# Study of Thermal Energy Production by Combustion of Lard and Diesel Mixtures

Authors: J. F. San José Alonso; S. Alonso Miñambres; I. Gobernado Arribas
Journal: Journal of Combustion
 (2012)

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## Abstract

This work presents the experimental results of lard combustion with diesel for heating. The work is divided into two parts, the first of which deals with the identification of lard as fuels and characterization of diesel, as well as determining the chemical and thermodynamic properties of mixtures of both components. The second part studies the optimum combustion point of lard and oil mixtures in a conventional plant, varying the percentage of lard in mixing, air flow, and injection pressure.


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## Body

## 1.  Introduction

Meat consumption in the European Union entails livestock production of a wide range of species (ovine, porcine, bovine, and caprine). Statistical data for the livestock census in the European Community corresponding to 2005 are shown in Table1 [1].Table 1
EU livestock census (millions of animals) in December 2005.
Countries
Bovine
Ovine
Caprine
Porcine
Total
Austria
2.01
0.33
0.06
3.17
5.56
Belgium
2.60
0.00
0.00
3.40
6.00
Bulgaria
0.63
1.60
0.61
0.00
2.84
Cyprus
0.06
0.27
0.33
0.43
1.08
Czech Republic
1.35
0.19
0.02
2.72
1.56
Denmark
1.57
0.08
0.00
12.60
14.26
Estonia
0.25
0.05
0,00
0.35
0.66
Finland
0.95
0.09
0.01
1.44
2.48
France
18.93
8.76
1.25
15.12
35.30
Germany
12.38
2.04
0.17
26.86
41.45
Greece
0.71
9.18
5.53
1.04
16.45
Hungary
0.71
1.41
0.08
3.85
6.05
Ireland
6.19
4.53
0.01
1.68
12.40
Italy
6.46
7.95
0.94
9.20
24.56
Latvia
0.39
0.04
0.01
0.43
0.87
Lithuania
0.80
0.03
0.02
1.13
1.98
Luxembourg
0.18
0.00
0.00
0.08
0.28
Malta0
0.02
0.01
0.00
0.07
0.11
Netherlands
3.75
1.72
0.31
11.00
16.78
Poland
5.38
0.32
0.00
18.71
24.41
Portugal
1.44
3.58
0.55
2.34
7.91
Romania
2.77
7.54
0.68
0.00
11.00
Slovak Republic
0.53
0.32
0.04
1.11
2.00
Slovenia
0.45
0.13
0.03
0.55
1.15
Spain
6.46
22.91
2.84
24.880
54.26
Sweden
1.53
0.48
0.01
1.80
3.82
United Kingdom
10.15
23.93
0.10
4.76
38.93
Source: MAPA. General Suboffice for Food Statistics.This livestock is produced for human consumption. Animals must be sacrificed in specialized facilities, such as slaughterhouses, which are subject to strict health controls. Live animals of the main species of livestock are taken to these facilities to be sacrificed and subsequently processed for human consumption. The process carried out at these facilities involves separating products destined for human consumption and those to be used as animal subproducts not destined for human consumption (ASNDHC), which for commercial, health, and legal reasons must not form part of the food chain. Table2 provides an estimation of the amount of ASNDHC generated in Spain for the various species per animal sacrificed, calculated on the mean dressed weight [2].Table 2
Summary of the ASNDHC generated per animal species in Spanish slaughterhouses in 2005.
Species
Number of sacrifices (millions)
ASNDHC per animal sacrificed (kg animal−1)
ASNDHC Total (Gg)
Bovine 12 months old or less
1.53
166.25
254.70
Bovine over 12 months old
1.26
260.45
328.27
Caprine
1.66
8.05
13.39
Equine
0.25
152.6
3.86
Ovine
20.45
8.05
164.60
Porcine
38.06
10.79
410.72
Total
1,175.54The mad cow disease crisis (bovine spongiform encephalopathy (BSE)) forced the European Union to enforce highly restrictive [3] and stringent legislation regarding the handling of this kind of subproduct, including the possible final use which these products may be put to once transformed. One result of this was for subproducts to be considered waste.The present study aims to demonstrate the possible use of animal subproducts, in particular transformed fats, as fuel sources by mixing them with fossil fuels. Such a mixture would provide a range of benefits.(i)
Financial benefits: use of the energy properties of a waste product (transformed animal fat), through its possible use as a biofuel in combustion processes.(ii)
Environmental benefits: using renewable energy sources, such as animal-based biomass combined with conventional energy sources, has a lower environmental impact compared to exclusively fossil fuels.Lard may be transformed into biofuel and used directly in an engine or in a conventional burner. In the present work, the lard is burned directly so as to eliminate transformation costs and due to the major investment which such transformation plants involve.


## 2. Lard as a Fuel

In its 2008 publication on “The State of Food and Agriculture,” the Food and Agriculture Organization of the United Nations (FAO) [4] conducted a thorough review of the risks and opportunities offered by biofuels as well as the political challenges to be faced. The analysis concludes by stating that the rapid growth in the production and consumption of biofuels in numerous countries has far outstripped any understanding of their potential impact on food safety and the environment. This concern has led current fuel research and development programs to focus on second generation biofuels [5].“Second generation” biofuels are those obtained from nonfood sources, such as lignocellulosic biomass for production of ethanol, nonedible oleaginous seeds for the production of biodiesel, and ASNDHC livestock subproducts. Animal fats are a much cleaner renewable energy source than conventional diesel and can be converted into biodiesel by means of chemical processes used in existing refineries. This product might merge already mixed fuel with normal fuel and might be sold as such. A further option is direct use for heating without the need for it to undergo transformation up to a proportion of 50%. All that is required is preheating to 38°C with stirring.


## 3. Characterization of Lard

The laboratory receives the Lard from a waste management company, which only collects the product from pig slaughterhouses. This waste is subjected to the following processes. The raw material is first crushed and then heat-treated at high pressure to remove excess moisture and destroy microorganisms. Solid fraction is subsequently separated from the lard, with only the latter being used in this paper.At least four criteria need to be taken into account when assessing lard as a possible fuel: (i) inherent chemical quality (composition by elements and fatty ashes), (ii) mechanical quality of the fat (viscosity and density for different temperatures), (iii) energy quality (Calorific power), and (iv) possible uses (study of combustion processes). Table3 shows the chemical and physical characteristics of lard and diesel.Table 3
Chemical and physical properties of lard and diesel.
Unit
Test method
Lard
Diesel
Density at 15°C
(kg/m3)
ISO 3675
911
848
Density at 35°C
(kg/m3)
ISO 3675
899
635
Kinematic viscosity at 40°C
(mm2/s)
ISO 3104
40.87
2.7
Kinematic viscosity at 100°C
(mm2/s)
ISO 3104
8.46
1.2
S percent by mass
(kg/kg)
ASTM D-4239
0.03
0.07
C percent by mass
(kg/kg)
ASTM 5291
76.8
86.6
H percent by mass
(kg/kg)
ASTM 5291
11.6
12.3
O percent by mass
(kg/kg)
—
11.3
1.03
N percent by mass
(kg/kg)
ASTM 5291
0.2
—
Ashes
(kg/kg)
ASTM 5291
0.002
—
H.H.V.
(kJ/kg)
ASTM D-240
39,397
44,872
L.H.V.
(kJ/kg)
ASTM D-240
36,939
42,268


## 4. Mixing Lard and Diesel

The lard is mixed with commercial diesel fuel and complies with directive 2003/17/EC specifications. This directive covers two types of diesel: that used in combustion engines whose specifications meet with EN590 and the diesel used in boilers, which has other specifications, which do not meet with EN590. The manufacturer of the burner recommends not burning fuels with a viscosity above 3 mm2/s at 100°C.Our aim is to obtain the maximum percentage of lard mixed with diesel fuel with a viscosity below said limit, which will provide us with a homogeneous mixture [6]. Figure 1 shows how the mixtures of 40% lard and 60% diesel at room temperature are heterogeneous [7, 8]. Above 40°C, animal fats are homogeneous liquids. Below this temperature, they are solid, do not dissolve in diesel, and block the fuel line. Figure 2 shows the homogeneous mixtures (lard and diesel). Homogenization is subject to heating and stirring of the mixture. The procedure is carried out in a TestoTerm brand, model 7000/9000, thermal bath with a temperature range of −50–400°C and a resolution of 0.1°C.Figure 1
Heterogeneous mixture at room temperature, mixture of 40% fat and 60% diesel.Figure 2
Homogeneous mixture after undergoing heating and stirring.The viscosity value of a fuel is a function of the temperature. The manufacturer of the burner limits the fuel viscosity, referencing it to 100°C. Under normal conditions, the burner is fed by fuel at a room temperature of around 20°C. This means that the burner is running with a fuel that has a higher viscosity. However, mixtures must always be burnt at a temperature above 40°C, as a result of which the mixture viscosity in the burner is lower than that of diesel at 20°C.


## 5. Characteristics of Mixtures of PorkFat and Diesel

Each mixture was labeled with a two-letter code to indicate the fat used in the mixture (PR pork fat), followed by numbers indicating the percentage of pork fat used, ranging from 0% to 50% fat, the maximum imposed by the viscosity of the mixture, 9.5 mm2/s at 40°C.In this section, we analyze the different characteristics of the fats and their mixtures with diesel in order to predict their optimal behavior as a fuel. The characteristics of the mixtures are obtained: (i) from other known properties (derivatives), (ii) from a knowledge of said properties in the pure components that make up the mixture (theoretical), and (iii) from laboratory measurements (empirical). The chemical and physical characteristics of fat and their mixtures with diesel are shown in Table4.Table 4
Characteristics of the mixtures of diesel and lard.
Name
%C
%H
%O
%S
Density 15°C (kg/m3)
Viscosity 100°C (mm2/s)
L.H.V. (kJ/kg)
PR-0
86.60
12.30
1.03
0.07
848
1.20
42,268
PR-10
85.62
12.23
2.06
0.06
854.3
1.36
41,735
PR-20
84.64
12.16
3.08
0.06
860.6
1.62
41,202
PR-30
83.66
12.09
4.11
0.06
866.9
2.07
40,669
PR-40
82.68
12.02
5.14
0.05
873.2
2.45
40,136
PR-50
81.70
11.95
6.17
0.05
879.5
3.12
39,603


## 6. Parameters Characterizing the Combustionof Liquids

Combustion for heating is performed using burners, prepared for the controlled and optimized combustion of a specific fuel. The basic conditions to be met by the burner are the following.(i)
It should adapt to the combustion chamber where it is to be used.(ii)
It should be equipped with a suitable margin of regulation.(iii)
It should be possible to control the shape and size of the flame.(iv)
It should function in a stable manner.(v)
It should be equipped with safety and regulation systems to ensure automatic functioning.In the case of burners for liquids, the following features are also required.(i)
Capacity to achieve correct combustion intensity, (amount of fuel per specific volume).(ii)
Capacity to operate with a minimum amount of excess air (maximum flame temperature).Burners for liquid fuels are based on two technologies: fuel vaporization and fuel atomization in small drops. This study uses a pressure atomization burner enabling regulation of the pressure between 2,000 and 3,000 kPa and the air flow through which combustion is performed. If we add the mixture percentages to these two control parameters, we have the three parameters to be controlled and optimized in combustion for generating heating using lard and diesel mixtures. Figure3 shows an operating diagram of the burner used in the facility.Figure 3
Operating diagram of a pressure atomization burner.


## 7. Experimental Facility

The generating equipment consisted of a boiler with a conventional heating burner for houses. The characteristics of the boiler and the burner are shown in Table5 [9, 10].Table 5
Characteristics of the generating equipment used in the combustion tests.
Boiler model AR/25GT (ROCA)
Boiler type
Cast iron
Calorific power
26.7 kW
Water capacity
26 liters
Approximate weight
210 kg
Maximum working temperature
110°C
Burner model KADET-TRONIC (ROCA)
GPH Nozzle
Angle
Pump pressure
Flow
Air regulation
(kPa)
(L/h)
(m3/h)
0.6
60°
800–1,600
2.3
22–40Heat dissipation is through a two-tube radiator facility with direct return. Figure4 shows the layout of the facility.Figure 4
Layout of the experimental facility.Fuel is fed into the burner from a preheated and stirred tank. An outline of the facility is shown in Figure5.Figure 5
Feed tank for the mixtures of pork fat and diesel.The facility control parameters are shown in Table6. These values should be kept within a specific interval for the test to be considered stationary, [11–13].Table 6
Control parameters in the facility.
Parameters
Units
Operating value
Error
Description
T
inlet
(°C)
90
±1
Represent the water temperature in the distributor located in the inlet circuit
T
return
(°C)
80
±1
Indicate the water temperature in the return collector through which all the water circulates prior to returning to the boiler
P
supply
(kPa)
2,500
±0.2
Supply water pressure in the main circuit, immediately prior to the distributor
P
return
(kPa)
200
±0.2
Water pressure in the return water pump located before entry into the distributor
P
supply fuel
(kPa)
500–3,000
±0.1
Supply pressure in the fuel pump
P
return fuel
(kPa)
500
±0.1
Return pressure in the fuel pump
T
fuel
(°C)
40
±0.5
Temperature of the fuel located in the tank
T
boiler
(°C)
85
±1
Water temperature when passing through the boiler
T
room
(°C)
20
±1
Room temperature


## 8. Measuring Equipment

Combustion products are measured when the installation is running under the conditions set, which is assumed to occur when it is functioning in accordance with the parameters listed in Table6. The control parameter and fuel condition measuring gauge, shown in Table 7, allow us to determine excess air, unburnt product, and smoke temperature.Table 7
Measuring equipment used in the tests, with the measuring range.
Fume analyzer (one piece of equipment)
Make and model
TESTO model 342-3
Type K thermometer
Range −40 at 1,200°C ± 0.1°C
Electrochemical O2 probe
Range 0% at 21%
CO probe (with H compensation)
Range 0 at 4000 ppm.
NO electrolytic cell probe
Range 0 at 3000 ppm
Temperature probe (Five probes)
Termopar type
K
Measuring interval
−40° at 1,000°C ± 0.5°C
Pressure probe (four probes)
Manometer type
Spiral
Supply pressure interval
100 to 4,000 kPa precision 1%
Return pressure interval
20  to 100 kPa precision 1%


## 9. Test Plan

The experimental designs enable programming of the tests to be carried out to determine how they impact the factor values (levels) on the characteristics obtained (response). Table8 shows the factors and their corresponding levels.Table 8
Tests to be carried out with regard to control parameters.
Mixture
Supply pressure (kPa)
Air flow (m3/hour)
PR-10
1,000
26.5
PR-20
1,200
36.5
PR-30
1,400
37
PR-40
PR-50
Total number of tests: 5 × 3 × 3 = 45The factors to be modified in the combustion process are(1)
percentage of lard in diesel as a percent by mass,(2)
fuel input pressure on the atomization process,(3)
air flow of the mixed combustion at the combustion head, which varies with input pressure. Given that each mixture percentage has a different mass composition, each mixture shows a different excess air index for the same air flow.The number of tests to be performed in order to maintain orthogonality coincides with the product of the number of levels of all the factors:(1)5×3×3=45tests.


## 10. Combustion Results

Data were obtained from 45 combustion processes, varying the percentage of lard mixed with diesel, with the mechanical atomization burner functioning at different input pressures and at different air flow rates. Table9 shows the combustion results for all experiments and shows areas where combustion is not possible.Table 9
Results obtained in the combustion of diesel and lard mixture.
Mixture
Injection pressure (kPa)
Air flow (m3/hour)
CO (ppm)
O2 (%)
Temp. fumes (°C)
26.5
60
12.2
236.5
1,000
36.5
1260
13.5
250.5
37
1714
13.5
255.4
26.5
22
11.5
251
PR-10
1,200
36.5
194
12.9
265.7
37
265
13
264.8
26.5
36
10.4
250.3
1,400
36.5
35
12.1
277.7
37
48
12.3
279.7
26.5
2598
13.7
192.8
1,000
36.5
—
—
—
37
—
—
—
26.5
459
13
205.9
PR-20
1,200
36.5
—
—
—
37
—
—
—
26.5
143
12.8
211.3
1,400
36.5
4197
13.9
233.4
37
3990
13.7
237.7
26.5
—
—
—
1,000
36.5
—
—
—
37
8856
11.2
168.8
26.5
808
12.4
208.8
PR-30
1,200
36.5
—
—
—
37
—
—
—
26.5
91
11.8
228.6
1,400
36.5
3896
13.4
240.5
37
—
—
—
26.5
—
—
—
1,000
36.5
—
—
—
37
—
—
—
26.5
1050
11.6
210.1
PR-40
1,200
36.5
—
—
—
37
—
—
—
26.5
—
—
—
1,400
36.5
—
—
—
37
8413
12.9
168.5
26.5
901
12.1
245.9
1,000
36.5
—
—
—
37
—
—
—
26.5
35
11.5
267.1
PR-50
1,200
36.5
46
11.5
264.3
37
12822
10.6
220.2
26.5
369
10.8
278.5
1,400
36.5
80
10.7
275.3
37
—
—
—


### 10.1. Analysis of the Results

To assess results of a combustion process, data from three aspects need to be studied: (a) efficiency of the combustion process, (b) greenhouse effect of the process, and (c) contamination caused during the process.The efficiency of the combustion processis seen as a link between the useful heat and the heat provided. In other words, the efficiency of the combustion process determines the maximum heat that can be used. To determine performance, a balance must be obtained between the mass of fluids involved in the combustion process and the energy balance.During combustion, heat loss may be caused by the following.(a)
The sensible heat of flue gases produced in combustion (gases at high temperature). This effect is known as sensible heat loss.(b)
The combustion process does not achieve full oxidation of the fuel, as a result of which the fuel constituents do not release the maximum energy. This is known as heat loss from incomplete combustion.Combustion efficiency is defined by the following expression:(2)ηcomb=LHV-Ps-PiLHV,
where Ps is sensible heat loss (kJ/kgcomb), Pi is heat loss from incomplete combustion (kJ/kgcomb), and LHV is lower heating value (kJ/kgcomb). Sensible heat loss (Ps) corresponds to the energy the combustion gases have when extracted compared to the reference conditions of the combustion process. The greater the internal energy of the flue gas (flue gas temperature), the higher these losses. They also increase with flue gas flow, which increases with excess air, as this increases the flow of flue gas, thereby transporting a greater amount of heat.Sensible heat loss is defined by the following percentage expression:(3)Ps=MHs1CpA(TH-Tref.)LHV100,MHs1 mass of dry flue gas per kilogram of fuel in (kg/kgfuel), CpA mean specific heat of flue gases at constant pressure in (kJ/kgC°), TH temperature of fuel gases at exit of heating device in C° and Tref. temperature of combustion air in C°. Heat loss from incomplete combustion (Pi) corresponds to the energy of the combustion products that have not been totally oxidized. This occurs in cases of incomplete combustion, the loss being greater the higher the amount of unburnt gas is. When total carbon oxidation does not occur, the combustion product will be CO rather than CO2:
(4)Pi=VHs1LHVCOρCO(CO)LHV,VHs1 volume of dry flue gas per kilogram of fuel in (m3/kgfuel), LHVCO is the lower heating value of CO in (kJ/kgCO), ρCO is the density of CO in (kg/m3), (CO) is the percentage by volume in the flue gas, and LHV is lower heating value of the fuel in (kJ/kgcomb) [14].Heat loss from the boiler due to heat transfer has not been considered in this study as it is the same for all the assays since the facility is steady state in all cases. This paper presents fuel performance and not generator performance.Figure6 shows the combustion efficiency results of lard mixtures and diesel. As can be seen from the Figure 6, in general terms, combustion efficiency decreases when the air inlet is more open. This is because the fat contains oxygen. As the amount of air in combustion increases, the excess air in the fumes also increases, as does sensible heat loss in the fumes. No significant variations were observed in combustion efficiency when the air flow is 26.5 m3/h, even if the percentage of lard in the mixture was increased.Figure 6
Variation in performance depending on mixture percentage, injection pressure, and air flow.The greenhouse effect of the process will only take into account CO2 emissions occurring during combustion, distinguishing between emissions from fossil fuels and biomass. No evaluation is made of the overall lifecycle of the fuel. Table 10 shows the CO2 reduction of fossil fuels when increasing the amount of lard.Table 10
CO2 emissions linked to combustion of the various mixtures of lard and diesel.
Mixture
CO2 (kg/kg of fuel)
Fossil
Non fossil
Total
PR-0
3.17
0
3.17
PR-10
2.86
0.28
3.14
PR-20
2.54
0.56
3.10
PR-30
2.22
0.84
3.06
PR-40
1.91
1.13
3.04
PR-50
1.59
1.41
3.00Pollution occurringduring the combustion process refers to emissions:(i)
unburnt gases (CO),(ii)
unburnt solids (Opacity),(iii)
nitrogen oxides (NOx).It also evidences that the increase in air flow increases the amount of unburnt fuel, allowing us to state that atomization at the nozzle is adequate for the mixtures. Figure7 shows CO emissions for a 1,400 kPa injection pressure, depending on the mixture and air flow percentage which, as can be seen, in no case exceeds the 300 ppm imposed by law for acceptable combustion.Figure 7
CO emissions depending on regulation intervals.Increased CO when there is a rise in atomization pressure may be due to a detachment of the flame in the combustion head.Lard has a higher viscosity than diesel, as seen in Table3, the combustion process in the best results being obtained for high injection pressures by improving the spraying process of lard.


## 10.1. Analysis of the Results

To assess results of a combustion process, data from three aspects need to be studied: (a) efficiency of the combustion process, (b) greenhouse effect of the process, and (c) contamination caused during the process.The efficiency of the combustion processis seen as a link between the useful heat and the heat provided. In other words, the efficiency of the combustion process determines the maximum heat that can be used. To determine performance, a balance must be obtained between the mass of fluids involved in the combustion process and the energy balance.During combustion, heat loss may be caused by the following.(a)
The sensible heat of flue gases produced in combustion (gases at high temperature). This effect is known as sensible heat loss.(b)
The combustion process does not achieve full oxidation of the fuel, as a result of which the fuel constituents do not release the maximum energy. This is known as heat loss from incomplete combustion.Combustion efficiency is defined by the following expression:(2)ηcomb=LHV-Ps-PiLHV,
where Ps is sensible heat loss (kJ/kgcomb), Pi is heat loss from incomplete combustion (kJ/kgcomb), and LHV is lower heating value (kJ/kgcomb). Sensible heat loss (Ps) corresponds to the energy the combustion gases have when extracted compared to the reference conditions of the combustion process. The greater the internal energy of the flue gas (flue gas temperature), the higher these losses. They also increase with flue gas flow, which increases with excess air, as this increases the flow of flue gas, thereby transporting a greater amount of heat.Sensible heat loss is defined by the following percentage expression:(3)Ps=MHs1CpA(TH-Tref.)LHV100,MHs1 mass of dry flue gas per kilogram of fuel in (kg/kgfuel), CpA mean specific heat of flue gases at constant pressure in (kJ/kgC°), TH temperature of fuel gases at exit of heating device in C° and Tref. temperature of combustion air in C°. Heat loss from incomplete combustion (Pi) corresponds to the energy of the combustion products that have not been totally oxidized. This occurs in cases of incomplete combustion, the loss being greater the higher the amount of unburnt gas is. When total carbon oxidation does not occur, the combustion product will be CO rather than CO2:
(4)Pi=VHs1LHVCOρCO(CO)LHV,VHs1 volume of dry flue gas per kilogram of fuel in (m3/kgfuel), LHVCO is the lower heating value of CO in (kJ/kgCO), ρCO is the density of CO in (kg/m3), (CO) is the percentage by volume in the flue gas, and LHV is lower heating value of the fuel in (kJ/kgcomb) [14].Heat loss from the boiler due to heat transfer has not been considered in this study as it is the same for all the assays since the facility is steady state in all cases. This paper presents fuel performance and not generator performance.Figure6 shows the combustion efficiency results of lard mixtures and diesel. As can be seen from the Figure 6, in general terms, combustion efficiency decreases when the air inlet is more open. This is because the fat contains oxygen. As the amount of air in combustion increases, the excess air in the fumes also increases, as does sensible heat loss in the fumes. No significant variations were observed in combustion efficiency when the air flow is 26.5 m3/h, even if the percentage of lard in the mixture was increased.Figure 6
Variation in performance depending on mixture percentage, injection pressure, and air flow.The greenhouse effect of the process will only take into account CO2 emissions occurring during combustion, distinguishing between emissions from fossil fuels and biomass. No evaluation is made of the overall lifecycle of the fuel. Table 10 shows the CO2 reduction of fossil fuels when increasing the amount of lard.Table 10
CO2 emissions linked to combustion of the various mixtures of lard and diesel.
Mixture
CO2 (kg/kg of fuel)
Fossil
Non fossil
Total
PR-0
3.17
0
3.17
PR-10
2.86
0.28
3.14
PR-20
2.54
0.56
3.10
PR-30
2.22
0.84
3.06
PR-40
1.91
1.13
3.04
PR-50
1.59
1.41
3.00Pollution occurringduring the combustion process refers to emissions:(i)
unburnt gases (CO),(ii)
unburnt solids (Opacity),(iii)
nitrogen oxides (NOx).It also evidences that the increase in air flow increases the amount of unburnt fuel, allowing us to state that atomization at the nozzle is adequate for the mixtures. Figure7 shows CO emissions for a 1,400 kPa injection pressure, depending on the mixture and air flow percentage which, as can be seen, in no case exceeds the 300 ppm imposed by law for acceptable combustion.Figure 7
CO emissions depending on regulation intervals.Increased CO when there is a rise in atomization pressure may be due to a detachment of the flame in the combustion head.Lard has a higher viscosity than diesel, as seen in Table3, the combustion process in the best results being obtained for high injection pressures by improving the spraying process of lard.


## 11. Conclusions

The mixtures of lard and diesel must not drop below 38°C since saturated fatty acids solidify and block all the combustion system filters.Mixtures of lard and diesel were successfully burned in a conventional facility, without the need for any treatment of the lard, as a result of which the two aims set out in the study have been achieved: (a) energy reuse of an abundant waste source and (b) evidencing that existing diesel facilities may be used, a preheated tank and stirring of the mixture being required.The lard used is an animal subproduct transformed by a livestock waste handling facility, as it is brought into the installation, meaning that abundant waste is available and requires no transformation.The mixing tank must preheat the mixture to a temperature of 38°C, the temperature at which the mixture offers the most homogenous characteristics. The mixture must also be stirred to avoid silting due to differences in density.Maximum performance of the mixtures requires an adjustment of the fuel parameters depending on the oxygen content of the lard and the injection pressure such that(i)
when lard is burned, air flow must be reduced, since animal lard composition contains oxygen as shown in Figure5,(ii)
an increase in pressure means that combustion air may be increased. This is because as the pressure increases, the fuel flows and therefore the required air flow increases, as can be seen in Figure5.Conventional diesel facilities offer two adjustable parameters: supply pressure and air flow. In the current work, we present the preestablished values to obtain optimum combustion.CO emissions are a key factor when considering whether combustion is acceptable under the 400 ppm maximum limit imposed by legislation.Future studies will address the use of other kinds of burners, which may use fuels with higher viscosities so as to burn lard without the need to mix with diesel.



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*Source: 912581-2012-07-24.xml*