WO2019210307A1

WO2019210307A1 - System and method for electricity production from pressure reduction of natural gas

Info

Publication number: WO2019210307A1
Application number: PCT/US2019/029674
Authority: WO
Inventors: Andrew Brash PEARSON
Original assignee: Anax Holdings, Llc
Priority date: 2018-04-27
Filing date: 2019-04-29
Publication date: 2019-10-31
Also published as: WO2019210309A1

Abstract

A system is disclosed that provides at least two turboexpanders operatively linked to a generator that generates electrical power from the reduction of the pressure of a natural gas stream wherein the system reduces the pressure of the natural gas stream in at least two pressure reduction stages, and wherein heat is added to the natural gas stream by the system to adjust the temperature before each pressure reduction stage. The generator can be a permanent magnet generator.

Description

Cross-Reference to Related Applications

[001] This application claims the benefit of U.S. Provisional Patent Application No.

62/664,009 filed April 27, 2018, and U.S. Provisional Patent Application No. 62/664,021 filed April 27, 2018, the contents of which are incorporated herein in their entirety.

Field Of The In vention

[002] The present disclosure relates to the production of electricity using the expansion of compressed natural gas coupled with waste heat recover ' from industrial processes. More specifically, the present disclosure relates to the production of electricity from a reduction in the pressure of the natural gas at a site in the pipeline distribution system for natural gas.

Description Of The Background

[003 ] Natural gas is obtained from wells drilled into in rock formations deep underground, where natural gas is found alone and association with oilier hydrocarbon fuels such as petroleum and coal deposits. In general, natural gas from such wells is cleaned, typically compressed, and is then distributed by a system of natural gas pipelines to the industrial and residential sites of use of the natural gas as a fuel. Since the natural gas in the distribution pipel ine is typically at a higher pressure than the pressure needed at the site of use, a pressure let down station is usually situated between the sites of use and the high pressure pipeline distribution system as a facility where the pressure of the natural gas can be reduced before the natural gas is delivered to where it will be used.

[004] The process of reducing the pressure of the natural gas at a pressure let down station provides an opportunity to recover useful energy without the combustion of the natural gas. It is desirable have an alternative to combustion, since complete combustion produces carbon dioxide a greenhouse gas and incomplete combustion can release methane, also a greenhouse gas, that is a major component of natural gas. From one perspective, the recovery of energy from the pressure differential between the natural gas in the distribution pipeline system and the natural gas downstream of the site of a pressure let down station can be regarded as the recovery of“waste heat,” energy that would otherwise be unavailable for use.

[005] Principle of operation. The energy contained in a gas at a certain pressure and temperature is called the enthalpy (h) and comprises the internal energy (u) plus the product of pressure (p) and volume (V). Thus h = u + pV (1)

[006] Pressure, volume and temperature (T) are related by the ideal gas laws that state, for example that pV ^::: TORT (2)

[007] Where m is the mass of gas in the system and R is the universal gas constant, and the definition of an expansion or compression process pVr = k (3)

[008] where g (gamma) is the index of compression (or expansion) and k is a constant value. These useful equati ons mean that if any two of the three conditions (pressure, volume and temperature) are known then the third can be calculated at that condition and that if one of them changes in accordance with the third equation, as is the case (approximately) in an expander, then the other two can be recalculated for that new condition.

[009] Enthalpy is a useful concept because the form of the energy is not specified, so heat energy, potential energy and work energy are all subject to the same rules and can be treated the same way. For a consistent set of calculations, the enthalpy is given relative to a datum point so care must be taken in comparing different calculations done at different times by different people to ensure that they used the same datum. It is usual to consider the enthalpy per mass of the gas, sometimes called the specific enthalpy, which is measured in BTU per pound, or in the metric system, in kJ per kg. [0010] When the pressure of a gas is reduced, its volume per pound and temperature are altered, and its specific enthalpy changes unless the gas undergoes adiabatic expansion. In adiabatic expansion the gas volume increases and the temperature drops. The reduction of temperature during pressure reduction by a regulating valve at the pressure let down station is an example of adiabatic expansion and is called the Joule-Thompson effect (named after two pioneers of thermodynamics, James Joule and Lord Kelvin, bom William Thompson).

However, the lack of a specifi c enthalpy change would result in no useful work output.

[0011] In a standard pressure let down station, the Joule-Thompson effect causes the outlet gas to cool, typically by about 5 °F per 100 psi pressure drop. For example, if the pressure of natural gas is reduced from 930 psig to 120 psig, a 810 psi (55.8 Bar) pressure drop, the gas might drop from an inlet temperature of 60 °F (15.6 °C) to about 9.4 °F (-12.6 °C). Natural gas at a temperature of 9.4 °F (-12.6 °C) is too cold for onward transmission, so pressure let down stations typically incorporate some form of heating, often just taking a small portion of the natural gas and burning it to heat a water bath which is used to wami up the gas flow either before or after expansion.

[0012] What is needed is a single solution for two problems, the solution that recovers the energy available due to the pressure differential between the inlet and the outlet of the pressure let down station, and without causing a reduction in temperature that would make the natural gas too cold for onward transmission to the site of its use.

SUMMARY OF THE INVENTION

[0013] A system is disclosed that provides at least two turboexpanders operatively linked to a generator that generates electrical power from the reduction of the pressure of a natural gas stream wherein the system reduces the pressure of tire natural gas stream at least two pressure reduction stages, and wherein heat is added to the natural gas stream by the system to adjust the temperature before each pressure reduction stage. In some implementations, the generator is a permanent magnet generator.

[0014] In certain implementations, an apparatus is disclosed that comprises a first stage turboexpander having a common shaft, an inlet configured to recei ve a flow of a process gas, wherein the process gas flow is characterized by a flow rate, a pressure and a temperature, and an outlet; a second stage turboexpander mounted with the first stage turboexpander on the common shaft, having an inlet configured to receive the flow of the process gas discharged from tire o utlet of the first stage turboexpander and an outlet; a generator mounted with the first stage turboexpander and the second stage turboexpander on the common shaft; and a pressurized housing that encloses the first stage turboexpander, the second stage turboexpander, the generator and the common shaft. The generator is configured to produce electricity when the common shaft rotates as a result of the process gas flowing from the inlet of the first stage turboexpander to the outlet of the second stage turboexpander. In certain implementations, the generator is a permanent magnet generator.

[0015] In certain implementations, common shafts can be provided with at least one bearing. In some implementations tire at least one bearing is an oil-free bearing. In certain

implementations the at least one bearing is a gas bearing operated by a regulated flow of filtered process gas. In other implementations the at least one bearing is a magnetic bearing, and in some implementations an active magnetic bearing. In some implementations the common shaft is provided with at least two journal bearings. In further implementations tire common shaft is provided with at least one thrust bearing. Magnetic bearings can be provided with gap sensor electronics and power amplifiers that supply current to electromagnets within the magnetic bearings.

[0016] In certain implementations, the process gas is heated by a first heat exchanger before it is received by the inlet of the first stage turboexpander. In certain implementations, the process gas is heated by a second heat exchanger before it is received by the inlet of the second stage turboexpander. In certain implementations, the process gas is heated by a heat exchanger after it leaves the outlet of the second stage turboexpander. In certain

implementations the process gas is heated by a first or second heat exchanger before it is received by the inlet of the second stage turboexpander. In certain implementations the process gas is heated by a first, second or third heat exchanger after it leaves the outlet of the second stage turboexpander.

[0017] In certain implementations, in use, the ratio of the pressure of the process gas flow at the fi rst stage turboexpander inlet to the pressure of the process gas flow at the outlet of the second stage turboexpander is about 1 .2 to about 3.9. In certain implementations, in use, the ratio of the pressure of the process gas flow at the inlet of tire first stage turboexpander to the pressure of the process gas flow at the outlet of the second stage turboexpander is about 1.2 to about 1.8. In certain implementations, in use, the ratio of the pressure of the process gas flow at the first stage turboexpander inlet to the pressure of the process gas flow at the outlet of the second stage turboexpander is about 1.8 to about 2.8. In certain implementations, in use, the ratio of the pressure of the process gas flow at the inlet of the first stage turboexpander to the pressure of the process gas flow at the outlet of the second stage turboexpander is about 2 8 to about 3.9. In certain implementations, the ratio of the pressure of the process gas flow at the inlet of the first stage turboexpander to the pressure of the process gas flow at the outlet of the first stage turboexpander is about 1.1 to about 1.6. In certain implementations, in use, the ratio of the pressure of the process gas flow at the inlet of the second stage turboexpander to the pressure of the process gas flow at the outlet of the second stage turboexpander is about 1.1 to about 1.6.

[0018] In certain implementations, the press ure of the process gas at the inlet of the first stage turboexpander is about 100 psig (6.9 Bar) to about 800 psig (55.2 Bar). In certain implementations, the pressure of the process gas at the outlet of the second stage

turboexpander is about 40 psig (2.8 Bar) to about 450 psig (31.0 Bar). In certain

implementations, the pressure of the process gas at the inlet of the first stage turboexpander is about 120 psig (8.3 Bar) to about 180 psig (12.4 Bar) and the pressure of the process gas at the outlet of the second stage turboexpander is about 40 psig (2 8 Bar) to about 80 psig (5.5 Bar). In certain implementations, the pressure of the process gas at the inlet of the first stage turboexpander is about 300 psig (20.7 Bar) to about 350 psig (24.1 Bar) and the pressure of the process gas at the outlet of the second stage turboexpander is about 80 psig (5 5 Bar) to about 180 psig (12.4 Bar). In certain implementations, the pressure of the process gas at the inlet of the first stage turboexpander is about 700 psig (48.3 Bar) to about 800 psig (55.2 Bar) and the pressure of the process gas at the outlet of the second stage turboexpander is about 200 psig (13.8 Bar) to about 450 psig (31.0 Bar).

[0019] In certain implementations the power generated by the apparatus is about 50kW to about 5Q0kW. In certain implementations the power generated by the apparatus is about 50kW to about lOOkW. In certain implementations the power generated by the apparatus is about lOOkW to about 200kW. In certain implementations the power generated by the apparatus is about 200kW to about 300kW. In certain implementations the power generated by the apparatus is about 300kW to about 500kW.

[0020] In certain implementations in which the apparatus is configured to operate in a high pressure range with a pressure ratio of about 3.5-3.6 and to generate 250kW of electrical output power, the flow' rate of the process gas at the inlet of the first stage turboexpander is typically about 2.0 kg/sec (6,018 scfin, 264 lb/min) to about 2.5 kg/sec (7,523 sefm, 330 Ib/min) In certain implementations in which the apparatus is configured to operate m a high pressure range with a pressure ratio of about 2.2-2.3 and to generate 25GkW of electrical output power, the flow rate of the process gas at the inlet of the first stage turboexpander is typically about 3.1 kg/sec (9,328 scfin, 409 lb/min) to about 3.8 kg/sec ( 11,434 scfin, 502 lb/min). In certain implementations in which the apparatus is configured to operate in a high pressure range with a pressure ratio of about 1.5-1.7 and to generate 250kW of electrical output power, the flow_' rate of the process gas at the inlet of the first stage turboexpander is typically about 4.9 kg/sec (14,744 scfin, 647 lb/min) to about 6.0 kg/sec (18,054 scfin, 792 Ib/min). In certain implementations with a generating capacity of 250kW of electrical output power, the apparatus is configured to operate with a flow- rate of the process gas at the inlet of the first stage turboexpander of about 4.5 kg/sec (13,541 scfin, 594 lb/min) to about 6.5 kg/sec ( 19,539 scfin, 858 lb/min). In certain implementations with a generating capacity of 250kW of electrical output power, the apparatus is configured to operate with a flow' rate of the process gas at the inlet of the first stage turboexpander of about 5 kg/sec (15,045 scfin,

660 lb/min) to about 6 kg/sec (18,054 scfin, 792 lb/min). It is evident that the mass flow rates quoted are proportionate to the generating capacity and the examples cited can be configured to suit other generating capacities within the scope of the in vention. [0021] In certain implementations, a system is disclosed that comprises a system inlet configured to receive a flow of a process gas, wherein the process gas flow is characterized by a flow rate, a pressure and a temperature; a first heat exchanger having a process gas inlet configured to receive the flow of the process gas from the system inlet a process gas outlet, a secondary fluid inlet and a secondary' fluid outlet, wherein the secondary fluid is

characterized by a flow' rate, a pressure and a temperature; a first stage turboexpander having a common shaft, an inlet configured to receive the flow of the process gas from the first heat exchanger process gas outlet and an outlet; a second heat exchanger having a process gas inlet configured to receive the flow of the process gas from the first stage turboexpander outlet, a process gas outlet, a secondary fluid inlet and a secondary fluid outlet; a second stage turboexpander mounted with the first stage turboexpander on the common shaft, having an inlet configured to receive the flow of the process gas from the process gas outlet of the second heat exchanger and an outlet; a generator mounted with the first stage turboexpander and the second stage turboexpander on the common shaft; a pressurized housing that encloses the first stage turboexpander, the second stage turboexpander, the generator and the common shaft; and a system controller. Typically, the system is mounted in a frame configured for commercial transportation.

[0022] In certain implementations, tire system controller further comprises at least one sensor sel ected from the group consisting of a sensor that is configured to detect the flow rate of the process gas, a sensor that is configured to detect the pressure of the process gas, a sensor that is configured to detect the temperature of the process gas, a sensor that is configured to detect the flow rate of tire secondary fluid, a sensor that is configured to detect the pressure of the secondary fluid, and a sensor that is confi gured to detect the temperature of the secondary fluid. In certain implementations, the system controller further comprises at least one actuator selected from the group consisting of a hydraulic actuator, an electric motor, a pneumatic actuator and an electrical relay.

[0023] In certain implementations, the system controller further comprises control electronics including a programmable logic controller. In certain implementations, wherein the system controller further comprises a computer comprising a microprocessor, a visual display, nonvolatile memory, RAM memory, and at least one user input device selected from a touch screen, a keypad, a keyboard, a mouse, a touch pad, track pad and a track ball. In certain implementations, the computer is connected to a local network by Ethernet or a wireless connection, and to the Internet.

[0024] In certain implementations, in use, the ratio of the pressure of the process gas flow at the system inlet to the pressure of tire process gas flow at the outlet of the second stage turboexpander is about 1 .2 to about 3.9. In certain implementations, in use, the ratio of the pressure of the process gas flow at the system inlet to the pressure of the process gas flow at the outlet of the second stage turboexpander is about 1.2 to about 1.8. In certain

implementations, in use, the ratio of the pressure of the process gas flow at the system inlet to the pressure of the process gas flow at the outlet of the second stage turboexpander is about 1.8 to about 2.8. In certain implementations, in use, the ratio of the pressure of the process gas flow at the system inlet to the pressure of the process gas flow at tire outlet of the second stage turboexpander is about 2.8 to about 3.9.

[0025] In certain implementations, the pressure of the process gas at the system inlet is about 120 psig (8.3 Bar) to about 750 psig (51 7 Bar). In certain implementations, the pressure of the process gas at the outlet of the second stage turboexpander is about 80 psig (5.5 Bar) to about 450 psig (31.0 Bar).

[0026 ] In certain implementations with a generating capacity of 250kW of electrical output power, the system is configured to operate with a flow rate of the process gas at the system inlet of about 4 kg/sec (12,039 sefm, 528 Ib/min) to about 7 kg/sec (21,063 scfm, 924 Ib/min) In certain implementations with a generating capacity of 250kW of electrical output power, the system is configured to operate with a flow rate of the process gas at the system inlet of about 4.5 kg/sec (13,541 scfm, 594 Ib/min) to about 6.5 kg/sec (19,449 scf , 858 Ib/min). In certain implementations with a generating capaci ty of 250kW of electrical output pow⁷er, the system is configured to operate with a flow rate of the process gas at the system inlet of about 5 kg/sec (15,045 scfm, 660 Ib/min) to about 6 kg/sec (18,054 scfm, 792 Ib/min).

[0027] In certain implementations, the ratio of the inlet gas pressure to the inlet gas pressure of the system (outlet pressure/inlet pressure) is less than 2 and the number of pressure reduction stages is at least two. In certain implementations, the pressure ratio of the system is less than 1.9. In certain implementations, the pressure ratio of the system is less than about 1.7. In certain implementations, the pressure ratio of a pressure reduction stage is less than about 1.7. In certain implementations, the pressure ratio of a pressure reduction stage is less than about 1.3. The ability of the system to generate electricity with a system pressure reduction of less than about 2 using at least two pressure reduction stages reduces the amount of heat that must be applied to the natural gas stream before each pressure reduction stage.

[0028] In certain implementations, the system accepts a nominal inlet pressure of about 750 psig (51.7 Bar), being able to tolerate inlet pressures of about 900 ps!g (62 Bar) to about 600 psig (41.4 Bar) and an outlet pressure of about 450 psig (31 Bar), having a system pressure ratio of 1.67. In certain implementations, the system accepts a nominal inlet pressure of about 350 psig (24.1 Bar) and an outlet pressure of about 80 (5.5 Bar) psig, having a system pressure ratio of 4.38. In certain implementations, the system accepts a nominal inlet pressure of about 300 psig (20.6 Bar) and an outlet pressure of about 180 (12.4 Bar) psig, having a system pressure ratio of 1.67.

[0029] In some implementations, tire system includes two pressure reduction stages provided by two turboexpanders, each of which is operati vely connected to a generator. In certain implementations, a turboexpander and the generator are mounted on the same shaft assembly. In some implementations, two turboexpanders and a generator are mounted on the same shaft assembly. In further implementations the generator is a permanent magnet generator.

[0030] In some implementations, the present disclosure provides systems for power generation, the systems comprising a first heat exchanger, a first turboexpander, one or more second heat exchangers, one or more second turboexpanders, one or more third heat exchangers, one or more third turboexpanders, and at least one electrical generator operatively coupled to one or more of the first turboexpander, the one or more second turbo expanders, and the one or more third turboexpanders.

[0031] In certain implementations, the present disclosure provides methods for generating power, the methods comprising receiving a first flow of a process gas, heating the first flow of process gas with a first heat exchanger to generate a second flow of the process gas, expanding the second flow with a first turboexpander to generate a third flow of the process gas, heating the third flow of the process gas wi th one or more second heat exchangers, each second heat exchanger generating a fourth flow of the process gas, expanding the one or more fourth flows of tire process gas with one or more second turboexpanders, each second turboexpander generati ng a fifth flow of the process gas, and produ ci ng electrical energy with at least one electrical generator operatively coupled to one or more of the first turboexpander and the one or more second turboexpanders. In some implementations the methods can further comprise heating the one or more fifth flows with one or more third heat exchangers, each third heat exchanger generating a sixth flow of the process gas, expanding the one or more sixth flows with one or more third turboexpanders, each third turboexpander generating a seventh flow of the process gas, and wherein the at least one electrical generator is operatively coupled to one or more of the first turboexpander, the one or m ore second turboexpanders, and the one or more third turboexpanders. In certain implementations, the methods can further comprise providing each of the first, second, and third heat exchangers with a supply flow of a heat-transfer fluid. In some implementations, the heat-transfer fluid can be provided at a temperature of less than about 25Q°F, less than about 200°F, less than about 15f)°F, less than about 130°F, less than about 110°F, or less than about 90°F.

[0032] The above described and other features are exemplified by the following figures and detailed description.

BRIEF DESCRIPTION OF THE DRAWINGS

[0033] The foregoing and other features and advantages will be apparent from the following more particular description of exemplary implementations of the disclosure, as illustrated in the accompanying drawings, in which like reference characters refer to tire same parts throughout the different view's. The drawings are not necessarily to scale, emphasis instead being placed upon illustrating the principles of the disclosure

[0034] FIG. 1A is a schematic diagram of an implementation of the disclosed system 10, showing the path of a process gas from a process gas inlet 50 passing through a first heat exchanger 410, a first stage turboexpander 110, a second heat exchanger 420, a second stage turboexpander 210, to a process gas outlet 60, where the first stage turboexpander 110 and the second stage turboexpander 210 are operatively coupled to a generator 310 by a shaft assembly 340, wherein, in use, the flow' of tire process gas through the system 10 from the process gas inlet 50 to the process gas outlet 60 produces an electrical output 80.

[0035] FIG. IB is a block diagram of an implementation of a system controller 500, showing the system controller 500 operatively connected to a first stage turboexpander 1 10, a second stage turboexpander 210, a generator 310, a DC / AC converter 380, a first heat exchanger 410, a second heat exchanger 420, a valve system 600 and a sensor system 700.

[0036] FIG. 2 is a schematic section view of an implementation of a disclosed turboexpander and generator unit 100 wherein a first stage turboexpander 110 and a second stage turboexpander 210 are operatively coupled to a generator 310 by a common shaft assembly 340.

[0037] FIG. 3 A is a top view of an implementation of a disclosed turboexpander and generator unit 100 including a first stage turboexpander 110, a second stage turboexpander 210, a generator 310, a first stage turboexpander inlet 1G1C, a first stage turboexpander outlet 101D, a second stage turboexpander inlet 101B, a second stage turboexpander outlet 101A, and a gas bearings inlet 10 IF.

[0038] FIG. 3B is a side view of an implementation of a disclosed turboexpander and generator unit 100 showing a first stage turboexpander outlet 10 ID, a terminal box 370, a terminal box cover 372, a second stage turboexpander outlet 101A, and a gas bearings inlet 101 F .

[0039] FIG. 3C is a perspective view' of an implementation of a disclosed turboexpander and generator unit 100 showing a first stage turboexpander outlet 10 ID, a first stage

turboexpander housing 120, a terminal box 370, a terminal box cover 372, a gas bearings inlet 10 IF, and a second stage turboexpander housing 220.

[0040 ] FIG. 3D is perspective view of an implementation of a disclosed turboexpander and generator unit 100 including a second stage turboexpander outlet 101 A, a second stage turboexpander housing 220, a second stage turboexpander inlet 101B, a terminal box 370, a terminal box cover 372, a gas bearings outlet 101E, a first stage turboexpander inlet 101C, and a first stage turboexpander housing 120.

[0041] FIG. 4 is a schematic diagram of an implementation of the present disclosure, showing an exemplary system 1000.

[0042] FIG. 5 is a schematic diagram of an implementation of the present disclosure, showing an exemplary sy stem 1001. DETAILED DESCRIPTION

[0043] As used herein, a“turboexpander” is a radial or axial flow turbine through which a relatively high pressure gas is expanded to produce work.

[0044] As used herein,“working fluid,”“process gas,” or“pipeline natural gas” refers to natural gas that has been processed and transported in a natural gas distribution pipeline system and which is available for use by the disclosed system and apparatus. Typically, certain components of the gas that is obtained from the wellhead are removed before the natural gas is introduced into a pipeline system. Examples of the typical chemical composition of pipeline natural gas are provided in Table l, below.

[0045 ] As used herein,“secondary fluid,” or“heat-transfer fluid” refers to a fluid that is used to heat or cool the process gas or the control electronics. In certain implementations, the secondary fluid is supplied to a heat exchanger to heat the process gas. In certain

implementations, the secondary' fluid is water or an aqueous solution. In certain

implementations, the secondary fluid can be an aqueous solution of an antifreeze additive, such as propylene glycol, ethylene glycol, glycerol, or combinations thereof. In some implementations, a heat-transfer fluid can be provided for use in heat exchangers as part of a heating circuit and can be any fluid suitable for transferring heat to a process gas, including but not limited to oils and aqueous solutions. In certain implementations, the heat-transfer fluid can he a dielectric fluid, including but not limited to one or more perfluorinated carbons, including but not limited to FLUORINERT™ (3M Company, St. Paul, MN), synthetic hydrocarbons, including but not limited to poiyaiphaolefms (PAQ), or combinations thereof. In some implementations, two distinct heat-transfer fluid circuits are provided, with a first heat-transfer fluid circuit provided for cooling the control electronics and a second heat- transfer fluid circuit provided for heating the process gas. In some implementations, heat that is remo ved from the control electronics can be used in the heating of the process gas by transferring heat between the first and second heat-transfer circuits.

[0046] An apparatus is disclosed comprising a process gas system inlet, a process gas system outlet, at least two turboexpanders (a centrifugal or axial flow turbine through which a high pressure process gas is expanded to produce work), and at least one electrical generator operatively coupled to the at least two turboexpanders wherein electrical energy is produced by using the pressure difference between the process gas system inlet and the process gas system outlet. In certain implementations the process gas is natural gas in a natural gas distribution pipeline system. In some implementations, an implementation of the disclosed system is placed at a site between a high pressure location in a natural gas distribution pipeline and a lower pressure location, such as a pressure let down station (also termed a ‘^‘city gate” station), in order to recover energy from the reduction in pressure required to provide the natural gas at a pressure suitable for consumers.

[0047] In some implementations of the present disclosure, the apparatus comprises a first stage turboexpander operatively coupled to the electrical generator, wherein the first stage turboexpander has a first process gas inlet and a first process gas outlet, an electrical generator operatively coupled to the first stage turboexpander, a second stage turboexpander operatively coupled to the electrical generator, wherein the second stage turboexpander has a second process gas inlet, and a second process gas outlet and control circuitry. Typically, the system includes a first heat exchanger effective to adjust the temperature of the process gas supplied to the first process gas inlet. Typically, the associated system includes a second heat exchanger effective to adjust the temperature of the process gas supplied to the second process gas inlet.

[0048] in some implementations of the present disclosure, the operative coupling between the first stage turboexpander and the electrical generator is a mechanical coupling. In certain implementations, the operative coupling between the second stage turboexpander and the electrical generator is a mechanical coupling. In certain implementations, the first stage turboexpander and the magnets of the electrical generator are mounted on a common shaft. In certain implementations, the first stage turboexpander, the magnets of the electrical generator and the second stage turboexpander are mounted on a common shaft.

[0049] In certain implementations of the disclosed system, the first heat exchanger is controlled to keep the temperature of the process gas at the first process gas inlet and the temperature of the process gas at the first process gas outlet within a predetermined range. In certain implementations, the first heat exchanger is controlled to keep the temperature difference of the process gas at the first process gas inlet compared to the first process gas outlet within a predetermined range. In certain implementations of the disclosed system, the second heat exchanger is controlled to keep the temperature of the process gas at the second process gas inlet and the temperature of the process gas at the second process gas outlet whlun a predetermined range. In certain implementations of the disclosed system, the second heat exchanger is controlled to keep the temperature difference of the process gas at the second process gas inlet compared to the second process gas outlet within a predetermined range

[0050] In certain implementations of the disclosed system, the process gas from the upstream natural gas supply network is passed through a first heat exchanger which transfers heat from a secondary fluid to the process gas and raises the temperature of the process gas to a suitable temperature for the process gas inlet of the first stage turboexpander, for example, typically 130-150 °F (54.4-65.6 °C) in certain implementations. The process gas passes through the first stage of expansion, dropping the pressure to an intermediate level as some of the enthalpy is used to produce electricity, thereby cooling die process gas. This cooled process gas then passes through a second heat exchanger, which raises die gas temperature, for example, back to 130-150 °F (54.4-65.6 °C). The second stage of expansion in the second stage turboexpander brings the temperature of the process gas back down to a temperature configured to further distribution, extracting enthalpy and lowering the pressure to the corresponding value. The low pressure warm gas from the second stage turboexpander outlet, in certain implementations at a temperature of at least 50 °F (10 °C), is fed into the downstream distribution network.

[0051] In certain implementations, the secondary fluid is an aqueous solution. In certain implementations, the secondary fluid comprises propylene glycol. In some implementations, the secondary fluid is a 30% aqueous solution of propylene glycol. In certain

implementations, the secondary fluid is heated by a suitable source of heat, such as a supply of warm water, waste heat generated by an electrical circuit, waste heat generated by a gas engine or a gas re-heater.

[0052 ] In some implementations, the source of heat for the secondary fluid or heat-transfer fluid is a low-grade waste heat source that provides a heat source with temperature less than about 450°F. In further implementations, the source of heat can be an ultra-low-grade waste heat source that provides a heat source with temperature less than about 250°F. In yet further implementations, the source of heat can be a very-low-grade waste heat source that provides a heat source with temperature less than about 200°F, less than about I90°F, less than about l80°F, less than about 170°F, less than about 160°F, less than about 150°F, less than about 140°F, less than about 130°F, less than about 1 l0°F, less than about 100°F, or less than about 90°F. [0053] Variations in process gas pressure at the system inlet are handled automatically by a control system which varies the turbine speed to match the process gas flow requirements and maximizes the recovered energy. If the demand for natural gas downstream of the disclosed system is higher than the flow rate provided by the disclosed system, then a bypass valve is opened to direct additional process gas to the downstream network. If the pressure differential across the pressure let down station is too high, leading to an electrical overload condition in the disclosed system, then the inlet regulator valve of the disclosed system will adjust the gas flow to maintain the optimal operating pressure differential across the disclosed system. This combination of inlet regulation, bypass and active control of die heat input permits the disclosed system to adapt automatically to enable the unit to operate over a wide range of inlet and outlet conditions.

[0054] FIG. 1A is a schematic diagram of an implementation of the disclosed system 10, showing the path of a process gas from a process gas inlet 50 passing through a first heat exchanger 410, a first stage turboexpander 110, a second heat exchanger 420; a second stage turboexpander 210, to a process gas outlet 60, where the first stage turboexpander 110 and the second stage turboexpande r 210 are operatively coupled to a gene rator 310 by a shaft assembly 340, wherein, in use, the flow of the process gas through the system 10 from the process gas inlet 50 to the process gas outlet 60 produces an electrical output 80.

[0055 ] In certain implementations, the turbine blades and nozzles of the disclosed turboexpanders are designed taking into consideration the typical chemical composition of pipeline natural gas. The chemical compositions of two reported analyses of pipeline natural gas with a range are presented in Table 1, below. Methane is the major component of pipeline natural gas, which also contains amounts of ethane, propane, butanes, hexane, nitrogen and carbon dioxide. In certain implementations, the turbine blades and nozzles of the disclosed turboexpanders are designed employed models using the compositions listed as“Nominal” or “Model” as the composition of pipeline natural gas. In certain implementations in which a first stage turboexpander, a second stage turboexpander and a generator a mounted on a common shaft assembly, the turbine blades and nozzles of the disclosed turboexpanders are designed to accommodate efficient function when the first stage turboexpander and the second stage turboexpander are mounted on a common shaft assembly.

[0056] FIG. IB is a block diagram of an implementation of a system controller 500, showing the system controller 500 operatively connected via actuators and sensors to a first stage turboexpander 110, a second stage turboexpander 210, a generator 310, a DC / AC voltage converter 380, a first heat exchanger 410, a second heat exchanger 420, a valve system 600 and a sensor system 700 Typically the sensor system 700 includes measurement of the rpm of the common shaft of the turboexpander and generator apparatus, temperature sensors, pressure sensors and flow meters. Typically, actuators include pneumatic actuators for air pressure controlled valves and electrical relays.

[0057] Referring to FIG. 1A, the process gas enters the process gas inlet 401C of the first heat exchanger 410 acting as a preheater to warm the process gas using heat provided by a secondary fluid flowing from the secondary fluid inlet 202B to the secondary fluid outlet 202A of the first heat exchanger 410. A suitable secondary fluid is an aqueous solution. In certain implementations, the secondary' fluid comprises propylene glycol. In some implementations, the secondary fluid is a 30% aqueous solution of propylene glycol

[0058] The process gas flows from the process gas outlet 40 ID of the first heat exchanger 410 to the process gas inlet 101 C of the first stage turboexpander 1 10 The flow rate and pressure of the process gas are controlled in the disclosed system by valves and regulators in the system upstream of the process gas inlet 401C by structures and methods known to one of skill in the art. The temperature, flow rate and pressure of the process gas are further adjusted by the first heat exchanger 410.

[0059] As shown in FIG. 1A, the process gas leaves the first stage turboexpander 110 though the process gas outlet 10 ID and flows to the process gas inlet 402B of the second heat exchanger 420 that act as an interheater to warm the process gas between the first stage turboexpander 110 and the second stage turboexpander 210 in order to adjust the temperature, flow rate and pressure of the process gas. The process gas entering the process gas inlet 402B of the second heat exchanger 420 is warmed by heat provided by a secondary fluid flowing front the secondary fluid inlet 202D to the secondary fluid outlet 202C of the second heat exchanger 420. A suitable secondary' fluid is an aqueous solution. In certain

implementations, the secondary fluid comprises propylene glycol . In some implementations, the secondary' fluid is a 30% aqueous solution of propylene glycol.

[0060] The process gas flow's from the process gas outlet 402A of the second heat exchanger 420 to the process gas inlet 101 B of the second stage turboexpander 210. Upon exiting the process gas outlet 101A of the second stage turboexpander 210, the process gas flow's to the system process gas outlet 30.

[0061 ] FIG. 2 is a schematic section view of an implementation of a disclosed turboexpander and generator unit 100 w'herein a first stage turboexpander 110 and a second stage turboexpander 210 are operatively coupled to a generator 310 by a common shaft assembly 340. The turboexpander and generator unit 100 is enclosed by a pressurized housing comprising the first stage turboexpander housing 120, the generator housing 320 and the second stage turboexpander housing 220 In some implementations, the disclosed

turboexpander and generator system is sealed within a hermetic pressure casing and is configured to withstand system inlet pressures up to 975 psig (67.2 Bar), enabling it to be used in the main backbone of a natural gas distribution network. In an implementation, a high pressure turboexpander and generator system is disclosed that is configured to provide a system outlet pressure about of 450 psig (31 Bar), and is configured to accept a system inlet pressure that is nominally about 750 psig (51.7 Bar), but varying between about 600 psig (41.4 Bar) and about 900 psig (62.1 Bar). In other implementations, the disclosed

turboexpander and generator system can be configured to accept lower system input pressures. In some implementations, the disclosed turboexpander and generator system is configured to provide a high ratio between the system inlet pressure and the system outlet pressure, typically a system inlet pressure of about 350 psig (24.1 Bar) and a system outlet pressure of about 80 psig (5 5 Bar). In other implementations, the disclosed turboexpander and generator system is configured to a lower ratio between the system inlet pressure and the system outlet pressure, typically a system inlet pressure of about 300 psig (20.7 Bar) and a system outlet pressure of about 180 psig (12.4 Bar).

[0062] In tire first stage turboexpander 110, process gas that has been pre-heated by the first heat exchanger, or preheater, 410 (FIG. 1A) flows into the first stage turboexpander inlet 101C, which is defined by the generator housing 320, past the first stage turbine 124 and flows out through the first stage turboexpander outlet 10 ID, which is defined by the first stage turboexpander housing 120, to the second heat exchanger, or terheater, 420 (FIG.

1A). The first stage turbine 124 is connected by the first stage turbine shaft 140 to the shaft assembly 340. In certain implementations, the first stage journal bearing 130 is a gas bearing. In certain implementations, the first stage journal bearing 130 is supplied with a regulated flow of filtered process gas. In alternative implementations, first stage journal bearing 130 is a magnetic bearing. In certain implementations the magnetic bearing can be an active magnetic bearing. The use of gas bearings or magnetic bearings provide the advantage of avoiding lubricant contamination of the process gas that is delivered to the consumer.

[0063] In the second stage turboexpander 210, process gas that has been reheated by the second heat exchanger, or interheater, 420 (FIG. 1A) flows into the second stage

turboexpander inlet 101B, which is defined by the second stage turboexpander housing 220, past the second stage turbine 224 and flows out through the second stage turboexpander outlet 101A, which is defined by the second stage turboexpander housing 220. The second stage turbine 224 is connected by the second stage turbine shaft 240 to the shaft assembly 340. In certain implementations, the second stage journal bearing 230 and the thrust bearing 330 are gas bearings. In certain implementations, the second stage journal bearing 230 and the thrust bearing 330 are supplied with a regulated flow of filtered process gas. In alternative implementations, second stage journal bearing 230 and the thrust bearing 330 can be magnetic bearings. In certain implementations the magnetic bearings can be active magnetic bearings. In further implementations, the first stage journal bearing 130 and the second stage journal bearing 230 can be magnetic bearings, and the thrust bearing 330 can be omitted because axial stabilization is provided by the magnetic journal bearings 130/230. [0064] The generator 310 is coupled to the first stage turbine shaft 140 and the second stage turbine shaft 240 by the shaft assembly 340. In use, the rotation of the shaft assembly 340 and the interaction of the permanent magnets 350 and the stator 324 produces an electrical current that flows through the power feed-through 360 that is makes electrical connections within the terminal box 370 (FIG. 3A - FIG. 3D).

[0065] FIG. 3A is a top view of an implementation of a disclosed turboexpander and generator unit 100 including a first stage turboexpander 110, a second stage turboexpander 210, a generator 310, a first stage turboexpander inlet 101C, a first stage turboexpander outlet !OID, a second stage turboexpander inlet !OIB, a second stage turboexpander outlet 101.4, and a gas bearings inlet 101F. In alternative implementations that include magnetic journal bearings 130/230 instead of gas bearings, the gas bearings inlet 101F can be omitted. In some implementations, an electrical connection to active magnetic bearings 130/230 can be provided.

[0066] FIG. 3B is a side view of an implementati on of a disclosed turboexpander and generator unit 100 showing a first stage turboexpander outlet 10 ID, a terminal box 370, a terminal box cover 372, a second stage turboexpander outlet 101A, and a gas bearings gas inlet 101 F . In alternative implementations that include magnetic journal bearings 130/230 instead of gas bearings, the gas bearings inlet 1 OIF can be omitted.

[0067] FIG. 3C is a perspective view of an implementation of a disclosed turboexpander and generator unit 100 showing a first stage turboexpander outlet 10 ID, a first stage

turboexpander housing 120, a terminal box 370, a terminal box cover 372, a gas bearings inlet gas 101F, and a second stage turboexpander housing 220. In alternative implementations that include magnetic journal bearings 130/230 instead of gas bearings, the gas bearings inlet 101 F can be omitted.

[0068] FIG. 3D is perspective view of an implementation of a disclosed turboexpander and generator unit 100 including a second stage turboexpander outlet 10 LA, a second stage turboexpander housing 220, a second stage turboexpander inlet 101B, a terminal box 370, a terminal box cover 372, a gas bearings gas outlet 10 IE, a first stage turboexpander inlet 101C, and a first stage turboexpander housing 120. In alternative implementations that include magnetic journal bearings 130/230 instead of gas hearings, the gas bearings outlet 101E can be omited. [0069] FIG. 4 is a schematic diagram of an implementation of the present disclosure, showing an exemplary system 1000. System 1000 can he used for power generation and includes three stages of pre -heating and turboexpansion. A first heat exchanger (1100A) can clude a first process-gas-heating inlet (1 102A), a first process-gas-heating outlet (1 104A), a first heat-transfer-fluid inlet (1106A), and a first heat-transfer-fluid outlet (1108A). A first turboexpander ( 1110A) can include a first process-gas inlet (1112A) configured to receive a fi rst process gas fluid flow from the first process-gas-heating outlet, and a first process-gas outlet (1114A). A second heat exchanger (1100B) can be provided, including a second process-gas-heating inlet (1102B), a second process-gas-heating outlet (1 104B), a second heat-transfer-fluid inlet (1106B), and a second heat-transfer-fluid outlet (1108B). A second turboexpanders (11 10B) can be provided, including a second process-gas inlet (1 1 12B) configured to receive a second process gas fluid flow from the second process-gas-heating outlet, and a second process-gas outlet (I I 14B). One or more third heat exchangers (1100C) can be provided, with each including a third process-gas-heating inlet (1102C), a third process-gas-heating outlet (1104C), a third heat-transfer-fluid inlet (1 106C), and a third heat- transfer-fluid outlet (11Q8C). In some implementations, the process gas flow exiting the second turboexpander 1110B via the second process-gas outlet 1114B can be split into two or more flow streams that are directed into two or more third heat exchangers 1100C. Three flow streams are depicted in FIG. 4, but in other implementations the process gas flow exiting the second turboexpander 1110B may remain as a single stream into a single third heat exchanger and third turboexpander, or the process gas flow exiting the second turboexpander can be split into two flow streams for two third heat exchangers and two third

turboexpanders, or the process gas flow exiting the second turboexpander can be split into four or more flow streams for associated third heat exchangers and third turboexpanders. One or more third turboexpanders (1110C) can be provided, with each including a third process- gas mlet ( 1 1 12C) configured to receive a third process gas fluid flow from the third process- gas-heating outlet, and a third process-gas outlet (1114C). The system further includes at least one electrical generator (1200) operatively coupled to one or more of the first turboexpander, the one or more second turboexpanders, and the one or more third turboexpanders. The at least one electrical generator (1200) can be operatively coupled to one or more of the turboexpanders by being mounted with the one or more turboexpanders on a common shaft (not shown in FIG. 4 for clarity). [0070] FIG. 5 is a schematic diagram of an implementation of the present disclosure, showing an exemplary system 1001. System 1001 can he used for power generation and includes three stages of pre -heating and turboexpansion. System 1001 differs from system 1000 in that two or more second turboexpanders 1 110B are included in the system 1001 . A first heat exchanger (1100A) can include a first process-gas-heating inlet (1102 A), a first process-gas-heating outlet (1104A), a first heat-transfer-fluid inlet ( 1106A), and a first heat- transfer-fluid outlet (1108A). A first turboexpander (1 1 10A) can include a first process-gas inlet (1112A) configured to receive a first process gas fluid flow from the first process-gas- heating outlet, and a first process-gas outlet (11 14A). One or more second heat exchangers (1100B) can be provided, with each including a second process-gas-heating inlet (1102B), a second process-gas-heating outlet ( 1104B), a second heat-transfer-fluid inlet ( 1 106B), and a second heat-transfer-fluid outlet ( 1108B). In some implementations, the process gas flow exiting the first turboexpander ( 1110A) via the first process-gas outlet (1114A) can be split into two or more flow streams that are directed into two or more second heat exchangers 1100B. Three such process gas flow streams are depicted in FIG. 5, but in other

implementations the process gas flow' exiting the first turboexpander 1110A may remain as a single stream into a single second heat exchanger 1100B and second turboexpander 1110B (as shown in FIG. 4), or the process gas flow exiting the first turboexpander 11 IGA can be split into two flow streams for two second heat exchangers 110GB and two second turboexpanders 1110B, or the process gas flow' exiting tire first turboexpander 1110A can be split into four or more flow streams for associated second heat exchangers 1100B and second turboexpanders 1 1 10B. One or more second turboexpanders (1 1 10B) can be provided, with each including a second process-gas inlet (1 112B) configured to receive a second process gas fluid flow from the second process-gas-heating outlet, and a second process-gas outlet (1114B). In some implementations, the process gas flow exiting the second turboexpander 1 HOB via the second process-gas outlet 1 1 14B can be split into two or more flow streams that are directed into two or more third heat exchangers 1100C. Three flow' streams are depicted in FIGs. 4 and 5, but in other implementations the process gas flow exiting the second turboexpander 1 1 10B may remain as a single stream into a single third heat exchanger and third turboexpander, or the process gas flow exiting the second turboexpander can be split into two flow' streams for two third heat exchangers and two third turboexpanders, or the process gas flow exiting the second turboexpander can be split into four or more flow streams for associated third heat exchangers and third turboexpanders. One or more third heat exchangers (1100C) can be provided, with each including a third process-gas -heating inlet (1102C), a third process-gas-heating outlet (1104C), a third heat-transfer-fluid inlet (1106C), and a third heat-transfer-fluid outlet (1 108C). One or more third turboexpanders (11 10C) can be provided, with each including a third process-gas inlet (1 1 12C) configured to receive a third process gas fluid flow' from the third process-gas-heating outlet, and a third process-gas outlet (1114C). The system further includes at least one electrical generator (1200) operatively coupled to one or more of the first turboexpander, the one or m ore second turboexpanders, and the one or more third turboexpanders. The at least one electrical generator (1200) can be operatively coupled to one or more of the turboexpanders by being mounted with the one or more turboexpanders on a common shaft (not shown in FIG. 5 for clarity).

[0071] In the implementations shown schematically in FIGs. 4 and 5, the process gas from an upstream gas supply network is supplied to the first heat exchanger 1100 A at the first process-gas-heating inlet 1102A. The first heat exchanger 1 100A is supplied with a heat- transfer fluid, also referred to as a secondary fluid, which transfers heat to the process gas and raises the temperature of the process gas to a suitable temperature for the first process-gas inlet 11 12A of the first stage turboexpander 1 1 I 0A, for example, typically 130-150 °F (54 4- 65.6 °C) in certain implementations. The process gas passes through the first stage of expansion, dropping the pressure to an intermediate level as some of the enthalpy is used to produce electricity, thereby cooling the process gas. This cooled process gas then passes through the one or more second heat exchangers 1100B, which raise the process gas temperature, for example, back to 130-150 °F (54.4-65.6 °C). The second stage of expansion in the second stage turboexpanders 11 10B brings the temperature of the process gas back down to an intermediate level, extracting enthalpy and lowering the pressure to the corresponding value. This cooled process gas then passes through the one or more third heat exchangers 1100C, which raise the process gas temperature, for example, back to 130-150 °F (54.4-65.6 °C). The process gas passes through the third stage of expansion, dropping the pressure to a distribution level as some of the enthalpy is used to produce electricity, thereby cooling the process gas. The low pressure warm gas from the third stage turboexpander outlet, in certain implementations at a temperature of at least 50 °F (10 °C), is fed into the downstream distribution network. Tire three-stage systems shown in FIGs. 4 and 5 can advantageously provide for pressure reduction from pipeline transmission levels, which can be from about 200 psig (13.8 Bar) to about 1500 psig (103.4 Bar), down to neighborhood or house distribution levels less than about 200 psig (13.8 Bar), less than about 100 ps!g (6.9 Bar), less than about 80 psig (5.5 Bar), less than about 60 psig (4.1 Bar), less than about 40 psig (2 8 Bar), less than about 25 psig (1 7 Bar), or less than about 15 psig (1.0 Bar). In certain implementations, the process gas entering the first process-gas-heating inlet 1102 A can have a pressure of about 750 psig (51.7 Bar). The heat-transfer fluid can be provided at a temperature of less than about 250°F, less than about 200°F, less than about 150°F, less than about 130°F, less than about 110°F, or less than about 90°F

[0072] The present disclosure provides for methods of generating power. The methods can comprise (i) receiving a first flow of a process gas, wherein the first flow is characterized by a first flow rate, a first pressure, and a first temperature, (ii) heating the first flow with a first heat exchanger to generate a second flow of the process gas, wherein the second flow is characteri zed by a second flow rate, a second pressure, and a second temperature, (iii) expanding the second flow with a first turboexpander to generate a third flow of the process gas, wherein the third flow is characterized by a third flow⁷ rate, a third pressure, and a third temperature, (tv) heating the third flow with one or more second heat exchangers, each second heat exchanger generating a fourth flow of the process gas, wherein the fourth flow⁷ is characterized by a fourth flow rate, a fourth pressure, and a fourth temperature, (v) expanding the one or more fourth flow s with one or more second turboexpanders, each second turboexpander generating a fifth flow of the process gas, wherein the fi fth flow is characterized by a fifth flow rate, a fifth pressure, and a fifth temperature, (vi) heating the one or more fifth flow's with one or more third heat exchangers, each third heat exchanger generating a sixth flow of the process gas, wherein the sixth flow⁷ is characterized by a sixth flow rate, a sixth pressure, and a sixth temperature, (vii) expanding the one or more sixth flows with one or more third turboexpanders, each third turboexpander generating a seventh flow⁷ of the process gas, wherein the seventh flow is characterized by a seventh flow rate, a seventh pressure, and a seventh temperature, and (viii) producing electrical energy with at least one electrical generator operatively coupled to one or more of the first turboexpander, the one or more second turboexpanders, and the one or more third turboexpanders. In certain implementations, the methods can further comprise providing each of the first, second, and third heat exchangers with a supply flow of a heat-transfer fluid in some implementations, the heat-transfer fluid can be provided at a temperature of less than about 250°F, less than about 200°F, less than about 150°F, less than about 130°F, less than about 1 l0°F, or less than about 90°F. In some implementations the at least one electrical generator is operati vely coupled to one or more of the first turboexpander, the one or more second turboexpanders, and the one or more third turboexpanders via a common shaft. In some implementations two or more electrical generators are operatively coupled to one or more of the first

turboexpander, the one or more second turboexpanders, and the one or more third turboexpanders via two or more common shafts. A torque can be imparted on each common shaft by the expanding gas in the one or more turboexpanders and the torque can be converted to electricity by the electrical generator. The electrical power output from the turboexpander and the electrical generator can pass to an inverter where it is first rectified to DC dien converted to AC at a voltage and frequency to be consistent with the characteristics of the local electricity grid. In some implementations, the electrical generator can be a permanent magnet generator. In certain implementations, the methods can further comprise sensing an operational characteristic using at least one sensor selected from the group consisting of a sensor that is configured to detect a flow' rate of the process gas, a sensor that is configured to detect a pressure of the process gas, and a sensor that is configured to detect a temperature of the process gas. In further implementations, the methods can further comprise sensing an operational characteristic using at least one sensor selected from the group consisting of a sensor that is configured to detect a flow rate of the heat-transfer fluid, a sensor that is configured to detect the pressure of the heat-transfer fluid, and a sensor that is configured to detect the temperature of the heat-transfer fluid.

[0073] The present disclosure provides for methods of generating power. The methods can comprise (i) receiving a first flow' of a process gas, wherein the first flow' is characterized by a first flow' rate, a first pressure, and a first temperature, (ii) heating the first flow' with a first heat exchanger to generate a second flow' of the process gas, wherein the second flow is characterized by a second flow rate, a second pressure, and a second temperature, (iii) expanding the second flow with a first turboexpander to generate a third flow of the process gas, wherein the third flow is characterized by a third flow rate, a third pressure, and a third temperature, (iv) heating the third flow with one or more second heat exchangers, each second heat exchanger generating a fourth flow of the process gas, wherein the fourth flow' is characterized by a fourth flow' rate, a fourth pressure, and a fourth temperature, (v) expanding the one or more fourth flow_'s with one or more second turboexpanders, each second turboexpander generating a fifth flow' of the process gas, wherein the fifth flow is characterized by a fifth flow rate, a fifth pressure, and a fifth temperature, and (viii) producing electrical energy with at least one electrical generator operatively coupled to one or more of the first turboexpander and the one or more second turboexpanders. In certain implementations, the methods can further comprise providing each of the first and second heat exchangers with a supply flow of a heat-transfer fluid. In some implementations, the heat-transfer fluid can be provided at a temperature of less than about 250°F, less than about 200°F, less than about 150°F, less than about 130°F, less than about 1 l0°F, or less than about 90°F. In some implementations the at least one electrical generator is operatively coupled to one or more of the first turboexpander and the one or more second turboexpanders via a common shaft. In certain implementations, the methods can further comprise sensing an operational characteristic using at least one sensor selected from the group consisting of a sensor that is configured to detect a flow rate of the process gas, a sensor that is configured to detect a pressure of the process gas, and a sensor that is configured to detect a temperature of the process gas. In further implementations, the methods can further comprise sensing an operational characteristic using at least one sensor selected from the group consisting of a sensor that is configured to detect a flow rate of the heat-transfer fluid, a sensor that is configured to detect the pressure of the heat-transfer fluid, and a sensor that is configured to detect the temperature of the heat-transfer fluid.

[0074] In certain implementations of the present disclosure, gas bearings are described in relation to shafts. In alternate implementations for all of these implementations, active magnetic bearings can substituted, provided that an appropriate electrical power source for the active magnetic bearings is provided. In such implementations utilizing active magnetic bearings, a regulated flow of filtered process gas and associated gas bearing inlets/outlets are not required, which can pro vide an advantage of simplifying tire system design. Acti ve magnetic bearings have been observed to be more robust for field use in comparison with gas bearings in some implementations.

[0075] The following non-limiting examples further illustrate the various implementations described herein.

[0076] In some implementations, a turboexpander and generator unit has a two stage process gas expander, each stage including a turboexpander and a heat exchanger. High pressure (HP process gas is first heated to increase the process gas volume and maintain the temperature inside the expander. The heated HP process gas then passes to the first stage turboexpander where it imparts a torque on the common shaft as it expands through the turbine. The process gas then leaves the first stage turboexpander at an inter-stage pressure lower than the pressure at the entry to the first stage turboexpander and is heated again. This second heating further increases the process gas volume, maintains the temperature inside the turboexpander and generator unit and ensures the process gas leaving the second stage turboexpander is not too cold. Finally, the process gas flows through the second stage turboexpander and imparts a torque on the common shaft as the process gas expands through the turbine.

[0077] The torque imparted on the common shaft by the expanding gas is converted to electricity by the permanent magnet generator. The electrical power output from the turboexpander and generator unit passes to the inverter where it is first rectified to DC then converted to AC at a voltage and frequency to be consistent with the characteristics of tire local electricity grid.

EXAMPLE 1

Turboexpander And Generator Unit

[0078] An implementation of the disclosed turboexpander and generator unit and associated system is produced as described above and as illustrated in FIGs 1A, IB, 2, 3A, 3B, 3C and

[0079] In certain implementations, the turboexpander turbines are configured to operate at a speed of about 20,000 to about 25,000 rpm . In certain implementations, the turboexpander turbines are configured to operate at a speed of about 21,500 to about 24,000 rpm. In some implementations, the turboexpander turbines are designed for a speed of about 22,500 rpm, and an inlet gas temperature of about 328 °K (54 85 °C, 130 °F). In exemplary

implementations, the design pressure ratios are as summarized in Table 2, below .

Table 2

System Inlet System Outlet

System Power

Pressure, Pressure, PSI

Output, kW Pressure Ratio

PSI (Bar) (Bar)

50 754 (52) 465.6 (32.1) 1.62

Inlet Pressure, Outlet

Pressure Ratio

PSI (Bar) Pressure, 754 (52) 594.7 (41) 1.27

2“^d Stage Inlet Pressure, Outlet Pressu re Ratio

PSI (Bar) Pressure,

591.8 (40.8) 465.6 (32.1) l .z /

[0080] The temperature of the process gas at the inlet of the first stage turboexpander and the temperature of the process gas at the inlet of the second stage turboexpander is maintained by using a first heat exchanger and a second heat exchanger, respectively, wherein the first heat exchanger and the second heat exchanger transfer heat from a secondary fluid, such as a 30% aqueous solution of propylene glycol, to the primary fluid or process gas, the natural gas. In certain implementations, the pressure of the process gas at the system inlet is about 754 psi (52 Bar), the pressure of the process gas at the system outlet is about 465.6 psi (32.1 Bar), and the system pressure ratio is 1.62. in certain implementations, the pressure of the process gas at the first stage inlet (i.e., the inlet of the first stage turboexpander) is about 750 psi (51.7 Bar), the pressure of the process gas at the first stage outlet (i.e., the outlet of the first stage turboexpander) is about 594.7 psi (41 Bar), and the first stage pressure ratio is 1.27. In certain implementations, the pressure of the process gas at the second stage inlet (i.e., the inlet of the second stage turboexpander) is about 591.8 psi (40.8 Bar), the pressure of the process gas at the second stage outlet (i.e., the outlet of the second stage turboexpander) is about 465.6 psi (32.1 Bar), and the second stage pressure ratio is 1.27.

[0081] In general, implementations of the disclosed turboexpander and generator unit and associated system operate with a flow rate of process gas of about 4 kg/sec (12,036 scfm, 528 ib/min) to about 7.5 kg/sec (22,568 scfm, 990 Ib/min). In certain implementations, the disclosed turboexpander and generator unit and associated system operate with a flow rate of process gas of about 4.5 kg/sec (13,541 scfm, 594 Ib/min) to about 6.5 kg/sec (19,559 scfm, 858 Ib/min). In certain implementations, the disclosed turboexpander and generator unit and associated system configured to the range of conditions exemplified by the values summarized in Table 2, above, operates with a fl ow rate of process gas of about 5 kg/sec (15,045 scfm, 660 Ib/min) to about 6 kg/sec (18,054 scfm, 792 Ib/min).

[0082] In certain implementations, the disclosed turboexpander and generator unit and associated system configured to the range of conditions operating in a range of conditions exemplified by tire values summarized in Table 2, above, can produce an electrical power output of about 225 to about 275 kw, more preferably about 238 to about 263 kW, and typically about 250 kW. In certain implementations, the disclosed turboexpander and generator unit and associated system configured to the range of conditions operating in a range of conditions exemplified by the values summarized in Table 2, above, can produce an electrical power output of about 250 kW.

EXAMPLE 2

Deployable Turboexpander And Generator Unit And Associated System

[0083] Idle basic turboexpander and generator unit is configured with related components in a readily transportable turn-key system having components including a controller system 500 operatively connected to a first stage turboexpander 1 10, a second stage turboexpander 210, a generator 310, a DC / AC converter 380, a first heat exchanger 410, a second heat exchanger 420, a valve system 600 and a sensor system 700 mounted in a frame comprising steel or a material having similar characteristics. The system is pre-configured with piping and wiring, and requires only connection to sources of natural gas, instalment grade compressed air, warm wnter and electricity. Typically, the required electrical supply to the assembly is three phase 480 volts, 60 Hz. Typically, the frame is configured for commercial containerized transportation.

[0084] In certain implementations of the deployabl e turboexpander and generator unit and associated system, the control electronics are contained in a purged cabinet and at least one panel that houses the control electronics is cooled by a heat exchanger system. In certain implementations, the control electronics are mounted in a control panel that is cooled by water or an aqueous solution. In certain implementations, the control panel is cooled by the secondary fluid, and waste heat extracted by cooling the control electronics can be supplied to the first heat exchanger 410 and the second heat exchanger 420 as a contribution to heating the process gas.

[0085] Typically, the electrical supply to the control panel is single phase 120 volts, 60 Hz.

In certain implementations, the control electronics include a programmable logic controller.

In certain implementations, the control electronics include a computer comprising a microprocessor, a visual display, nonvolatile memory', RAM memory, and at least one user input device selected from a touch screen, a keypad, a keyboard, a mouse, a touch pad, track pad and a track ball. In certain implementations, the computer is connected to a local network by ethemet or a wireless connection, and to the Internet.

[0086] The flow of fluids (process gas and secondary fluid) is controlled by pneumatic actuator driven valves and regulators, which are in turn controlled by the control electronics. Fluid pressure relief valves are also provided. Fluid piping includes filters and pressure regulators as known in the art. At least one pump is provided to circulate the secondary fluid through the respective heat exchangers.

[0087] Table 3, below, shows typical performance criteria for implementations of the disclosed turboexpander and generator system that are designed to operate at three pressure ratings, with the pressure ratio bands for each range. All implementations configured to operate in the three indicated pressure ranges are based upon a common generator and shaft configuration, but in each implementation, the turbine impellers of the first stage

turboexpander 110 and the second stage turboexpander 210 are designed specifically for the given pressure operating range to ensure that the turboexpanders operate at optimal efficiency. In these implementations, the temperature of the process gas at the process gas inlet 401C of the first heat exchanger 410 and at the process gas inlet 402B of the second heat exchanger 420 are maintained at 150 °F (65.6 °C).

[0088] In Table 3, below, the heat conversion percentage shows the amount of waste heat that is converted to useful electricity. In comparison, an organic rankine cycle system with waste heat available at 250°F (121.1 °C) would only achieve a heat conversion percentage of about 12.5% and would require a connection to a cooling tower or other cooling system to dispose of the residual heat once it had been processed.

[0089] Compared to a conventional organic Rankine cycle system, implementations of the disclosed turboexpander and generator system convert significantly more of the available heat to electricity, between about 30% and about 70% depending on the operating conditions. In implementations of the disclosed turboexpander and generator system, heat exchangers use the remainder of waste heat to warm the gas flow passing through the pressure reduction station, preventing condensation and protecting pipes from low temperature embrittlement. In some implementations, little or none of the waste heat recovered is rejected to atmosphere through cooling towers. In certain implementations, in fact the disclosed turboexpander and generator system can provide an advantageous way to dispose of excess heat from combustion processes, gas engines or kilns without the high capital and operating costs of running cooling towers.

[0090] As summarized in Table 3, above, in certain implementations of the disclosed system, the system is configured to accept an inlet pressure of about 750 psig (51.7 Bar) and the disclosed turboexpander and generator system is designed for a pre-selected pressure ratio (PR), the ratio of the of the pressure of the process gas at the system inlet to the pressure of the process gas at the outlet of the second stage turboexpander. As discussed above, the difference between the system inlet pressure and the second stage turboexpander outlet pressure affects the requirement for preheating by the first heat exchanger 410 and reheating by the second heat exchanger 420 to provide a suitable outlet temperature of the natural gas for downstream transmission to the sites of use. In certain implementations, the disclosed system can be configured to a pressure difference between a system inlet pressure of about 750 psig (51.7 Bar) to a system outlet pressure of about 200 psig (13.8 Bar). In certain implementations, the disclosed system can be configured to a pressure difference between a system inlet pressure of about 750 psig (51.7 Bar) to a system outlet pressure of about 325 psig (22.4 Bar). In certain implementations, the disclosed system can be configured to a pressure difference between a system inlet pressure of about 750 psig (51 .7 Bar) to a system outlet pressure of about 450 psig (31.0 Bar). In certain implementations of the disclosed system, the system is configured to accept an inlet pressure of about 750 psig (51 7 Bar) and is configured to operate with a flow rate of process gas of about 2.230 kg/sec (6,7! 1 scfm, 294.4 lb/min) to about 5.427 kg/sec (16,330 scfm, 716.4 lb/min).

[0091] In other implementations of the disclosed system, the system is configured to accept an inlet pressure of a medium pressure of about 300 psig (20.7 Bar) to about 350 psig (24.1 Bar), and the disclosed turboexpander and generator system is designed for a pre-selected pressure ratio (PR). In certain implementations, the disclosed system can be configured to a pressure difference between a system inlet pressure of about 300 psig (20.7 Bar) to a system outlet pressure of about 180 psig (12.4 Bar). In certain implementations, the disclosed system can be configured to a pressure difference between a system inlet pressure of about 325 psig (22.4 Bar) to a system outlet pressure of about 130 psig (9.0 Bar). In certain implementations, the disclosed system can be configured to a pressure difference between a system inlet pressure of about 350 psig (24.1 Bar) to a system outlet pressure of about 80 psig (5 5 Bar). In certain implementations of the disclosed system, the system is configured to accept an inlet pressure of about 300 psig (20.7 Bar) to about 350 psig (24 1 Bar) and is configured to operate with a flow rate of process gas of about 2.048 kg/sec (6,162 scfm,

270.3 lb/min) to about 5.42.7 kg/sec (16,330 scfm, 716.4 lb/min).

[0092] In other implementations of the disclosed system, the system is configured to accept an inlet pressure of a lower pressure of about 120 psig (8.3 Bar) to about 180 psig (12.4 Bar), and the disclosed turboexpander and generator system is designed for a pre-selected pressure ratio (PR). In certain implementations, the disclosed system can be configured to a pressure difference between a system inlet pressure of about 120 psig (8.3 Bar) to a system outlet pressure of about 80 psig (5.5 Bar). In certain implementations, the disclosed system can be configured to a pressure difference between a system inlet pressure of about 150 psig ( 10.3 Bar) to a system outlet pressure of about 60 psig (4.1 Bar). In certain implementations, tire disclosed system can be configured to a pressure difference between a system inlet pressure of about 180 psig (12.4 Bar) to a system outlet pressure of about 40 psig (2.8 Bar). In certain implementations of the disclosed system, the system is configured to accept an inlet pressure of about 120 psig (8.3 Bar) to about 180 psig (12.4 Bar) and is configured to operate with a flow rate of process gas of about 2.138 kg/sec (6,433 scfm, 282 2 lb/min) to about 7.284 kg/sec (21 ,917 scfm, 961.5 lb/min).

[0093] While the disclosure has been described with reference to exemplar}'

implementations, it will be understood by those skilled in the art that various changes may be made and equivalents may be substituted for elements thereof without departing from the scope of the disclosure. In addition, many modifications may be made to adapt a particular situation or material to die teachings of the disclosure without departing from the essential scope thereof. Therefore, it is intended that the disclosure not be limited to the particular implementation disclosed as the best mode contemplated for carrying out this disclosure, but that the disclosure will include all implementations falling within the scope of the appended claims.

Claims

1. An apparatus comprising:

a first stage turboexpander having a common shaft, an inlet configured to receive a flow of a process gas, wherein the process gas flow is characterized by a flow rate, a pressure and a temperature, and an outlet;

a second stage turboexpander mounted with the first stage turboexpander on the common shaft, having an inlet configured to receive the flow of the process gas discharged from the outlet of the first stage turboexpander and an outlet; a generator mounted with the first stage turboexpander and the second stage

turboexpander on the common shaft; and

a pressurized housing that encloses the first stage turboexpander, the second stage turboexpander, the generator and the common shaft.

2. lire apparatus of Claim 1 wherein the generator is configured to produce electricity when the common shaft rotates as a result of the process gas flowing from the inlet of the first stage turboexpander to the outlet of the second stage turboexpander.

3. The apparatus of Claim 1 wherein the generator is a permanent magnet generator.

4. The apparatus of Claim 1 wdierein the common shaft has at least one journal bearing and at least one thrust bearing.

5. The apparatus of Claim 1 wherein the flow of the process gas is heated by a first heat exchanger before it is received by the inlet of the first stage turboexpander.

6. The apparatus of Claim 1 wherein the flow of the process gas is heated by a second heat exchanger before it is received by the inlet of the second stage turboexpander.

7. The apparatus of Claim 1 wherein, in use, the ratio of the pressure of the process gas flow at the first stage turboexpander inlet to the pressure of the process gas flow⁷ at the outlet of the second stage turboexpander is about 1.4 to about 3.9.

8. The apparatus of Claim 7 w herein, m use, the ratio of the pressure of the process gas flow at the inlet of the first stage turboexpander to the pressure of the process gas flow at the outlet of the second stage turboexpander is about 1 .4 to about 2.0.

9. The apparatus of Claim 7 wherein, in use, the ratio of the pressure of the process gas flow at the inlet of the first stage turboexpander to the pressure of the process gas flow' at the outlet of the second stage turboexpander is about 1.4 to about 1.9.

10. The apparatus of Claim 1 wherein, in use, the ratio of the pressure of the process gas flow at the inlet of the first stage turboexpander to the pressure of the process gas flow at the outlet of the first stage turboexpander is about 1 .1 to about 1 6.

1 1. The apparatus of Claim 1 wherein, use, the ratio of the pressure of the process gas flow' at the inlet of the second stage turboexpander to the pressure of the process gas flow' at the outlet of the second stage turboexpander is about 1.1 to about 1.6.

12. The apparatus of Claim 1 wherein the pressure of the process gas at the inlet of the first stage turboexpander is about 120 psig (8.3 Bar) to about 750 psig (51.7 Bar).

13. The apparatus of Claim 1 wherein the pressure of the process gas at the outlet of the second stage turboexpander is about 80 psig (5.5 Bar) to about 450 psig (31.0 Bar).

14. The apparatus of Claim 1 wherein the apparatus is configured to operate with a flow' rate of the process gas at the inlet of the first stage turboexpander of about 4 kg/sec (12,036 sefm, 528 lb/min) to about 7.5 kg/sec (22,568 sefm, 990 lb/min).

15. The apparatus of Claim 1 wherein the apparatus is configured to operate with a flow rate of the process gas at the inlet of the first stage turboexpander of about 4.5 kg/sec (13,541 sefm, 594 lb/min) to about 6.5 kg/sec (19,559 sefm, 858 lb/min).

16. The apparatus of Claim 1 wherein the apparatus is configured to operate with a flow rate of the process gas at the inlet of the first stage turboexpander of about 5 kg/sec (15,045 sefm, 660 lb/min) to about 6 kg/sec (18,054 sefm, 792 lb/min).

17. A system comprising :

a system inlet configured to receive a flow of a process gas, wherein the process gas flow is characterized by a flow rate, a pressure and a temperature; a first heat exchanger having a process gas inlet configured to receive the flow of the process gas from the system inlet, a process gas outlet, a secondary fluid inlet and a secondary' fluid outlet, wherein the secondary' fluid is characterized by a flow rate, a pressure and a temperature;

a first stage turboexpander having a common shaft, an inlet configured to receive the flow of the process gas from the first heat exchanger process gas outlet and an outlet;

a second heat exchanger having a process gas inlet configured to receive the flow of the process gas from the first stage turboexpander outlet, a process gas outlet, a secondary fluid inlet and a secondary fluid outlet;

a second stage turboexpander mounted with the first stage turboexpander on the common shaft, having an inlet configured to receive the flow of the process gas from the process gas outlet of the second heat exchanger and an outlet; a generator mounted with the first stage turboexpander and the second stage

turboexpander on the common shaft;

a pressurized housing that encloses the first stage turboexpander, the second stage turboexpander, the generator and tire common shaft; and

a system controller.

18. The system of Claim 17 wherein the generator is a permanent magnet generator.

19. The system of Claim 17 wherein the system is mounted in a frame configured for transportation.

20. The system of Claim 17 wherein the system controller further comprises at least one sensor selected from the group consisting of a sensor that is configured to detect the flow rate of the process gas, a sensor that is configured to detect the pressure of the process gas, a sensor that is configured to detect the temperature of the process gas, a sensor that is configured to detect the fl ow rate of the secondary fluid, a sensor that is configured to detect the pressure of the secondary fluid, and a sensor that is configured to detect the temperature of the secondar ' fluid.

21. The system of Claim 17 wherein the system controller further comprises at least one actuator selected from the group consisting of a pneumatic actuator, hydraulic actuator, electric motor and an electrical relay.

22. The system of Claim 17 wherein the system controller further comprises control electronics including a programmable logic controller.

23. The system of Claim 17 wherein the system controller further comprises a computer comprising a microprocessor, a visual display, nonvolatile memory, RAM memory, and at least one user input device selected from a touch screen, a keypad, a keyboard, a mouse, a touch pad, track pad and a track ball.

24. The system of Claim 23 wherein the computer is connected to a local network by ethernet or a wireless connection, and to the Internet.

25. The system of Claim 17 wherein, in use, the ratio of the pressure of the process gas flow' at the system inlet to the pressure of the process gas flow at the outlet of the second stage turboexpander is about 1.4 to about 3.9.

26. The system of Claim 17 wherein, in use, the ratio of the pressure of the process gas flow at the system inlet to the pressure of the process gas flow at the outlet of the second stage turboexpander is about 1.4 to about 2.9

27. The system of Claim 17 wherein the pressure of the process gas at the system inlet is about 120 psig (8.3 Bar) to about 750 psig (51.7 Bar)

28. The system of Claim 17 wherein the pressure of the process gas at the outlet of the second stage turboexpander is about 80 psig (5.5 Bar) to about 450 psig (31.0 Bar).

29. The system of Claim 17 wherein the system is configured to operate with a flow rate of the process gas at the system inlet of about 4 kg/sec (12,036 scfin, 528 lb/min) to about 7.5 kg/sec (22,568 scfin, 990 lb/min).

30. The system of Claim 17 wherein the system is configured to operate with a flow rate of the process gas at the system inlet of about 4.5 kg/sec (13,541 scfin, 594 lb/min) to about 6.5 kg/sec (19,559 scfin, 858 lb/min).

31. The system of Claim 17 wherein the system is configured to operate with a flow rate of the process gas at the system inlet of about 5 kg/sec (15,045 scfin, 660 lb/min) to about 6 kg/sec (18,054 scfin, 792 lb/min).

32 A method for generating power, the method comprising: receiving a first flow of a process gas, wherein the first flow is characterized by a first flow rate, a first pressure, and a first temperature;

heating the first flow with a first heat exchanger to generate a second flow of the process gas, wherein the second flow is characterized by a second flow rate, a second pressure, and a second temperature;

expanding the second flow with a first turboexpander to generate a third flow of the process gas, wherein the third flow is characterized by a third flow rate, a third pressure, and a third temperature;

heating the third flow with one or more second heat exchangers, each second heat exchanger generating a fourth flow of the process gas, wherein the fourth flow is characterized by a fourth flow rate, a fourth pressure, and a fourth temperature; expanding the one or more fourth flows with one or more second turboexpanders, each second turboexpander generating a fifth flow of the process gas, wherein the fifth flow is characterized by a fifth flow rate, a fifth pressure, and a fifth temperature; and

producing electrical energy with at least one electrical generator operatively coupled to one or more of the first turboexpander and the one or more second

turboexpanders.

33. The method of Claim 32, tire method further comprising:

heating the one or more fifth flows with one or more third heat exchangers, each third heat exchanger generating a sixth flow of the process gas, wherein the sixth flow is characterized by a sixth flow rate, a sixth pressure, and a sixth temperature; and expanding the one or more sixth flows with one or more third turboexpanders, each third turboexpander generating a seventh flow⁷ of the process gas, wherein the seventh flow is characterized by a seventh flow rate, a seventh pressure, and a seventh temperature; and

wherein the at least one electrical generator is operatively coupled to one or more of the first turboexpander, the one or more second turboexpanders, and the one or more third turboexpanders.

34 The method of one of Claim 32 or Claim 33, the method further comprising: providing each of the first and second heat exchangers with a supply flow of a heat- transfer fluid.

35. The method of Claim 34, wherein the heat-transfer fluid is provided at a temperature of less than about 250°F.

36. The method of Claim 34, wherein the heat-transfer fluid is provided at a temperature of less than about 200°F.

37. The method of Claim 34, wherein the heat-transfer fluid is provided at a temperature of less than about 150°F.

38. The method of Claim 34, wherein the heat-transfer fluid is provided at a temperature of less than about 130°F.

39. The method of Claim 34, wherein the heat-transfer fluid is provided at a temperature of less than about 110°F.

40. The method of Claim 34, wherein the heat-transfer fluid is provided at a temperature of less than about 90°F.

41. The method of Claim 32, the method further comprising;

sensing an operational characteristic using at least one sensor selected from the group consisting of a sensor that is configured to detect a flow rate of the process gas, a sensor that is configured to detect a pressure of the process gas, and a sensor that is configured to detect a temperature of the process gas.

42. The method of Claim 34, the method further comprising:

sensing an operational characteristic using at least one sensor selected from the group consisting of a sensor that is configured to detect a flow rate of the heat-transfer fluid, a sensor that is configured to detect the pressure of the heat-transfer fluid, and a sensor that is configured to detect the temperature of the heat-transfer fluid.

43. A system for power generation comprising:

a first heat exchanger ( 1100A) comprising a first process-gas-heating inlet { 1102A), a first process-gas-heating outlet (1104A), a first heat-transfer-fluid inlet (1106A), and a first heat-transfer-fluid outlet (1108A); a first turboexpander ( ! 1 10 A) comprising a first process-gas inlet (1112 A) configured to receive a first process gas fluid flow from the first process-gas-heating outlet, and a first process-gas outlet (11 14A);

one or more second heat exchangers (1 100B), each comprising a second process-gas- heating inlet ( 1102B), a second process-gas-heating outlet (1104B), a second heat- transfer-fluid inlet (1106B), and a second heat-transfer-fluid outlet (1108B); one or more second turboexpanders (1 H OB), each comprising a second process-gas inlet (1112B) configured to receive a second process gas fluid flow from the second process-gas-heating outlet, and a second process-gas outlet ( 1114B); one or more third heat exchangers (1100C) comprising a third process-gas -heating inlet ( 1 102C), a third process-gas-heating outlet ( 1104C), a third heat-transfer- fluid inlet ( 1106C), and a third heat-tran fer-fluid outlet ( 1108 C) ;

one or more third turboexpanders (1110C), each comprising a third process-gas inlet (1 112C) configured to receive a third process gas fluid flow from the third process-gas -heating outlet, and a third process-gas outlet (1 1 14C); and at least one electrical generator (1200) operatively coupled to one or more of the first turboexpander, tire one or more second turboexpanders, and the one or more third turboexpanders.