1. Introduction

JPEE

Journal of Power and Energy Engineering

2327-588X

Scientific Research Publishing

10.4236/jpee.2022.102003

JPEE-115544

Articles

Engineering

Performance Evaluation of a Micro-Steam Turbine Powered Electric Generator under Changeable Bed and Drive Mechanisms

Rasheed

Aina

¹^*Buliaminu

Kareem

¹Adegoke

Ayodeji

¹Rasheed

Shittu

Department of Industrial & Production Engineering, The Federal University of Technology, Akure, Nigeria

21022022

1002293627, November 202125, February 2022 28, February 2022

2014

This work is licensed under the Creative Commons Attribution International License (CC BY). http://creativecommons.org/licenses/by/4.0/

Machines are growth engines of the economy; each sector of the economy achieves its demand by the use of the machine. They are installed in various establishments for the purpose of using them to perform certain functions or others. However, as a result of the kind of forces, dynamic and static loads, they transmitted to their adjoining surroundings when used, they are often mounted on supporting structures, foundations or a combination of them to achieve adequate or appropriate safe operation and stability. When a machine is operating, it is subjected to several time - varying forces and as a result of which it tends to exhibit vibrations. In such a situation or process, a certain quantity of this force is transmitted to the foundation, which could undermine the life of the foundation and also affect its performance and the operation of any other machine s on the same foundation. Hence, it makes sense to minimize this force transmission. This research aimed at developing an adjustable steel - framed structure for supporting the major components of a 5.0 kW micro- steam power unit (steam, turbine and alternator) and evaluating the performance of the unit with or without the vibration isolator when they are axially connected with flexible flange coupling or transversely connected with sets of belt s and pulley s , in succession, respectively. The results showed that reduction in the force transmitted to the supporting structure occurred when the vibration produced by the unit is isolated from its base by the use of a vibration isolator, maximum reduction of 99.95% achieved when axially coupled and 99.91% when transversely connected with belt and pulley system. The results also showed that bette r performance would be attained when the steam turbine is axially coupled to the alternator than when connected with belt and pulley; The maximum voltage of 52 V and speed of 1000 rpm at 77 dB sound level attained with coupling connection, and voltage of 20 V and speed of 752 rpm at 75 dB with belt a nd pulley connection.

Vibration Isolator Axially Coupled Transverse Couple Adjustable Bed

1. Introduction

Machines are the growth engines of the economy. Each sector of the economy fulfils its demand by the use of the machine. Machines play a vital role in the economy. The use of the machine since the past few decades has been increasing rapidly and it is not only in industrial/rural areas but also in small isolated/rural areas. When a machine is operating, it is subjected to several time-varying forces and as a result of which it tends to exhibit vibrations (period and aperiodic oscillations) [1] [2] [3]. In the process, a certain quantity of this force is transmitted to the foundation—which could undermine the life of the foundation and also affect the operation of any other machines on the same foundation [4]. Hence, it makes sense to minimize this force transmission. The demand for electrical energy has been on the increase ever since when man achieved the breakthrough and continual advancement in technology, series of energy-consuming appliances have been produced to meet the increasing standard of living of the populace/consumers [5]. In contrast, not all the units of energy generated in every kind of power plant are available for transmission and onward distribution; some are wasted by the energy-generating plants, which could not easily be accounted for. According to Chattopadhyay (2004), about 10% of the energy generated in power industries cannot be accounted for and is viewed as unaccountable energy losses. One of the factors responsible for this is the unwanted vibration of the rotating component of the unit. Vibration could cause machinery to consume excessive power, damage product quality and ultimately knock it out of service and halt plant production [3] [4]. There have been some effective attempts at reducing the vibration intensity in some of the rotating machines, like a steam turbine, but the interventions have not yet optimal results. The scope of the research would be limited to the development of an adjustable steel-frame structure, as a supporting structure for mounting a 5.0 kW∙h micro-steam turbine-alternator, prior to its mounting on a block-type concrete foundation [6]. The steel-frame supporting structure was made adjustable to facilitate adjustment of the major components of the micro-steam thermal unit in cases when they were axially coupled together with flexible flange coupling or transversely connected together with sets of belts and pulleys. The vibration investigation and analysis would be of a single degree of freedom type (1 d.o.f) as it would be limited to the isolation of the vibration transmitted by the machine (combined steam generator and alternator) to the developed adjustable steelframed supporting bed only (vibration transmitted to the concrete box-type foundation would not be considered) [7] [8]. Due to the fact of the reduction of the force transmitted to the supporting structure can be monitored/investigated at varied damping factors and frequency ratios. The selection of the vibration isolator (pads) for cushioning the vibration effect would be done based on the values of the damping factor and frequency ratio that gives the least force transmissibility factor [9].

2. Materials and Methods2.1. Overview of Properties of Existing Isolating Materials

Isolators are made from a wide variety of resilient media having diverse characteristics. Each type of isolator has characteristic properties tailored to certain specialized applications. For the purpose of making the best use of available isolators, designer needs to: understand the basic properties of each type, be familiar with the requirements for isolators for various types of equipment, and keep in mind that not all isolators can be manufactured out of any material [10]. They are usually specified by their static deflection, that is, how much they deflect when the weight of the machine is placed on them Vibro-isolators used for reducing vibration of machinery mounted on supporting structures or foundation include the cork, felt, rubber, and metal springs. In practice, isolators are not massless as assumed in classical analysis [11].

The choice of method to reduce transfer of vibration between a system and surrounding varied depending on the applications, properties of isolators, excitation frequency and condition of the machine environment. Table 1 provides a guide to the isolator type and alongside with the static deflection over given values of operating speed and isolation efficiency. While isolate a system the procedure for using this table involves reading the minimum static deflection against the system disturbing (excitation) frequency and required isolation efficiency. In this study, since the estimated isolation efficiency is R ≥ 80 % at r = 4, and disturbing speed of 1500 rpm, based on this, the choice of isolator that would be considered is rubber mounting [12].

Detailing below are the properties of the steam turbine, alternator and the isolator Mass of machine:

Turbine ( m t ): 10.0 kg

Alternator ( m a l ): 15. 0 kg

Number of buckets ( n b ): 15

Total mass of the buckets 1.0 kg

Steam consumption ( m s l ): 68 kg/hr

Table 1 The stiffness values of typical isolators

Material	Deflection (mm)	Frequency (Hz)
Cork or felt	0.1 - 0.5	50 - 25
Rubber	0.1 - 10	50 - 5
Metal springs	5 - 50	5 - 1

Source: vehicle refinement controlling noise and operation in road vehicles, Harrison (2004).

Balance quality factor (Q) G2.5

Dimensions of the isolator (each) 100 mm × 50 mm × 25 mm

Adjustable bed dimensions: Length of 100 mm, breadth or width 50 mm and height of 25 mm

Unbalanced rotating mass ( m u ): 2.133 kg

Non-rotating mass ( M − m u ) 23.9997 kg

F e 87.71611 N

Number of mounts ( n p ) 4

Stiffness of the vibration isolator 141.91 N/MM

2.2. Experimental ProcedureExperiment Data and Analysis

The experimental data obtained in the course of the experimentation are as detailed in Table 2 and Table 3 below. Table 2 shows the data recorded with the attached instrumentations when the two main components (steam turbine and alternator) test rig were connected transversely with belt and pulley system whilst Table 3 shows the experimental data when they are axially connected with flexible flange coupling. Figure 1 shows both axial and transverse assembly form of the system. The axial connection is with the aid of coupling while transverse is with bell and pulley [13] [14].

3. Results and Discussions

This study aimed at evaluating the contributory effect of vibration isolator on

Table 2 Experimental data obtained with the test rig connected together using belt and pulley system

s/n	With test rig mounted on vibration isolator					Test rig not mounted on vibration isolator
s/n	S (mm)	v (mm/s)	a (mm/s²)	V (V)	N (rpm)	S (mm)	v (mm/s)	a (mm/s²)	V (V)	N (rpm)
1	2.7	63.0	1.4	20.0	752	1.2	75	0.9	10.0	656
2	1.7	47.0	1.1	5.0	549	1.0	55	0.6	8.0	599

Table 3 Experimental data obtained with the test rig connected together using Flange coupling system

s/n	With test rig mounted on vibration isolator					Test rig not mounted on vibration isolator
s/n	S (mm)	v (mm/s)	a (mm/s²)	V (V)	N (rpm)	S (mm)	vel (mm/s)	a (mm/s²)	V (V)	N (rpm)
1	1.33	43.1	12.2	52	1000	1.175	43.4	12.37	52	1000
2	1.192	43.3	17.7	52	1000	1.122	44.1	18.2	52	1000
Displacement	Vel. (mm/s)	Mmls Acc	Voltap	8 pm speed	Displacement	vel	acc	Volt	Speed
940/3/2.7	6.3	1.4	20.0	752	1.2	7.5	0.9	10v	656
17	4.4	1.1	50	549	10	5.5	0.6
1.263	41.8	11.1	560	950	1.211	4.5		53	1030
1.33	43.1	12.2	5.2	1000	1.175	43.4		52	1000
1.193	43.3	17.7	5.2	1000	1.121	43.1		52	1000

the performance of the major components of micro-steam thermal unit mounted on an adjustable steel framed bed before mounted on a concrete floor [1] [2].

This section presents the results and discussions of the analysis of the experimental data obtained in the course of the experimentations, when the steam turbine and alternator were axially connected with a flange coupling or transversely connected with sets of belt and pulley systems and when they were supported at their bases with vibration isolator before mounting on the developed adjustable steel framed bed and when mounted directly on the steel frame without the insertion of vibration isolator, in succession, respectively [3].

For the purpose of evaluating the effect of vibration isolator on the performance of the steam turbine-alternator unit, the parameters utilized for comparing the performance are: the ratios of the damped frequency to the undamped frequency of the test rig when with/without vibration isolators and vibration isolator reduction efficiency [4].

Table 4 presents results of the Performance of the test rig when mounted on the developed adjustable steel-framed bed with/without insertion of vibration isolator with respect to the ratio of the damped frequency to the undamped frequency and vibration reduction efficiency [5].

Tables 2-4 present a detail of comparison of the observed experimental when the combined steam-turbine-alternator was mounted on the developed adjustable bed as shown in Figure 1, with vibration isolator inserted and when not inserted between them and the bed.

From Table 4, it was observed that the resistance offered by the isolator when used to cushion, the effect of vibration of the machine against the supporting adjustable bed, is more than when the machine is directly mounted on the supporting bed [6] [7]. The resistance offered with the use of sets of belt and pulley systems as a power transmission is greater than when a flange coupling is used; the reason is that with the use of belt and pulley, both torsional and bending moments are experienced by the machine as the steam turbine shaft and alternator

Table 4 Summary of the calculated results with reference to the experimental data obtained

s/n	Particular	Equation	Calculated values (belt and pulley system)		Calculated values (coupling system)
s/n	Particular	Equation	With isolator	Without isolator	With isolator	Without isolator
1	Ratio of consecutive amplitude	x 1 x n + 1	1.588235294	1.20	1.114836547	1.048171276
	Logarithmic decrement	log e [ x 1 x n + 1 ] = a	4.895102885	3.320116923	3.049069757	2.852430037
	Operating frequency (rad/s)	ω = 2 π N 60	50π	50π	50π	50π
	Natural frequency (rad/s)	ω n = ω f r	25π	12.5π	12.5π	12,5π
	Damping frequency (rad/s)	ω d = ω n 2 − a 2	78.38711712	39.12930502	39.15135836	39.16617585
	Isolator resistance to vibration (Ns/m)	c = 2 ⋅ a ⋅ m m	244.7551443	166.0058462	152.4534879	142.6215019
	Damped-undamped frequency ratio	ω d ω n = f d / u	0.4990278866	0.9964195702	0.9969811538	0.9973584782
	Periodic time (second)	t p = 2 π ω d	0.1612577416	0.1605749273	0.1604844779	0.1604237629
	Static deflection (mm)	m g k i s = δ s t	1.728208019		1.728208019
	Transmitted force reduction (%)	{ ⌊ ( 2 π N o 60 ) 2 m k i s ⌋ − 2 ⌊ ( 2 π N o 60 ) 2 m k i s ⌋ − 1 } = R	99.90838315		99.94821063
	Force transmitivity (%)	1 − R = T f	99.82796470

shaft are transversely positioned to each other, but when a flexible flange coupling is used as the power transmission system, only the two components of the micro power plant is subjected to only torsional moment.

The results also showed that the use of vibration isolator reduction the quantity of the force transmitted to the supporting bed is reduced, with the maximum reduction achieved when the unit was axially connected with coupling than when transversely connected with sets of belt and pulley systems [8].

However, maximum power was generated with the use of flange coupling than when the machine was connected with belt and pulley system; this could be attributed to the fact that: with the use of coupling the two components (steam turbine and alternator) worked same speed ratio of unity (1.0) or speed of 1500 rpm, hence little or no opposing force was offered by the alternator to the motion of the steam turbine, but with the use of belt and pulley system the speed ratio of turbine to alternator is 1:3 (or speed of 1500 rpm to 4500 rpm) a value outside the range of e design property of the manufacturer design and working capacity of the alternator hence the opposing force offered by the alternator was higher than with coupling and this accounted for reduction in the power generated when belt and pulley was utilized as the power transmission system [9].

4. Conclusions

The primary objective of this study was the performance assessment of micro-steam turbine-alternator mounted on the developed adjustable steel-framed bed as shown in Figure 1 when their shafts were either axially connected together with flexible flange coupling or transversely with sets of belt and pulley power transmission. Also, the evaluation was done, in succession, when these components were isolated from the bed by the insertion of vibration isolator between their bases and developed bed and when they were mounted directly on the bed without the use of vibration isolator respectively. To achieve this aim, experimental data were obtained, with the aid of the attached instrumentations, when they were connected with coupling, or belt and pulley system and isolated from the developed bed with vibration isolator, and when connected with any of these two power transmission systems in succession and mounted directly on the developed bed without the use of vibration isolator respectively [10] [11]. The results showed that the performance of the components of the micro steam thermal unit is not only being influenced by the kinds of power transmission systems used to connect them together, but also whether the vibration produced by them is isolated/cushioned or transmitted directly to their supporting structures. Based on this, the following conclusions have been made from the experimental investigation:

1) Reduction in the force transmitted to the supporting bed was when the two components were isolated from their supporting structures with the insertion of a vibration isolator [12];

2) Better performance was achieved when the components were axially connected with coupling than transversely with sets of belt and pulley systems. The maximum voltage of 52 V and speed of 1000 rpm at 77 dB sound level attained with coupling connection, and voltage of 20 V and speed of 752 rpm at 75 dB with belt and pulley connection.

Acknowledgments

We hereby acknowledged Quintas Renewable Energies Solution Limited for allowing this experimentation to be done in their companies and at the same time Professor B. Kareem (Mechanical Engineering Department), Federal University of Technology Akure for supporting this research to come to reality.

Conflicts of Interest

The authors declare no conflicts of interest regarding the publication of this paper.

Cite this paper

Aina, R., Kareem, B., Ayodeji, A. and Shittu, R. (2022) Performance Evaluation of a Micro-Steam Turbine Powered Electric Generator under Changeable Bed and Drive Mechanisms. Journal of Power and Energy Engineering, 10, 29-36. https://doi.org/10.4236/jpee.2022.102003

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