CSD500 CUTTER SUCTION DREDGER

Detailed description of CSD500 cutter suction dredger：1. General

The CSD500 Cutter Suction Dredger of steel construction, the non self-propelled, dismountable type, is able

to berth and dredge at any waters both in the coastal area and inland rivers, with similar conditions to that in

navigation area “A” or below the “A”-line specified in code for inland river steel engineering ship

manufacture of P.R.China.

The dredger can be used to excavate and transport cohesive sediment below the class specified in Ⅲ code for

dredging engineering construction technique issued by Ministry of Water Resources(MWR) of P.R.China.

In the course of technical designing, we have considered special requirements for tropical climate conditions

of Bangladesh such as meteorological and waters distributing state etc.

It’s hull consists of a main pontoon, two side pontoons and one spud carriage pontoon, to be easy to

dismantle or mount for transportation by road, rail or water, and is to be easy to reassemble at project site.

The dredger is powered by diesel engines. the main diesel engine is to drive the dredge pump, and the

auxiliary diesel engine will in turn power other all equipments such as cutter, swing and ladder winches, and

the spud rams etc.

2. Arrangement in whole

You can see the following from foreword to end of the dredger:

------cutter

------cutter ladder

------ladder gantry

------anchorboom

------swing winches

------ladder winch

------operating cabin

------emergency diesel engine generator set

------deck crane

------dredge pump

------main diesel engine

------auxiliary diesel engine

------generator and high pressure hydraulic pump, emergency hydraulic pump

------two spuds and spud hoisting rams

3. Main parameters

total length(cutter ladder in horizontal position): abt.41.5m

total length of pontoons: 29.8m

breadth: 8.4m

depth:

main pontoon: 2.46m

side pontoon: 2.44m

mean draught with full bunkers approx.: 1.5m

max. standard dredging depth: 14m

suction/discharge pipe diameter: 550/500mm

continuous power of main diesel engine at 1600r/min which drives dredge pump: 895KW

continuous power of auxiliary diesel engine at 1800r/min: 339KW

output: 500m3/h

4. Technical characters

1) Hull

A. Main pontoon

dimension: 13.0×3.4×2.46m

steel plating thickness:

bottom plating: 8mm; shell plating: 6mm; deck plating: 6,8,10,12mm

number: 1

B.Side pontoon

dimension: 21.0×2.44×2.44m

C.Spud carriage pontoon

dimension: 7.6×4.0×2.44m

total contents of fuel oil tank: 59m3

contents of fresh water tank: 3.5m3

aboard:

swing anchor(two): 800Kg(each)

swing wire length(two): 120m(each)

mooring wire length: 28m(each)

2) Suction/discharge equipments

dredging distance: 1500m

dredge pump:

type: YWB3100-62

speed: 466rpm

suction pipe:

inner diameter: 550mm

wall thickness: 8mm

discharge pipe:

inner diameter: 500mm

wall thickness: 8mm

3) Cutter

power at shaft: 170Kw

speed(max.): 34rpm

type: YWJ1450-170, 5-bladed with serrated edges

diameter of cutter: Φ1450mm

4) Spuds

diameter: Φ600mm

length: 19m

5) Deck machinery

A.Ladder winch:（one）

line pull, 1st layer: 100KN

line speed, 1st layer: 0-20 m/min

wire diameter: Φ28 mm

B.Swing winches(two)

line pull, 1st layer: 100KN

line speed, 1st layer: 0-20 m/min

wire diameter: Φ28 mm

C.Anchorboom winches(two)

line pull, 1st layer: 40KN

line speed, 1st layer: 0-25 m/min

wire diameter: Φ18 mm

6）Deck crane

lifting power: 30KN（3t）

outreach: 3.5m

7) Grease apparatus

voltage: 220/380V, 50HZ

power: 0.37KW

contents of tank: 8L

8) Electric installation

A.Emergency diesel engine generator set

voltage: 230/400V,50HZ

emergency generator power: 24KW

B.Accumulator battery set

number: 1set

9) Power engines

A.Main diesel engine

continuous power: 895KW

speed: 1800rpm

type: KTA38-M2

make: Cummins in China

B.Auxiliary diesel engine

continuous power: 339KW

speed: 1800rpm

type: KTA19-M

make: Cummins in China

10) Auxiliary equipments

A.Gland pump

number: 2

capacity: 50m3/h

manometric head: 0.8Mpa

B.Cooling water pump

capacity: 40m3/h

manometric head: 0.3Mpa

C.Oily-water separator

capacity: 50m3/h

discharge distance: 20m

D.Hydraulic motor

number:

for cutter drive: 1

for ladder winch: 1

for swing winches: 1 each

E. Spud hoisting rams

diameter: 160mm

ram stroke: 2.1m

F. Ventilation

number of fans: 2

capacity (each): 5,000 m3/h

5. Building & Equipments

1) Hull

The hull of the dredger has a rectangular shape and is subdivided into 3 pontoons:

---one main pontoon

---one side pontoons on port side

---one side pontoons on starboard side

---one spud carriage pontoon on the end of main pontoon

The hull is of all welded, steel construction to give the dredger the necessary strength required for dredging

operations. The side pontoons are connected to the main pontoon by means of bolts.

2) Deck arrangement

Manholes, tanks, hatches to the engine room, a hatch to permit passage of dredge pump parts are fitted on the

pontoons, including open railing, ventilation, signal mast, nameplates etc., and corresponding bollards, lights,

hawsers too.

3) Piping systems

For the draining of the dredger a bilge pump with pipes is installed. The ballast tanks are executed with

suction/filling pipeline, fuel tanks and waste oil tank are provided with air pipeline, filling pipeline and

lubricating pipeline. In addition, fuel oil pipeline, lubricating oil pipeline, cooling water pipeline, and

hydraulic oil pipeline etc. are provided.

4) Dredge pump system

Dredge pump is connected with main diesel engine though a reduction gearbox. The casing and impeller is

made of abrasive resistant metal alloys. Water flushing sealing is arranged on the suction and shaft sides of

the pump. Reduction installation has a clutch and lubrication cooling system. Suction pipe is connected to

suction cover of the pump though suction hose pipe. A non-return valve is installed on board in the discharge

line, in addition, included vacuum and pressure gauges for dredge pump etc.

5) Cutter

The cutter is of the 5-bladed crown type with serrated cutting edges, and the heavy duty one piece cutter is

replaceable edges. Hydraulic motor drives the cutter mounted on the cutter ladder which is hinged to the main

pontoon, and the suction pipeline is fitted under the ladder by means of brackets, has a special suction mouth.

6)Deck auxiliaries

Two swing winches is positioned on the deck, and driven by a hydraulic motor. The cable speed can be

regulated, the winches can be braked.

Other one ladder winches is positioned on the deck, and also driven by a hydraulic motor. The cable speed

can be regulated, the winches can be braked, and secured by a hand-operated locking pin.

Deck crane is equipped with a hand-operated tackle for hoisting pump parts, can be gyred.

Operating cabin is positioned such as to give good view in all directions, and arranged two control master

console and corresponding instrumentation, signal and operating & control switches. A separate intercom

system is provided between control and engine room, to ensure that one man can handle the controls all

whole dredger conveniently, effectively and safely.

The two spuds are of heavy wall tubular steel with cast steel points positioning holes and pins at the aft end

of the dredger, and titling facilities for spuds is equipped on the dredger in order to keep water level for

spuds, is good to navigation and transfer to project site.

7) Hydraulic system

The hydraulic system is to consist of two double vane hydraulic pumps with high pressure driven by the

auxiliary engine, to supply hydraulic oil for overall hydraulic installations, and to include filters, coolers, and

corresponding indicating gauges, simultaneously to provide emergency hydraulic pump to supply power, in

case of stoppage of auxiliary engine.

8) Electrical system

Electrical system is to consist of a emergency diesel engine generator set of 24KW to supply power for all

electrical power installations: lighting, signals, battery charger, funs.

Electrical system is equipped with switch boards and power take off panels.

Electrical system is equipped with an accumulator battery set for starting diesel engines, emergency lighting

and electromagnetism valves controlling.

9) Power engines

the dredger has a main diesel engine to drive dredge pump, an auxiliary diesel engine to drive generator and

high pressure hydraulic pump, an emergency diesel engine generator set to drive emergency hydraulic pump

and supply electrical power at case of stoppage of dredger, for protection of all auxiliary equipments of

dredger. Diesel engines and emergency diesel engine generator set both have corresponding indicating

gauges, and warning devices.

10) painting

All steel surfaces are prepared to receive marine type zinc primes prior to painting. Pursuant to relevant code

or fitting buyer’s requirements, dredger is painted with non-corrosive marine grade enamel or other one

which is used in the salt water.

6. Trial and inspection

A pre-shipment trial of diesel engines, generator, hydraulic system etc. of the dredger, is carried out to adjust

and test by supplier.

7. Pipeline system (total length 500m, including 350m floating pipe, 150m shore pipe)

Pursuant to buyer’s requirements, the supplier may provide the pipeline of floating and shore section at extra

cost, not included in the dredger price, and warranty their reliable performance and quality to fit the

requirements for transporting soils and sands.

The design is to include the number of pipe sections, pipe sections with flanges, hoses, floaters, and all other

necessary components and equipment.

The modeling of the swing winches of a cutter dredge in relation with simulators

 

S.A. Miedema1[1]

 

Abstract 

When developing a simulator for cutter suction dredges, the different processes have to be considered non-stationary and dynamical. A simulator usually consists of a combination of input by a user and hard- and software processing this input and generating output. In the case of a cutter suction dredge simulator the manual control of the swing winches, by means of joysticks, is one of the important inputs for the simulation process.

 

The position of the joysticks determines a set point for either the swing velocity or the revolutions of the hauling swing winch. By means of a control algorithm the hauling winch will generate a hauling torque, while the braking winch exerts a brake torque. This results in pulling forces in both the swing wires. These forces, combined with the cutting forces and the current forces, result in a rotation around the active spud. This rotation can be described with the equilibrium equation of the dredge around the active spud.

 

Introduction 

The dredge motions consist of the six degrees of freedom of the pontoon complemented with the rotation of the ladder around the ladder bearings. This gives a total of 7 degrees of freedom (surge, sway, heave, roll, pitch, yaw and ladder rotation). For a dredge operating in still water, when wave forces are ignored, the motions in the horizontal plane are relevant (surge, sway and yaw) as well as the ladder rotation. The three pontoon motions can be reduced to the rotation around the spud if the spud is considered to be infinitely stiff. If the ladder rotation is considered not to be the result of a mass-spring system, but controlled by the ladder winch, only one equilibrium equation has to be solved, the rotation of the pontoon around the spud. The other 6 equilibrium equations are of interest when working offshore, when wave forces have to be taken into account, but using these equations increases the calculations to be carried out enormous.

1[1] Associate Professor, Chair of Dredging Technology, Director of Education, Mechanical Engineering, Delft University of Technology.

 

The motions of the dredge 

The equilibrium equation of rotation around the spud is a second order non-linear differential equation, with the following external forces:

 

The inertial forces of pontoon and ladder The water damping on pontoon and ladder The spring forces resulting from the swing wires The external forces resulting from the current The external forces resulting from the cutting process The external forces resulting from the swing winches The external forces resulting from the pipeline The reaction forces on the spud

 

 

1.        The inertial forces (moments) determine whether there is an acceleration or deceleration of the rotation around the spud. These forces are the result of the equilibrium equation and thus of the external forces.

Fig. 1: The display of the top view of the cutterdredge, also showing the channel.

 

2.        The water damping and the current forces depend on the value and the direction of the current and on the rotational speed of the pontoon around the spud.

 

3.        The spring forces resulting from the swing wires and the forces resulting from the swing winches strongly depend on the characteristics of the winches and the wires and the winch control system. The position of the anchors in relation to the position of the spud and the position of the swing wire sheaves on the ladder determines the direction of the swing wire forces and thus of the resulting moments around the spud. Figure 4 shows the winch output of a research simulator.

 

Fig. 2: The display of the back view of the cutterdredge, also showing the cross-sectional channel profile.

 

4.        The forces and moment excerted on the pontoon by the current influence the rotation around the spud depending on the current speed and the swing speed. For small values of the current speed this effect can however be neglected. For high values of the current speed the influence depends on the direction of the current and the swing angle. It may occur that the swing winches do not have enough power to pull back the pontoon out of a corner due to the angle of the swing wires and a high current speed.

 

5.        The cutting forces and the cutting torque strongly influence the rotation around the spud, these will be discussed in the paragraph concerning the cutting forces.

6.        The winch forces and the winch moment strongly influence the rotation around the spud, these will be discussed in the paragraph concerning the swing winch characteristics.

 

7.        The forces resulting from the pipeline can be neglected if the position of the swivel elbow is close to the position of the work spud, because in this case this force hardly influences the rotation of the pontoon around the spud.

 

8.        The reaction forces on the spud can be determined by the equilibrium equations of forces and complement this equilibrium. These forces however do not contribute to the moment around the spud.

 

The rotation of the pontoon around the spud is dominated by the cutting forces, the winch characteristics, the inertia of pontoon and ladder and placement of the anchors, while damping and current play a less important role. The equilibrium equation can be formulated as:

 

(1)

 

The water damping is combined with the current moment, the wire spring force, the pipeline moment and the spud moment are not taken into consideration. Equation 1 thus reduces to:

 

(2)

 

The equilibrium equation in question is non-linear, while some of the data is produced by interpolation from tables. This implies that the equation will have to be solved in the time domain, using a certain time step. This is also necessary because the simulation program has to interact with the console (the user input). To simulate the motions of the dredge real time, a time step of at least two times per second is required. A time step of 5 to 10 times per second would be preferred.

 

Fig. 3: The display of the side view of the cutterdredge, also showing the longitudinal channel profile.

 

The influence of the swing angle on the wire moment

 

With fixed anchor positions, the angle of attack of the swing wires relative to the axis system of the pontoon, changes continuously with the value of the swing angle. With large swing angles this may result in a large decrease of the effective pulling or braking moment of the swing wires. This decrease of course depends on the anchor positions relative to the pontoon.

 

In this paper the following coordinate system definitions are applied:

 

1.        The origin is placed in the centerline of the work spud.

2.        The two wire sheaves are positioned on the centerline through the work spud and the cutterhead.

3.        The positive swing direction is counter clock wise, with an angle of zero degrees when the centerline of the dredge matches the vertical axis (y-axis).

4.        The distance from the center of the workspud to the center of the sheaves is Lss.

 

 

Fig. 4: The output of the winch parameters.

 

With the coordinates if the swing sheaves on the ladder xss and yss according to:

 

(3)

 

And

 

(4)

 

 

Fig. 5: The coordinate system with the dredge in the neutral position.

 

The length of the port wire and the angle of the port wire with the centerline of the channel can be determined according to:

 

(5)

 

and

 

(6)

 

The length of the starboard wire and the angle of the starboard wire with the centerline of the channel can be determined according to:

 

(7)

 

and

 

(8)

Fig.

6: The coordinate system with the dredge at a swing angle s.

 

The angle of the port wire with the centerline of the dredge is:

 

(9)

 

The angle of the starboard wire with the centerline of the dredge is:

 

(10)

 

The moment around the spud, resulting from the forces in the swing wires can now be determined by:

 

(11)

 

The relation between the rope speed of the port wire and the angular speed of the dredge is now:

 

(12)

 

The relation between the rope speed of the starboard wire and the angular speed of the dredge is now:

 

(13)

 

 

This results in loss of effective power of both winches. The power mobilized by the winches to the angular speed of the dredge is:

 

(14)

 

The power consumed by the winches is:

 

(15)

 

The winch characteristics

 

The torque speed characteristic of the winches consists of two parts if an electric drive is assumed. The first part runs from 0 revolution up to full revolutions and has a linear decrease of the torque, from a maximum at zero revolutions to the full torque at full revolutions. At this last point also the full power of the drive is reached. At higher revolutions the drive will use field weakening, while the power stays constant. In the simulator it is assumed that the characteristics for hauling and braking are equal.

If

one winch is in hauling mode, the other one will always be in braking mode.

Fig. 7: The torque-speed characteristic of the winches.

 

The control system of the winches

 

The hauling winch is controlled by a setpoint for the winch revolutions. The braking winch is controlled by a setpoint for the braking torque. So for the hauling winch, the available torque results from the revolutions, while the pulling force also results from the drumdiameter and the number of layers on the drum. The mobilized torque also depends on the loads (cutter and current) and on the angular acceleration of the dredge around the spud pole.

 

Fig.8 shows the actual revolutions of the hauling winch, the setpoint of the hauling winch, the setpoint of the braking winch and the load curve for the hauling winch. The load curve includes the cutting process, the current and water damping and the braking winch. The difference between the available torque and the torque resulting for the loads is available for the acceleration of the pontoon. In the example given in fig. 8, it is assumed that the actual revolutions of the winch are smaller then the setpoint and that the available torque is larger then the required torque for compensating the loads.

 

The actual torque mobilized by the hauling winch, is always the resulting torque necessary to reach or stay on the setpoint. If in a certain situation, the torque available is less then the torque required, then the available maximum torque is assumed.

In this case the working point is the intersection point of the load curve with the vertical dotted line through the setpoint of revolutions. The maximum available torque is not fully mobilized.

 

Fig.

8: The torque-speed characteristic of the winches with the setpoints. Case where the required torque is sufficient.

 

Fig.

9: The torque-speed characteristic of the winches with the setpoints. Case where the required torque in the setpoint is not sufficient.

 

Fig. 9 shows the case where the winch torque required in the setpoint is not sufficient. In this case, the working point is the intersection point of the load curve with the torque-speed curve.

The maximum available torque is fully mobilized. The setpoint is not reached because there is not sufficient torque available.

 

Fig. 10 shows the case where the setpoint is smaller then the actual revolutions. In this case, the pontoon will decelerate. The working point is the intersection point of the vertical through the setpoint and a minimum torque required keeping the wire from going slack.

 

Fig.

10: The torque-speed characteristic of the winches with the setpoints. Case where the setpoint is smaller then the actual revolutions.

 

Case studies.

 

To show the behavior of the dredge-winch system two cases will be shown. In the first case the dredge starts on the centerline of the channel. The dredge and winch layouts are shown in Figure 11.

 

Fig. 11: The dredge, winch and channel layout.

 

Fig. 12: The dredge 30 degrees to port (left) and 30 degrees to starboard (right).

 

Case 1:

 

The winches have a drum diameter of 0.84 m, a full power of 158 kW at 8.87 rpm. The resulting full torque is 167 kNm. The anchor positions are symmetrical with respect to the centerline and are 65 m in horizontal direction and -21.5 m in vertical direction, away from the sheaves on the ladder. The ladder is not in contact with the bank and is moving free through the water.

 

The following actions are taken:

 

1.        The setpoint for the swingspeed is set to 24 m/min to starboard.

2.        The dredge swings from 0 to 30 degrees to starboard.

3.        The setpoint for the swingspeed is set to 24 m/min to port.

4.        The dredge swings from 30 degrees starboard to 30 degrees port.

5.        The setpoint for the swingspeed is set to 24 m/min to starboard.

6.        The dredge swings from 30 degrees port to the centerline.

 

Fig. 13 shows the rope speeds and pulling forces for both the port and the starboard winch. It is clearly shown in the graphs in Figure 13 that, while the rope forces increase instantly, the rope speed increases or decreases according to a first or second order system. This is caused by the mass-spring-damper system according to equation 1, but also by the inertia of the winches themselves. In the simulator, the winches are modeled as a first order system. The winches and the dredge need some time to accelerate or decelerate.

 

The deceleration requires more time in case 1 then the acceleration, because the braking force is set to 30% of the maximum force, which is about 180 kN. The pulling force however, can be much higher, depending on the characteristic of the winches. Setting the braking force to a higher value, will increase the speed of the deceleration.

 

Typical for this case is, that the pulling wire is more and more perpendicular to the ladder when the swing angle approaches 30 degrees. This results in a decreasing pulling force, which can be seen in Figure 13. The braking force is set to a constant value and will only differ from this value if the braking force is larger then the torque-speed curve permits it to be. In that case the braking force will follow the torque speed curve.

 

Fig

. 13: The rope speeds and forces for case 1.

 

Case 2:

 

The winches have a drum diameter of 0.84 m, a full power of 158 kW at 8.87 rpm. The resulting full torque is 167 kNm. The anchor positions are symmetrical with respect to the centerline and are 65 m in horizontal direction and +3.5 m in vertical direction, away from the sheaves on the ladder, as is shown in Figure 15.

The ladder is not in contact with the bank and is moving free through the water.

 

The following actions are taken:

 

1.        The setpoint for the swingspeed is set to 24 m/min to starboard.

2.        The dredge swings from 0 to 30 degrees to starboard.

3.        The setpoint for the swingspeed is set to 24 m/min to port.

4.        The dredge swings from 30 degrees starboard to 30 degrees port.

5.        The setpoint for the swingspeed is set to 24 m/min to starboard.

6.        The dredge swings from 30 degrees port to the centerline.

 

Fig. 14 shows the rope speeds and pulling forces for both the port and the starboard winch. Because the anchors are moved 25 m forward in the channel, now the angle between the pulling wire and the ladder decreases when the dredge approaches the 30 degrees swing angle. This results in an increase of the pulling force as is visible in Figure 14. The start and stop behavior is almost equal to case 1.

 

 

 

Fig

14: The rope speeds and forces for case 2.

 

CONCLUSIONS

 

The modeling of the winches and the wires consists of solving the equilibrium equation of motions of the dredge around the spudpole in combination with the characteristics of the winches. The two cases show that it takes about 10 seconds to accelerate to a swing speed of 24 m/min. The time required for the deceleration is of the same magnitude, but depends of course on the setpoint of the brake force.

 

The two cases also show, that the shape rope speed and force as a function of time, strongly depend on the position of the anchors relative to the sheave positions at the ladder. The two cases describe symmetrical configurations, which of course is not always the case. An infinite number of configurations can be chosen. Which configuration is the best depends on the work to be carried out and on the boundary conditions of the work to be carried out.

 

Recommendations

 

In a next paper the control system of the winches will be described in greater detail. Also the influence of the current and the cutting process will be included more extensively.

 

Fig. 15: The dredge and anchor layout for case 2.

 

REFERENCES

 

Cox, C. M., Eygenraam, J. A., Granneman, C. C. O. N., and Njoo, M., A Training Simulator for Cutter Suction Dredgers: Bridging the Gap between Theory and Practice, Proceedings of World Dredging Congress, WODCON XIV, Amsterdam, The Netherlands, November, 1995.

Digital Automation and Control Systems (DACS), Hydraulic Dredging Simulator, Houston, Texas, 1994.

Miedema, S. A. Considerations in Building and using Dredge Simulators, Proceedings of the Western Dredging Association XIX Technical Conference and 31st Texas A&M Dredging Seminar, Louisville, KY, Center for Dredging Studies, Texas A&M University, College Station, TX, May 15-18, 1999.

Miedema, S. A. Modeling and Simulation of the Dynamic Behavior of a Pump/Pipeline System, Proceedings of the WEDA Technical Conference and Texas A&M Dredging Seminar, New Orleans, June 1996.

Miedema, S. A., Production Estimation Based on Cutting Theories for Cutting Water Saturated Sand, Proceedings of World Dredging Congress, WODCON XIV, Amsterdam, The Netherlands, November, 1995.

Randall, R. E. and Albar, A. Cutter Suction Dredge Simulator Training Manual, Center for Dredging Studies, Ocean Engineering Program, Civil Engineering Department, Texas A&M University, College Station, Texas, January 2000.

Randal, R.E. and deJong, P.S. and Miedema, S.A., Experiences with Cutter Suction Dredge Simulator Training. Proceedings of the WEDA Technical Conference and Texas A&M Dredging Seminar, Rhode Island, June 2000.

 

 

LIST OF SYMBOLS USED

 

cyaw Spring constant of the yaw motion kNm/radFpw Rope force of the port wire kNFsw Rope force of the starboard wire kNIyaw Mass moment of inertia of pontoon in yaw direction kNms2/radkyaw Damping coefficient of pontoon in yaw direction kNms/radLpw Length of the port wire mLss Distance from working spud to swing sheaves on ladder mLsw Length of starboard wire mMcurrent Moment around the spud exerted by the current kNmMcutting Moment around the spud exerted by the cutting process kNmMpipe Moment around the spud exerted by the floating pipeline kNmMspud Moment around the spud exerted by the spud kNmMwires Moment around the spud exerted by the swing wires kNmnfull Full revolutions of the swing winch rpmPpw Power of the port winch kWPpwm Power of the port winch mobilized on the dredge kWPsw Power of the starboard winch kWPswm Power of the starboard winch mobilized on the dredge kWPw Power of both winches kWPwm Power of both winches mobilized on the dredge kWTacc Winch torque available for acceleration or deceleration kNmTfull Full torque of the winches kNmTmax Maximum torque of the winches kNmvpw Rope speed of the port winch m/secvsw Rope speed of the starboard winch m/secxpw X coordinate of the port anchor mxss X coordinate of the swing sheaves on the ladder mxsw X coordinate of the starboard anchor mypw Y coordinate of the port anchor myss Y coordinate of the swing sheaves on the ladder mysw Y coordinate of the starboard anchor mfs Swing angle radjpw Port wire angle radjsw Starboard wire angle rad

 

 

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HydraMaster Selection Chart 

MODEL

IMPELLER

DIAMETER Inches (mm)

SUCTION

I.D. Inches

(mm)

DISCHARGE

I.D.Inches (mm)

SHAFT

SIZE Inches

(mm)

WEIGHT Lbs (Kg)

NOMINAL

HORSEPOWER HP

HDM 32-10x8-C 32 (406) 10 (254) 8 (203)4.4375

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7760

(3520)365

HDM 32-12x10-C 32 (406) 12 (305) 10 (254)4.4375

(113)

7905

(3585)365

HDM 36-12x10-C 36 (914) 12 (305) 10 (254)5.4375

(138)

11600

(5260)520

HDM 36-14x12-C 36 (914) 13.33 (337) 12 (305)5.4375

(138)

10700

(4850)520

HDM 36-14x14-C 36 (914) 13.33 (337) 13.33 (337)5.4375

(138)

11750

(5330)520

HDM 42-14x12-C 42 (1067) 13.33 (337) 12 (305)5.4375

(138)

15600

(7076)725

HDM 42-16x14-C 42 (1067) 15 (381) 13.33 (337)6.4375

(164)

16425

(7450)850

HDM 42-16x16-C 42 (1067) 15 (381) 15 (381)6.4375

(164)

16325

(7405)725

HDM 42-18x16-C 42 (1067) 17 (432) 15 (381)6.4375

(164)

19190

(8705)850

HDM 46-20x16-C 46 (1168) 19 (483) 15 (381)7.1875

(183)

19900

(9025)1125

HDM 46-20x18-C 46 (1168) 19 (483) 17 (432)7.1875

(183)

20520

(9310)1125

HDM 46-20x20-C 46 (1168) 19 (483) 19 (483)7.1875

(183)

21670

(9830)1125

HDM 50-24x20-C 50 (1270) 23 (584) 19 (483)7.1875

(183)

23300

(10570)1700

HDM 60-24x20-C 60 (1524) 23 (584) 19 (483)9.000

(229)

36070

(16360)2150

HDM 72-28x24-C 72 (1829) 27 (686) 23 (584)11.500

(292)

56800

(25765)2875

HDM 80-28x24-C 80 (2032) 27 (686) 23 (584)11.500

(292)

62650

(28420)3600

HDM 80-32x28-C 80 (2032) 32 (813) 27 (686) 11.500 68890 3600

(292) (31250)

Note: This information is presented for general sizing purposes only. For detailed capacity calculations, please contact DredgeMasters International, Inc.

Contact DredgeMasters for pump requirements that are not listed above.

© 2011 DredgeMasters International, Inc. All rights reserved

IHC Beaver 5514 C Cutter Suction Dredger

The IHC Beaver is well known for its robust construction, reliable

operation and excellent performance. To date, IHC Holland has

supplied more than 600 of these standard cutter and wheel dredgers,

worldwide.

Intensive research combined with the latest technology mean that the

New Generation IHC Beaver Dredgers are available to the dredging

industry. The improvements in efficiency and savings in fuel

consumption are spectacular. The relationship between installed

power and type designation in past dredgers is no longer applicable.

The installed power in the NG series is significantly lower than with

its predecessors, yet equivalent or even higher dredging output is still

provided.

The full range of demountable standard dredgers consists of

several models of both cutter dredger and wheel dredger. The

NG dredgers have catamaran-shaped hull, with the engine room

located at deck level. The dredgers are equipped with a single

high-pressure submerged dredge pump, mounted on the ladder.

This high efficiency pump is directly driven by the diesel engine,

via the IHC Pivoting Gearbox.

The prime mover for the dredge pump is a modern computer-

controlled diesel engine with low fuel consumption, and low NOx

and soot emissions.

This combination results in the lowest possible costs per cubic

meter of dredged material, for both cutter and wheel dredgers.

The type designation of the NG IHC Beaver series relates to the

diameter of the delivery pipeline, the dredging depth and the

cutting tool.

This type is designated the NG IHC Beaver 5514 C.

55 – diameter of the delivery pipeline is 550mm

14 – max. dredging depth is 14 metres

C – dredger is equipped with a cutter

The dredger can also be supplied as a standard wheel dredger,

designated the NG IHC Beaver 5014 W, with a delivery pipeline

with a diameter of 500mm.

IHC Beaver 5514 C – Cutter Suction Dredger

Features

Highly efficient fuel consumption and overall operating costs

New highly effective cutter/wheel drive system

Fresh water cooling system

Hull consists of two side pontoons connected by small coupling pontoons

Completely assembled and fully tested before delivery

Very simple and fast assembly, afloat of onshore

Ready for operation on arrival at site

Standard design, allowing short delivery times

Standard spare parts available from stock

Designed as standard to qualify for Coastal Waters Certificate

Optional equipment available

Principal particulars

Length overall, ladder raised

Length over pontoons, moulded

Breadth, moulded

Depth, moulded

Side pontoons, moulded

Mean draught with full bunkers approx.

(standard design)

Maximum standard dredging depth

Internal diameter of suction tube

Internal diameter of discharge pipes

Total installed power

Total dry weight approx.

Dredge pump

Type IHC HR/MD 101-21-50

Power at shaft

885kW (1,204hp)

Prime mover: Caterpillar 3512 B-SCAC developing 954kW (1,298hp)

continuous power at 1,600rev/min. Specific fuel consumption 214g/kWhr

Dredge pump driven via pivoting gearbox

Ball clearance

213mm

Auxiliary power (cutter, winches, spuds)

Caterpillar 3412 DI-TA developing 537kW (730hp) medium duty power

at 1,800rev/min. Specific fuel consumption 213g/kWhr

Electrical installation

Voltage

Battery capacity

Voltage (50Hz)

Installed electrical power

Cutter

Type IHC 20CB-1700-265

Power at shaft

Diameter

Maximum speed (approx.)

2000

Pump output in m3 of in situ solids

per effective pumping hour

1800

1600

1400

1200

1000

800

600

400

200

0

0

36.80m

26.00m

10.64m

2.75m

26.00 x 2.97 x 2.75m

1.80m

14.00m

550mm

550mm

1,491kW (2,028hp)

235t

19m

711mm

7,837kg

353kN

2.10m

3.05m

32.50m

41.00m

20kN

3.50m

24V DC

770Ah

230/400V AC

20kVA

280kW (380hp)

1,700mm

30rev/min

Winches (ladder winch / swing winches)

Line pull, 1st layer

150/150kN

Max. line speed

20/20m/min

Wire diameter

28/28mm

Drum diameter

610/610mm

All winches have independent hydraulic drive

The two swing winches are supplied with wires of 125m and anchors

of 750kg

Spuds

Length

Diameter

Weight

Spud hoisting rams

Force

Ram stroke

Spud stroke (each time approx.)

Swing width with 35° swing each side

At max. dredging depth

At min. dredging depth

Deck crane

Lifting power

Outreach

Classification

Bureau Veritas Class I, X Hull dredger coastal area Engine installation

after construction Ÿ MOT

Tools

Special tools are supplied for connecting and disconnecting pontoons and

cutter ladder, and for maintenance of dredge pump and diesel engine

Optional equipment

Anchor booms

Spud carrier

Increased dredging depth

Double walled dredge pump

Dredge automation systems

Swivel bend

Spud tilting facility

Air conditioning

Harbour set

Production measuring equipment

internal diameter of discharge line 550mm

maximum standard dredging depth

maximum volumetric concentration of in situ solids of 30%

final elevation at end of pipeline 4m

Output calculated for:

Soil type

A fine sand

B medium sand

C coarse sand

D coarse sand + gravel

E gravel

Decisive grain size

100µm

235µm

440µm

1.30mm

7.00mm

Situ density

1,900kg/m3

1,950kg/m3

2,000kg/m3

2,100kg/m3

2,200kg/m3

D

E

1000

2000

3000

4000

5000

Pipeline length in meters

C

A

B

6000

7000

IHC Holland bv

Molendijk 94

P.O. Box 204

3360 AE Sliedrecht

The Netherlands

Phone +31 (0)184 41 15 55

Fax +31 (0)184 41 18 84