# Dimensionless Analysis on the Characteristics of Pneumatic Booster Valve with Energy Recovery

Authors: Fan Yang; Kotaro Tadano; Gangyan Li; Toshiharu Kagawa
Journal: Mathematical Problems in Engineering
 (2016)

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## Abstract

Factories are increasingly reducing their air supply pressures in order to save energy. Hence, there is a growing demand for pneumatic booster valves to overcome the local pressure deficits in modern pneumatic systems. To further improve energy efficiency, a new type of booster valve with energy recovery (BVER) is proposed. The BVER principle is presented in detail, and a dimensionless mathematical model is established based on flow rate, gas state, and energy conservation. The mathematics model was transformed into a dimensionless model by accurately selecting the reference values. Subsequently the dimensionless characteristics of BVER were found. BVER energy efficiency is calculated based on air power. The boost ratio is found to be mainly affected by the operational parameters. Among the structural ones, the recovery/boost chamber area ratio and the sonic conductance of the chambers are the most influential. The boost ratio improves by 15%–25% compared to that of a booster valve without an energy recovery chamber. The efficiency increases by 5%–10% depending on the supply pressure. A mathematical model is validated by experiment, and this research provides a reference for booster valve optimisation and energy saving.


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## Body

## 1. Introduction

Pneumatic systems are widely used because of their low cost, high reliability, simplicity, and ease of maintenance. They typically account for 10%–20% of most national industrial electricity consumption [1]. Growing economic and environmental concerns indicate that pneumatic efficiency is the major constraint on system development, and improving them is now a major concern. Previous research has shown that decreasing the supply pressure by 0.1 MPa leads to an 8% drop in energy consumption [2]. Many factories save energy in this way. Consequently, they have insufficient pneumatic pressure to drive heavy loads or operate high-pressure equipment. Thus, more efficient pneumatic booster valves are being sought by industries to locally increase the pressures.Compressed-air energy savings can be made by minimising leaks and pressure loss and by optimising the system [3]. In general, the basic way to enhance system efficiency is to decrease the energy input and increase the energy output. For the former, reducing the supply pressure has already been mentioned. High-pressure ratio in a booster valve indicates that the supply pressure can be lower for the same pressure output. An asymmetric booster valve has been proposed [4, 5] but its high boost ratio came at the expense of flow rate as well as too much pressurised exhaust air. The expansion energy-used (EEU) booster valve has been proposed for reducing air supply [6, 7]. This involves the air being cut off before the piston reaches the end of its stroke and using the expansion energy of the air for the remainder. However, this energy becomes insufficient when the supply pressure is lowered. To increase the energy output, recovering energy and minimising friction are widely adopted in driving cylinders [8–10]. The energy is recovered and stored in a tank for secondary use [8]. The discharge chamber of the cylinder can be linked with the charge one by differential driven [9, 10]. This helps to enhance the efficiency but at the expense of the steadiness of piston’s motion. Given that the return stroke of the cylinder is useless, an extra two-way solenoid value can be used to cut off the air supply to save energy [11]. The problems of previous studies can be summarised as follows: It is a waste to have pressurised exhaust air. The pressure ratio is limited for a symmetric booster valve. Further, more energy used in the cylinder would be recovered if pressure fluctuations were reduced.To solve these problems, a new type of booster valve with energy recovery (BVER; patent pending [12]) is proposed here. Its main performance characteristics are studied systematically using a dimensionless method [13–15] based on boost pressure ratio, flow rate, pressure fluctuation, and energy efficiency, the results from which provide the basis for booster-valve optimisation.


## 2. BVER Principles

In a traditional booster valve, compressed air in the drive chamber exhausts directly to the atmosphere, causing significant energy loss over time. In order to recover some of the lost energy, a BVER has two recovery chambers but the discharge chamber is not linked directly with the charge one. This helps to recover energy that flows into the recovery chamber instead of the driver one to avoid large pressure fluctuations. A schematic diagram of a BVER is shown in Figure1. It comprises two boost chambers, two recovery chambers, four check valves, a regulator, a magnetic switch, and a two-position seven-port solenoid valve. The structure of the solenoid valve is shown in Figure 2, which helps to improve the integrated level of the BVER.Figure 1
Booster valve with energy recovery (BVER) structure: (1) drive chamber A, (2) piston, (3) boost chamber A, (4) air source, (5) recovery chamber A, (6) recovery chamber B, (7) check valve, (8) boost chamber B, (9) piston rod, (10) drive chamber B, (11) magnetic switch, (12) magnetic ring, (13) two-position seven-port solenoid valve, (14) regulator, and (15) power source.Figure 2
Two-position seven-port solenoid valve.The piston is located initially at the left and moves to the right as shown in Figure1. The solenoid valve is in the state shown in Figure 2, in which one branch of the air source connects with booster chamber B while the other connects with driver chamber A through the regulator and the solenoid valve. As air flows into these two chambers, its pressure rises and generates thrust to drive the piston to the right, thus reducing the volume of boost chamber A. As a result, the pressure in that chamber increases until it is higher than that in the tank. The check valve then opens and the boost chamber air begins to exhaust to the tank. Meanwhile, as the piston moves to the right, the air in drive chamber B is recycled by recovery chamber A and is reused by pushing the piston, while the low-pressure air in recovery chamber B discharges to the atmosphere. When the piston reaches the right end, a magnetic signal is generated to change the solenoid-valve state. The discharge and charge chambers exchange roles so the piston can move in reverse and discharge high-pressure air twice each cycle. Setting the regulator (14 in Figure 2) to a different opening changes the boost ratio. When the output pressure is sufficiently high, it drives the regulator to decrease the opening; overpressure protection limits the out pressure to protect the system.The air in the drive chamber flows into the recovery one through the solenoid valve rather than exhausting to the atmosphere. Its energy is reused in pushing the piston, which helps to increase the boost ratio and energy efficiency by recovering the high-pressure gas.


## 3. Mathematical Model and Nondimensionalization

In order to analyse the BVER, the following assumptions were made:(i)
The air in the system is an ideal gas that is governed by the ideal gas law.(ii)
The system is leak-free, for example, piston and fittings.(iii)
The valve chambers are initially at atmospheric temperature, and the air source is equal to atmosphere pressure.(iv)
The dead volume of each chamber end can be neglected, and the volumes of the in-port are the same.


### 3.1. Mathematical Model of BVER

The BVER comprises six chambers in which the pressure, temperature, and volume vary with piston motion. Hence, its characteristics are described in principle by >20 equations. However, three chambers are discharging while the rest are charging during each stroke. The charge/discharge chambers have the same control equations but the structural parameters are different. Thus, the BVER is modelled mathematically in relation to its charge/discharge chambers. These models are then transferred to stand Simulink subsystems whose parameters can be redefined in simulation. This is an effective way of enhancing the modelling efficiency.


#### 3.1.1. Gas State Equation

The chamber pressure, temperature, and volume satisfy the ideal gas law:(1)pV=mRθ.The mass flux in the chambers is equal to that into or out of each chamber, so(2)±G=dmdt.Differentiating (1) with respect to time, we have pdV/dt=pSu since the variable chamber volume is equal to Sx. Hence, the pressures in the discharge and charge chambers are governed, respectively, by(3)Vddpddt=-GdRθd+pdSdu+pdVdθddθddt,(4)Vcdpcdt=GcRθc-pcScu+pcVcθcdθcdt.


#### 3.1.2. Energy Conservation Equation

Given that each BVER chamber is a variable system and the system as a whole satisfies energy conservation (i.e., it is leak-free), the energy changes in the system can be expressed as(5)dU=hdm+dW+dQ,where dU is the internal energy change, hdm is the enthalpy in or out of the system, dW is the work done on the system, and dQ is the heat transfer from the cylinder wall.A similar approach is applied to the gas state equation, leading to the temperature in each chamber being governed by(6)mdcvdθddt=-RθdGd+pdSdu+hShdθa-θd,mccvdθcdt=cvGcθa-θc+RθaGc-pcScu+hShcθa-θc,where Shd and Shc are the heat exchange areas. These are always changing as the piston moves so they are taken to be half the inner cylinder area to facilitate modelling.


#### 3.1.3. Flow-Rate Equation

The main pneumatic flow-rate parameters are the sonic conductance and critical pressure ratio defined by ISO6358. The flow rate depends on the upstream pressure, temperature, and pressure ratio, while the mass flux in or out of each chamber can be expressed as(7)G=Cp1ρ0θ0θ1φp,where φp is a function of the pressure ratio and determines whether the flow is a chock or subsonic one:(8)φp=1p2p1≤b1-p2/p1-b1-b20.5b<p2p1≤1.


#### 3.1.4. Piston Motion Equation

The pressure and force distributions on the piston are illustrated in Figure3 for the piston moving from left to right.Figure 3
Piston force diagram.The piston equation of motion can be determined by Newton’s second law:(9)Mdudt=pda-pdbSda-pba-pbbSba+pra-prbSra-Ff,x≠0,L0,x=0,L.The friction forceFf on the piston can be represented by a mixed friction model comprising Coulomb and viscous frictions [16]:(10)Ff=cu+Fsfu=0Fdfsign⁡uu≠0,where Fsf is the maximum static friction and Fdf is the dynamic friction whose direction depends on the piston velocity.


#### 3.1.5. Pressure in the Tank

Booster valves are always used with tank to decrease pressure fluctuations; the opening of the BVER check valve depends on the tank pressure. Pressure feedback exists between the BVER and the tank, so an associated BVER/tank model helps improve the accuracy and reflect the real system output. The tank heat exchange area is sufficiently large for adequate heat exchange with the surroundings. It can be treated as an isothermal chamber with constant temperature, giving the tank pressure response as(11)dptdt=RθaVtGin-Gout,where Gin is the air flow into the tank dependent on the BVER/tank pressure differential. The flow rate Gout through the restriction is considered to be the real output of the booster system that is supplied directly to downstream devices.


### 3.2. Dimensionless Model of BVER

Dimensionless analysis can simplify problems in which we want to know the influence of each parameter. Each parameter in the model becomes dimensionless, indicating that dimensions have no effect on the results, which in turn become simpler. In other words, if we know the value of a parameter relative to its reference value, we can understand its performance irrespective of the type of BVER.


#### 3.2.1. Dimensionless Parameters

To nondimensionalise the equations derived in Section2, 11 reference values were determined as shown in Table 1. These were chosen as follows:(i)
The parameter value is a known quantity, for example,ps, θa.(ii)
The parameter value is relatively large or can be easily decreased, for example,L, Cda.(iii)
The parameter can be derived directly from other reference values, for example,Vda, G0, and u0.Table 1
Dimensionless parameters.
Parameters Reference Dimensionless Pressure p s Supply pressure p ∗ = p p s  Temperature θ a Atmospheric temperature θ ∗ = θ θ a  Volume V d a = S d a L Volume of drive chamber A V ∗ = V V d a  Sonic conductance C d a Sonic conductance of drive chamber A C ∗ = C C d a  Piston area S d a Piston area of drive chamber A S ∗ = S S d a  Mass flow rate G 0 = C d a p s ρ 0 θ 0 θ a Flow rate under reference pressure, temperature, and sonic conductance G ∗ = G G 0  Velocity u 0 = R C d a ρ 0 S d a θ a θ 0 Piston velocity under reference flow rate u ∗ = u u 0  Stroke L Piston stroke x ∗ = x L  Time T p = L u 0 Motion time of piston underu0 t ∗ = t T P  Energy E 0 = p s V d a Energy under reference pressure and volume E ∗ = E E 0 Air power P 0 = E 0 T p Air power with reference energy and time P ∗ = P P 0


#### 3.2.2. Dimensionless Gas State Equations

Substituting the reference values into (3) and (4), the dimensionless gas state equations are given by (12)Vd∗dpd∗dt∗=-Gd∗θd∗+pd∗Sd∗u∗+pd∗Vd∗θd∗dθd∗dt∗,Vc∗dpc∗dt∗=Gc∗θc∗-pc∗Sc∗u∗+pc∗Vc∗θc∗dθc∗dt∗.


#### 3.2.3. Dimensionless Energy Conservation Equations

Similarly, converting the energy conservation equations to dimensionless quantities gives(13)dθd∗dt∗=Gd∗θd∗2pd∗Vd∗1-κ+θd∗Sd∗u∗Vd∗κ-1+Ka1-θd∗,dθc∗dt∗=Gc∗θc∗pc∗Vc∗κ-θc∗-θc∗Sc∗u∗Vc∗κ-1+Ka1-θc∗,where Ka is the Kagawa coefficient [17] reflecting the rapidity of heat exchange between the inner cylinder and its surroundings. This can be defined as (14)Ka=TpTh=Shhθ∗cvG0p∗.


#### 3.2.4. Dimensionless Flow-Rate Equation

When the dimensionless pressure ratio of the restriction is less than the critical pressureb (i.e., p2∗/p1∗≤b), the dimensionless flow rate is(15)G∗=Ci∗p1∗1θ1∗.When b<p2∗/p1∗≤1, the dimensionless flow rate is(16)G∗=Ci∗p1∗1θ1∗1-p2∗/p1∗-b1-b20.5.


#### 3.2.5. Dimensionless Equation of Motion

The natural periodTf and the inertia J were introduced to simply (9) [18]. The dimensionless equation of motion can then be obtained by dividing (9) by Mu0/Tp. The natural period of the BVER is(17)Tf=2πMLpsSdaand the inertia coefficient is (18)J=SdapsLMu02.Substituting (17) and (18) into (9), the dimensionless equation of motion becomes(19)du∗dt∗=2πTf∗2pda∗-pdb∗-pba∗-pbb∗Sba∗+pra∗-prb∗Sra∗-Ff∗,x∗≠0,10,x∗=0,1.The dimensionless friction force and other parameters are given as follows:(20)Ff∗=c∗u∗+Fsf∗u∗=0Fdf∗sign⁡uu∗≠0,c∗=cu0psSda,Fsf∗=FsfpsSda,Fdf∗=FdfpsSda.


#### 3.2.6. Dimensionless Pressure Response in Tank

With the reference values in Table1, (11) can be made dimensionless as (21)dpt∗dt∗=Gin∗-Gout∗Vt∗.


## 3.1. Mathematical Model of BVER

The BVER comprises six chambers in which the pressure, temperature, and volume vary with piston motion. Hence, its characteristics are described in principle by >20 equations. However, three chambers are discharging while the rest are charging during each stroke. The charge/discharge chambers have the same control equations but the structural parameters are different. Thus, the BVER is modelled mathematically in relation to its charge/discharge chambers. These models are then transferred to stand Simulink subsystems whose parameters can be redefined in simulation. This is an effective way of enhancing the modelling efficiency.


### 3.1.1. Gas State Equation

The chamber pressure, temperature, and volume satisfy the ideal gas law:(1)pV=mRθ.The mass flux in the chambers is equal to that into or out of each chamber, so(2)±G=dmdt.Differentiating (1) with respect to time, we have pdV/dt=pSu since the variable chamber volume is equal to Sx. Hence, the pressures in the discharge and charge chambers are governed, respectively, by(3)Vddpddt=-GdRθd+pdSdu+pdVdθddθddt,(4)Vcdpcdt=GcRθc-pcScu+pcVcθcdθcdt.


### 3.1.2. Energy Conservation Equation

Given that each BVER chamber is a variable system and the system as a whole satisfies energy conservation (i.e., it is leak-free), the energy changes in the system can be expressed as(5)dU=hdm+dW+dQ,where dU is the internal energy change, hdm is the enthalpy in or out of the system, dW is the work done on the system, and dQ is the heat transfer from the cylinder wall.A similar approach is applied to the gas state equation, leading to the temperature in each chamber being governed by(6)mdcvdθddt=-RθdGd+pdSdu+hShdθa-θd,mccvdθcdt=cvGcθa-θc+RθaGc-pcScu+hShcθa-θc,where Shd and Shc are the heat exchange areas. These are always changing as the piston moves so they are taken to be half the inner cylinder area to facilitate modelling.


### 3.1.3. Flow-Rate Equation

The main pneumatic flow-rate parameters are the sonic conductance and critical pressure ratio defined by ISO6358. The flow rate depends on the upstream pressure, temperature, and pressure ratio, while the mass flux in or out of each chamber can be expressed as(7)G=Cp1ρ0θ0θ1φp,where φp is a function of the pressure ratio and determines whether the flow is a chock or subsonic one:(8)φp=1p2p1≤b1-p2/p1-b1-b20.5b<p2p1≤1.


### 3.1.4. Piston Motion Equation

The pressure and force distributions on the piston are illustrated in Figure3 for the piston moving from left to right.Figure 3
Piston force diagram.The piston equation of motion can be determined by Newton’s second law:(9)Mdudt=pda-pdbSda-pba-pbbSba+pra-prbSra-Ff,x≠0,L0,x=0,L.The friction forceFf on the piston can be represented by a mixed friction model comprising Coulomb and viscous frictions [16]:(10)Ff=cu+Fsfu=0Fdfsign⁡uu≠0,where Fsf is the maximum static friction and Fdf is the dynamic friction whose direction depends on the piston velocity.


### 3.1.5. Pressure in the Tank

Booster valves are always used with tank to decrease pressure fluctuations; the opening of the BVER check valve depends on the tank pressure. Pressure feedback exists between the BVER and the tank, so an associated BVER/tank model helps improve the accuracy and reflect the real system output. The tank heat exchange area is sufficiently large for adequate heat exchange with the surroundings. It can be treated as an isothermal chamber with constant temperature, giving the tank pressure response as(11)dptdt=RθaVtGin-Gout,where Gin is the air flow into the tank dependent on the BVER/tank pressure differential. The flow rate Gout through the restriction is considered to be the real output of the booster system that is supplied directly to downstream devices.


## 3.1.1. Gas State Equation

The chamber pressure, temperature, and volume satisfy the ideal gas law:(1)pV=mRθ.The mass flux in the chambers is equal to that into or out of each chamber, so(2)±G=dmdt.Differentiating (1) with respect to time, we have pdV/dt=pSu since the variable chamber volume is equal to Sx. Hence, the pressures in the discharge and charge chambers are governed, respectively, by(3)Vddpddt=-GdRθd+pdSdu+pdVdθddθddt,(4)Vcdpcdt=GcRθc-pcScu+pcVcθcdθcdt.


## 3.1.2. Energy Conservation Equation

Given that each BVER chamber is a variable system and the system as a whole satisfies energy conservation (i.e., it is leak-free), the energy changes in the system can be expressed as(5)dU=hdm+dW+dQ,where dU is the internal energy change, hdm is the enthalpy in or out of the system, dW is the work done on the system, and dQ is the heat transfer from the cylinder wall.A similar approach is applied to the gas state equation, leading to the temperature in each chamber being governed by(6)mdcvdθddt=-RθdGd+pdSdu+hShdθa-θd,mccvdθcdt=cvGcθa-θc+RθaGc-pcScu+hShcθa-θc,where Shd and Shc are the heat exchange areas. These are always changing as the piston moves so they are taken to be half the inner cylinder area to facilitate modelling.


## 3.1.3. Flow-Rate Equation

The main pneumatic flow-rate parameters are the sonic conductance and critical pressure ratio defined by ISO6358. The flow rate depends on the upstream pressure, temperature, and pressure ratio, while the mass flux in or out of each chamber can be expressed as(7)G=Cp1ρ0θ0θ1φp,where φp is a function of the pressure ratio and determines whether the flow is a chock or subsonic one:(8)φp=1p2p1≤b1-p2/p1-b1-b20.5b<p2p1≤1.


## 3.1.4. Piston Motion Equation

The pressure and force distributions on the piston are illustrated in Figure3 for the piston moving from left to right.Figure 3
Piston force diagram.The piston equation of motion can be determined by Newton’s second law:(9)Mdudt=pda-pdbSda-pba-pbbSba+pra-prbSra-Ff,x≠0,L0,x=0,L.The friction forceFf on the piston can be represented by a mixed friction model comprising Coulomb and viscous frictions [16]:(10)Ff=cu+Fsfu=0Fdfsign⁡uu≠0,where Fsf is the maximum static friction and Fdf is the dynamic friction whose direction depends on the piston velocity.


## 3.1.5. Pressure in the Tank

Booster valves are always used with tank to decrease pressure fluctuations; the opening of the BVER check valve depends on the tank pressure. Pressure feedback exists between the BVER and the tank, so an associated BVER/tank model helps improve the accuracy and reflect the real system output. The tank heat exchange area is sufficiently large for adequate heat exchange with the surroundings. It can be treated as an isothermal chamber with constant temperature, giving the tank pressure response as(11)dptdt=RθaVtGin-Gout,where Gin is the air flow into the tank dependent on the BVER/tank pressure differential. The flow rate Gout through the restriction is considered to be the real output of the booster system that is supplied directly to downstream devices.


## 3.2. Dimensionless Model of BVER

Dimensionless analysis can simplify problems in which we want to know the influence of each parameter. Each parameter in the model becomes dimensionless, indicating that dimensions have no effect on the results, which in turn become simpler. In other words, if we know the value of a parameter relative to its reference value, we can understand its performance irrespective of the type of BVER.


### 3.2.1. Dimensionless Parameters

To nondimensionalise the equations derived in Section2, 11 reference values were determined as shown in Table 1. These were chosen as follows:(i)
The parameter value is a known quantity, for example,ps, θa.(ii)
The parameter value is relatively large or can be easily decreased, for example,L, Cda.(iii)
The parameter can be derived directly from other reference values, for example,Vda, G0, and u0.Table 1
Dimensionless parameters.
Parameters Reference Dimensionless Pressure p s Supply pressure p ∗ = p p s  Temperature θ a Atmospheric temperature θ ∗ = θ θ a  Volume V d a = S d a L Volume of drive chamber A V ∗ = V V d a  Sonic conductance C d a Sonic conductance of drive chamber A C ∗ = C C d a  Piston area S d a Piston area of drive chamber A S ∗ = S S d a  Mass flow rate G 0 = C d a p s ρ 0 θ 0 θ a Flow rate under reference pressure, temperature, and sonic conductance G ∗ = G G 0  Velocity u 0 = R C d a ρ 0 S d a θ a θ 0 Piston velocity under reference flow rate u ∗ = u u 0  Stroke L Piston stroke x ∗ = x L  Time T p = L u 0 Motion time of piston underu0 t ∗ = t T P  Energy E 0 = p s V d a Energy under reference pressure and volume E ∗ = E E 0 Air power P 0 = E 0 T p Air power with reference energy and time P ∗ = P P 0


### 3.2.2. Dimensionless Gas State Equations

Substituting the reference values into (3) and (4), the dimensionless gas state equations are given by (12)Vd∗dpd∗dt∗=-Gd∗θd∗+pd∗Sd∗u∗+pd∗Vd∗θd∗dθd∗dt∗,Vc∗dpc∗dt∗=Gc∗θc∗-pc∗Sc∗u∗+pc∗Vc∗θc∗dθc∗dt∗.


### 3.2.3. Dimensionless Energy Conservation Equations

Similarly, converting the energy conservation equations to dimensionless quantities gives(13)dθd∗dt∗=Gd∗θd∗2pd∗Vd∗1-κ+θd∗Sd∗u∗Vd∗κ-1+Ka1-θd∗,dθc∗dt∗=Gc∗θc∗pc∗Vc∗κ-θc∗-θc∗Sc∗u∗Vc∗κ-1+Ka1-θc∗,where Ka is the Kagawa coefficient [17] reflecting the rapidity of heat exchange between the inner cylinder and its surroundings. This can be defined as (14)Ka=TpTh=Shhθ∗cvG0p∗.


### 3.2.4. Dimensionless Flow-Rate Equation

When the dimensionless pressure ratio of the restriction is less than the critical pressureb (i.e., p2∗/p1∗≤b), the dimensionless flow rate is(15)G∗=Ci∗p1∗1θ1∗.When b<p2∗/p1∗≤1, the dimensionless flow rate is(16)G∗=Ci∗p1∗1θ1∗1-p2∗/p1∗-b1-b20.5.


### 3.2.5. Dimensionless Equation of Motion

The natural periodTf and the inertia J were introduced to simply (9) [18]. The dimensionless equation of motion can then be obtained by dividing (9) by Mu0/Tp. The natural period of the BVER is(17)Tf=2πMLpsSdaand the inertia coefficient is (18)J=SdapsLMu02.Substituting (17) and (18) into (9), the dimensionless equation of motion becomes(19)du∗dt∗=2πTf∗2pda∗-pdb∗-pba∗-pbb∗Sba∗+pra∗-prb∗Sra∗-Ff∗,x∗≠0,10,x∗=0,1.The dimensionless friction force and other parameters are given as follows:(20)Ff∗=c∗u∗+Fsf∗u∗=0Fdf∗sign⁡uu∗≠0,c∗=cu0psSda,Fsf∗=FsfpsSda,Fdf∗=FdfpsSda.


### 3.2.6. Dimensionless Pressure Response in Tank

With the reference values in Table1, (11) can be made dimensionless as (21)dpt∗dt∗=Gin∗-Gout∗Vt∗.


## 3.2.1. Dimensionless Parameters

To nondimensionalise the equations derived in Section2, 11 reference values were determined as shown in Table 1. These were chosen as follows:(i)
The parameter value is a known quantity, for example,ps, θa.(ii)
The parameter value is relatively large or can be easily decreased, for example,L, Cda.(iii)
The parameter can be derived directly from other reference values, for example,Vda, G0, and u0.Table 1
Dimensionless parameters.
Parameters Reference Dimensionless Pressure p s Supply pressure p ∗ = p p s  Temperature θ a Atmospheric temperature θ ∗ = θ θ a  Volume V d a = S d a L Volume of drive chamber A V ∗ = V V d a  Sonic conductance C d a Sonic conductance of drive chamber A C ∗ = C C d a  Piston area S d a Piston area of drive chamber A S ∗ = S S d a  Mass flow rate G 0 = C d a p s ρ 0 θ 0 θ a Flow rate under reference pressure, temperature, and sonic conductance G ∗ = G G 0  Velocity u 0 = R C d a ρ 0 S d a θ a θ 0 Piston velocity under reference flow rate u ∗ = u u 0  Stroke L Piston stroke x ∗ = x L  Time T p = L u 0 Motion time of piston underu0 t ∗ = t T P  Energy E 0 = p s V d a Energy under reference pressure and volume E ∗ = E E 0 Air power P 0 = E 0 T p Air power with reference energy and time P ∗ = P P 0


## 3.2.2. Dimensionless Gas State Equations

Substituting the reference values into (3) and (4), the dimensionless gas state equations are given by (12)Vd∗dpd∗dt∗=-Gd∗θd∗+pd∗Sd∗u∗+pd∗Vd∗θd∗dθd∗dt∗,Vc∗dpc∗dt∗=Gc∗θc∗-pc∗Sc∗u∗+pc∗Vc∗θc∗dθc∗dt∗.


## 3.2.3. Dimensionless Energy Conservation Equations

Similarly, converting the energy conservation equations to dimensionless quantities gives(13)dθd∗dt∗=Gd∗θd∗2pd∗Vd∗1-κ+θd∗Sd∗u∗Vd∗κ-1+Ka1-θd∗,dθc∗dt∗=Gc∗θc∗pc∗Vc∗κ-θc∗-θc∗Sc∗u∗Vc∗κ-1+Ka1-θc∗,where Ka is the Kagawa coefficient [17] reflecting the rapidity of heat exchange between the inner cylinder and its surroundings. This can be defined as (14)Ka=TpTh=Shhθ∗cvG0p∗.


## 3.2.4. Dimensionless Flow-Rate Equation

When the dimensionless pressure ratio of the restriction is less than the critical pressureb (i.e., p2∗/p1∗≤b), the dimensionless flow rate is(15)G∗=Ci∗p1∗1θ1∗.When b<p2∗/p1∗≤1, the dimensionless flow rate is(16)G∗=Ci∗p1∗1θ1∗1-p2∗/p1∗-b1-b20.5.


## 3.2.5. Dimensionless Equation of Motion

The natural periodTf and the inertia J were introduced to simply (9) [18]. The dimensionless equation of motion can then be obtained by dividing (9) by Mu0/Tp. The natural period of the BVER is(17)Tf=2πMLpsSdaand the inertia coefficient is (18)J=SdapsLMu02.Substituting (17) and (18) into (9), the dimensionless equation of motion becomes(19)du∗dt∗=2πTf∗2pda∗-pdb∗-pba∗-pbb∗Sba∗+pra∗-prb∗Sra∗-Ff∗,x∗≠0,10,x∗=0,1.The dimensionless friction force and other parameters are given as follows:(20)Ff∗=c∗u∗+Fsf∗u∗=0Fdf∗sign⁡uu∗≠0,c∗=cu0psSda,Fsf∗=FsfpsSda,Fdf∗=FdfpsSda.


## 3.2.6. Dimensionless Pressure Response in Tank

With the reference values in Table1, (11) can be made dimensionless as (21)dpt∗dt∗=Gin∗-Gout∗Vt∗.


## 4. Simulation Model and Analysis

### 4.1. Simulation Model and Parameter Determination

The gas state and energy conservation equations are different for the charge and discharge chambers, but the flow-rate one is the same. Five standard subsystems were modelled in MATLAB/Simulink based on the control equations in Section3. Combining these and the tank model, a BVER simulation model was established according to the work flow shown in Figure 4. The control equations were solved using the ODE45 solver with a variable step size, in order to judge the stroke end automatically.Figure 4
Work flow of BVER.The reference parameters in Table1 were set to unity in the simulation program. The initial values of the other parameters are shown in Table 2; these can be divided into two categories: structural or operational. Structural parameters are the original design ones that cannot be changed and so should be configured properly when designed. Operational parameters are those that can be adjusted by the user. Details of these dimensionless parameters are shown in Main BVER Parameters in Nomenclature.Table 2
Initial simulation values.
C b ∗ C r ∗ S r a ∗ K a T f ∗ F s f ∗ F d f ∗ c ∗ C t h ∗ V t ∗ p r ∗ p a ∗ 0.8 3.0 1.5 1.0 0.2 0.016 0.01 0.012 0.3 10 1.0 0.2With these parameter settings, the BVER system characteristics can be solved as shown in Figures5 and 6, where the ordinates are dimensionless values.Figure 5
Pressure and flow rate of BVER and tank.Figure 6
Velocity and displacement of piston.Figure5 shows the pressure and flow-rate responses in the BVER and the tank. Initially, the former cannot reach the required boost ratio for the low restriction in the latter. The BVER works at high frequency and has large exhaust-pressure fluctuations. As the tank pressure increases, the operational cycle, boost ratio, and flow rate stabilise gradually. The tank pressure and flow rate are clearly smaller than those of the BVER and are discontinuous when the piston changes direction, so they reflect the real output of the BVER.The piston motion is shown in Figure6 when the BVER works in its steady state. The velocity fluctuates when the piston changes direction, but otherwise it is steady.


### 4.2. Influence of Structural Parameters

The structural parameters in Nomenclature are changed first for comparison. Because the tank pressure represents the real BVER output, we focused on the pressure response variation in the tank. Figure7 shows the tank pressure response according to different structural parameters.Figure 7
Influence of structural parameters.
(a)
Pressure response withCb∗ (b)
Pressure response withCr∗ (c)
Pressure response withSr∗ (d)
Pressure response withKa (e)
Pressure response withTf∗ (f)
Pressure response withc∗  (g)
Pressure response withFsf∗ (h)
Pressure response withFdf∗Figures7(a) and 7(b) show that the sonic conductance of the boost chambers has an obvious effect on the BVER pressure response. This is because the flow rate is determined by the sonic conductance. With increasing sonic conductance Cb∗, the pressurised gas can be exhausted to the tank immediately. However, it reaches its maximum when Cb∗= 2.0 because the flow rate is finite. Similarly, by increasing the sonic conductance Cr∗, the pressurised gas can be exhausted to the atmosphere immediately to avoid negative work. As it increases, so does the boost ratio.Figure7(c) shows that the boost ratio increases with increasing area ratio. The recovered gas can output more energy to drive the piston as the area of the recovery chamber increases, thus increasing the boost ratio as the area ratio increases. However, a finite amount of air is recovered because the drive chamber volume is constant; hence, it does not increase for Sr∗≤ 2.0.Figures7(d) to 7(h) show that the influences of these five parameters are relatively small. This is because the heat energy and friction force are smaller than the pressure energy and pressure-driven force, respectively.


### 4.3. Influence of Operational Parameters

The BVER performance is different depending on its running conditions, so the operational parameters were changed to determine the BVER characteristics for different operational conditions.


#### 4.3.1. Influence of Load Characteristic

The load characteristic is the compressed-air consumption of the downstream devices. We used different throttle-valve openings to simulate the diversity of devices. This means the sonic conductance of the throttle valve is changed through the simulation. Figure8 shows the pressure response in the BVER and tank. It is clear that the BVER boost ratio decreases as the load increases and that the pressure output of the booster valve system is much lower than that of the BVER. For example, when Cth∗= 0.7, the BVER boost ratio is 1.4 but the tank output pressure is approximately equal to the supply one, meaning that the BVER does not boost the pressure.Figure 8
Pressure responses of BVER and tank.


#### 4.3.2. Influence of Tank Volume

Pressure fluctuations can be minimised by using a tank of the correct volume. Figure9 illustrates the pressure responses in tanks of different volumes, and it also shows that tank volume has no effect on pressure magnitude. However, with increasing tank volume, a relatively steady pressure is achieved at the expense of the charging time.Figure 9
Pressure response withVt∗.The pressure fluctuations are shown in the maganified figure of Figure9. When the (dimensionless) tank volume is 30, the fluctuation amplitude is <1%. This helps to select a tank of the correct volume.


#### 4.3.3. Influence of Regulator Coefficient

The regulator coefficient is the opening of the regulator (14 in Figure1). When Pr= 1.0, the flow pressure in the drive chamber equals the supply pressure; as Pr decreases, so does the flow pressure. The pressure response is plotted in Figure 10.Figure 10
Pressure response withPr.Figure10 shows that the boost ratio increases with the regulator coefficient. This is because the pressure in the drive chamber is controlled directly by the regulator coefficient; when the latter increases, the former increases simultaneously. This increases both the drive force and the boost ratio.


#### 4.3.4. Influence of Supply Pressure

When the reference pressure is the supply one, the larger the value ofpa∗ the smaller the supply pressure. Figure 11 shows the relationship between boost ratio and supply pressure. When the supply pressure increases, the boost ratio increases as more energy is supplied to the system to drive the piston. Consequently, the efficiency decreases as more energy exhausts to the atmosphere, a detailed analysis of which is presented in Section 5.Figure 11
Pressure response withpa∗.


### 4.4. Summary of Parameter Influences

Based on the simulation results, the degree of influence of each parameter is shown in Figure12 and is summarised below.(i)
The supply pressure has the greatest influence on the boost ratio; the boost ratio increases with supply pressure.(ii)
The regulator is useful for adjusting the boost ratio, which can be changed continuously.(iii)
The boost ratio clearly decreases as the downstream load increases. When the (dimensionless) sonic conductance reaches 0.7, the boost effect becomes negligible.(iv)
The boost ratio continuously increases with the recovery/boost chamber diameter ratio; however, the increase is imperceptible when recovery/boost chamber diameter ratio is >1.6.(v)
The larger the sonic conductance of the boost/recovery chambers, the larger the boost ratio.(vi)
The cycle period, Kagawa coefficient, and viscous friction coefficient have little effect on the boost ratio.Figure 12
Change rate of each parameter.In Figure12, the change rate is the ratio of the output pressure change as each dimensionless parameter is changed from its reference value to its maximum one, with the output pressure remaining approximately constant. This is useful for evaluating the design influence of each parameter.The pressure-flow characteristics of the BVER system are summarised in Figures13 and 14. Figure 13 shows that the BVER boost pressure ratio decreases as air consumption increases. The boost pressure ratio equals 1 when the (dimensionless) flow-rate consumption reaches 0.7; that is, the booster valve is useless.Figure 13
BVER flow-rate characteristics.Figure 14
Pressure fluctuation in tank.Figure14 shows the pressure fluctuation in the tank. Its magnitude is directly determined by the tank volume; when the (dimensionless) tank volume is 20, the pressure fluctuation is <1%.


## 4.1. Simulation Model and Parameter Determination

The gas state and energy conservation equations are different for the charge and discharge chambers, but the flow-rate one is the same. Five standard subsystems were modelled in MATLAB/Simulink based on the control equations in Section3. Combining these and the tank model, a BVER simulation model was established according to the work flow shown in Figure 4. The control equations were solved using the ODE45 solver with a variable step size, in order to judge the stroke end automatically.Figure 4
Work flow of BVER.The reference parameters in Table1 were set to unity in the simulation program. The initial values of the other parameters are shown in Table 2; these can be divided into two categories: structural or operational. Structural parameters are the original design ones that cannot be changed and so should be configured properly when designed. Operational parameters are those that can be adjusted by the user. Details of these dimensionless parameters are shown in Main BVER Parameters in Nomenclature.Table 2
Initial simulation values.
C b ∗ C r ∗ S r a ∗ K a T f ∗ F s f ∗ F d f ∗ c ∗ C t h ∗ V t ∗ p r ∗ p a ∗ 0.8 3.0 1.5 1.0 0.2 0.016 0.01 0.012 0.3 10 1.0 0.2With these parameter settings, the BVER system characteristics can be solved as shown in Figures5 and 6, where the ordinates are dimensionless values.Figure 5
Pressure and flow rate of BVER and tank.Figure 6
Velocity and displacement of piston.Figure5 shows the pressure and flow-rate responses in the BVER and the tank. Initially, the former cannot reach the required boost ratio for the low restriction in the latter. The BVER works at high frequency and has large exhaust-pressure fluctuations. As the tank pressure increases, the operational cycle, boost ratio, and flow rate stabilise gradually. The tank pressure and flow rate are clearly smaller than those of the BVER and are discontinuous when the piston changes direction, so they reflect the real output of the BVER.The piston motion is shown in Figure6 when the BVER works in its steady state. The velocity fluctuates when the piston changes direction, but otherwise it is steady.


## 4.2. Influence of Structural Parameters

The structural parameters in Nomenclature are changed first for comparison. Because the tank pressure represents the real BVER output, we focused on the pressure response variation in the tank. Figure7 shows the tank pressure response according to different structural parameters.Figure 7
Influence of structural parameters.
(a)
Pressure response withCb∗ (b)
Pressure response withCr∗ (c)
Pressure response withSr∗ (d)
Pressure response withKa (e)
Pressure response withTf∗ (f)
Pressure response withc∗  (g)
Pressure response withFsf∗ (h)
Pressure response withFdf∗Figures7(a) and 7(b) show that the sonic conductance of the boost chambers has an obvious effect on the BVER pressure response. This is because the flow rate is determined by the sonic conductance. With increasing sonic conductance Cb∗, the pressurised gas can be exhausted to the tank immediately. However, it reaches its maximum when Cb∗= 2.0 because the flow rate is finite. Similarly, by increasing the sonic conductance Cr∗, the pressurised gas can be exhausted to the atmosphere immediately to avoid negative work. As it increases, so does the boost ratio.Figure7(c) shows that the boost ratio increases with increasing area ratio. The recovered gas can output more energy to drive the piston as the area of the recovery chamber increases, thus increasing the boost ratio as the area ratio increases. However, a finite amount of air is recovered because the drive chamber volume is constant; hence, it does not increase for Sr∗≤ 2.0.Figures7(d) to 7(h) show that the influences of these five parameters are relatively small. This is because the heat energy and friction force are smaller than the pressure energy and pressure-driven force, respectively.


## 4.3. Influence of Operational Parameters

The BVER performance is different depending on its running conditions, so the operational parameters were changed to determine the BVER characteristics for different operational conditions.


### 4.3.1. Influence of Load Characteristic

The load characteristic is the compressed-air consumption of the downstream devices. We used different throttle-valve openings to simulate the diversity of devices. This means the sonic conductance of the throttle valve is changed through the simulation. Figure8 shows the pressure response in the BVER and tank. It is clear that the BVER boost ratio decreases as the load increases and that the pressure output of the booster valve system is much lower than that of the BVER. For example, when Cth∗= 0.7, the BVER boost ratio is 1.4 but the tank output pressure is approximately equal to the supply one, meaning that the BVER does not boost the pressure.Figure 8
Pressure responses of BVER and tank.


### 4.3.2. Influence of Tank Volume

Pressure fluctuations can be minimised by using a tank of the correct volume. Figure9 illustrates the pressure responses in tanks of different volumes, and it also shows that tank volume has no effect on pressure magnitude. However, with increasing tank volume, a relatively steady pressure is achieved at the expense of the charging time.Figure 9
Pressure response withVt∗.The pressure fluctuations are shown in the maganified figure of Figure9. When the (dimensionless) tank volume is 30, the fluctuation amplitude is <1%. This helps to select a tank of the correct volume.


### 4.3.3. Influence of Regulator Coefficient

The regulator coefficient is the opening of the regulator (14 in Figure1). When Pr= 1.0, the flow pressure in the drive chamber equals the supply pressure; as Pr decreases, so does the flow pressure. The pressure response is plotted in Figure 10.Figure 10
Pressure response withPr.Figure10 shows that the boost ratio increases with the regulator coefficient. This is because the pressure in the drive chamber is controlled directly by the regulator coefficient; when the latter increases, the former increases simultaneously. This increases both the drive force and the boost ratio.


### 4.3.4. Influence of Supply Pressure

When the reference pressure is the supply one, the larger the value ofpa∗ the smaller the supply pressure. Figure 11 shows the relationship between boost ratio and supply pressure. When the supply pressure increases, the boost ratio increases as more energy is supplied to the system to drive the piston. Consequently, the efficiency decreases as more energy exhausts to the atmosphere, a detailed analysis of which is presented in Section 5.Figure 11
Pressure response withpa∗.


## 4.3.1. Influence of Load Characteristic

The load characteristic is the compressed-air consumption of the downstream devices. We used different throttle-valve openings to simulate the diversity of devices. This means the sonic conductance of the throttle valve is changed through the simulation. Figure8 shows the pressure response in the BVER and tank. It is clear that the BVER boost ratio decreases as the load increases and that the pressure output of the booster valve system is much lower than that of the BVER. For example, when Cth∗= 0.7, the BVER boost ratio is 1.4 but the tank output pressure is approximately equal to the supply one, meaning that the BVER does not boost the pressure.Figure 8
Pressure responses of BVER and tank.


## 4.3.2. Influence of Tank Volume

Pressure fluctuations can be minimised by using a tank of the correct volume. Figure9 illustrates the pressure responses in tanks of different volumes, and it also shows that tank volume has no effect on pressure magnitude. However, with increasing tank volume, a relatively steady pressure is achieved at the expense of the charging time.Figure 9
Pressure response withVt∗.The pressure fluctuations are shown in the maganified figure of Figure9. When the (dimensionless) tank volume is 30, the fluctuation amplitude is <1%. This helps to select a tank of the correct volume.


## 4.3.3. Influence of Regulator Coefficient

The regulator coefficient is the opening of the regulator (14 in Figure1). When Pr= 1.0, the flow pressure in the drive chamber equals the supply pressure; as Pr decreases, so does the flow pressure. The pressure response is plotted in Figure 10.Figure 10
Pressure response withPr.Figure10 shows that the boost ratio increases with the regulator coefficient. This is because the pressure in the drive chamber is controlled directly by the regulator coefficient; when the latter increases, the former increases simultaneously. This increases both the drive force and the boost ratio.


## 4.3.4. Influence of Supply Pressure

When the reference pressure is the supply one, the larger the value ofpa∗ the smaller the supply pressure. Figure 11 shows the relationship between boost ratio and supply pressure. When the supply pressure increases, the boost ratio increases as more energy is supplied to the system to drive the piston. Consequently, the efficiency decreases as more energy exhausts to the atmosphere, a detailed analysis of which is presented in Section 5.Figure 11
Pressure response withpa∗.


## 4.4. Summary of Parameter Influences

Based on the simulation results, the degree of influence of each parameter is shown in Figure12 and is summarised below.(i)
The supply pressure has the greatest influence on the boost ratio; the boost ratio increases with supply pressure.(ii)
The regulator is useful for adjusting the boost ratio, which can be changed continuously.(iii)
The boost ratio clearly decreases as the downstream load increases. When the (dimensionless) sonic conductance reaches 0.7, the boost effect becomes negligible.(iv)
The boost ratio continuously increases with the recovery/boost chamber diameter ratio; however, the increase is imperceptible when recovery/boost chamber diameter ratio is >1.6.(v)
The larger the sonic conductance of the boost/recovery chambers, the larger the boost ratio.(vi)
The cycle period, Kagawa coefficient, and viscous friction coefficient have little effect on the boost ratio.Figure 12
Change rate of each parameter.In Figure12, the change rate is the ratio of the output pressure change as each dimensionless parameter is changed from its reference value to its maximum one, with the output pressure remaining approximately constant. This is useful for evaluating the design influence of each parameter.The pressure-flow characteristics of the BVER system are summarised in Figures13 and 14. Figure 13 shows that the BVER boost pressure ratio decreases as air consumption increases. The boost pressure ratio equals 1 when the (dimensionless) flow-rate consumption reaches 0.7; that is, the booster valve is useless.Figure 13
BVER flow-rate characteristics.Figure 14
Pressure fluctuation in tank.Figure14 shows the pressure fluctuation in the tank. Its magnitude is directly determined by the tank volume; when the (dimensionless) tank volume is 20, the pressure fluctuation is <1%.


## 5. Energy Efficiency Analysis and Experimental Study

### 5.1. Energy Efficiency of Booster Valve

Exhausted compressed air is recovered and reused by the BVER, which helps enhance the boost ratio and also improves the energy efficiency. The boost ratio was discussed in the previous section. We are concerned here with BVER energy efficiency, which is defined as the ratio of the energy output to input. Thus, the definition of air power given in [19, 20] is introduced, from which the energy input of each stroke is(22)Ein=∫0tpaQaln⁡pspadt=paVbb+Vdaln⁡pspa.The dimensionless input energy is(23)Ein∗=pa∗1+Vb∗ln⁡1pa∗.Similarly, the energy output of each stroke becomes(24)Eout=∫0tpaQaln⁡ptpadtand the dimensionless output energy is(25)Eout∗=pa∗∫0tGt∗ρ0ln⁡pt∗pa∗dt.Thus, the BVER energy efficiency can be expressed as(26)η=Eout∗Ein∗=Gt∗/ρ0ln⁡pt∗/pa∗tp1+Vb∗ln⁡1/pa∗.Based on these equations, the BVER efficiency of each stroke is as shown in Figure15. It is clear that the BVER is initially inefficient; however, it improves as the booster valve stabilises. The difference in efficiency is ≤20% for two different operational configurations, so rational parameter allocation helps to enhance the efficiency.Figure 15
BVER energy efficiency.


### 5.2. Booster Valve Experiment

Air power is a function of pressure and flow rate and can be measured using an air power metre (APM) [21]. The main part of an APM is a responsive flow sensor that can translate pressure and flow rate into air power immediately.The experimental circuit shown in Figure16 consists of two APMs (APM-800S-L, TOKYO METER) that are accurate to 3%. One is located at the upstream inlet of the booster valve, while the other is at the downstream of the tank rather than at the outlet of the booster valve. From the above analysis, we know that the flow rate out of the BVER is discontinuous, so it is difficult to measure the instantaneous air power accurately because of system response delay. However, the air power output from the tank is continuous and its fluctuation is small, so it is much easier to use it for precise measurement.Figure 16
Schematic diagram of booster valve test: (1) air source, (2) regulator, (3) air power metre, (4) booster valve, (5) flow metre, (6) air tank, (7) air power metre, (8) throttle valve, (9) silencer, and (10) pressure sensor.A test bench was built as shown in Figure17 based on the schematic diagram.Figure 17
Energy efficiency test bench.


### 5.3. Test Results and Comparison

The dimensionless air power output from the tank is shown in Figure18; the air power increases simultaneously with the supply pressure. The simulation has a short time delay due to the isothermal adjustment in the tank, which indicates that the simulation model works well and can reflect the characteristics adequately.Figure 18
Dimensionless air power output.To verify the performance improvement of the BVER, a VBA booster valve (SMC Corp.) was used for comparison. The boost ratio and efficiency of the VBA and BVER are shown in Figures19 and 20, respectively.Figure 19
Boost ratio comparison of VBA and BVER.Figure 20
Efficiency comparison of VBA and BVER.It is clear that the boost ratio increases by 15%–25% according to the supply pressure, and the efficiency increases by 5%–10%. This proves that the compressed air recovered by BVER is being reused to enhance the boost ratio and efficiency, and the recovery chambers help restrain the pressure fluctuation.


## 5.1. Energy Efficiency of Booster Valve

Exhausted compressed air is recovered and reused by the BVER, which helps enhance the boost ratio and also improves the energy efficiency. The boost ratio was discussed in the previous section. We are concerned here with BVER energy efficiency, which is defined as the ratio of the energy output to input. Thus, the definition of air power given in [19, 20] is introduced, from which the energy input of each stroke is(22)Ein=∫0tpaQaln⁡pspadt=paVbb+Vdaln⁡pspa.The dimensionless input energy is(23)Ein∗=pa∗1+Vb∗ln⁡1pa∗.Similarly, the energy output of each stroke becomes(24)Eout=∫0tpaQaln⁡ptpadtand the dimensionless output energy is(25)Eout∗=pa∗∫0tGt∗ρ0ln⁡pt∗pa∗dt.Thus, the BVER energy efficiency can be expressed as(26)η=Eout∗Ein∗=Gt∗/ρ0ln⁡pt∗/pa∗tp1+Vb∗ln⁡1/pa∗.Based on these equations, the BVER efficiency of each stroke is as shown in Figure15. It is clear that the BVER is initially inefficient; however, it improves as the booster valve stabilises. The difference in efficiency is ≤20% for two different operational configurations, so rational parameter allocation helps to enhance the efficiency.Figure 15
BVER energy efficiency.


## 5.2. Booster Valve Experiment

Air power is a function of pressure and flow rate and can be measured using an air power metre (APM) [21]. The main part of an APM is a responsive flow sensor that can translate pressure and flow rate into air power immediately.The experimental circuit shown in Figure16 consists of two APMs (APM-800S-L, TOKYO METER) that are accurate to 3%. One is located at the upstream inlet of the booster valve, while the other is at the downstream of the tank rather than at the outlet of the booster valve. From the above analysis, we know that the flow rate out of the BVER is discontinuous, so it is difficult to measure the instantaneous air power accurately because of system response delay. However, the air power output from the tank is continuous and its fluctuation is small, so it is much easier to use it for precise measurement.Figure 16
Schematic diagram of booster valve test: (1) air source, (2) regulator, (3) air power metre, (4) booster valve, (5) flow metre, (6) air tank, (7) air power metre, (8) throttle valve, (9) silencer, and (10) pressure sensor.A test bench was built as shown in Figure17 based on the schematic diagram.Figure 17
Energy efficiency test bench.


## 5.3. Test Results and Comparison

The dimensionless air power output from the tank is shown in Figure18; the air power increases simultaneously with the supply pressure. The simulation has a short time delay due to the isothermal adjustment in the tank, which indicates that the simulation model works well and can reflect the characteristics adequately.Figure 18
Dimensionless air power output.To verify the performance improvement of the BVER, a VBA booster valve (SMC Corp.) was used for comparison. The boost ratio and efficiency of the VBA and BVER are shown in Figures19 and 20, respectively.Figure 19
Boost ratio comparison of VBA and BVER.Figure 20
Efficiency comparison of VBA and BVER.It is clear that the boost ratio increases by 15%–25% according to the supply pressure, and the efficiency increases by 5%–10%. This proves that the compressed air recovered by BVER is being reused to enhance the boost ratio and efficiency, and the recovery chambers help restrain the pressure fluctuation.


## 6. Conclusions

In this study, a new BVER was presented and its principles were discussed. A dimensionless mathematical model was proposed by properly selecting the reference values, whereupon the boost ratio and efficiency were calculated using Simulink. An experiment was conducted to contrast the BVER with a VBA valve, which validated the dimensionless model and proved that the BVER has better performance. The conclusions of this study are as follows.(i)
The tank pressure reflects the real boost ratio of the booster valve system, which should not be confused with the boost ratio of the booster valve.(ii)
The major structural parameters affecting the boost ratio are the sonic conductance and the diameter ratio.(iii)
The energy efficiency was influenced strongly by the operational parameters, with a maximum difference of 20%. Hence, these should be selected carefully.(iv)
The pressure boost ratio increases with the supply pressure, but the energy efficiency decreases.(v)
The BVER boost ratio increased by 15%–25% and its efficiency increased by 5%–10% compared to a booster valve without energy recovery.This study determined the main parameters that affect the boost ratio of a BVER. Its characteristics, in particular, pressure response and efficiency, were analysed systematically. Energy recovery was shown to enhance the boost ratio and the efficiency. This study provides a suitable reference for booster valve design and energy saving and also helps optimise the structure of booster valves.



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*Source: 2804816-2016-10-27.xml*