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More Ideas in Light and Energy - The Blog

Power Fluids – Possible Fluids for Minto Wheels, Rankine Cycles …

All kind of Rankine or steam engines need a suitable  fluid, that reacts to heating with an increase in pressure. The increased pressure of the fluid will be used to drive a piston, a turbine blade, lift a mass … and generate power. In this sense the fluid can be called “power fluid”. The following charts show graphs of the vapor pressure (bar) versus the temperatures (°C) for several fluids. The second chart uses a logarithmic vertical axis. The fluids are:

1. Propan – C3H8
2. Refrigerant R134a
3. N-Butan – C4H10
4. Refgrigerant R254fa
5. Dichlormethan (Methylenchlorid) – CH2Cl2
6. Aceton – C3H6O
7. Methanol – CH4O

The solid red curve shows the pressure rise of normal air resulting from isochoric (constant volume) heating. Note: this is only a limited collection and not all of those fluid have been tested for a steam engine application.

 

 

 

Filed under: cogeneration,minto wheel,rankine engine,thermodyna,Uncategorized — exergia posted 27/08/2012 at 12:18 pm



Energy stored in a pressurized Fluid – The Expansion process

How much mechanical energy, i.e. exergy could one extract from a gaseous, pressurized  fluid at a pressure P1 and temperature T1 when it expands in an adequate engine? We assume the equilibrium the surrounding condition to be P0, T0.

The first question we have to answer is how an ideal gas behaves when it is expanded. The thermodynamic theory of an ideal process without heat input (adiabatic) and without friction (isentropic) yields to a set of the following equations:

P2/P1 = (V1/V2) ^ n
<=>
V1/V2 = (P2/P1) ^ (1/n)

 

V1/V2 = (T2/T1) ^ 1/(n-1)
<=>
T2/T1  = V1/V2^ (n-1)

 

T1/T2 = (P1/P2) ^ ((n-1)/n)
<=>
P1/P2 = (T1/T2) ^ (n/(n-1))

 

The equations relate the initial state 1 characterized by temperature T1, pressure P1 and volume V1 to the final state 2 (T2, P2, V2).  n is characterising the gas and depending related on the heat capacities at constant pressure Cp and at constant volume Cv:

n = Cp/Cv

This ratio is called the isentropic exponent. Here some characteristic values:

  • Mono atomic gas -  Argon: n= 1.67
  • Diatomic gas – nitrogen, Hydrogen , “normal air”: n = 1.4
  • “Multi-atomic” gas – organic fluid – refrigerant R11: n =1.13
  • “Multi-atomic” gas – organic fluid – Butane: n =1.09

The above equations only hold for a situation, where energy is reversible transferred from the gas to a macroscopic body, i.e. a piston.  So the gas is cooled and decreases its temperature. In a situation where an ideal gas freely expands without energy transfer, the temperature will remain constant. In contrast to the isentropic expansion this is a irreversible process.

Using the above equations with  c_exp = V/V1, the expansion ratio, yields to

P(V) = P1  (V1/V) ^ n = P1  c_exp^(-n) = P(c_exp)

The following plot shows the pressure decrease depending on the expansion ration during an expansion process for the four typical fluids Argon,  Hydrogen, refrigerant R11 and Butane. Initial pressure is 10 bar. Note: In technical applications, e.g. characterizing air motors, people normally talk about pressure differences to atmospheric pressure. So a  pressure of 1 bar in a data sheet of an air motor means actually an absolute pressure of 2 bar.

Analogous there is a temperature decrease. The following diagram shows to typical expansion processes: Air is expanded via an air motor starting at low temperature T1 = 25°C , a temperature you  have in a compressed air tank. The second process starts at 100°C a situation that may arise in an Organic Rankine cycle.

T(V) = T1  (V1/V) ^(n-1) = T1  c_exp^(1-n) = T(c_exp)

 

To calculate the maximal energy we can extract from the pressurized fluid we have to use a total isentropic  process. Isentropic means, that every step of the process has to be reversible and finally the fluid ends with atmospheric conditions (T0,P0). Let’s further assume we are using  an ideal  positive displacement engine, for example a “massive” piston sliding frictionless in a cylinder. The whole process can be divided in 4 steps:

1.) Input process, filling the piston to volume V1

2.) Expansion of  the fluid from V1 -> V2, choose V2 so that the pressure becomes equal to the surrounding atmospheric pressure: P2 = P0

3.) In most of the cases after the expansion the gas temperature T2 is not equal to the surrounding air temperature. So there is  a potential source to extract further exergy via a heat engine: T2 ->  T0

4.) Output exhaust process, emptying the piston in pushing the fluid to the surrounding

The total pressure P-P0 acting on the piston

1.) During the filling process of the empty piston to a volume V1 a total constant pressure of P1-P0 acts on the piston. So we get

L_input = (P1-P0)  V1

2.) The generated mechanical energy is calculated via integrating this pressure over the expansion volume

L_expansion
= Integral(P(V)-P0, V1, V2)
= Integral(P(V), V1, V2) – P0 (V2 – V1)
= 1/(1-n)  P1 V1  ((V2/V1)^(1-n) – 1) – P0 (V2 – V1)

Import point here is, that for an ideal expansion the final volume has to be chosen in a way, that the end pressure after expansion equals the surrounding’s pressure. So:

(V2/V1)^(1-n) = P2 V2/(P1*V1)

and finally

L_expansion = 1/(1-n) (P2 V2 -  P1 V1) – P0 (V2 – V1)
= Cv (T2 – T1) -
P0 (V2 – V1)

3.)  We neglect for the moment

L_heatengine = ?

4.) During the output process after opening the exhaust no force is acting on the piston. So

L_output = 0

The following diagram shows input cycle and expansion work as corresponding areas in the pressure volume chart:

 

A more intuitive formulation is to transfer to the analogous equations for power instead of energy and normalize by dividing by the input volume flow Vflow1:

Lp_spec_input =  Lp_input/Vflow1 = (P1-P0)

 

Lp_spec_expansion =  Lp_expansion/Vflow1
= 1/(1-n) (P2 Vflow2/Vflow1 -  P1) – P0 (Vflow2/Vflow1 – 1)

Using the relations for  optimal expansion

c_exp_opti = Vflow2/Vflow1 = (P1/P2)^(1/n)

and

P0 = P2

yields to

Lp_spec_expansion = 1/(1-n) (P2  c_exp_opti -  P1) – P2 (c_exp_opti – 1)

The following plot shows the two parts of the specific expansion power of air resulting from the input cycle (red)  and isentropic expansion (blue). The blue line shows the sum of both. Let’s see an example: To generate 1000 Watt of mechanical power with an ideal engine you need an air input stream of 1 l/sec at approx. 7 bar. In this case it splits into 600 Watt resulting from the input cycle and  400 Watt from the expansion. For real machines the inlet air consumption may be 3 to 15 times higher.

 

 

 

Filed under: air engine,airmotor,rankine engine,thermodyna — exergia posted 26/04/2012 at 7:14 pm



Thermodyna – Small sized Organic Rankine Cycle Heat Motor – 2. Expander

Something new from the blog  …

Here the first post regarding an old idea lying in the drawer for several years: Small sized Organic Rankine Cycle Heat Motor. Project name is Thermodyna. Step by step we will publish the latest results regarding 1. cycle configuration, 3. working fluid, 4. generator, … Today we start with the logical number 2, the expander.

2. Expander / Expansionsmaschine

The most important part in a Rankine cycle system is the expander, tbe unit converting the energy stored in the pressurized fluid into mechanical i.e. rotational energy. Off the shelf industrial parts driven by pressurized air are airmotors. Many different types are available:

2.1. Radial Piston Engine / Radialkolbenmotor

Radial engine in a cut-away view

http://en.wikipedia.org/wiki/File:Radial_engine.gif

 

Section Drawing


Type P1V-P, Parker Hannifin Catalog

 

2.1.1 Huco Dynatork


Type Dynatork 7, Huco Catalog

Specification:

- Maximal input pressure: ~7 bar
- Maximal temprature: < 70 deg.
- Oil required: yes
- Operation time: ?
- Power, air consumption, speed: see below

 

2.1.2 Globe Airmotors

 


Type RM110 – Datasheet – Globe. Globe Catalog

Specification:

- Maximal input pressure: ~8 bar
- Maximal temperature: <80 deg.
- Oil required: yes
- Operation time: 5000 – 8000h
- Power, air consumption, speed: see below
- Inside the housing there has to be a pressure of ~1 bar

2.1.3 Parker

Germany – Karrst

 


Type P1V-P SERIES – Datasheet – Parker, Parker Hannifin Catalog

Specification:

- Maximal input pressure: ~7 bar
- Maximal temperature: < 70
- Oil required: yes
- Operation time: ?
- Power, air consumption, speed: see below

 

2.1.4 Tonson

2.2 Rotor Vane Motor / Lamellenmotor

Section Drawing


Parker Hannifin Catalog

 

2.2.1 Gast


Type:  NL – Non-Lubricated Air Motor, www.gastmfg.com
No lubrication necessary for these corrosion resistant air-motors.


Type: AM (SS) Series – Lubricated / Stainless Steel Air Motor, www.gastmfg.com
Fully sealed and sanitary design, these corrosion resistant


Type: AM – Lubricated Air Motors, Datasheet – Gast

 

2.2.2 Parker


Type: P1V-A SERIES – Datasheet – Parker, Parker Hannifin Catalog

 

Specification:

- Maximal input pressure:
- Maximal temperature:
- Oil required:
- Operation time:
- Power, air consumption, speed: see below

2.2.3 Ober Italy

 

2.3 Gas Pressure Motor / Drehkolbenmotor

2.3.1 Armak


Type GGP04 – Datasheet – Armak, www.armakmotor.com

Specification:

- Maximal input pressure: ~15 bar
- Maximal temperature: < 150 deg.
- Oil required: no
- Operation time: ?
- Power, air consumption, speed: see below

 

 

Manfacturers characterize their engines with diagramms showing the mechanical energy versus rotational speed and air consumption versus speed for different air intake pressures. Information about the engine’s efficiency are hard to find. As a first attempt to compare different engine’s efficiencies we suggest to calculate the normalized value  of specific power, the quotient of power  devided by air consumption ( [ ] = W / (l/sec) ) and plot it versus intake pressure. The results are shown below. The data values have been taken from the abowe cited data sheets. The plot also includes the maximum power that could be achived from pressurized air. As comparative process we use an isentropic expansion. The red curve shows power generated by filling the engine’s volume and the green power generated by expansion. The mathematical model is published here. We are in an ongoing process to discuss those results with some manufacturers.

Normalized Power per Inlet Air Consumption

Normalized Power per Exhaust Air Consumption (Free Air)

 

 

Filed under: air engine,airmotor,cogeneration,exergia's projects,rankine engine,thermodyna — exergia posted 11/03/2012 at 9:13 am



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