PROPOSAL FOR A 

LUNAR TUNNEGBORING MACHINE 

iy 

Christopher S. Allen 

David W. Cooper 

David Dada Jr. 

Christopher S. Mahendra 

Michael A. Tagaras 

presented to 

Professor Stan Lowy 

Department of Aerospace Engineering 

Texas AM University 

May 5,1988 

IliASA-CR- 184Vb6) PBOPCSAL ECfr A LUIAR #89- '17753 

lENPEL*BCBIYC MACEIICE Final Fc:fcrt (Texas 

BE8 Univ.) 67 F CSCL 13B 

Unc la d 

H1/31 0189653 

NASANSRA GRANT , 

A 
A need exists for obtaining a safe and habitable Lunar Base that is free from the 

hazards of radiation, temperature gradient, and micrometeorites. A device for excavating 

lunar material and simultaneously generating living space in the subselenian environment 

has been researched and developed at the conceptual level. Preliminary investigations 

indicate that a device using a mechanical head to shear its way through the lunar material 

while creating a rigid ceramic-like lining meets design constraints using existing technology. 

The Lunar Tunneler is total11 automated and guided by a laser communication system. 

There exists the potential for the excavated lunar material to be used in conjunction with 

a surface mining process for the purpose of the extraction of oxygen and other elements. 

Experiments into lunar material excavation and further research into the concept of .a 

mechanical Lunar Tunneler are suggested. 

.. 

11 
The authors would like to thank the following people for the assistance they provided 

in making this report possible. Professor Stan Lowy and Dr. Tibor Rozgonyi provided 

invaluable guidance. Special thanks also to Dr. Thomas C. Pollock, Dr. T. Schobeiri, and 

Dr. Erian Baskharone. 

... 

111 
Abstract 

Acknowledgments 

List of Figures 

Introduction 

Cutterhead 

Glass- Forming Sections 

Propulsion? Maneuvering, and Control 

Material Excavation System 

Internal Power Cycle 

Conclusion 

References 

Appendix A: Mechanical Cutterhead Specifications 

Appendix B: Equations for Internal Power Cycle 

.. 

11 

... 

111 

v 

1 

- 

1 

14 

25 

35 

41 

56 

58 

60 

61 

iv 
Figure 

1. Radiation Dosage on Lunar Surface 

2. Micrometeorite Flux on Lunar Surface 

3. Lunar Tunneler 

4. Rotating Mechanical Head with Disc Cutters 

5. Disc Cutter Schematic 

6. Cutter Ring Schematic 

7. Heating Section 

8. Ceramic Section 

9. Cooling Section 

10. Thrust Cylinder 

11. End View Showing ‘‘X” Configuration of Grippers 

12. Propulsion System by Lovat 

13. Hydraulic Annular Steering Segment 

14. ZED Instruments Control System 

15. Location of ZED Target Unit and Inclinometer 

16. ZED Instruments Axes 

17. Possible Obstruction of Laser Beam 

18. Bucket-Type Conveyors 

19. Excavation System from Flexowall, Inc. 

20. Excavation Systems 

21. Excavation Concept 

22. Holding Tank 

Page 

2 

3 

6 

8 

10 

11 

1; 

19 

21 

26 

26 

2; 

28 

31 

31 

32 

35 

37 

38 

39 

41 

42 

V 
23. Holding Tank Operation 

24. Excavation Dump Truck 

25. Dump Truck Suspension 

26. Dump Truck Frame 

27. Internal Power Cycle for Lunar Tunneler 

28. Schematic of SP-100 Reactor 

29. Los Alamos Heat Pipe 

30. Disconnecting Reactor 

31. Radial Turbine Data 

32. Power Requirements for Lunar Tunneler 

33. Percent Down-Time for Lunar Tunneler 

43 

44 

45 

46 

48 

50 

50 

51 

52 

35 

56 

vi 
A Lunar Base is being considered by NASA because of the numerous advantages it 

would offer. These advantages include use as a vacuum testing ground for conducting 

experiments, mining of certain elements, and a threshold for further space exploration. 

Problems such as high radiation, solar flare danger, large temperature changes, and micrometeorite damage arise when locating a base on the surface of the Moon. A method 

must be obtained to shield the Lunar Base from these environmental hazards while minimizing transport weight and cost. 

An underground Lunar Base is preferred over a surface base for various reasons. Two 

methods. trenching and back-covering, could be used in the design of a protected Lunar 

Base. However, neither of these techniques is able to provide total environmental protection, and both require extensive ground-moving equipment. A base located 10 to 30 

meters (about 30 to 100 feet) beneath the lunar surface will be effectively shielded from all 

environmental hazards. Xormal radiation dosage on the lunar surface is approximately 30 

rem per year, increasing to approximately 70 rem per hour during an intense solar flare. 

(See Figure 1.) Long-term exposure to these radiation levels has been proven to be fatal. 

Establishment of a lunar base at the suggested depth will ensure that the radiation levels 

do not affect the inhabitants. A second argument in favor of the underground base is the 

large temperature change. The Moon, having a temperature difference of approximately 

250°K between lunar day and night, creates heating and cooling difficulties, associated 

structural deformities, and health hazards. For a subsurface Lunar Base the temperature 

change is reduced to a negligible amount. In addition, micrometeorites call for design considerations to account for structural damage, limiting travel on the lunar surface as well 

1 
as requiring a larger quantity and weight of structural elements to be brought from Earth. 

(See Figure 2.) With all of the above design considerations in mind, it was proposed 

that large living spaces might be created beneath the lunar surface instead of locating 

the base on the surface itself. These living spaces could be created be placing habitation 

modules inside the tunneled-out areas and then sealing the tunnels through an air-locking 

technique. A tunnel-boring machine, a Lunar Tunneler, was considered to be the most 

efficient method of creating large amounts of living space. 

I IRadiation Dose for a Person Exposed on the Lunar Surface 

GCR -30 REtl/yr 

Avg . 

Sol a r 

Bc kg rd - 

Large 

Sol a r 

ilrrc up to 70 REM/hr 

negl i gi bl e 

2 
.1 

1 

10 

100 

1000 

30,000 

1,200 

300 I 

.6 

-00 1 

There were several preliminary general design considerations for the Lunar Tunneler. 

These included total automation, lack of dCbris removal, absence of utility lines, and the 

ability to handle lunar material of different sizes and hardness values. For reasons outlined 

below neither of the methods reviewed, melting or mechanical, could meet the constraint 

of no dibris removal. 

I 

In considering a Lunar Tunneler, the trade-offs and advantages of different methods had to be examined. The lack of an atmosphere reduced the considerations to two 

methods, thermal melting and mechanical excavation. Choices for power generation were 

3 
between solar and nuclear because of the constraints for a totally automated tunneler and 

elimination of the need for fuel. Using a small nuclear power plant was preferred over solar 

power generation because the latter could not produce sufficiently high amounts of energy 

due to low efficiency and the problem of energy storage during lunar night. 

Purely mechanical tunnelers and tunnelers that rely only on melting both offer several 

advantages and disadvantages that were evaluated in coming up with a Lunar Tunneler 

design. Initially, thermal melting was assumed to be the best method because of the 

small number of moving parts and less down-time expected. It was also considered that 

melting would have allowed the lunar material to be packed into a much smaller space 

through density changes, obviating the need to dispose of any excavated waste material. 

Because of the lack of mechanical dkbris removal equipment this method was believed to be 

comparatively fast. As a consequence, this kind of tunneler was assumed to have greater 

potential for total automation. However, a nuclear power source would not meet the heat 

requirements of such a design. For this reason the mechanical tunneler was examined 

in greater detail. Initially. this type of tunneler was thought to be relatively labor- and 

equipment-intensive. Consequently, it was thought to be a slower method than melting 

as well. However, further research revealed that both techniques yield approximately the 

same tunneling rate. In addition, with the mechanical technique, producing sufficient 

energy to meet the high temperature requirements is no longer a factor. Extensive data 

from tunnel-boring machines on Earth indicate that down time due to breakage of moving 

parts is not as great as initially thought. Also, automation can be easily achieved. 

An underlying design objective was to use as much existing technology as possible in 

the design in order to lower cost and minimize down-time. Most Earthly tunneling devices 

4 
use mechanical means; melting tunneling devices are almost nonexistent. Digging through 

lunar material would be executed by using a rotating mechanical head with disc cutters. 

This head design was derived from methods used in sizing existing Earth tunneling devices. 

Propelling the Tunneler through the lunar material would be performed by adapting a system produced by Lovat' of Ontario, Canada. To control and guide the Lunar Tunneler. 

a laser communication and.computer system was adapted from existing technology produced by ZED Instruments, Ltd.2 in the U.K. Transporting the excavated lunar material 

would be accomplished by a conveyor belt design manufactured by Flexowall, I~c.~ By 

using these existing systems in conjunction with the new technologies developed for lining 

and supporting the tunnel, a viable Lunar Tunneler has been conceived. 

The Lunar Tunneler design is illustrated in Figure 3. The device essentially consists 

of a rotating mechanical head which shears its way through the lunar material while 

simultaneously creating a rigid glass-like ceramic lining to support the tunnel walls. In 

order to propel the tunneler forward a hydraulic gripper propulsion system is used. The 

excavated lunar material travels to the material holding tank in the rear of the tunneler 

using the conveyor system. Periodically, the lunar material contained in the holding tank 

is transferred to the dump truck which then dumps the excavated material outside the 

tunnel. 

5 
Above, in Figure 3, is the general design concept for a Lunar Tunneler. 

detailed explanation of each section is discussed in the remainder of this report. 

X more 

6 
The rock-cutting technique is the primary means by which the Lunar Tunneler creates 

space beneath the lunar surface. Rock cutting involves impressing the rock surface with 

a cutting tool while simultaneously pushing forward. The groove that is created by the 

cutter then fractures, and the crushed rock is left behind as it progresses forward. In 

order to indent the rock effectively, a normal force, or thrust, must be imparted to the 

rock surface. Also, a forward rolling force is required to propel the tunnel-boring machine. 

The rolling force, combined lvith a torque to rotate the cutterhead. drives the machine 

forward through the rock. -4 tunnel-boring machine is designed to supply these forces. 

The machine acts to generate thrust to push the cutterhead forward while simultaneously 

producing a torque to turn the cutter and oppose the tangential resistive forces. 

The face of the cutter, shown in Figure 4, rotates using motors located behind the 

back panel of the cutterhead. The torque reaction acts through the main beam, which is 

connected to the cradle assembly and gripper pads. It is then transmitted to the cutterhead 

by way of pinion gears connected to a fairly large diameter bull gear which enables the 

cutterhead to rotate around the main bearing. 

7 
The determining factor in the operation of the torque system is the quantity of power 

used by the motors, expressed in terms of amperage: if the motors draw too much electric 

current, they could overheat and cause internal damage. Motors are usually designed to 

provide 149kW (200 horsepower) at a maximum amperage of 216A. On Earthly tunnelboring machines, ammeters on each motor allow the human operator to make adjustments 

in the thrust, thereby keeping the amperage close to the maximum operating rating. 

The equation for determining the amount of torque transmitted to the face is expressed 

8 
as 

LVm Pe 

2n s To = ~ 

where To is the torque, II’, is the number of motors, P is the power consumed by each 

motor, e is the motor efficiency, and S is the rotational speed of the cutterhead in revolutions per unit time. hlotor efficiency can be estimated from the operator records of 

average amperage consumed in a given work shift. The combined efficiency of the motor 

and drive train is usually about 85%. 

The average rolling force per cutter blade, t, can be estimated by calculating the 

product of the torque, To. and the inverse of the weighted average cutter distance from 

the center of the face. R. It is expressed as 

-Ym Pe 

nZnSR 

t= 

Whole face tunnel-boring machines commonly use a single disc cutter as the cutting 

tool, and this type is employed in the Lunar Tunneler. (See Figure 5.) This class of cutter 

is composed of a disc on a hub connected to a central shaft protruding from either side 

of the unit. The cutter is mounted on a steel saddle so that it can freely rotate about its 

longitudinal axis. This steel saddle, in turn, is bolted to the face of the cutterhead. The 

typical single disc cutter is 39.4cm (15.5in) in diameter and can transmit up to 45,000 

pounds of force to the rock face. 

9 
W 

b 

I 

1 

F'IGWU 5: DISC CUTTER SCHEMATIC (FROM THESIS BY PRISCILLA WELSON) 

uFThe cutter ring, shown in Figure 6, is composed of a highly alloyed heat-treated steel. 

The cutter ring is attached to the hub by first heat-shrinking it and then locking it in 

place with a welded split ring. The hub rotates on tapered roller bearings that are isolated 

within the hub behind metal-to-metal face seals. The inside of the hub is filled with oil to 

protect and lubricate all moving parts. 

10 
Cutters are differentiated according to their locations on the face of the cutterhead. 

The four central cutters are usually about 30.5cm (12in) in diameter and are mounted 

on two twin-disc assemblies. These middle-most cutters rotate within the central 30.5cm 

(12in) radius of the cutterhead; consequently, they must withstand significant scuffing. The 

next set of cutters are the face cutters. They are generally 39.4cm (15.5in) in diameter 

and are located between the center cutters and the outer edge of the cutterhead face. The 

face cutters tend to be positioned across the face profile on a line with a constant radius of 

curvature. The outermost cutters are the gage cutters. These cutters are generally 39.4cm 

(15.5in) in diameter and are positioned on the outer extremes of the cutterhead 

11 

where it 
curves to form the edge of the three-dimensional tunneler. 

In order to determine the number of cutters required for a cutterhead of a certain 

diameter, the total diameter of the cutterhead is divided by the ideal diameter stroke for 

each cutter. The ideal diamter stroke is taken as 15.2cm (sin) for the Lunar Tunneler, since 

this size would be just sufficient to loosen the lunar material while minimizing abrasion and 

friction. Accordingly, the centrifugal force would cause the lunar material to spread out 

to the perimeter of the tunnel, after which it would be collected by the hoppers. For a 4m 

(13ft) diameter cutterhead on the Lunar Tunneler: twenty-six cutters would be required. 

Cutterhead specifications are given in Appendix A. 

The gage cutter derives its name from a term used by the drilling industry to describe 

drilling tools that determine the diameter of the bore hole. The gage cutter functions to 

excavate rock only along the diameter of the tunnel. Several gage cutters are positioned 

at increasingly greater angles to the direction of thrust as the transition from face to side 

excavation occurs. Consequently, the gage cutters are subjected to substantial tangential 

forces that act perpendicular to the rolling direction. Abrasion of the disc ring and damage 

to the roller bearings result from these forces. As the radial distance from the center of 

the cutterhead increases, the distance between the gage cutter paths decreases rapidly. By 

contrast, the paths of the face cutters are typically 7.5cm (3in) apart and constant. 

The performance of tunnel-boring machines is generally measured in terms of progress 

or advance rate. The two main factors determining the advance rate are the rate of 

excavation or penetmtion rate of the tunnel-boring machine and the amount of time allowed 

for the excavation process. The advance rate is defined as the product of the penetration 

12 
rate and machine utilization. Machine utilization is the percentage of available work shift 

time during which excavation or rock penetration takes place. 

Several factors affect the performance of the tunnel-boring machine. The overall 

machine configuration is the major element. This includes thrust, torque, gripper reactions, 

gripper configurations, capacities, steering mechanism, and overall machine stiffness. A 

second factor is cutterhead design, which includes the cutterhead profie, spatial array 

of the cutters, spacing of the cutters, and muck-removal components. In addition, the 

design of the cutters themselves plays a major part in the performance of the tunnelboring machine. Included in this category are the type of cutter, composition, geometry. 

and roller bearing capacities. .Also, it should be noted that the disc: hub, and steel saddle 

of a gage cutter may be subjected to more abrasion than those of a central cutter. 

Operation of a tunnel-boring machine necessitates careful record- keeping and examination of wear-prone parts. Operating shifts should be numbered sequentially and include 

the day, date, shift times, and shift duration. A shift is defined as the total distance 

traveled by the cutterhead due to the thrust in one maneuver. The tunnel stations should 

be recorded at the beginning and end of each shift. In order to determine the operating 

hydraulic pressure, the thrust cylinder pressure and gripper cylinder pressure should be 

recorded for each thrust cylinder restroke. Cutterhead motor status can be determined 

by recording the number of functioning motors and operating amperage for each thrust 

cylinder restroke. The hydraulic fluid and lubricating oil temperature should be checked at 

least once during each shift. In order to maintain an adequate cutter wear record, several 

items should be checked at each cutter change. These include recording the cutter position 

number, cutter hub identification, type of disc on the cutter, a full description of reason for 

13 
replacement, and time of replacement. Finally, front and rear laser target readings should 

be recorded at least for the beginning and end of each operating shift. 

Down-time for the mechanical cutterhead assembly occurs in the areas of electrical 

systems, hydraulics, cutter replacement, stroke recycle, cutterhead motors, and the excavation conveyor. Electrical system down time is due to loose or broken wires in the control 

panel or defective arc welding; it is estimated at 1.6% of work time. Hydraulics down-time 

is due to leaks in gripper cylinders and replacement of hydraulic hoses and pressure valves: 

it is estimated at 8.2%. Cutter replacement can take place kyhile the system is already 

down. A 0.3% down-time is estimated for motor overheating, and a 1.5% downtime is 

estimated for repair and splicing of the belt conveyor. Stroke recycle down-time amounts 

to an estimates 3.9%. 

Several areas of further research into the mechanical cutterhead are suggested. Linear 

cutter tests chould be performed on a wide variety of rocks of diverse strength, stiffness, 

and porosity. Replacement rates for bearing deterioration and defective wear should be 

analyzed. Also, muck gradation analysis can aid in determining comparative machine 

efficiencies in different rocks. Finally, the hopper between the cutterhead and main beam 

should be arranged to provide the greatest access to remove muck blockages and to reduce 

the chance of recurring blockages. 

Just behind the cutterhead would lie the heating section of the Lunar Tunneler. The 

14 
heating section would serve to melt a layer of lunar material within the excavated tunnel 

to a depth of only a few inches. This molten material could then be cooled to form a rigid 

ceramic material suitable for lining the interior of the tunnel. 

The ceramic lunar material would provide designers with a virtually inexhaustible 

supply of strong, rigid structural material. Unlike ceramic on Earth, lunar ceramic can 

withstand much greater forces and support larger loads. The anhydrous hard vacuum 

conditions on the Moon cause the silicate materials to have different mechanical properties 

compared to what they would haye on Earth. 

On Earth, the damage state of the surface and the corrosion process, due to the 

presence of water in microcracks, are used in determining the fracture strength of brittle 

amorphous and crystalline materials. Crystalline silicates are greatly affected by dislocation motion caused by the presence of small amounts of water at high temperatures and 

pressures. Polar water molecules will cause fragile hydrogen bonds to substitute for the 

Si0 bond. This hydrolyzation is the weakening mechanism in the Si0 bonds since the 

network-forming action of the Si0 bond produces the inherent strength of the silicates. 

Dislocations and highly stressed microcrack edges are the primary sites where the 

hydrolyzation occurs. At these locations the water causes increased movement of the dislocations, so that the cracks can be propagated with a lower applied stress; the net result 

is a general weakening of the structure. Since hydrolyzation is a thermally activated progression, it affects all temperature-dependent mechanical properties of silicates, including 

brittle and plastic creep, fatigue, and crack growth. 

15 
Experimentally obtained data attest to the fact that anhydrous conditions allow for 

greater strength in lunar materials. When samples of simulated rock from lunar maria were 

degassed and subjected to strength tests in a moderate vacuum, compressive strength was 

found to be twice as great as that under conditions of one hundred percent humidity. 

In addition, it has been found that a decrease in the partial pressure of water vapor 

directly reduces the subcritical crack velocities in simulated lunar glass by several orders 

of magnitude. From this it can be deduced that, in the presence of a strong vacuum 

environment, static fatigue processes will be severely restricted or completely absent. The 

dissipation of vibratory energy in lunar rocks has also been found to be affected by minute 

quantities of water. Hydrolysis of crack surfaces and the resulting loss of surface energy 

is a probable cause for this diffusion. Finally, lunar soil samples that were subjected to 

atmospheric moisture contamination under moderate to strong vacuum conditions were 

found to have sharply different mechanical properties from those that were not. 

The hydrolytic weakening process is inescapable on Earth due to the presence of water 

during the fabrication of manmade and natural materials into useful products. Its effects 

are felt in such diverse areas as solid earth mechanics, drilling and mining, glass and 

ceramic technology, fiber optic communications, and laser optics. 

The small amounts of water present in lunar soil samples are probably due to contamination of some sort. This contamination could have been oxidation of hydrogen deposited 

by the solar wind, or it could have occurred after the specimens were brought to Earth. 

Consequently, contamination of all kinds must be avoided in order to protect lunar materials from water-induced weakening. 

16 
With the above soil considerations in mind, the heating section was designed to use 

electrical resistance heating elements in conjunction with a thermally conductive, chemically nonreactive shield. (See Figure 7.) Carbon-carbon composite is proposed for the 

heating element, and a molybdenum-tungsten alloy, Mo-30W, is proposed for the shield. 

The heating section would be two meters (six and a half feet) long. 

I HEATING SECTION 

1) MELTS AT @1500°K 

2) TOTAL RESISTANCE HEATING 

WlTH ELECTRICITY SUPPLIED 

BY RADIAL TURBINE SYSTEM 

3) MATERIAL MAKEUP OF 

TEMP. OF 2829°C AND 

IS INERT TO GLASS. 

MO-30W WITH A MELTING 

4) CARBON/CARBON COMPOSITE 

FOR RESISTANCE HEATING 

5) ARGON GAS USED TO 

MAXIMIZE HEAT TRANSFER 

I FIGURE '7: HEATING SECTION 

17 
Fireproofed carbon-carbon composite is suggested for the resistance heating element 

because of its light weight and very high melting point of 3,550"C. Carbon-carbon composites also have strengths that are among the highest for fiber-reinforced composites. 

Although nichrome and carbon are both viable resistant elements and less expensive than 

carbon-carbon composite, they were ruled out for this application because they both have 

lower strengths and lower melting points. 

A shield composed of k10-30LV is proposed to uniformly distribute the heat to all of 

the lunar material to which it comes into contact. Alloy ?vlo-301i- is one of the most readily 

available and least expensive of refractory alloys and has a high melting temperature of 

2,829"C. Its excellent thermal conductivity makes it ideal for this application. In fact, only 

silver, gold, copper, and aluminum have better thermal conductivities than molybdenum 

and tungsten, and all have drawbacks that preclude their use in this application. Other 

important properties of hlo-30n' are its ease of fabrication and cleaning and chemical 

nonreactivity to most molten glasses. 

Argon gas would be used to fill any gaps between the heating element and outer shield. 

Argon would be used in order to maximize heat transfer from the heating elements to the 

shield without the losses associated with air. Because argon is a noble gas, it would not 

decompose or react with the Mo-30W shield or the carbon-carbon composites. 

The ceramic section of the Lunar Tunneler would serve to separate the heating section 

from the cooling section, thereby minimizing heat transfer between them. (See Figure 8.) 

18 
This section would be four meters (thirteen feet) long. Glass-ceramics provide a wide 

choice of materials for fulfilling the primary requirements as well as the requirements of 

resisting liquid permeation and nonreactivity to the molten glass. 

CERAMIC SECTION (STOPS HEAT TRANSFER) 

HEATRON W GLASS 

CERAMIC 

MANUFACTURED BY 

FUJI FILM CO. 

______ 

FIGURE 8: CERAldIC SECTION 

19 
Glass-ceramic materials are defined as polycrystalline solids containing a minimal glass 

phase. They are manufactured by melting glass and controlling the crystallization, number 

of crystals, crystal growth rate, and crystal size by the appropriate heat treatment. 

For the purpose of evaluating mechanical properties, glass-ceramics can be regarded 

as composite non-porous materials consisting of minute crystals evenly distributed through 

the glass phase. Glass-ceramics in general have improved mechanical properties over 

glass while retaining the characteristic features of glass, such as transparency. They have 

greater bending strengths and greater elastic moduli than do glass and ceramics separately. 

Through modifications of the surface of the glass-ceramic, even higher strengths can be 

achieved. Thermal properties can be altered by controlling the size of the glass phase. For 

optimum chemical resistance to be achieved, the residual glass phase must be free of high 

concentrations of alkali metals. 

Heatron W, a glass-ceramic product manufactured by the Fuji Photo Film Company. 

is proposed for the ceramic section of the Lunar Tunneler. This glass-ceramic is highly 

resistant to thermal shocks, exhibits low thermal conductivity, and has a maximum working 

temperature of approximately 1,500"K. The maximum working temperature can be raised 

even higher if the amount of glass is limited upon formation of the glass-ceramic. Chemical 

resistance and lack of reacttivity were also factors influencing this choice, and Heatron W 

has superior properties in both cases. 

The cooling section would act to lower the temperature of the molten lunar material 

20 
so that the material would crystallize and form the rigid ceramic needed to support the 

tunnel walls. (See Figure 9.) The cooling section is not intended to cool the molten glass 

to the temperature of the surrounding undisturbed lunar material but rather to cool it 

sufficiently so that a crystallization phase change can take place. Once this ceramic lining 

has hardened, it can be further reinforced by sealing with rubber or another liner such as 

sputter-coated metal. This second reinforcement may be required to protect the tunnel 

wall from weakening due to hydrogen and any other gases that may remain trapped in the 

tunnel. 

COOLING SECTION ( @%OO K) 

1-COOLING SUPPLIED BY 

DUMPING EXCESS HEAT 

TO EXCAVATED REGOLITH 

AND BY COOL SIDE 

OF ME TURBINE SYSTEM 

2-FLUID: LITHIUM 

FLOWING IN PIPING 

3-LITHIUM THEN RETURNS 

SP-100 NUCLEAR 

FOR REHEATING 

4-ARGON GAS USED TO 

MAXIMIZE HEAT TRANSFER 

5-MATERIAL: MO-SOW 

FIGURE 0: COOLING SECTION 

21 
Perhaps the most economical tunnel liner would be a form of lunar concrete. A lunar 

concrete or cementitious product could be used to line the tunnel wall and protect against 

solar wind, cosmic rays and other types of radiation, and micrometeorites. On Earth 

cement is primarily composed of limestone, clay, and iron ore. Lunar materials have been 

found to contain sufficient quantities of silicates, alumina, and calcium oxide to make it 

possible for a cementitious material to be produced. However, the quantity of calcium 

oxide on the Moon is rather low compared to that of the silicates and alumina. Also, 

quenched shock-melted lunar glass has been found to be amorphous and has the potential 

for use as a cementitious material if crushed to a very fine particle size. This quenched 

shock-melted glass is found in abundance in the crater rims. 

The cementitious elements present on the lunar surface have been determined to have 

condensation temperatures around 1,400"K. This condensation temperature is estimated 

to be at least 200°K above those of the non-cementitious materials. Consequently, the 

separation of cementitious and non-cementitious is not a problem and can easily be achieved 

through a melting process. In such a process, a high temperature of 3,OOO"K would be 

required for elemental evaporation. 

There is an abundant supply of aggregates for use in a lunar cement. Lunar concrete, 

like Terrestrial concrete, would be composed would be composed of a cement paste and 

aggregates. Lunar rocks generally have specific gravities close to 2.6 and are believed to 

be suitable for use as aggregates. 

22 
The effects of temperature changes on the lunar concrete should be minimal. While 

the surface temperature on the Moon varies from -150°C at night to 120°C during daylight, the strength of concrete is virtually unaffected by the extreme temperatures. Also, 

in the presence of zero percent humidity, concrete neither gains nor loses strength as the 

temperature drops. Consequently, with only minimal hydrogen in the lunar soils, a lunar 

councrete should retain its strength well. Because concrete exhibits low thermal conductivity, high specific heats, and thermal stability up to 600”C, lunar concrete should prove 

to be an excellent heat-resistant structural material. 

Several other properties make lunar concrete worth considering for lining and structural applications. It exhibits satisfactory gamma-ray absorption and resists abrasion well. 

In addition, a loss of free moisture under hard vacuum conditions would have no effect on 

the strength of concrete. 

The cooling section operates by using a LIo-30W outer shield and liguid lithium 

contained in thermal pipes. The pipes would bring refrigerated lithum coolant from the 

SP-100 atomic reactor (see “Internal Power Cycle”) and circulate it directly behind the 

hfo-30W shield. The shield would help to uniformly transfer the cooling action of the 

lithium to the molten lunar material while simultaneously removing the heat from the 

lunar material. The liquid lithium then carries the heat through the Lunar Tunneler and 

uses it to partially heat the excavated lunar material in the holding tank (see ‘‘Material 

Excavation System”). Since more of the lunar material is excavated than heated, the 

excavated lunar material will only be gradually heated rather than melted because the 

heat will be transferred to a large quantity of material. Also, the heat losses experienced 

in the lithium pipes as the lithium travels from the glass-forming section to the holding 

23 
tank would lower the temperature such that melting of the excavated lunar material could 

not occur even if it were a design objective. The space between the lithium thermal pipes 

and the Mo-SOTV shield is backfilled with argon gas to maximize heat transfer between 

the pipes and the shield. Lithium is suggested as the coolant because it would achieve 

minimal heat loss while circulating through the Lunar Tunneler after leaving the nuclear 

reactor. Based on heat transfer calculations, twelve meters (thirty-nine feet) is the ideal 

length for this section. 

24 
The Lunar Tunneler would be provided thrust and torque by hydraulic systems similar to those used in tunnel-boring machines on Earth by Lovat Tunnel Equipment, Inc. 

of Toronto and Atlas Copco Jarva, Inc. of Solon, Ohio.'t4 A system of hydraulic cylinders provides for the generation of thrust and torque for the rotary cutterhead and for 

 maneuver^.^ Maneuvering is automated in conjunction with a laser/inclinometer guidance 

system. Information given by Nelson4 concerning thrust and torque systems is outlined 

below. 

Hydraulic cylinders are located around the drive shaft as shown in Figure 10. Eight 

gripper pads in an "X" configuration anchor the Lunar Tunneler to the tunnel wall (see 

Figure ll), and the thrust is transferred to the cutterhead through the torque reaction tube 

shown in Figure 10. Thrust would be applied in cycles, and each cycle should advance 

the Lunar Tunneler by 1.2 to 1.5m (3.9 to 4.9ft). The maximum pressure in the cylinders 

on Terrestrial machines is around 25MPa (3,6OOpsi), providing a maximum forward thrust 

of around 9,000kN (2,00Okip), and loads of the same order are expected on the Lunar 

Tunneler. Simply moving the cuttinghead forward without touching the rock face would 

require about 3.5MPa (5lOpsi). Typically, the thrust cylinders in tunnel-boring machines 

are about 330mm (13in) in diameter and have a stroke length of about 1.5m (4.9ft). 

25 
ORIGIN 

OF PO( 

PAGE 

QUAL1 

TOROUE REACTION TUBE 

;INGLE DISC SUPPORT LEG 

CUTTER 

b) Thrust System 

IS 

TY 

CUTTER MEA0 

[: CMYOQ 

' BULLGEAR SUPPORT LEG 

[MAIN BEAR INC. SHAFT 

SINGLE MSC 

rUTTER 

FIGURE 10:THRUST CYLINDER (THESIS BY PRICILLA WEISON) 

FIGURE .11: END YIEW SHOWING 'xf CONFIGURATION OF GRIPPER PADS 
(-JRI,Gp:p.L F:3,Z IS 

OF POOR QGALIT'f 

Figure 12 illustrates the four-step thrust cycle for an Atlas Copco Java machine. First, 

the gripper pads are extended to anchor the main body. Second, the drive shaft is driven 

forward until the hydraulic cylinders have been extended the entire stroke length. Third, 

a support leg is lowered and the gripper pads retracted. Finally, the main body is pushed 

forward into position, the gripper pads are extended and the support leg retracted, and 

the cycle begins anew. In practice, the thrust actually transmitted to the cutterhead is 

the force produced by the hydraulic cylinders less the sliding resistances of the machine. 

FROM LOVAT 

EXISTING 

FOUR GRIPPER SYSTEM 

SINGLE MAIN THRUSTER 

HIGH HYDRAULIC PRESSURE 

FROM PRESSURE AMPLIFIER 

:I Pads IMtractcd and war Leu Extendeddl Main Dodv worad Forward 

For generation of torque for the cutterhead, motors are anchored to a frame at the rear 

of the drive shaft as shown in Figure 10. The gripper cylinders connecting the main body to 

the gripper pads provide reaction for torque, and torque is transfered through pinion gears 

27 
and bull gear located at the rear of the drive shaft. Thrust and torque are transmitted 

to the cutterhead by way of a system of tapered roller bearings. The combined weight of 

the hydraulic thrust and torque system and cutterhead is around 2,600k;”i (58Okip). The 

motors used to produce torque are described under “Cuttinghead.” 

The hydraulic cylinders can also be used to maneuver the machine. The cylinders are 

connected to a rear segment of the tunnel-boring machine, and different pressures can be 

applied by the hydraulic cylinders to the face of this segment. The resulting angle between 

the segment and the rest of the machine can be controlled for steering left, right, up, or 

down. (See Figure 13.) 

HYDRAULIC CYLINDER / 

I II I \\ II 

SEGMENT’ CONTAINING 

ZED EQUIPMENT 

__ ~~ - 

FIGURE 13 HYDRAWC ANNULAR STEERING 8EGMENT 
While tunnel-boring machines on Earth are usually manned by an operator, this would 

not be feasible for the Lunar Tunneler due to heat and radiation. (See “Glass-Forming 

Sections” and “Internal Power Cj-cle.”) The Lunar Tunneler would have a computer in 

the rear portion of the machine to serve as the operator. Desired tunnel axis, maneuvers. 

and other inputs would be programmed into the computer as needed before operation, as 

well as commands to shut off power after a specified time or in the event of a fault condition. This “automated operator,” coupled with the automated guidance system described 

hereafter, would be a powerful tool for accurate maneuvering. Although there is at present 

little experience with automated steering systems in tunnel-boring machines on Earth. the 

capability exists, and it is expected that they will be used more frequently in the 1990s. 

A TG-260 Tunnel Guidance System. manufactured by ZED Instruments, Ltd.’ in the 

lT.K., is proposed for guidance of the Lunar Tunneler. This system. which represents the 

state of the art in automated guidance systems, uses a laser beam and inclinometer to 

provide precise position and attitude information. Such a system would obviate the need 

for surveying and measurement: this would save not only time but also the maintenance 

and material costs that could ensue from deviations by the Tunneler from the desired tunnel 

axis. These Tunnel Guidance Systems have been in use on Earth for several years, and they 

have proven to be reliable tools for precise tunneling about any of the three orthogonal axes 

of motion. They have also been useful for rendering even the most cumbersome tunnelboring machines easy to steer. Information provided by ZED Instruments’ is outlined 

below. 

On the proposed Lunar Tunneler, steering is guided by a computer located in the 

rear portion. The computer reads all position and attitude data provided by the TG-260 

29 
and makes any needed course corrections. ZED Instruments could provide hardware and 

software that would be compatible with the guidance system. 

The components of the TG-260 system are shown in Figure 14. From some distance 

behind, a collimated helium-neon laser beam would be aimed at a target unit located in 

the rear of the Lunar Tunneler but in front of the Dump Truck (see “Material Excavation 

System”) as shown in Figure 15. (The Dump Truck would be designed to not obstruct the 

beam.) The laser would require less than 2mlV (2.682 x hp) of power and would have 

a spot size of 12mm to 25mm (0.47in to 0.98in). The inclinometer would also be located 

in the rear of the Tunneler, along with linear distance measuring equipment located on the 

Tunneler. An engineer’s unit that receives all survey data is located near the laser, and 

a remote computer with a terminal and printer is located above ground. possibly several 

kilometers away. On a Terrestrial tunnel-boring machine. an operator’s monitor usually 

would be located on the machine; the unmanned Lunar Tunneler would not require this. 

30 
I ZED INSTRUMENTS LTD. LASER CONTROL SYSTEM 

ANNULAR STEERING SEGMENT 

ZED TARGET UNIT 

ZED INCLINOMETER I -\LDUMP TRUCK 

SEGMENT CONTAINING 

ZED EQUIPMENT 

L 

FIGURE 15: IDCATION OF ZED TARGET UNIT AND INCLINOYETER 

I 

I 

-1 -z 
The TG-260 system determines five coordinates from the laser beam and inclinometer. 

Coordinates 2, y, and lead are determined relative to the laser beam; coordinates roll and 

look-up are determined relative to the vertical. Moreover, the linear distance measuring 

equipment provides a z coordinate, the distance along the tunnel. (See Figure 16.) 

I 

I 

I 

I 

I 

I 

d...: 1, -. I. 

* 

The data are provided continuously in digital form to the steering computer; they 

are alm made available at the engineer's unit at some distance behind the Tunneler and 

at the above-ground terminal. Using the data, the computer would steer the machine 

to minimize deviations. The data can also be used to provide predicted position and 

attitude data. For example, angular deviations can be shown before the Tunneler leaves 

the desired axis. These would not only eliminate the need for large course corrections but 

32 
also allow for better understanding of the Tunneler maneuverablity. A complete record of 

the survey data with corresponding dates and times can be printed at a remote terminal 

automatically at regular intervals or at any time on command. Moreover, the data can 

remain in storage for thirty days after the power is shut off. Thus, a power failure or 

shutdown for maintenance does not destroy the survey data. 

The laser target of a TG-260 system has a range of reception of k58mm (i2.3in), a 

resolution of lmm (0.04in), and a precision of f2mm (50.08in) for the x and y coordinates. 

For the lead coordinate, the reception range, resolution, and precision are i100, =1. and 

12 milliradians (~5.7'~ 50.057", and +O.ll"), respectively. For the roll and look-up 

coordinates. the inclinometer has a reception range, resolution, and precision of i100, 0.1. 

and k1 milliradian (25.7": 0.0057", and &0.057'), respectively. 

The linear distance measuring equipment provides absolute measurements of distance 

along the tunnel length. The correct distance is registered and maintained. even in the 

event of movement after the power is shut off. Distance is measured from an arbitrary 

reference point with a reception range of -199.99m to +999.99m (-656.13ft to -3280.8ft)) 

resolution of lcm (0.4in), and precision of ilcm (~0.4in). 

The engineer's unit reads as input zero offsets (f999 milliradians/f57.2") for roll, 

lead, and look-up. Target coordinates with an allowed range of f9999mm (393.7in) are 

also read. For output the engineer's unit displays present and predicted x and y coordinates 

in millimeters and lead, look-up, and roll in milliradians. An analog monitor could also be 

provided to display the plan section and elevation graphically. 

33 
The above-ground computer reads as input designed tunnel axis points, wherein r 

and z have a possible range of i999.999m (i3280.83ft) and y has an possible range of 

z99.999m (k328.08ft) in intervals of 0.5m or lm (1.6ft or 3.3ft). Laser position is read 

as one point and bearing and zenith angles. The computer also reads other information. 

including date and time. The outputs on the monitor are the designed tunnel axis points 

as given, interpolated tunnel axis points, design data, survey and control data, and other 

information. A printer displays survey data as described before as well as any other output 

requested. 

A few problems are foreseen regarding placement of the laser. In the earliest stages of 

tunneling. the laser and engineer's unit can be placed at the tunnel entrance. If a curved 

tunnel is made. however. obstruction of the target view could necessitate repositioning of 

the laser inside the tunnel, thus changing the required r, y, and lead offsets. (See Figure 

17.) However, this problem has been confronted in small-bore tunneling on Earth and 

should not be insuperable. Another unresolved source of concern is that the laser and 

engineer's unit behind the Lunar Tunneler could prevent the Dump Truck from traveling 

to the tunnel entrance when necessary. Also, settling of dust in the tunnel sometimes 

affects the integrity of the laser beam. If the TG-260 system is used for the Tunneler, 

ZED Instruments can provide advice on these matters. 

34 
Md7E722dL &XCdVd7ZU,4r SYS7&M 

The problem of tunnel excavation is age-old, and to this day the rate of excavation 

is the limiting factor on how fast tunnels can be dug on Earth. In fact, the excavation 

rate of Earthly tunnels has not been increased significantly since the advent of tunnel 

digging. The excavation rate of the Lunar Tunneler, however, will not be the limiting 

factor. Because of the slow pace of the glass-forming process, the rate of lunar excavation 

must be adequate but not record-breaking. 

35 
After the lunar material is cleaved off by the rotating cutterhead, it is necessary to 

immediately move the material through the Tunneler and out to the rear so the progress of 

the Tunneler will not be impaired. It is then necessary to completely remove the material 

from the tunnel in order to leave behind space for radiation-free habitation. Finally, the 

excavated material should be placed so it may be easily recovered for future oxygen, water? 

or fuel production. 

The first problem is to move the excavated material to the rear of the Tunneler. The 

easiest way to accomplish this task is to use a belt conveyor. Several belt conveyors were 

looked at. beginning with designs that were already existing on Earthly tunnel-boring 

machines. 

The first and second designs that were looked at each use a bucket elevator. (See 

Figure 18.) This bucket elevator is located immediately after the cutterhead in the first 

design and at the rear of the Tunneler in the second. 

36 
These designs create problems in feasibility because of the systems' proximity to the 

heating section. Also introduced is a large amount of down-time and retardation of the 

excavation rate, due to the complex structure and precision-tuned nature of the bucket 

elevator. 

The problem was solved by taking into account the abundance of empty space in 

the center of the glass-forming section. The belt conveyor moves the loose material from 

directly behind the cutterhead up an incline over the heating section to the top of the 

Tunneler. The comparatively simple conveyor then levels off it continues to process the 

37 
material along the top of the Tunneler and over the propulsion section to the rear of the 

machine. (See Figure 19.) 

INNER EXCAVATION SYSTEM FROM FIlX0MI.L INC. 

SECTION TO HOLDING TANK 

EXISTING 

RELIABLE 

GREAT VOLUME CAPACITY 

CORD CONSTRUCTION 

38 
Several designs were examined to excavate the material entirely from the Tunnel. 

Two of these included methods of vertically transferring the material from the inside of 

the tunnel directly to the surface of the Moon. (See Figure 20.) 

The first of these methods has two problems: first, the amount of power required; 

second, the awkwardness of drilling upward through the glass lining and lunar soil while 

physically pushing the loose lunar material up to the surface. The disadvantage of the 

second method is that in would require a separate system on the surface of the Moon to 

drill downward and pump the material to the surface. The system should be as autonomous 

39 
as possible. 

An alternative to drilling more holes in the Moon is to take the material out through 

the mouth of the tunnel. The circular shape and relatively smooth walls of the tunnel 

could be used to act as a track for a modified Dump Truck that could be maneuvered with 

a computer, similar to that used to guide the Tunneler, to dump the material at a specific 

location. This concept was adopted for the Lunar Tunneler. 

Other considerations in the design of the excavation system include the need to dissipate excess heat created by the tunneling system and the desire to tunnel as continuously 

as possible without having to stop and wait for the Dump Truck. These added requirements led to the concept of a holding tank. This tank would not only store the excavated 

lunar material: it would also heat the material so the excess heat and lunar material can 

be excavated simultaneously. Putting the pieces together, the total concept for the Lunar 

Tunneler excavation system would be as shown in Figure 21. 

40 
r-iHr-i I I I 

I 1111 I I I I I 

NUCLEAR REACTOR TANK 

The belt conveyor adopted for the Tunneler is an existing design by Flexo~all.~ This 

conveyor system has high reliability, low down-time, high strength, and good flexibility. 

With large capabilities and high belt speeds, the belt conveyor capacity is much greater 

than necessary. Flexowall can also construct the conveyor with a heat-resistant material 

so that any heat transfer due to the heating section or friction of the rotating cutterhead 

will not impair the device. 

The holding tank would be a dual pan system as shown in Figure 22. A shallow pan 

used to maximize the slow process of heat transfer to the loose lunar material would be 

41 
placed above a larger holding cell that stores the already heated material while the Dump 

Truck is detached from the Tunneler. The heating system would be comprised of carboncarbon electrical resistance heating elements, much like in the heating section, powered by 

a radial turbine that utilizes the heat given off by the molten lunar material in the cooling 

section. The shallow pan would move further toward the rear as the belt conveyor dumps 

the material into it. When it is at capacity, a section in the bottom of the shallow pan 

opens, and the entire pan retracts while a stationary plate pushes the lunar material out of 

the hole and into a larger holding cell below. Material gathers in the large holding cell until 

the Dump Truck reattaches to the rear of the Tunneler below the larger cell. The bottom 

of the cell would then open, like double doors. and the material would be transferred into 

the Dump Truck. The doors would close and the Dump Truck would detach and dump. 

(See Figure 23.) 
FlGURE 23 HOLDING TANK OPERATION 

43 
The Dump Truck is the most complex and important component of the proposed 

excavation system. It should use the tunnel as a track but also be able to propel itself 

on the lunar surface. Moreover, the Dump Truck must dump the lunar material in a spot 

that will not impede its own movements. 

It was decided to make the Dump Truck cylindrical, with small wheels around its 

perimeter in conjunction with large drive wheels to keep the Dump Truck on track. (See 

Figure 24.) Hydraulic systems would be used to extend and retract the drive wheels for 

surface or tunnel drive and to move the bed of the Dump Truck to dump the material. (See 

Figure 25.) The material would be unloaded off to the side, so that once out of the tunnel 

the vehicle can drive in a relatively straight line without blocking the tunnel entrance. 

TRTTPIZ 

1 SIX ELECTRlCAlLY 

2 lW0 RECHARCABLE 

POWERED WHEELS 

STORAGE BATTERIES 

TMP 

11L U bJ.1 3 REMOTELYOPERATED 

6Y THE ZED USER 

CONTROL SYSlEM 

/' 

0 n 

I I 

I CAPACITY (mS) 

4 

6 

25 

37 

W I 0 
REAR VIEW 

OF DUMP TRUCK 

( SUSPENSION ) 

IN TUNNEL ON FLAT LAND 

The Dump Truck would be powered by a rechargeable battery system. These batteries 

are charged initially and plugged into the Tunneler power system to be charged each time 

the Dump Truck returns from a dump. The batteries would power six sealed electrical 

motors that would turn six lm (3.3ft) diameter spherical wheels. 

Guidance of the Dump Truck would be performed by a computer using components 

manufactured by ZED Instruments. The computer would be preprogrammed to control 

vehicle motion and monitor vital signs such as hydraulic pressure. 

45 
-411 support systems and driving would be mounted on a framelike structure located 

below the bed as shown in Figure 26. This structure is intended to maximize the space 

available for transportation of lunar material and to act as a stable base for relative movement of the rest of the vehicle. Left in a row of mounds, the lunar material would be 

readily accessible for strip-mining for chemical processing. 

RECHARGABLE 

BATTERIES 

MOTORS 

FIGURE 26: DUMP TRUCK lrRAyE 

With a diameter of 4 meters (13 feet) and length of 4, 6, or 8 meters (13, 20, or 26 

feet), the capacity of the Dump Truck would be 25, 37, or 50 cubic meters (880, 1,300, 

or 1,800 cubic feet), respectively. Since the Tunneler is projected to create approximately 

nine meters of tunnel per Terrestrial day, the 4, 6, or 8 meter Dump Truck would need to 

make 4.5, 3.0, or 2.2 dumping trips per Terrestrial day. Thus, even the shortest vehicle 

46 
would meet the dump rate requirement. 

This concept of the Lunar Tunneler excavation system was designed optimizing simplicity to reduce the cost and down-time of each of the components in the system. Many 

components utilize existing designs to further lower the cost of design and production. 

Problems exist within the hazardous environment of the Moon. M-ith a vacuum 

present, the problem of heat dissipation from the tunnel, molten lunar material. and all 

mechanical devices becomes the greatest constraint in developing a mechanical tunneling 

device that uses the glass-forming sections with their required high temperatures. Heat 

generated inside the tunnel cannot escape through normal conduction means; therefore, 

an internal cycle must be developed which not only dissipates heat from the tunnel but 

cools the molten lunar material to its relatively cool glass-ceramic form. This raises the 

problems of how to cool the working fluid while keeping the Tunneler totally automated. 

The internal power cycle of the Lunar Tunneler, shown in Figure 27, begins with a 

nuclear reactor which uses liquid lithium as the working medium for cooling. Lithium 

was chosen for its ability to remain liquid at very high temperatures and for its proven 

ability in heat transfer uses. The reactor feeds heated liquid lithium to a radial turbine 

47 
which drives a generator to electrically power all components of the Tunneler. After the 

lithium leaves the turbine, the relatively cool fluid is circulated through the cooling section 

to cool the molten lunar material to its ceramic form. This operation raises the lithium 

temperature again, and the fluid is circulated through another radial turbine to lower the 

fluid temperature and further generate electricity. After the relatively cool liquid lithium 

leaves the second radial turbine, it is pumped back to the nuclear reactor for cooling 

purposes and to be reheated, thereby completing the cycle. 

COOLING SECTON REGOLITH IN HOLDING TANK 

ADIAL TURBINE 

HEAT SECTION 

PUMP SYSTEM TRUCK 

48 
The nuclear reactor, shown in Figure 28! is a high speed SP-100 fission device which 

uses the standard control rods to regulate the reactor output. These control rods can be 

inserted or extracted in varying amounts to increase or decrease the reaction rate and thus 

vary the reactor temperature. Heat pipes carrying liquid lithium are contained throughout 

the interior of the nuclear reactor. The basic components of the heat pipes proposed for 

the Lunar Tunneler are of the type developed by Los Alamos.’ The heat pipe, shown in 

Figure 29, is a gas-tight tube containing lithium liquid and vapor; one end of the tube 

is an evaporator. the other a condenser. For nuclear applications the evaporator end is 

placed directly at the inlet to the first radial turbine. The interior of the heat pipe is lined 

with multiple layers of woven wire screen called a wick. The liquid lithium within this wire 

matrix is heated and thus evaporated inside the nuclear reactor. The continuously forming 

vapor fills the interior of the heat pipe and flows toward the cooler condenser end. At the 

condenser end the vaporized lithium rejects its latent heat and returns to the evaporator 

end by means of capillary movement through the wick. The process begins again to keep 

the cycle continuous. The advantage of the heat pipe with evaporator and condenser ends 

is its ability to maintain very high heat fluxes with very small temperature differences 

between the ends. This happens because the thermal exchange involves the latent heat of 

vaporization instead of the temperature difference of only one phase. 

49 
7 r HEAT PIPE 

\ / /-FUEL CONTROL 

ROD 7 

FIGURE 28: SCHEUTIC OF SP-100 REACTOR(REP0RT BY IL)S UOS) 

?IGURE 29: US UOS REAT PIPE(REP0RT BY WS ALAMOS) 
Because of the problems of heat pipe breakage inside the reactor, exhaustion of fuel, 

and other factors, it is necessary to be able to replace the nuclear core. This would 

allow the exchange of fuel elements and broken components within the core. By having a 

section within the core where the heat pipes can be disconnected from the core, robotic 

maintenance devices can replace the core without any extensive disconnecting of hardware. 

(See Figure 30.) 

REACTOR 

FIGURF, SO: DXSCONNECTING REACTOR (REPORT BY IDS UOS) 

51 
After the nuclear reactor heats the lithium, the liquid is circulated to the first radial turbine. The turbine, using the liquid lithium as the working 

medium, is about one meter (three feet) in diameter with inlet and exit temperatures 

of 1,200"K (2,160"R) and 750°K (1,350"R): respectively. With an assumed efficiency of 

75%, the characteristics of lithium and the power requirements dictate a mass flow energy 

of 1.6861 kg.s-I (0.1 15slUg-S- ) (See Appendix B for mass flow calculations.) The 

design power output of the first turbine is approximately 2,500kiY (3,400hp). To maximize 

the inlet temperature, and hence the power output of the turbine: the distance between 

the reactor and turbine should be minimized. (A small distance is needed to maximize 

heat transfer between the turbine and reactor.) The first turbine has two purposes: lithium 

temperature decrease and power generation. The turbine would produce shaft work while 

lowering the temperature of the liquid lithium by approximately 450°K (810"R). This 

temperature decrease across the turbine would allow the relatively cool lithium to circulate through the cooling section, thereby allowing formation of the glass-ceramic from 

the molten lunar material. Power generation is created by converting the turbine shaft 

work through a gear box, which in turn drives an electrical generator, which produces 

approximately 2,500kW (3,400hp) of power. This power would be available for driving the 

mechanical cutterhead, operating the hydraulic propulsion system, supplying heat to the 

heating section, operating all pumping and instrument systems, driving the belt conveyor, 

and recharging the Dump Truck. 

(See Figure 31.) 

52 
LIQUID LITHIUM RADIAL TURBINE DATA 

c . TURBINE 1 

LITHIUM DENSITY = 526 Kg/m3 

SPECIFIC HEAT = 4.3932 KJ/Kg K 

CHANGE IN ENTHALPY = 1976.94 KJ/Kg 

TURBINE EFFICIENCY = 75% 

MASS FLOW = 1.6861 Kg/sec. 

DESIGN POWER OUTPUT = 2500 Kw 

The cooling system accepts the 750°K (1,350‘R) liquid lithium and! in turn, circulates 

it through the exterior hIo-30%’ alloy shell. (See “Glass-Forming Sections.”) The lithium, 

by means of heat transfer, accepts approximately 500°K (900”R) of the heat from the 

molten lunar material to transform the material to glass-ceramic form. At this point the 

lithium is at a temperature of 1,250”K (2,250”R) and is too hot to return to the reactor. 

In order to dump as much excess heat from the lithium as possible, the fluid is directed 

to another radial turbine. The second turbine has three purposes: to provide additional 

power for the Lunar Tunneler, to generate resistance heating inside the non-heated lunar 

material holding tank (see “Material Excavation System”), and to lower the temperature of 

53 
the liquid lithium. By generating the resistive heat inside the holding tank, excess heat can 

be transferred to the non-heated lunar material and dumped outside the tunnel whenever 

the Dump Truck dumps its load. By directing the lithium fluid through the turbine the 

temperature is lowered to approximately 800°K (1,440"R). Lithium at this temperature 

can return to the nuclear reactor for cooling purposes and reheating to continue the cycle. 

With this cycle in place, the Lunar Tunneler can be operated for as long as the fuel in the 

nuclear reactor is sufficient to heat the lithium fluid to 1,200"K (2,160"R). 

Power requirements for all systems and components (except the heating section and 

Dump Truck) were obtained by extensive research on six Robbins earth rock tunneling 

deyices. This research obtained a power requirement of iOOkV- (938hp) for the propulsion system. all other hydraulic systems, cutterhead, and belt conveyor. The heating 

section power requirement was estimated at 500kiV (6;0hp), considered to be a conservative amount. The rechargeable system for the Dump Truck had a power requirement 

estimated to be 30kU- (4Ohp). This gives a total power requirement for the Lunar Tunneler of 1,230kW (1,65Ohp), which is less than half of the design power output of the first 

turbine. (See Figure 32.) Excess power is included in the design of the Lunar Tunneler for 

reasons of safety and convenience. 

54 
POWER REQUIREMENTS FOR LUNAR BORE 

I 

PROPULSION SECTION 

MECHANICAL HEAD 

PUMPING SYSTEMS 

EXCAVATION SYSTEMS 

HEATING SECTION (?) 500 Kw 

DUMP TRUCK 

700 Kw 

30 Kw 

TOTAL POWER REQUIRED FOR LUNAR BORE = 1230 Kw 

POWER TO BE SUPPLIED BY TURBINE = 2500 Kw 

I FIGURE 32: POWEX3 REQ'tmzEMENTS FOR LUNAR TUNNELER 

Percent down-time of six Robbins earth-tunneling devices were studied to give average 

numbers as estimates for the Lunar Tunneler. (See Figure 33.) Neglecting factors that 

pertain only to the Earth's atmosphere and taking into account technological progress in 

hydraulic sealings, an estimate of 25.3% down-time was reached. Even with this relatively high down-time percentage, the generation of many cubic feet of safe living space 

can be obtained before any maintenance is required. With further research in the areas 

of hydraulic seals, materials, disc cutter wear, and stroke recycle time, this down-time 

percentage can be brought to a lower value. 

55 
PERCENT DOWNTIME FOR LUNAR TUNNELER 

CUTTER CHANGE 2.6% - 

GEN. MAIN. k INS. 

LUBE OIL 

HYDRAULICS 

MOTORS 

CONVEYOR 

ELECTRI CAL 

POWER SUPPLY 

SURVEY 

GRIPPER DIFF. 

STROKE RECYCLE 

4.2% 

0.9% 

5.0% 

0.3% 

1.5% 

1.6% 

0.3% 

0.1 % 

0.2% 

3.9% 

\ 

\ 

TOTAL DOWNTlME=25.3% > 

OTHER 4.7% 

FIGURE 33 PERCENT DO- ?’OR LUNAR TUNNELER 

From the findings presented in this report, it is concluded that a mechanical Lunar 

Tunneler is a viable and efficient technique for creating large amounts of underground 

living space. An SP-100 high speed atomic reactor is the best choice for supplying the 

power requirements in this application because of its compactness, longevity under adverse 

conditions, and ability to provide ample power for lunar tunneling. The completely mechanical cutterhead, with twenty-six disc cutters, would be able to shear its way through 

the lunar material without using the large amounts of power required by a melting tun56 
neler. The mechanical head is based on a proven design and should be very reliable with 

minimal down-time. In addition, using a mechanical head would eliminate the problem of 

transporting the molten lunar material through the interior of the tunnel-boring machine. 

Using the existing lunar materials to form a rigid ceramic structure was found to be totally 

viable and more efficient than transporting structural lining materials from Earth. Propulsion of the Lunar Tunneler would be performed by a proven existing design built by Lovat 

and other companies. Features of the propulsion system include low power requirements, a 

hydraulically activated gripper system: and the ability to maneuver in all directions. Kavigation of the Lunar Tunneler is accomplished by using an existing laser system developed 

by ZED Instruments. The Lunar Tunneler can be guided with a computer operating in 

conjunction with the laser guidance system. Removal of the unheated lunar material to 

the rear of the Tunneler would be accomplished by an existing conveyor system developed 

by Flexowall. This conveyor system is very reliable with adjustable speed control and 

has the advantage of a large capacity for transporting excavated material. The conveyor 

system would move the excavated lunar material into a holding tank, where excess heat 

would be transferred to the material. Once the holding tank is filled, it transfers its load 

to the Dump Truck for removal from the tunnel. This would eliminate the accumulation 

of heat within the tunnel while not requiring the addition of further cooling elements. For 

the above reasons the Lunar Tunneler should prove to be a straightforward and reliable 

design. 

57 
1. Lovat Tunnel Equipment, Inc., 441 Carlington Dr., Toronto, Ontario MSLt’ZG7, 

Canada. 

2. ZED Instruments, Ltd., hlolesey Ave., West Molesey, Surrey 14T8 ORY, England. 

3. Flexowall, Inc., 2336 Merced Street, San Leandro, Calif. 94577. 

4. Pricilla ?;elson, “Tunnel-Boring Machine Performance in Sedimentary Rock,” Ph.D. 

thesis, Cornel1 Vniversity. hlay 1983. 

5. E. S. Robinson et al.. “-\ Preliminary Study of the Xuclear Subterrene,” Los -4larnos 

Scientific Laboratory of the University of California. Los Alamos. Sew Mexico, -4pril 

1971. 

6. R. D. Bennett, “State-of-the-.ht Construction Technology for Deep Tunnels and 

Shafts in Rock.” Geotechnical Laboratory, U.S. Army Engineer IYaterways Experiment Station, Vicksburg. Miss. 

7. Kenneth Budinski, Engineering Jlaterials: Properties and Selection, Reston Publishing, 1985. 

8. I. I. Cherkasov, Lunar Soil Science, Israeli Program for Science, Jerusalem, 1975, pp. 

146-1 68. 

9. Brian H. Mason, The Lunar Rocks, Wiley-Interscience, New York, 1970, pp. 62-79. 

10. W. W. Mendel, Lunar Bases and Space Activities of the tlst Century, Lunar and 

Planetary Institute, Houston, 1985, pp. 381-401, 465-476, 487-494, 571-580. 

11. Tony V. Nero, Guidebook to Nuclear Reactors, U.C. Berkeley Press, 1979, pp. 9-11. 

12. Eric N. Simons, Guide to Uncommon Metals, Hart, New York, 1967, pp. 115-121, 

211-216. 

58 
13. R. F. Smallwood, Refractory hletals and Their Industrial Applications, ASTM Special 

Publications, Philadelphia, 1984, pp. 3-17, 82-105. 

14. Zdenek Strnad, Glass- Ceramic hlaterials, Elsevier Publishing, New York, 1986. pp. 

166-184, 207-209. 

15. A. N. Zelikman, Metallurgy of Rare hietals, Israeli Program for Science, Jerusalem, 

1966, pp. 1-7, 60-62, 439-445. 

59 
Diameter 

Length 

Weight 

dPP&,VDDZX d 

Mechanical Cut t erhead Specificat ions 

No. of drive motors 

Drive motor rating 

Rotation speed 

Average thrust power per cutter 

No. of thrust cylinders 

Cylinder diameter 

Stroke length 

Maximum cylinder pressure 

Average operating pressure 

Cylinder pressure to move 

No. of cutters 

Cutter type 

Rolling distance 

(mx106) 

(ft x 106) 

No. of changes 

per 1,OOOft of tunnel 

per cutter position 

Cutter clock life 

(hours) 

4.0m (13ft) 

lm (3.3ft) 

2.8MN (630kip) 

6 

149kW (200hp) 

2.93 RPM 

93.6kW (126hp) 

at amperage 216.4 

4 

330mm (1 3.0in) 

1.5m (4.9ft) 

2-l.lhlPa (3,500psi) 

18.3MPa (2,650psi) 

4.lhZPa (59Opsi) 

26 

single disc 

Cutter Specifications 

Center Face 

0.05 0.78 

0.16 2.56 

0.78 0.74 

189 28 1 

Gage 

0.77 

2.53 

1.55 

141 

60 
Equations for Internal Power Cycle 

- Specific heat of liquid lithium cP = 4.3932kJ.kg-’ (47,3OOft *lb*slug-’ ) 

Turbine power output , P = 2,500kJ-s-’ (1,840,00Oft*Ib*~-’ ) 

Turbine efficiency q = 0.75 

For temperature T and enthalpy h of the fluid, 

c,AT = Ah 

For AT = 450°K (810”R), 

Ah = 1,976.9.lkJ*kg-’ (38,313,000ft*lb~~l~g-’) 

For mass flow rate T+Z, 

Thus, 

61