least a portion of the electrical component.

Claims

1. A turbine generator assembly comprising: a turbine drivably connected to an electrical generator; the turbine including a propellant input and a spent propellant exhaust, the spent propellant exhaust being connected to an exhaust flow path, wherein the exhaust flow path exhausts the spent propellant from the turbine generator assembly; an electrical component connected to an output of the electrical generator such that the electrical component is powered by the electrical generator, wherein the electrical component has a power discharge efficiency of at most 50% when converting electrical power to an action; and a first heat exchanger including a cooling fluid inlet connected to the exhaust flow path and a cooled feature configured to be cooled by fluid received through the cooling fluid inlet, wherein the cooled feature is at least a portion of the electrical component.

2. The turbine generator assembly of claim 1, wherein the cooled feature is a cooled fluid loop configured to cool the electrical component.

3. The turbine generator assembly of claim 1, wherein the cooled feature is a convective cooling surface of the electrical component.

4. The turbine generator assembly of claim 3, wherein the convective cooling surface includes at least one cooling fin protruding into cooling fluid flowpath of the first heat exchanger.

5. The turbine generator assembly of claim 1, further comprising a second heat exchanger including a second cooling fluid inlet connected to the exhaust flow line, a second cooling fluid outlet connected to the exhaust flow line, and a second cooled fluid outlet connected to a gear system, the gear system mechanically connecting the turbine to the electrical generator.

6. The turbine generator assembly of claim 5, wherein the second heat exchanger further comprises a third cooled fluid inlet connected to the electrical generator, and wherein a cooled fluid path passes through the gear system to the electric generator.

7. The turbine generator assembly of claim 6 wherein the second heat exchanger is disposed between the spent propellant exhaust and the cooling fluid inlet of the first heat exchanger.

8. The turbine generator assembly of claim 1, wherein the turbine is a cold gas driven turbine.

9. The turbine generator assembly of claim 1, wherein the propellant input is a metered nozzle configured to expand and supercool a propellant entering the turbine.

10. The turbine generator assembly of claim 1, further comprising a turbine housing containing the turbine, the electrical generator and the first heat exchanger.

11. The turbine generator assembly of claim 1, further comprising a pressurized propellant source connected to the propellant input.

12. The turbine generator of claim 11, wherein the pressurized propellant source comprises at least one pre-pressurized canister.

13. The turbine generator of claim 12, wherein the pressurized propellant source comprises at least one cold propellant generator.

14. The turbine generator assembly of claim 11, wherein the spent propellant exhaust has a temperature in the range of 300 to 150 degrees F. (184.4 to 101.11 degrees C.).

15. The turbine generator of claim 11, wherein the turbine is configured such that expansion of the propellant across the turbine super cools the propellant.

16. The turbine generator assembly of claim 1, wherein the electrical component has a power discharge efficiency of at most 25% when converting electrical power to the action.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 schematically illustrates a land based vehicle according to a first embodiment.

(2) FIG. 2 schematically illustrates a more detailed land based vehicle according to a second embodiment.

(3) FIG. 3 schematically illustrates a more detailed land based vehicle according to a third embodiment.

(4) FIG. 4 schematically illustrates a more detailed land based vehicle according to a fourth embodiment.

DETAILED DESCRIPTION

(5) FIG. 1 schematically illustrates a land based vehicle 10. The land based vehicle 10 includes a high power dissipation electrical component 20. The high power dissipation electrical component 20 can be any electrical component or system that utilizes a large amount of power and has a low efficiency for converting the power to a desired action. In some examples, the high power dissipation electrical component 20 can have an efficiency of lower than 50%. In alternative examples, the efficiency can be at most 25%.

(6) Due to the high power requirements for the high power dissipation electrical component 20, the vehicle 10 includes a dedicated electrical generation system. The dedicated electrical generation system includes an electrical generator 30 and a cold gas turbine 40. The dedicated electrical generation system provides the operational electric power to the high power dissipation electrical component 20. The cold gas turbine 40 receives a cooled propellant gas, and the cooled propellant gas drives the cold gas turbine 40 to rotate according to any conventional turbine system. Rotation of the turbine 40 is passed to the electrical generator 30 via a shaft 42. The rotation drives the electrical generator 30 to generate electricity, and the electricity is provided to the high power dissipation electrical component 20 via any conventional power distribution system.

(7) The pressurized propellant provided to the cold gas turbine 40 is expanded across the turbine 40, and is exhausted from the turbine 40 in a super cooled state. In some examples, the exhaust gas can be in the range of 300-150 degrees F. (184.4-101.11 degrees C.). In order to cool the high power dissipation electrical component 20, a heat exchanger 50 intercepts the exhaust flow 60 and transfers heat from the high power dissipation electrical component 20 to the exhaust flow 60. The output of the heat exchanger 50 is then returned to the exhaust flow 60 and exhausted from the vehicle 10. In some examples, the heat exchanger 50 utilizes the entire exhaust flow 60 in the heat exchange process. In alternative examples, only a portion of the exhaust flow 60 is redirected through the heat exchanger 50.

(8) With continued reference to FIG. 1, FIG. 2 schematically illustrates an exemplary cold gas turbine generator assembly 100 including a turbine 110 and a generator 120 contained within a turbine system 102. The cold gas turbine generator assembly 100 includes a cold gas inlet 104 that receives pressurized propellant from a propellant source 401 (illustrated in each of FIGS. 1-4), and provides the pressurized propellant to the turbine 110. In some examples, the pressurized propellant can be sourced from canisters storing pre-pressurized propellant. In alternative examples, the propellant can be sourced from a gas generator on board the vehicle 100. In yet further examples the propellant can be sourced from a combination of the two. The propellant is provided to the turbine 110 through a nozzle 106. The nozzle 106 meters and expands the propellant as it is provided to the turbine 110. Expansion of the propellant through the nozzle further causes the gas to be super cooled resulting in very cold exhaust temperatures.

(9) As the propellant is expanded across the turbine 110, the turbine 110 is driven to rotate. The rotation of the turbine 110 drives rotation of the generator 120 via a shaft 112 connecting the generator 120 to the turbine 110. The shaft 112 can be either a direct mechanical connection, as in the illustrated example, or a geared connection allowing the generator 120 to rotate at either a stepped up or a stepped down speed, relative to rotation of the turbine 110. Electrical power is provided from the generator 120 to a high power dissipation electrical component 130, which is outside of the turbine system 102. Spent propellant is exhausted from the turbine 110 along an exhaust flowpath 114, and is expelled from the turbine system 102.

(10) A heat exchanger 132 thermally connects the exhaust flowpath 114 with the high power dissipation electrical component 130. In the illustrated example of FIG. 2, the heat exchanger 132 is a plate and fin heat exchanger that utilizes a convective surface 134 exposed to the exhaust flowpath 114 to directly cool the high power dissipation electrical component 130. The plate and fin heat exchanger 132 also includes one or more fins 136 protruding into the exhaust flowpath 114. Each of the fins 136 further enhances the cooling effect provided by the heat exchanger 132 by increasing the surface area of the heat exchanger 132 that is exposed to the exhaust flowpath 114.

(11) With continued reference to the embodiments of FIGS. 1 and 2, FIG. 3 schematically illustrates an alternative embodiment of a cold gas turbine generator assembly 200 including a fluid based heat exchanger 232 for cooling a high power dissipation electrical component 230. As with the embodiment of FIG. 2, a turbine 210 receives a compressed propellant from a propellant source at a propellant input 204, expands the compressed propellant, and exhausts the spent propellant along an exhaust flowpath 214. The cold gas generator assembly 200 of FIG. 3 connects the turbine 210 to a generator 220 via shaft 212 connected to a gear system 214.

(12) In order to lubricate and cool the gear system 214, a second heat exchanger 250 can be incorporated into the exhaust flowpath 214, and can cool the lubricant provided to the gear system 214 via a convention gas-oil heat exchange system. In one variation of the illustrated cold gas turbine generator assembly 200, a lubricant loop 252 that provides the cooled lubricant to the gear system 214, and returns the spent lubricant to the heat exchanger 250, is extended through the electrical generator 220. In this variation, the cooled lubricant further cools the generator 220 in addition to the gear system 214.

(13) With continued reference to FIG. 3, FIG. 4 schematically illustrates another example embodiment cold gas turbine generator assembly 300, utilizing heat exchangers 350, 332. Aside from the heat exchanger configuration, and the coolant flowpaths 352, 334, the embodiment of FIG. 4 is identical to the embodiment of FIG. 3. In the example of FIG. 4, the second heat exchanger 350 and the first heat exchanger 332 are cascaded, with the coolant loop 352 passing through the first heat exchanger 332 as the cooling fluid, and cooling a second coolant loop 334 that passes through the high power discharge electrical component 330.

(14) It is further understood that any of the above described concepts can be used alone or in combination with any or all of the other above described concepts. Although an embodiment of this invention has been disclosed, a worker of ordinary skill in this art would recognize that certain modifications would come within the scope of this invention. For that reason, the following claims should be studied to determine the true scope and content of this invention.