Field of the invention

This invention relates to thermodynamic cycles and useful expansion machines.

Background and prior art :

The PCT documents SE 2012 050 319 and SE 2013 / 051 059

(assigned to Climeon AB) disclose a novel thermodynamic cycle using C02 gas as working fluid and alkaline liquids (amines) as temporary and reversible C02 absorbents. C02 is liberated from C02-saturated amines in the hot section (e.g. 90 °C) , generating 1-10 bar pressure, and, following expansion through a turbine, absorbed by non-saturated amine in the cold section of the process. The steady-state pressure in the cold section is significantly below atmospheric pressure such that pressure ratios between the hot and cold side of the process between 25 and 4 can be realized. Variations and improvements are

disclosed in SE 1300 576-4, SE 1400 027-7 and SE 1400 160-6, all assigned to Climeon, hereby incorporated by reference. General background relating to expansion machines is found in the following disclosures and references:

Moustapha, Zelesky, Baines & Japikse, "Axial and radial turbines", Concepts NREC, 2003, ISBN 0-933283, see especially Figure 8.19. Japikse & Baines, "Introduction to

turbomachinery" . Balje 0., "Turbomachines - A Guide to Design Selection and Theory", 1981, ISBN 0-471-06036-4.

Among patent disclosures, EP 2 669 473 (Mitsubishi, 2012) and US 2013/0280 036 (Honeywell) are recent examples of

technological progress in the construction of radial turbines. US 5 408 747 (United Technologies Corp., 1994) describes a CFD approach to the design of radial-inflow turbines.

Regarding the removal of condensing liquids from the turbine during the expansion, the following disclosures are of general interest: EP 2092 165 by ABB (2007), EP 2128 386 by Siemens (2008), EP 1925 785 by Siemens (2006), EP 1103 699 by

Mitsubishi (2007), EP 0812 378 by Joel H. Rosenblatt (1995) . The latter publication discloses the management of two-phase systems such as ammonia-water in multi-stage turbines. This invention differs from the a.m. disclosures in the sense that one-stage radial turbines are employed which pose very

different challenges compared to axial turbines.

For the invention, it is relevant to appreciate that expansion machines can be selected on the basis of the Cordier/Bal je diagram of dimensionless parameters including the rotation frequency, average volume flow and the isentropic heat drop. Comparing axial and radial turbines, the optimum performance range of axial turbines as function of the dimensionless specific speed is rather broad. By contrast, radial turbines have a rather narrow range where the turbine efficiency is above 80, or >85 or >88% of theoretical maximum. Provided the dimensionless specific speed is about 0.7 (range 0.5-0.9), a single stage radial turbine can be as efficient as a one- or two-stage axial turbine (see Balje) . Brief description of figures:

Figure 1 shows an embodiment of a radial turbine with specific features. The turbine blades are arranged on an axle defining the Z direction. From the side, high pressure gas, e.g.

between 1-3 bars enters the turbine and acts on blades 4. The turbine is stabilized by at least one bearing 3. A labyrinth 2 reduces gas flow from the high pressure side to the top side of the turbine and the bearing space. At least one hole 1, but typically a plurality roughly in z-direction, allows high pressure gas to escape the bearing space towards the low pressure regime at the bottom of figure 1. Brief description of the invention:

Given that the C3 thermodynamic cycle as disclosed in SE 2012 050 319 and SE 2013 / 051 059 as well as SE 1300 576-4, SE 1400 027-7 and SE 1400 160-6, hereby incorporated by

reference, can generate pressure ratios of far above 10, the natural choice of a suitable expansion machine is an axial multi-stage turbine. However, in the desired effect range of 100 kW electricity production, few products are available, and both the design and production of suitable axial turbines are very or even prohibitively expensive. Surprisingly, it was found by the inventors that the C3 process can be adjusted by proper choice of chemistry and working fluid composition

(absorption enthalpy in the range of preferably 700 - 1400 kJ/kg C02, and suitable evaporation enthalpies of co-solvents in the range of 200-1100, preferably 300-800 kJ/kg solvent,), heat exchangers etc., such that a significantly cheaper single stage radial turbine can be employed at the optimum point of performance, where axial and radial turbines perform equally well. It appears counter-intuitive to employ a turbine most suitable for a pressure of about 8 when the system would allow the use of multi-stage turbines and pressure ratios of >>10 on the basis of pressure generation capability at high

temperature, and vacuum generation capability at low

temperature. However, careful modelling of the single stage configuration and the associated flows (saturated amine, unsaturated amine, both volatile or non-volatile as defined by boiling points above or below 100 °C at atmospheric pressure, C02 gas, solvents) reveals the unexpected benefits. As far as limitations of the configuration are concerned, systems with absorption enthalpies below 700, below 800, below 900, or 1000 or 1100 kJ/kg C02 would be characterized by very large liquid flows unless the temperature on the hot side is raised to above 100 °C. It should be clear that the optimum configuration from a cost point-of-view is found by modelling, and balancing costs of especially the turbine and the necessary heat

exchangers .

Detailed description of preferred embodiments This invention concerns in one aspect a method to generate electricity from low value heat streams such as industrial process heat, heat from engines or geothermal or solar heat at the lowest cost possible, i.e. with economic equipment

resulting in low depreciation costs. Surprisingly, radial turbines offer not only reasonable costs, but they also offer certain technical advantages, such as: A radial turbine can be designed without bearings on the exit side. This offers the possibility of having a highly-effective diffuser for optimum turbine performance. The required bearings will be on the alternator side of the unit (commonly referred to as

"overhang". There will therefore be no need for bearing struts in the diffuser. The diffuser recovery will be improved if no struts are present in the flow path.

Further, no shaft seal is needed in the low pressure regime. By virtue of the "overhang design" of the bearings, the turbine has no shaft-seal on the low-pressure (or absorber) side. This means that the risk of air leaking into the cycle is effectively removed.

Also, the "swallowing capacity" / choking effect can be used advantageously, allowing to let the rotational frequency control upstream pressure. An un-choked radial turbine has a rather large speed influence on the turbine swallowing

capacity (i.e. the flow-pressure-temperature-relation) . This feature can be used to optimize the cycle pressure, hence chemistry, at various off-design conditions, by varying the turbine speed. The turbine speed is controlled by the power electronics .

Finally, the diffusor can be integrated into the absorption chamber in various ways, at a 0-90 degree angle, generating swirl etc in order to ensure maximum interaction of gas and liquid absorbent. The diffusor may be placed vertically or horizontally or at any angle. The turbine diffuser and the absorber can be combined into a single part, where the

absorption process starts already in the turbine diffuser, provided that nozzles can be placed without too severe

aerodynamic blockage. Providing a liquid flow on the inner walls of the diffusor is an option to prevent build-up of residues such as ice or crystals in the diffuser.

Turbine design: as temperature is low, the aerodynamic profile can be optimized since no scalloping will be required. The C3 temperature level is lower than e.g. in automotive

applications and there is no need for additional stress reduction such as removing the hub at the turbine inlet. The efficiency of the turbine can be increased by two to four points by avoiding the scalloping. This feature is unique for the C3-cycle with a radial turbine. No scalloping needed = supporting elements on the downstream side of the turbine wheel, to improve the mechanical stability in case of exposure to high temperature. No compromise is required.

The invention enables the use of cheaper materials for

construction, including thermoplastics or glass/carbon fiber reinforced thermosets or thermoplastics, as a direct consequence of low maximum temperatures (60-120 °C) and low pressures (< 10 bar) prevalent in the C3 process and its embodiments as described above. Also the preferred rotation speed of the turbine in the range of 18 000 to 30 000

revolutions per minute (rpm), preferably between 20 000 and 25 000 revolutions per minute, fits to cheap engineering materials .

In one embodiment, the turbine design is modified to enable the removal of a condensing liquid. Said liquid may e.g. be amine or water or any component which condenses first from a composition of at least two working fluids. Condensing liquids in general may cause erosion, corrosion, and a lowering of the obtainable efficiency, e.g. due to friction, changed inlet angle etc. In axial turbines, removal of condensing liquid is state-of-the-art, however, in radial turbines no designs have been published. For the application according to the

invention, a preferred embodiment includes the positioning of slits or openings downstream of the inlet channels, but upstream of the rotating blades. At that position, a

significant pressure is available for removing condensing liquid. Liquid may be transported away from the turbine towards the condenser using said pressure difference through pipes and optional valves. Said valves may be triggered by sensors which detect the presence of liquid, e.g. by measuring heat conductivity.

In one embodiment of the above solution to remove condensing liquid, it may be beneficial to also extract condensing liquid prior to working gas/fluid entering the stator or the inlet channels. Working gas enters the space upstream of the stator, and especially during start-up of the machine, some fluid/gas may condense. From a process point-of-view, the disclosed combination of radial turbines and the C3 process fits to most of the systems and chemistries described in the a.m. disclosures.

In a specific embodiment, a working fluid composition of a) amines such as dibutylamine or diethylamine, 0-80% by weight, b) solvent selected from the group consisting of acetone

(preferred due to its excellent expansion characteristics), isopropanol, methanol and ethanol, at least 20% by weight and c) C02, not more than 0.5 mol per mol amine, and d) optionally water (0 - 100% by weight) is chosen. The working gas entering the turbine comprises a mixture of C02, amine, solvent and optionally water at a ratio defined by the process parameters and the working fluid composition. The exact composition of the working gas is preferably chosen such that the working gas expands in a "dry" mode, i.e. avoiding condensation and drop formation on the turbine blades.

In one embodiment, water is part or constitutes 100% of the working fluid composition. Whilst water is affecting the partial pressures of all components, benefits relating to fire risks result. Further, the absorption enthalpies of the amine/C02 reaction is reduced.

In one embodiment, volatile amines such as diethylamine (DEA) are employed. DEA has a boiling point of 54 °C and is therefore part of the working gas and is removed from the equilibrium of amine and C02. This result in complete C02 desorption from the carbamate based on C02 and DEA. This mode of operation

obviates the need for using a central heat exchanger, or allows to use a smaller heat exchanger.

In one embodiment, non-volatile amines such as dibutylamine (DBA) are employed. In one embodiment relating to turbine technology and the risk of solvents dissolving lubricants in bearings, magnetic bearings are employed. Alternatively, the bearing space is continuously evacuated, or a small gas stream, e.g. C02, is led into the bearing space at a slightly higher pressure than prevalent in the process, such that solvent condensation in the bearing space is avoided. Gas leaking from the bearing space into the process can be evacuated e.g. using techniques described in as yet unpublished patent applications. In one embodiment, further relating to minimizing the risk that lubricant is removed or washed out from bearings, but also relating to the risk that bearings wear out prematurely due to non-ideal loads in axial or radial direction, the turbine is modified in a way which is further shown in figure 1 showing an embodiment of a radial turbine with specific features. The turbine blades are arranged on an axle defining the Z direction. From the side, high pressure gas, e.g.

between 1-3 bars enters the turbine and acts on blades 4. The turbine is stabilized by at least one bearing 3. A labyrinth 2 reduces gas flow from the high pressure side to the top side of the turbine and the bearing space. At least one hole 1, but typically a plurality roughly in z-direction, allows high pressure gas to escape the bearing space towards the low pressure regime at the bottom of the figure. Typical

dimensions for a 100 kW turbine may be: hole diameter 1-6 mm, turbine height in z direction 90 mm. A range of hole diameters is given. The diameter may be different for different working media. The important criterion for selecting balancing hole geometries is, that the pressure drop over all balancing holes shall be lower than the pressure drop over the labyrinth. As a consequence, the labyrinth serves as bottleneck, and the pressure in the bearing space is reduced and approaches the pressure downstream of the turbine. This embodiment is preferred because the bearings are exposed to a minimum of chemicals which may dissolve lubricant. Further, gas pressure in z direction on the turbine, causing undesirable pressure and load on bearing 3 is minimized by at least 20%, or 30%, or 40%, or 50%, or 60% or 75% or more as the pressure is at least reduced accordingly by 20%, or 30%, or 40%, or 50%, or 60%, or 75% or more. Improved embodiments may comprise a load cell which dynamically adjusts the distance between labyrinth and rotating turbine and keeps it to a minimum value. The

labyrinth may be made of polymeric materials.

In one embodiment, the purpose of the turbine modification, namely the reduction of the gas pressure in the space where the bearing is placed, is achieved by fluidly connecting said space by a pipe or bypass leading towards the low pressure side, i.e. the absorber or condenser. Said pipe may comprise a valve which can be regulated. Another bypass from the high pressure gas side into the bearing space, with a regulating valve, may serve to adjust the pressure and the axial load onto the bearings. Various configurations are conceivable, e.g. a solution with two labyrinth sections with different diameters whereby the inner section between the smallest labyrinth and the axle is kept at minimum pressure in order to protect the bearing, and the section between the two

labyrinths is kept at higher pressure to adjust the axial load on the bearing.

One special advantage of the solutions described here is that the electrical generator which may be in fluid connection with the bearing space can be kept at low pressure. This prevents condensation of working medium also in the generator. The solution involves a small loss such as between 0.1 and 5% of high pressure gas which otherwise would be available for power generation, however, the benefits such as prevention of working liquid condensation in the generator or on the bearing and the reduction of undesirable forces onto the bearings, and therefore extended lifetime of the turbine, outweigh the loss. In one embodiment, from known bearing solutions for turbines, such as roller bearings, magnetic bearings and the like, a hydrostatic bearing is chosen. In a preferred embodiment, the working gas or medium or fluid itself is carrying the load. This solution is especially preferred in case a solvent such as acetone, butanol, isopropanol, ethanol, amines and water or solvent mixtures. The working fluid may be pumped into the space between the static parts and the rotating parts by means of a pump, e.g. an external separate pump or a process pump which is pumping working fluid within the system. The pressure may be in the interval 2-10 bar, preferably below 5 bar. The rotational speed is preferably in the range 20 000 - 30 000 rpm for power generation systems producing 50-200 kW but may be much higher (> 100 000) for small-scale systems, e.g. 10 kW systems. One particular advantage of hydrostatic bearings, apart from enabling high rotational speeds, is that lubricant or grease in conventional bearings is not needed in

hydrostatic bearings. There would otherwise be a certain risk that lubricant or components in lubricant such as mineral oil would be extracted from the bearing area. This would deplete the bearing from necessary lubricant, and the extracted lubricant component would accumulate in the process.

It should be understood that the concepts in the different embodiments may be combined.

All embodiments are characterized by the fact that below atmospheric pressure prevails on the cold or absorption / condensation side of the process. Depending on temperature of the cooling stream, the pressure may be < 0.8 bar, < 0.7 bar, < 0.6 bar or preferably < 0.5 bar. This pressure can be maintained by providing cooling in the absorber, e.g. a heat exchanger, and/or by recirculating condensed working fluid and cooling said liquid inside or outside of the absorption / condensation chamber as described elsewhere.

In Fig. 1 the reference characters have the following meaning:

1 balancing hole through turbine axle (one of a plurality)

2 labyrinth, to reduce gas flow from high pressure side to bearing space

3 bearing

4 turbine blade

Z = direction of axle