# Dynamic Stability of Cylindrical Shells under Moving Loads by Applying Advanced Controlling Techniques Part  I—Using Periodic Stiffeners

Authors: Khaled M. Saadeldin Eldalil; Amr M. S. Baz
Journal: Advances in Acoustics and Vibration
 (2009)

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## Abstract

The load acting on a cylindrical shell, with added periodic stiffeners,
under a transient pressure pulse propelling a pullet (gun case) has been experimentally
studied. This study is based on two modes of velocities, the first is subcritical mode and
the second is supercritical mode. The stiffeners are added to the gun tube of an
experimental gun facility, of 14 mm bore diameter. The radial strains are measured by
using high-frequency strain gage system in phase with a laser beam detection system.
Time-resolved strain measurement of the wall response is obtained and both precursor
and transverse hoop strains have been resolved. The time domain analysis has been done
using “wavelet transform package” in order to determine the frequency domain
modes of vibrations and detect the critical frequency mode. A complete comparison
of the dynamic behavior of the shell tube before and after adding periodic stiffeners has
been done, which indicated that a significant damping effect reaches   values between 61.5
and 38% for subcritical and critical modes. The critical frequency of the stiffened shell
is increased, so the supercritical mode is changed to subcritical mode. The amplification
and dispersion factors are determined and constructed; there is a reduction in the
corresponding speed frequencies by about 10%. Also the radial-bending vibrations and
tube muzzle motions are detected at muzzle velocity ratio of 0.99%, the results indicated
that there is a significant improvement in increasing the number of rounds per second by
about 36% and increasing the pointing precision by about 47%.


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## Body

## 1. Introduction

The analysis  of moving loads  on elastic structures has drawn the attention of many researchers over the last century. The extent of the efforts dedicated to studying this problem is justified by the wide variety of structures which are subjected to moving loads, such as bridges, gun barrels, rails, work pieces during machining operations, as well as fluid-conveying pipes. In all these structures, the emphasis is placed on studying two basic phenomena. The first phenomenon deals with the amplification of the dynamic deflections caused by the moving loads, as compared with the deflections resulting from the static application of the same loads. The second considered phenomenon is associated with the dynamic instabilities that can be generated when the velocity of the moving loads exceeds certain critical values.Vibration of gun barrels is one of the most affected because it leads to dispersion of shot patterns. Decreasing dispersion will lead to a more lethal (more likely to hit), survivable (the sooner the enemy is hit the less likely they are to hit you), and sustainable (less rounds need to achieve the desired effect) weapon system. An intuitive way to reduce dispersion is to reduce the vibrations of the barrel. The end of the barrel is the antinode for all vibration modes, so increased exit velocity requirements have led to a demand for longer barrels. Longer barrels are more susceptible to these vibrations, Fryba [1].Recently, the demand of increasing muzzle velocity arises strongly for defending considerations, so increasing shell length is becoming essential to satisfy the main target together with increasing stability and decreasing weapon mass. These challenging counteractions lead many investigators to propose theoretical and experimental solutions.    The dynamic behavior of cylindrical shells was studied experimentally by Finlayson [2], Simkins [3, 4],  Beltman et al. [5], Thomas [6], and Baz et al. [7], the results indicated that increasing bullet velocity by expanding pressure step causing the axisymmetric radial vibration to be several times higher than that produced by the static application of the same load. So, the traveling velocity of the moving load affects the amplitude of the radial response and critical velocity, above which the shell response becomes unstable.Many authors have been involved  with the theoretical determination of the dynamic response of structures subjected  to moving loads, Abu-Hilal and Mohsen [8], and Lin and Trethewey [9]. Several theoretical techniques have been considered in order to define the stability limits and conditions for different structures, Nelson and Conover [10], Steele [11, 12], and Bolotin [13].Ruzzene and  Baz  [14, 15] studied theoretically the vibrations of cylindrical shells induced by a moving projectile propelled by an internal pressure wave and controlled by placing stiffening rings periodically along the length of the shell. They suggested that the shell response is, therefore, given by the combination of rotationally symmetric and bending motions, which are coupled by the interaction between the moving projectile, the internal pressure, and the shell vibrations. They developed a finite-element model to predict the transient response of stiffened cylindrical shells loaded by a moving projectile propelled by an internal pressure wave. The model is formulated to account for the interaction between moving mass, internal pressure, and shell vibration and to capture the resulting coupling between bending and rotationally symmetric response. Their results demonstrate the capability of periodically stiffened shells of reducing bending vibrations and, therefore, of stabilizing the overall shell response, before and after the projectile leaves the shell. Aldraihem and Baz  [16, 17] investigated theoretically the dynamic stability and response of stepped tubes subjected to a stream of moving objects excitations. They found that the stability of certain tube modes can be improved by providing the tube with appropriately spaced steps.It is obvious that the  increased susceptibility of long gun tubes to operation-induced vibration affects precision and accuracy of firing as well as barrel/round interactions during firing. A lightweight, low-cost method is desired to damp firing induced vibrations thereby increasing performance of the gun system. A relatively inexpensive and lightweight method of damping vibrations in some structures is to apply a surface treatment of a stiffening material. The stiffeners are clamped to the base material of the gun tube, in our case. Radial and transverse vibrations in the system result in radial and shear deformation of the stiffening material, which in turn redistribute and dissipate the energy. The presented experimental work provides guidelines and clear vision for the design of gun barrels with increased firing velocity, improved accuracy, and enhanced structural stability.To the best of our knowledge, investigating the gun tube with added stiffeners as a periodic damped structure has not been investigated experimentally.This work deals with studying the gun tube with added stiffeners along its length under moving pressure pulse and mass. The length of the shell is about 130 times the caliber (about three times the present practical ratio) and it may increase to double this ratio to account for supercritical dynamics. A gun test facility is constructed, in the “Noise and control laboratory’’ at the University of Maryland, USA, to account for investigating and measuring the gun dynamics at subcritical and supercritical velocity modes. A complete comparison of the plain and stepped tube is presented. The dispersion and amplification curves are constructed. The configuration of the stepped shell which is chosen herein is quite similar to that of reference [14].


## 2. Experimental Setup

### 2.1. Pneumatic 6/12-Feet Gun Tube Facility

#### 2.1.1. Setup Main Components

The experiment was carried out with in-door helium gun in the vibration and noise control laboratory at University of Maryland, it has a stainless steel tube length of 6 feet, and can be extended to the similar length in the case of running supercritical bullet velocities, as discussed in details by Baz et. al. [7]. Figure 1 shows schematic diagram of the gun system components and Figure 2 shows a view picture of the test setup facility.Figure 1
Experimental layout.Figure 2
Setup view picture.As shown in Figure1, the gun facility is composed of four main parts as follows.Part 1:
pullet decelerator (1),Part 2:
stainless steel tube assembly (2, 14),Part 3:
pneumatic gun machinery (3, 4, 6, 7, 8, 9, 10, 11, 12, 13),Part 4:
firing control box (5).All the four mentioned parts are assembled on the main base structure (15).


#### 2.1.2. Shooting Mechanism

The bullets are installed in the magazine (3) in Figure1 and the system power supply is turned on (115 v ac). When Turning “ON’’ the firing switch in the control box, the air will permit to feed the main and booster cylinders (11) and (6) by low air pressure (220 psi). This will make their push rods to proceed forward to release one bullet from the magazine end and move it to the front of the gun core (12).  When the bullet attains this location, a pulse of high-pressure helium will applied on the back of it, then it starts to move through the accelerator (13) which has sloped inlet bore and smaller diameter than the bullet at the rest of it, as shown in Figures 3(a) and 3(b).  Due to this diameter difference, the bullet will be extruded and the helium pressure starts to grow up to almost near its maximum value.  At this moment, the pressure forces will release the bullet by very high acceleration value. The high-pressure accumulator is used to keep the pressure pulse almost constant during the firing operation until the bullet leaves the muzzle.Scheme of shooting mechanism.
(a)
The bullet comes inside gun core(b)
The piston moves the bullet forwardAfter the bullet comes out from the gun tube, the feeding air of the cylinders will reverse and the piston rods will move back to their original positions.  When the firing switch is on single shooting position, the piston will stay at its original location but if the firing switch is on automatic position, the shooting cycle will be repeated until the magazine will get empty.  The kinetic energy of the bullet will be absorbed in the decelerator box(1).  It partitioned to several rooms containing layers of foam sheets and its walls are made from hard aluminum of 0.5′′ thickness.


#### 2.1.3. Experimental Measurements

The gun tube is made from stainless steel; it has inner and outside diameters of 14.097 and 15.113 mms.  The tube has a length of 1830 mms (130 times the caliber); it may be fixed directly on the bullet accelerator outlet or to the end of transition tube (another 130 caliber) at the advanced support (14) as shown in Figure1. The transition tube is used to extend the expansion process and get supercritical bullet velocities and it has the same length and inner diameter as the gun tube but the outside diameter is bigger. The gun tube is supported as clamped-free to account for bending vibration response and as clamped-simple for radial vibration response measurements.Five Micro Measurements strain gages of type “CEA-09-062UW-350’’ and signal conditioning amplifier were used to record the transition response of the gun tube.  The strain gages were located at 150 (number 1), 760 (number 2), 1350 (number 3), 1525 (number 4), and 1725 (number 5) mms from the tube inlet, as shown in Figure5.  When extending the gun tube for supercritical measurements, we use only three strain gages locations, they are numbers 1, 4, and 5, as shown in Figure 19.   The strain gages were mounted to measure the circumferential strains on the gun tube surface, so it adhered in a perpendicular direction to the tube axis.The average steady-state deformation strain and the position of the bullet are measured by hand-made piezoelectric foil transducers of type PVDF film, adhered on the gun tube outside surface, and located at the same location plane of the strain gages but at orientation angle of90°. The ac. signals are rectified by using full wave rectifier and displayed directly without any modulations. The average velocity of the bullet is obtained by measuring the strain gage signals and at the point just ahead of it (e.g., 1 and 2, then 2 and 3, etc.), the time difference between two consecutive points is measured and the distance is known, so, the average velocity is estimated. Also in order to confirm these results by additional measurements, a laser beam analog sensor is located at the outlet of the gun tube.


#### 2.1.4. Experimental Procedure

The experiment was first done for gun tube free from stiffeners (plain tube) and a basic reference is completed and confirmed by many trails at the same conditions (pressure, bullet size, and weight).   The experiments were done when the gun tube is evacuated at short and double tube length, in order to obtain low (subcritical) and high (supercritical) bullet velocities.


#### 2.1.5. Controlling Stiffeners

The control stiffeners are used to redistribute and dissipate the energy of the structure. Its optimum number and size is chosen similar to that theoretically studied in [14]. The size of the stiffener is S=3.175 mms long, outside and inside diameters (OD and ID) are 20.828 and 15.113 mms.  The stiffener is composed from two part, outer ring and inner two half rings. The numbers of stiffeners were found to be 17 and the distance apart is L=100 mms.  The weight of the total stiffeners (the mass added to the gun tube) is found to be 23.32 g, about 5.6% of the tube weight. Figure 4 shows the shell stiffeners configuration.Figure 4
Tube-stiffeners configuration.Figure 5
Measuring point locations on the  plain and stepped gun tube for subcritical velocities.


#### 2.1.6. Critical Parameters Prediction

The projectile critical velocity may be estimated by the followin expresion [18]:(1)Vcr=EhρR[13(1-ν2)]0.25,
where E:  Young’s modulus of elasticity of the tube; H: tube wall thickness;  ρ: denesity of the tube material;  R: tube average radius; ν  Poisson’s ratio of  the tube material.The critical radial  frequency for  infinite length for thin shells of  thickness to radius ratio is less than 1/30 may be estimated with reasonable accuracy according to the findings of Baron and Bleich [19, 20] and Tang [21]:(2)ϖcr=KaGhm,
where   G:   shear modulus  =E/2(1+ν), N/m²;  m:  mass of shell per unit of area =ρh,  kg/m²;  K:  factor,  =πa/L  in case of fundamental frequency n=0,    L:   half wave length, m;  a: tube mean diameter, m,  then
(3)ϖcr=KaE2.6ρrad/s.
The estimated critical frequency will be 11462.5 Hz, also the value of the critical radial frequency is the same as estimated by [18].


## 2.1. Pneumatic 6/12-Feet Gun Tube Facility

### 2.1.1. Setup Main Components

The experiment was carried out with in-door helium gun in the vibration and noise control laboratory at University of Maryland, it has a stainless steel tube length of 6 feet, and can be extended to the similar length in the case of running supercritical bullet velocities, as discussed in details by Baz et. al. [7]. Figure 1 shows schematic diagram of the gun system components and Figure 2 shows a view picture of the test setup facility.Figure 1
Experimental layout.Figure 2
Setup view picture.As shown in Figure1, the gun facility is composed of four main parts as follows.Part 1:
pullet decelerator (1),Part 2:
stainless steel tube assembly (2, 14),Part 3:
pneumatic gun machinery (3, 4, 6, 7, 8, 9, 10, 11, 12, 13),Part 4:
firing control box (5).All the four mentioned parts are assembled on the main base structure (15).


### 2.1.2. Shooting Mechanism

The bullets are installed in the magazine (3) in Figure1 and the system power supply is turned on (115 v ac). When Turning “ON’’ the firing switch in the control box, the air will permit to feed the main and booster cylinders (11) and (6) by low air pressure (220 psi). This will make their push rods to proceed forward to release one bullet from the magazine end and move it to the front of the gun core (12).  When the bullet attains this location, a pulse of high-pressure helium will applied on the back of it, then it starts to move through the accelerator (13) which has sloped inlet bore and smaller diameter than the bullet at the rest of it, as shown in Figures 3(a) and 3(b).  Due to this diameter difference, the bullet will be extruded and the helium pressure starts to grow up to almost near its maximum value.  At this moment, the pressure forces will release the bullet by very high acceleration value. The high-pressure accumulator is used to keep the pressure pulse almost constant during the firing operation until the bullet leaves the muzzle.Scheme of shooting mechanism.
(a)
The bullet comes inside gun core(b)
The piston moves the bullet forwardAfter the bullet comes out from the gun tube, the feeding air of the cylinders will reverse and the piston rods will move back to their original positions.  When the firing switch is on single shooting position, the piston will stay at its original location but if the firing switch is on automatic position, the shooting cycle will be repeated until the magazine will get empty.  The kinetic energy of the bullet will be absorbed in the decelerator box(1).  It partitioned to several rooms containing layers of foam sheets and its walls are made from hard aluminum of 0.5′′ thickness.


### 2.1.3. Experimental Measurements

The gun tube is made from stainless steel; it has inner and outside diameters of 14.097 and 15.113 mms.  The tube has a length of 1830 mms (130 times the caliber); it may be fixed directly on the bullet accelerator outlet or to the end of transition tube (another 130 caliber) at the advanced support (14) as shown in Figure1. The transition tube is used to extend the expansion process and get supercritical bullet velocities and it has the same length and inner diameter as the gun tube but the outside diameter is bigger. The gun tube is supported as clamped-free to account for bending vibration response and as clamped-simple for radial vibration response measurements.Five Micro Measurements strain gages of type “CEA-09-062UW-350’’ and signal conditioning amplifier were used to record the transition response of the gun tube.  The strain gages were located at 150 (number 1), 760 (number 2), 1350 (number 3), 1525 (number 4), and 1725 (number 5) mms from the tube inlet, as shown in Figure5.  When extending the gun tube for supercritical measurements, we use only three strain gages locations, they are numbers 1, 4, and 5, as shown in Figure 19.   The strain gages were mounted to measure the circumferential strains on the gun tube surface, so it adhered in a perpendicular direction to the tube axis.The average steady-state deformation strain and the position of the bullet are measured by hand-made piezoelectric foil transducers of type PVDF film, adhered on the gun tube outside surface, and located at the same location plane of the strain gages but at orientation angle of90°. The ac. signals are rectified by using full wave rectifier and displayed directly without any modulations. The average velocity of the bullet is obtained by measuring the strain gage signals and at the point just ahead of it (e.g., 1 and 2, then 2 and 3, etc.), the time difference between two consecutive points is measured and the distance is known, so, the average velocity is estimated. Also in order to confirm these results by additional measurements, a laser beam analog sensor is located at the outlet of the gun tube.


### 2.1.4. Experimental Procedure

The experiment was first done for gun tube free from stiffeners (plain tube) and a basic reference is completed and confirmed by many trails at the same conditions (pressure, bullet size, and weight).   The experiments were done when the gun tube is evacuated at short and double tube length, in order to obtain low (subcritical) and high (supercritical) bullet velocities.


### 2.1.5. Controlling Stiffeners

The control stiffeners are used to redistribute and dissipate the energy of the structure. Its optimum number and size is chosen similar to that theoretically studied in [14]. The size of the stiffener is S=3.175 mms long, outside and inside diameters (OD and ID) are 20.828 and 15.113 mms.  The stiffener is composed from two part, outer ring and inner two half rings. The numbers of stiffeners were found to be 17 and the distance apart is L=100 mms.  The weight of the total stiffeners (the mass added to the gun tube) is found to be 23.32 g, about 5.6% of the tube weight. Figure 4 shows the shell stiffeners configuration.Figure 4
Tube-stiffeners configuration.Figure 5
Measuring point locations on the  plain and stepped gun tube for subcritical velocities.


### 2.1.6. Critical Parameters Prediction

The projectile critical velocity may be estimated by the followin expresion [18]:(1)Vcr=EhρR[13(1-ν2)]0.25,
where E:  Young’s modulus of elasticity of the tube; H: tube wall thickness;  ρ: denesity of the tube material;  R: tube average radius; ν  Poisson’s ratio of  the tube material.The critical radial  frequency for  infinite length for thin shells of  thickness to radius ratio is less than 1/30 may be estimated with reasonable accuracy according to the findings of Baron and Bleich [19, 20] and Tang [21]:(2)ϖcr=KaGhm,
where   G:   shear modulus  =E/2(1+ν), N/m²;  m:  mass of shell per unit of area =ρh,  kg/m²;  K:  factor,  =πa/L  in case of fundamental frequency n=0,    L:   half wave length, m;  a: tube mean diameter, m,  then
(3)ϖcr=KaE2.6ρrad/s.
The estimated critical frequency will be 11462.5 Hz, also the value of the critical radial frequency is the same as estimated by [18].


## 2.1.1. Setup Main Components

The experiment was carried out with in-door helium gun in the vibration and noise control laboratory at University of Maryland, it has a stainless steel tube length of 6 feet, and can be extended to the similar length in the case of running supercritical bullet velocities, as discussed in details by Baz et. al. [7]. Figure 1 shows schematic diagram of the gun system components and Figure 2 shows a view picture of the test setup facility.Figure 1
Experimental layout.Figure 2
Setup view picture.As shown in Figure1, the gun facility is composed of four main parts as follows.Part 1:
pullet decelerator (1),Part 2:
stainless steel tube assembly (2, 14),Part 3:
pneumatic gun machinery (3, 4, 6, 7, 8, 9, 10, 11, 12, 13),Part 4:
firing control box (5).All the four mentioned parts are assembled on the main base structure (15).


## 2.1.2. Shooting Mechanism

The bullets are installed in the magazine (3) in Figure1 and the system power supply is turned on (115 v ac). When Turning “ON’’ the firing switch in the control box, the air will permit to feed the main and booster cylinders (11) and (6) by low air pressure (220 psi). This will make their push rods to proceed forward to release one bullet from the magazine end and move it to the front of the gun core (12).  When the bullet attains this location, a pulse of high-pressure helium will applied on the back of it, then it starts to move through the accelerator (13) which has sloped inlet bore and smaller diameter than the bullet at the rest of it, as shown in Figures 3(a) and 3(b).  Due to this diameter difference, the bullet will be extruded and the helium pressure starts to grow up to almost near its maximum value.  At this moment, the pressure forces will release the bullet by very high acceleration value. The high-pressure accumulator is used to keep the pressure pulse almost constant during the firing operation until the bullet leaves the muzzle.Scheme of shooting mechanism.
(a)
The bullet comes inside gun core(b)
The piston moves the bullet forwardAfter the bullet comes out from the gun tube, the feeding air of the cylinders will reverse and the piston rods will move back to their original positions.  When the firing switch is on single shooting position, the piston will stay at its original location but if the firing switch is on automatic position, the shooting cycle will be repeated until the magazine will get empty.  The kinetic energy of the bullet will be absorbed in the decelerator box(1).  It partitioned to several rooms containing layers of foam sheets and its walls are made from hard aluminum of 0.5′′ thickness.


## 2.1.3. Experimental Measurements

The gun tube is made from stainless steel; it has inner and outside diameters of 14.097 and 15.113 mms.  The tube has a length of 1830 mms (130 times the caliber); it may be fixed directly on the bullet accelerator outlet or to the end of transition tube (another 130 caliber) at the advanced support (14) as shown in Figure1. The transition tube is used to extend the expansion process and get supercritical bullet velocities and it has the same length and inner diameter as the gun tube but the outside diameter is bigger. The gun tube is supported as clamped-free to account for bending vibration response and as clamped-simple for radial vibration response measurements.Five Micro Measurements strain gages of type “CEA-09-062UW-350’’ and signal conditioning amplifier were used to record the transition response of the gun tube.  The strain gages were located at 150 (number 1), 760 (number 2), 1350 (number 3), 1525 (number 4), and 1725 (number 5) mms from the tube inlet, as shown in Figure5.  When extending the gun tube for supercritical measurements, we use only three strain gages locations, they are numbers 1, 4, and 5, as shown in Figure 19.   The strain gages were mounted to measure the circumferential strains on the gun tube surface, so it adhered in a perpendicular direction to the tube axis.The average steady-state deformation strain and the position of the bullet are measured by hand-made piezoelectric foil transducers of type PVDF film, adhered on the gun tube outside surface, and located at the same location plane of the strain gages but at orientation angle of90°. The ac. signals are rectified by using full wave rectifier and displayed directly without any modulations. The average velocity of the bullet is obtained by measuring the strain gage signals and at the point just ahead of it (e.g., 1 and 2, then 2 and 3, etc.), the time difference between two consecutive points is measured and the distance is known, so, the average velocity is estimated. Also in order to confirm these results by additional measurements, a laser beam analog sensor is located at the outlet of the gun tube.


## 2.1.4. Experimental Procedure

The experiment was first done for gun tube free from stiffeners (plain tube) and a basic reference is completed and confirmed by many trails at the same conditions (pressure, bullet size, and weight).   The experiments were done when the gun tube is evacuated at short and double tube length, in order to obtain low (subcritical) and high (supercritical) bullet velocities.


## 2.1.5. Controlling Stiffeners

The control stiffeners are used to redistribute and dissipate the energy of the structure. Its optimum number and size is chosen similar to that theoretically studied in [14]. The size of the stiffener is S=3.175 mms long, outside and inside diameters (OD and ID) are 20.828 and 15.113 mms.  The stiffener is composed from two part, outer ring and inner two half rings. The numbers of stiffeners were found to be 17 and the distance apart is L=100 mms.  The weight of the total stiffeners (the mass added to the gun tube) is found to be 23.32 g, about 5.6% of the tube weight. Figure 4 shows the shell stiffeners configuration.Figure 4
Tube-stiffeners configuration.Figure 5
Measuring point locations on the  plain and stepped gun tube for subcritical velocities.


## 2.1.6. Critical Parameters Prediction

The projectile critical velocity may be estimated by the followin expresion [18]:(1)Vcr=EhρR[13(1-ν2)]0.25,
where E:  Young’s modulus of elasticity of the tube; H: tube wall thickness;  ρ: denesity of the tube material;  R: tube average radius; ν  Poisson’s ratio of  the tube material.The critical radial  frequency for  infinite length for thin shells of  thickness to radius ratio is less than 1/30 may be estimated with reasonable accuracy according to the findings of Baron and Bleich [19, 20] and Tang [21]:(2)ϖcr=KaGhm,
where   G:   shear modulus  =E/2(1+ν), N/m²;  m:  mass of shell per unit of area =ρh,  kg/m²;  K:  factor,  =πa/L  in case of fundamental frequency n=0,    L:   half wave length, m;  a: tube mean diameter, m,  then
(3)ϖcr=KaE2.6ρrad/s.
The estimated critical frequency will be 11462.5 Hz, also the value of the critical radial frequency is the same as estimated by [18].


## 3. Experimental Results and Analysis

### 3.1. Subcritical Case

The measurements were taken at five locations on the gun tube of length 1.825 m (130 calipers), as shown in Figure5, for plain and with 17 single stiffeners.


#### 3.1.1. Plain Tube Measurements

Samples of the time domain measurements of plain tube at location points that are specified  before are shown in Figures6(a), 6(b), and 6(c).(a) Time domain output at location number 3. (b) Time domain output at location number 4. (c) Time domain output at location number 5.
(a)(b)(c)As stated in [7], the projectile velocity at location number 1 is very low (about 85 m/s) and the pressure puls is at its maximum value of 1600 psi. The resulting vibration is due to the detonation effect (sudden pressure rise) of the compressed helium at the intry of the accelerator chamber. The obtained vibration is considered as a radial circumference flextural mode (6.8 kHz), Blevins [18].  At location number 2, the velocity is increased to 515 m/s and the pressure value starts to become almost constant due to controlling the rate of injected Helium to be balanced with its expansion rate.At location number 3, the velocity is increased to 810 m/s, and became about 80% from the theoretically calculated critical velocity (1045 m/s) so the radial vibration frequency increased and the radial deformations started to grow up.  The amplification(ε) factor (normalized amplitude) became more than unity and its value can be calculated by(4)ε=max·strain/Lamedeformation.
At location number 4, the projectile velocity reaches 917 m/s, that is, 88% and the head frequency is increased to 92 kHz and trailing wave became about 120 kHz. As the projectile proceeds toward the tube muzzel, the velocity increases to 980 m/s at location number 5 and the head wave frequency is found to be 80 kHz and the trailing wave reached to 145 kHz. These variations in the wave frequency, which decrease the head wave and increase the trailing wave, extrapolate that the critical velocity may be happening. The projectile leave the tube muzzle  at a velocity of about 1015 m/s, that is, 97% of the  critical velocity. So, some very large deformations occurred at the tube muzzel due to these transient transformation to the critical case. The velocity profile of the bullet inside a vacuum tube is shown in Figure 7. The avarage static deformation (Lame deformation) is found to be equal to the equevelant output strain voltage of 0.25  v.Figure 7
Bullet velocity profile with vacuum for tube length of 260 calibers at pressure pulse of 1600 psi.


#### 3.1.2. Shell with Added Stiffeners Measurements

A comparison time domain measurements of the shell after adding stiffeners to its surface at the same location points, which are specified  before, are shown in Figures8, 10, 12, 14, and 16. The amplitude is normalized according to the L'me deformation and the time is shifted to starts from zero.Figure 8
Comparison time domain measurements at location number 1.The effect of adding stiffeners is found to be significant. At location number 1 (Figure8), where the low frequencies are the most, the amplification is reduced by 61.5%. The shape of the strain signal is transferred to a classical subcritical signal shape. The same effect is continued at all the subsequent four locations; as shown in Figures 10, 12, 14, and 16. At locations numbers 2 and 3, the frequency starts to increase, so the total period of the signals is suppressed in shorter time. The stiffened tube amplification factor is decreased by 20% at locations numbers 3 and 4 and by 38% at location number 5.The frequency analysis have been done using “wavelet transform (WT)’’ instead of “fast Fourier transform (FFT)’’ in order to detect the stronger high frequency modes which are built-in with the resulting vibrations. The ability of the wavelet transforms to detect very high frequencies is due to its very narrow scanning window (time span) which may be equal to the sampling period, so, it can deal well with the dynamic waves and the signal decomposition will be obtained perfectly. Also the wavelet transform gives frequency modes corresponding to its time domain locations, so the interfering noise could be avoided which may be prevent any confused results.Contrarily, the fast Fourier transform has a wide scanning window, so it detects only stationary signals which have limited frequency changes over long periods. Also, the frequency and time information of a signal at some certain point in the time-frequency plane cannot be known. In other words, we cannot know what spectral component exists at any given time instant, so the analysis will comprise trickery results.A comparison of the time-frequency decomposition domains is illustrated in Figures9, 11, and 13 at locations numbers 1, 2, and 3, respectively. The figures indicate that the frequency domain appears as a colorization area (pink color), it changes from dark to bright as the amplitude increases from minimum to maximum; also the frequency is defined by a so-called parameter “Scale’’ which is proportional to the inverse of the frequency multiplied by a certain factor depending on the used decomposition function of WT family. The figures indicate that the high frequency modes are suppressed due to using stiffeners; also they indicate that the frequency modes decomposition is carried out corresponding to its time domain location.Time-frequency representation at location number 1.
(a)
Plain tube(b)
Stepped tubeFigure 10
Comparison of time domain measurements at location number 2.Time-frequency representation at location number 2.
(a)
Plain tube(b)
Stepped tubeFigure 12
Comparison of time domain measurements at location number3.Time-frequency representation at location number 3.
(a)
Plain tube(b)
Stepped tubeFigure 14
Comparison of time domain measurements at location number 4.Figures15 and 17 show the results of signal processing (decomposition) at locations (4 and 5) by using discrete wavelet transforms. The modes herein are called coefficients, a1 represents the most very lower frequency mode. The higher frequency modes are represented by coefficients d5 to d1 (from low to high). It is obvious, from the figures, that there is higher amplitude frequencies for coefficients d3, d2, and d1 in the case of plain tube, but these corresponding coefficients are suppressed to lower amplitude values in the case of stepped tube.Time-frequency representation at location number 4.
(a)
Plain tube(b)
Stepped tubeFigure 16
Comparison of time domain measurements at location number 5.Time-frequency representation  at location number 5.
(a)
Plain tube(b)
Stepped tubeFigure18 shows a comparison of the frequency domain analysis at the five mentioned tube locations before and after using stiffeners. The figure indicates that the absolute value of the signal amplitude is increased at locations numbers 4 and 5, where the critical and supercritical symptoms are started.Figure 18
Frequency-domain analysis at locations 1, 2, 3, 4, and 5, red color for original and blue color for  stepped tube.Figure 19
Supercritical measuring locations.


### 3.2. Supercritical Measurements

As mentioned earlier, the supercritical measurements are taken with the aid of extension tube, which is similar to the subcritical tube in length but it has double wall thickness.  This double wall thickness tube has higher values of critical velocity and frequency, so, running the experiment will be safer and its damage will be avoided.


#### 3.2.1. Plain Tube Measurements

The measurement locations are shown in Figure19. Samples of the obtained supercritical measurements are shown in Figures 20(a) and 20(b) at locations numbers 6 and 8.(a)  The output signals at location 6, plain tube. (b) The output signals at location 8, plain tube.
(a)(b)At location number 6, the velocity was found to be 1050 m/s, that is, about 100.5% above the critical velocity. The signal shape is resembles the classical super critical signal of   [4].  At locations number 7, the signal amplitude is decreased but the velocity increased to 1176.5 m/s, then at location number 8, the velocity increased to 1190 m/s, about 113.9% of the critical velocity and the frequency amplitude continued in decreasing.At location number 7, the detected frequency of the head wave is found to be 70 kHz, and the trailing wave is 155 kHz and at location number 8, the trailing wave frequency is found to be more than 200 kHz.


#### 3.2.2. Shell with Added Stiffeners Measurements

A comparison of the time domain measurements of plain and stiffened tube are shown in Figures21(a), 21(b), and 21(c). The amplification factor at location number 6 is decreased to a value of 25% of that obtained of the plain tube, and the signal shape is changed to be as a typical classical subcritical shape, that is, the supercritical condition is transferred to subcritical case. At location number 7, the amplitude of the high frequency of the stiffened tube is increased by about 90% of that of the plain tube, this is due to increasing the bullet velocity and frequency. At location number 8, the amplification factor is increased to about 100% than that of the plain tube.(a) Comparison of time domain measurements at location number 6. (b) Comparison time domain measurements at location number 7. (c) Comparison of time domain measurements at location number 8.
(a)(b)(c)The signal decomposition diagrams at locations numbers 6, 7, and 8 are shown in Figures22, 23, and 24. The figures show that the amplitude of vibrations at location number 6 of coefficients d2 and d1 are decreased due to using stiffeners, it is just aft-critical location. The component d1 of the stiffened tube is reduced or almost vanished. The high-frequency mode amplitude d2 of the stiffened tube at locations number 7 is started to increase together with the head wave frequency and continued increasing at location number 8 where it includes the vibration modes of d2 and  d1.Strain signal decomposition at location number 6.
(a)
Plain tube(b)
Stepped tubeStrain signal decomposition at location number 7.
(a)
Plain tube(b)
Stepped tubeStrain signal decomposition at location number 8.
(a)
Plain tube(b)
Stepped tubeThe frequency domain analysis of the high-frequency modes for both plain and stiffened tube (d's coefficients), at the corresponding measurement locations, are shown in Figure 25. The figure indicates that the supercritical appearance at location number 6 is transformed into subcritical mode by using periodic stiffeners. Contrarily, the critical and supercritical symptoms are obviously started at locations numbers 7 and 8 of the stiffened tube.Figure 25
Frequency domain analysis at locations numbers 6, 7, and 8, red color for original and blue color for stepped tube.The amplification factor diagram is shown in Figure26, it is obvious that the stiffened tube frequencies are shifted to lower values than the plain tube by about 10%, and the critical velocity is increased to about 1190 m/s.  The dispersion curve is constructed and shown in Figure 27, the figure indicates that the expected critical frequency is 114 kHz and the critical velocity is 1045 m/s for the case of plain tube, as obtained by  [18–21]. The critical velocity and critical frequency is increased, in the case of using stiffeners to about 1190 m/s and 200 kHz, respectively. So, adding stiffeners to the plain tube leads to increasing the critical velocity and frequency.Figure 26
Amplification factor.Figure 27
The dispersion curve.


### 3.3. Measurements of Radial-Bending Vibrations

The radial-bending vibrations of plain and stiffened tube are shown in Figures28 and 29. The tube support is changed to clamped-free, while in the previous study, it was clamped-simple. It is obvious that the stability time which the tube walls taken to rebound is decreased in the case of stiffened tube from 140 ms to 90 ms, by a  ratio of about 36%. So, this will lead to increasing the number of rounds from 7 to 11 rounds per second with good retargeting precision.Figure 28
The radial-bending vibrations of plain tube.Figure 29
The radial-bending vibrations of the stiffened tube.


### 3.4. Measurements of Tube End Traverse Pointing Motion

The motion of the gun tube end is very important to satisfy high-accuracy pointing precision although it is considered as an antinode point. Figures30(a) and 30(b) illustrate  the bullet position in the shell versus the normalized displacement, for plain and stiffened tube. The figure shows that the shell response to the bullet is delayed until the bullet reaches about 50% of the shell tube length and the maximum deflection is reduced from 0.33 to 0.175 by a ratio of 47%.Output signals at location number 2.
(a)
Plain Tube(b)
Stiffened tube


## 3.1. Subcritical Case

The measurements were taken at five locations on the gun tube of length 1.825 m (130 calipers), as shown in Figure5, for plain and with 17 single stiffeners.


### 3.1.1. Plain Tube Measurements

Samples of the time domain measurements of plain tube at location points that are specified  before are shown in Figures6(a), 6(b), and 6(c).(a) Time domain output at location number 3. (b) Time domain output at location number 4. (c) Time domain output at location number 5.
(a)(b)(c)As stated in [7], the projectile velocity at location number 1 is very low (about 85 m/s) and the pressure puls is at its maximum value of 1600 psi. The resulting vibration is due to the detonation effect (sudden pressure rise) of the compressed helium at the intry of the accelerator chamber. The obtained vibration is considered as a radial circumference flextural mode (6.8 kHz), Blevins [18].  At location number 2, the velocity is increased to 515 m/s and the pressure value starts to become almost constant due to controlling the rate of injected Helium to be balanced with its expansion rate.At location number 3, the velocity is increased to 810 m/s, and became about 80% from the theoretically calculated critical velocity (1045 m/s) so the radial vibration frequency increased and the radial deformations started to grow up.  The amplification(ε) factor (normalized amplitude) became more than unity and its value can be calculated by(4)ε=max·strain/Lamedeformation.
At location number 4, the projectile velocity reaches 917 m/s, that is, 88% and the head frequency is increased to 92 kHz and trailing wave became about 120 kHz. As the projectile proceeds toward the tube muzzel, the velocity increases to 980 m/s at location number 5 and the head wave frequency is found to be 80 kHz and the trailing wave reached to 145 kHz. These variations in the wave frequency, which decrease the head wave and increase the trailing wave, extrapolate that the critical velocity may be happening. The projectile leave the tube muzzle  at a velocity of about 1015 m/s, that is, 97% of the  critical velocity. So, some very large deformations occurred at the tube muzzel due to these transient transformation to the critical case. The velocity profile of the bullet inside a vacuum tube is shown in Figure 7. The avarage static deformation (Lame deformation) is found to be equal to the equevelant output strain voltage of 0.25  v.Figure 7
Bullet velocity profile with vacuum for tube length of 260 calibers at pressure pulse of 1600 psi.


### 3.1.2. Shell with Added Stiffeners Measurements

A comparison time domain measurements of the shell after adding stiffeners to its surface at the same location points, which are specified  before, are shown in Figures8, 10, 12, 14, and 16. The amplitude is normalized according to the L'me deformation and the time is shifted to starts from zero.Figure 8
Comparison time domain measurements at location number 1.The effect of adding stiffeners is found to be significant. At location number 1 (Figure8), where the low frequencies are the most, the amplification is reduced by 61.5%. The shape of the strain signal is transferred to a classical subcritical signal shape. The same effect is continued at all the subsequent four locations; as shown in Figures 10, 12, 14, and 16. At locations numbers 2 and 3, the frequency starts to increase, so the total period of the signals is suppressed in shorter time. The stiffened tube amplification factor is decreased by 20% at locations numbers 3 and 4 and by 38% at location number 5.The frequency analysis have been done using “wavelet transform (WT)’’ instead of “fast Fourier transform (FFT)’’ in order to detect the stronger high frequency modes which are built-in with the resulting vibrations. The ability of the wavelet transforms to detect very high frequencies is due to its very narrow scanning window (time span) which may be equal to the sampling period, so, it can deal well with the dynamic waves and the signal decomposition will be obtained perfectly. Also the wavelet transform gives frequency modes corresponding to its time domain locations, so the interfering noise could be avoided which may be prevent any confused results.Contrarily, the fast Fourier transform has a wide scanning window, so it detects only stationary signals which have limited frequency changes over long periods. Also, the frequency and time information of a signal at some certain point in the time-frequency plane cannot be known. In other words, we cannot know what spectral component exists at any given time instant, so the analysis will comprise trickery results.A comparison of the time-frequency decomposition domains is illustrated in Figures9, 11, and 13 at locations numbers 1, 2, and 3, respectively. The figures indicate that the frequency domain appears as a colorization area (pink color), it changes from dark to bright as the amplitude increases from minimum to maximum; also the frequency is defined by a so-called parameter “Scale’’ which is proportional to the inverse of the frequency multiplied by a certain factor depending on the used decomposition function of WT family. The figures indicate that the high frequency modes are suppressed due to using stiffeners; also they indicate that the frequency modes decomposition is carried out corresponding to its time domain location.Time-frequency representation at location number 1.
(a)
Plain tube(b)
Stepped tubeFigure 10
Comparison of time domain measurements at location number 2.Time-frequency representation at location number 2.
(a)
Plain tube(b)
Stepped tubeFigure 12
Comparison of time domain measurements at location number3.Time-frequency representation at location number 3.
(a)
Plain tube(b)
Stepped tubeFigure 14
Comparison of time domain measurements at location number 4.Figures15 and 17 show the results of signal processing (decomposition) at locations (4 and 5) by using discrete wavelet transforms. The modes herein are called coefficients, a1 represents the most very lower frequency mode. The higher frequency modes are represented by coefficients d5 to d1 (from low to high). It is obvious, from the figures, that there is higher amplitude frequencies for coefficients d3, d2, and d1 in the case of plain tube, but these corresponding coefficients are suppressed to lower amplitude values in the case of stepped tube.Time-frequency representation at location number 4.
(a)
Plain tube(b)
Stepped tubeFigure 16
Comparison of time domain measurements at location number 5.Time-frequency representation  at location number 5.
(a)
Plain tube(b)
Stepped tubeFigure18 shows a comparison of the frequency domain analysis at the five mentioned tube locations before and after using stiffeners. The figure indicates that the absolute value of the signal amplitude is increased at locations numbers 4 and 5, where the critical and supercritical symptoms are started.Figure 18
Frequency-domain analysis at locations 1, 2, 3, 4, and 5, red color for original and blue color for  stepped tube.Figure 19
Supercritical measuring locations.


## 3.1.1. Plain Tube Measurements

Samples of the time domain measurements of plain tube at location points that are specified  before are shown in Figures6(a), 6(b), and 6(c).(a) Time domain output at location number 3. (b) Time domain output at location number 4. (c) Time domain output at location number 5.
(a)(b)(c)As stated in [7], the projectile velocity at location number 1 is very low (about 85 m/s) and the pressure puls is at its maximum value of 1600 psi. The resulting vibration is due to the detonation effect (sudden pressure rise) of the compressed helium at the intry of the accelerator chamber. The obtained vibration is considered as a radial circumference flextural mode (6.8 kHz), Blevins [18].  At location number 2, the velocity is increased to 515 m/s and the pressure value starts to become almost constant due to controlling the rate of injected Helium to be balanced with its expansion rate.At location number 3, the velocity is increased to 810 m/s, and became about 80% from the theoretically calculated critical velocity (1045 m/s) so the radial vibration frequency increased and the radial deformations started to grow up.  The amplification(ε) factor (normalized amplitude) became more than unity and its value can be calculated by(4)ε=max·strain/Lamedeformation.
At location number 4, the projectile velocity reaches 917 m/s, that is, 88% and the head frequency is increased to 92 kHz and trailing wave became about 120 kHz. As the projectile proceeds toward the tube muzzel, the velocity increases to 980 m/s at location number 5 and the head wave frequency is found to be 80 kHz and the trailing wave reached to 145 kHz. These variations in the wave frequency, which decrease the head wave and increase the trailing wave, extrapolate that the critical velocity may be happening. The projectile leave the tube muzzle  at a velocity of about 1015 m/s, that is, 97% of the  critical velocity. So, some very large deformations occurred at the tube muzzel due to these transient transformation to the critical case. The velocity profile of the bullet inside a vacuum tube is shown in Figure 7. The avarage static deformation (Lame deformation) is found to be equal to the equevelant output strain voltage of 0.25  v.Figure 7
Bullet velocity profile with vacuum for tube length of 260 calibers at pressure pulse of 1600 psi.


## 3.1.2. Shell with Added Stiffeners Measurements

A comparison time domain measurements of the shell after adding stiffeners to its surface at the same location points, which are specified  before, are shown in Figures8, 10, 12, 14, and 16. The amplitude is normalized according to the L'me deformation and the time is shifted to starts from zero.Figure 8
Comparison time domain measurements at location number 1.The effect of adding stiffeners is found to be significant. At location number 1 (Figure8), where the low frequencies are the most, the amplification is reduced by 61.5%. The shape of the strain signal is transferred to a classical subcritical signal shape. The same effect is continued at all the subsequent four locations; as shown in Figures 10, 12, 14, and 16. At locations numbers 2 and 3, the frequency starts to increase, so the total period of the signals is suppressed in shorter time. The stiffened tube amplification factor is decreased by 20% at locations numbers 3 and 4 and by 38% at location number 5.The frequency analysis have been done using “wavelet transform (WT)’’ instead of “fast Fourier transform (FFT)’’ in order to detect the stronger high frequency modes which are built-in with the resulting vibrations. The ability of the wavelet transforms to detect very high frequencies is due to its very narrow scanning window (time span) which may be equal to the sampling period, so, it can deal well with the dynamic waves and the signal decomposition will be obtained perfectly. Also the wavelet transform gives frequency modes corresponding to its time domain locations, so the interfering noise could be avoided which may be prevent any confused results.Contrarily, the fast Fourier transform has a wide scanning window, so it detects only stationary signals which have limited frequency changes over long periods. Also, the frequency and time information of a signal at some certain point in the time-frequency plane cannot be known. In other words, we cannot know what spectral component exists at any given time instant, so the analysis will comprise trickery results.A comparison of the time-frequency decomposition domains is illustrated in Figures9, 11, and 13 at locations numbers 1, 2, and 3, respectively. The figures indicate that the frequency domain appears as a colorization area (pink color), it changes from dark to bright as the amplitude increases from minimum to maximum; also the frequency is defined by a so-called parameter “Scale’’ which is proportional to the inverse of the frequency multiplied by a certain factor depending on the used decomposition function of WT family. The figures indicate that the high frequency modes are suppressed due to using stiffeners; also they indicate that the frequency modes decomposition is carried out corresponding to its time domain location.Time-frequency representation at location number 1.
(a)
Plain tube(b)
Stepped tubeFigure 10
Comparison of time domain measurements at location number 2.Time-frequency representation at location number 2.
(a)
Plain tube(b)
Stepped tubeFigure 12
Comparison of time domain measurements at location number3.Time-frequency representation at location number 3.
(a)
Plain tube(b)
Stepped tubeFigure 14
Comparison of time domain measurements at location number 4.Figures15 and 17 show the results of signal processing (decomposition) at locations (4 and 5) by using discrete wavelet transforms. The modes herein are called coefficients, a1 represents the most very lower frequency mode. The higher frequency modes are represented by coefficients d5 to d1 (from low to high). It is obvious, from the figures, that there is higher amplitude frequencies for coefficients d3, d2, and d1 in the case of plain tube, but these corresponding coefficients are suppressed to lower amplitude values in the case of stepped tube.Time-frequency representation at location number 4.
(a)
Plain tube(b)
Stepped tubeFigure 16
Comparison of time domain measurements at location number 5.Time-frequency representation  at location number 5.
(a)
Plain tube(b)
Stepped tubeFigure18 shows a comparison of the frequency domain analysis at the five mentioned tube locations before and after using stiffeners. The figure indicates that the absolute value of the signal amplitude is increased at locations numbers 4 and 5, where the critical and supercritical symptoms are started.Figure 18
Frequency-domain analysis at locations 1, 2, 3, 4, and 5, red color for original and blue color for  stepped tube.Figure 19
Supercritical measuring locations.


## 3.2. Supercritical Measurements

As mentioned earlier, the supercritical measurements are taken with the aid of extension tube, which is similar to the subcritical tube in length but it has double wall thickness.  This double wall thickness tube has higher values of critical velocity and frequency, so, running the experiment will be safer and its damage will be avoided.


### 3.2.1. Plain Tube Measurements

The measurement locations are shown in Figure19. Samples of the obtained supercritical measurements are shown in Figures 20(a) and 20(b) at locations numbers 6 and 8.(a)  The output signals at location 6, plain tube. (b) The output signals at location 8, plain tube.
(a)(b)At location number 6, the velocity was found to be 1050 m/s, that is, about 100.5% above the critical velocity. The signal shape is resembles the classical super critical signal of   [4].  At locations number 7, the signal amplitude is decreased but the velocity increased to 1176.5 m/s, then at location number 8, the velocity increased to 1190 m/s, about 113.9% of the critical velocity and the frequency amplitude continued in decreasing.At location number 7, the detected frequency of the head wave is found to be 70 kHz, and the trailing wave is 155 kHz and at location number 8, the trailing wave frequency is found to be more than 200 kHz.


### 3.2.2. Shell with Added Stiffeners Measurements

A comparison of the time domain measurements of plain and stiffened tube are shown in Figures21(a), 21(b), and 21(c). The amplification factor at location number 6 is decreased to a value of 25% of that obtained of the plain tube, and the signal shape is changed to be as a typical classical subcritical shape, that is, the supercritical condition is transferred to subcritical case. At location number 7, the amplitude of the high frequency of the stiffened tube is increased by about 90% of that of the plain tube, this is due to increasing the bullet velocity and frequency. At location number 8, the amplification factor is increased to about 100% than that of the plain tube.(a) Comparison of time domain measurements at location number 6. (b) Comparison time domain measurements at location number 7. (c) Comparison of time domain measurements at location number 8.
(a)(b)(c)The signal decomposition diagrams at locations numbers 6, 7, and 8 are shown in Figures22, 23, and 24. The figures show that the amplitude of vibrations at location number 6 of coefficients d2 and d1 are decreased due to using stiffeners, it is just aft-critical location. The component d1 of the stiffened tube is reduced or almost vanished. The high-frequency mode amplitude d2 of the stiffened tube at locations number 7 is started to increase together with the head wave frequency and continued increasing at location number 8 where it includes the vibration modes of d2 and  d1.Strain signal decomposition at location number 6.
(a)
Plain tube(b)
Stepped tubeStrain signal decomposition at location number 7.
(a)
Plain tube(b)
Stepped tubeStrain signal decomposition at location number 8.
(a)
Plain tube(b)
Stepped tubeThe frequency domain analysis of the high-frequency modes for both plain and stiffened tube (d's coefficients), at the corresponding measurement locations, are shown in Figure 25. The figure indicates that the supercritical appearance at location number 6 is transformed into subcritical mode by using periodic stiffeners. Contrarily, the critical and supercritical symptoms are obviously started at locations numbers 7 and 8 of the stiffened tube.Figure 25
Frequency domain analysis at locations numbers 6, 7, and 8, red color for original and blue color for stepped tube.The amplification factor diagram is shown in Figure26, it is obvious that the stiffened tube frequencies are shifted to lower values than the plain tube by about 10%, and the critical velocity is increased to about 1190 m/s.  The dispersion curve is constructed and shown in Figure 27, the figure indicates that the expected critical frequency is 114 kHz and the critical velocity is 1045 m/s for the case of plain tube, as obtained by  [18–21]. The critical velocity and critical frequency is increased, in the case of using stiffeners to about 1190 m/s and 200 kHz, respectively. So, adding stiffeners to the plain tube leads to increasing the critical velocity and frequency.Figure 26
Amplification factor.Figure 27
The dispersion curve.


## 3.2.1. Plain Tube Measurements

The measurement locations are shown in Figure19. Samples of the obtained supercritical measurements are shown in Figures 20(a) and 20(b) at locations numbers 6 and 8.(a)  The output signals at location 6, plain tube. (b) The output signals at location 8, plain tube.
(a)(b)At location number 6, the velocity was found to be 1050 m/s, that is, about 100.5% above the critical velocity. The signal shape is resembles the classical super critical signal of   [4].  At locations number 7, the signal amplitude is decreased but the velocity increased to 1176.5 m/s, then at location number 8, the velocity increased to 1190 m/s, about 113.9% of the critical velocity and the frequency amplitude continued in decreasing.At location number 7, the detected frequency of the head wave is found to be 70 kHz, and the trailing wave is 155 kHz and at location number 8, the trailing wave frequency is found to be more than 200 kHz.


## 3.2.2. Shell with Added Stiffeners Measurements

A comparison of the time domain measurements of plain and stiffened tube are shown in Figures21(a), 21(b), and 21(c). The amplification factor at location number 6 is decreased to a value of 25% of that obtained of the plain tube, and the signal shape is changed to be as a typical classical subcritical shape, that is, the supercritical condition is transferred to subcritical case. At location number 7, the amplitude of the high frequency of the stiffened tube is increased by about 90% of that of the plain tube, this is due to increasing the bullet velocity and frequency. At location number 8, the amplification factor is increased to about 100% than that of the plain tube.(a) Comparison of time domain measurements at location number 6. (b) Comparison time domain measurements at location number 7. (c) Comparison of time domain measurements at location number 8.
(a)(b)(c)The signal decomposition diagrams at locations numbers 6, 7, and 8 are shown in Figures22, 23, and 24. The figures show that the amplitude of vibrations at location number 6 of coefficients d2 and d1 are decreased due to using stiffeners, it is just aft-critical location. The component d1 of the stiffened tube is reduced or almost vanished. The high-frequency mode amplitude d2 of the stiffened tube at locations number 7 is started to increase together with the head wave frequency and continued increasing at location number 8 where it includes the vibration modes of d2 and  d1.Strain signal decomposition at location number 6.
(a)
Plain tube(b)
Stepped tubeStrain signal decomposition at location number 7.
(a)
Plain tube(b)
Stepped tubeStrain signal decomposition at location number 8.
(a)
Plain tube(b)
Stepped tubeThe frequency domain analysis of the high-frequency modes for both plain and stiffened tube (d's coefficients), at the corresponding measurement locations, are shown in Figure 25. The figure indicates that the supercritical appearance at location number 6 is transformed into subcritical mode by using periodic stiffeners. Contrarily, the critical and supercritical symptoms are obviously started at locations numbers 7 and 8 of the stiffened tube.Figure 25
Frequency domain analysis at locations numbers 6, 7, and 8, red color for original and blue color for stepped tube.The amplification factor diagram is shown in Figure26, it is obvious that the stiffened tube frequencies are shifted to lower values than the plain tube by about 10%, and the critical velocity is increased to about 1190 m/s.  The dispersion curve is constructed and shown in Figure 27, the figure indicates that the expected critical frequency is 114 kHz and the critical velocity is 1045 m/s for the case of plain tube, as obtained by  [18–21]. The critical velocity and critical frequency is increased, in the case of using stiffeners to about 1190 m/s and 200 kHz, respectively. So, adding stiffeners to the plain tube leads to increasing the critical velocity and frequency.Figure 26
Amplification factor.Figure 27
The dispersion curve.


## 3.3. Measurements of Radial-Bending Vibrations

The radial-bending vibrations of plain and stiffened tube are shown in Figures28 and 29. The tube support is changed to clamped-free, while in the previous study, it was clamped-simple. It is obvious that the stability time which the tube walls taken to rebound is decreased in the case of stiffened tube from 140 ms to 90 ms, by a  ratio of about 36%. So, this will lead to increasing the number of rounds from 7 to 11 rounds per second with good retargeting precision.Figure 28
The radial-bending vibrations of plain tube.Figure 29
The radial-bending vibrations of the stiffened tube.


## 3.4. Measurements of Tube End Traverse Pointing Motion

The motion of the gun tube end is very important to satisfy high-accuracy pointing precision although it is considered as an antinode point. Figures30(a) and 30(b) illustrate  the bullet position in the shell versus the normalized displacement, for plain and stiffened tube. The figure shows that the shell response to the bullet is delayed until the bullet reaches about 50% of the shell tube length and the maximum deflection is reduced from 0.33 to 0.175 by a ratio of 47%.Output signals at location number 2.
(a)
Plain Tube(b)
Stiffened tube


## 4. Conclusion

The load acting on a cylindrical shell, with added periodic stiffeners, under a transient pressure pulse propelling a pullet has been experimentally studied.The study comprises of two modes of velocity, the first is subcritical velocity mode and the second is the supercritical velocity mode. The measured time domain strain signals have been analyzed in order to get the frequency domain modes of vibration using “wavelet transform (WT) package’’ instead of “fast Fourier transform (FFT),’’ the package is found to be very powerful, and the decomposition of the signals by this way gave us a clear and good knowledge about the phenomena that we are looking for.Adding periodic stiffeners has a significant effect on the damping of the shell vibrations; it reaches to values between 38 and 75% for subcritical and critical velocity modes.  The critical frequency of the stiffened shell is increased to about the running velocity, so the supercritical mode is changed to subcritical.The critical velocity of the stiffened tube is increased to about 1190 m/s and the critical frequency is increased to about 200 kHz, by ratios of about 113.9% and 174.5%, respectively, when adding stiffeners which have a mass ratio of 5.6% of the mass of the plain tube.The amplification and dispersion factors are determined and constructed; they indicated that the corresponding speed and frequencies are shifted to lower values by about 10%, less than that plain tube for subcritical velocity modes.The radial-bending vibrations and tube muzzle motions are detected at muzzle velocity ratio of 0.99%; the results indicated that there is a possibility of significant increase in the number of rounds per second by about 36% and also  increasing the  pointing precision by about 47%.



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*Source: 317202-2009-10-22.xml*