# Drilling Load Model of an Inchworm Boring Robot for Lunar Subsurface Exploration

Authors: Weiwei Zhang; Shengyuan Jiang; Dewei Tang; Huazhi Chen; Jieneng Liang
Journal: International Journal of Aerospace Engineering
 (2017)

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## Abstract

In the past decade, the wireline robot has received increasing attention due to the advantages of light weight, low cost, and flexibility compared to the traditional drilling instruments in space missions. For the lunar subsurface in situ exploration mission, we proposed a type of wireline robot named IBR (Inchworm Boring Robot) drawing inspiration from the inchworm. Two auger tools are utilized to remove chips for IBR, which directly interacted with the lunar regolith in the drilling process. Therefore, for obtaining the tools drilling characteristics, the chips removal principle of IBR is analyzed and its drilling load model is further established based on the soil mechanical theory in this paper. And then the proposed theoretical drilling load model is experimentally validated. In addition, according to the theoretical drilling load model, this paper discusses the effect of the drilling parameters on the tools drilling moments and power consumption. These results imply a possible energy-efficient control strategy for IBR.


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## Body

## 1. Introduction

Scientific targets such as the physical and mechanical properties and heat flux of regolith are critical evidences for human studying the planetary origin and evolution [1]. Drilling is an effective method and is widely utilized in the planetary subsurface exploration missions [2, 3]. Though these missions are capable of sampling the regolith or rack by using of the drill with its inbuilt coring tube, these drills are generally designed less than two meters because of the constraints of power, payload, and volume. For obtaining more valuable and reliable scientific data, the depth of implementing investigation should be more than three meters which is beyond the significant thermal cycles [4]. If long drills such as MARTE [5] and SPECES [6] which coupled with multiple drill sections are utilized to achieve greater depth, they will unavoidably increase the mass and complexity of the system.To sidestep the drawbacks of traditional drill, a type of wireline robot has been proposed for deep subsurface exploration. The wireline robot has the capability of accessing the target position in the planet and implementing scientific investigation by internal instruments. Compared with the traditional drill, the wireline robot does not have rigid connection to the surface but has a tether which provides the wireline robot with power and data communication [7]. According to the boring method of penetrating or excavating, the wireline robot can be classified as two types of penetrator and excavating robot. Serval penetrators such as MUPUS [8] (Rosetta mission), Insight [9] (InSight mission), and KRET [10] (future lunar robotic mission) were proposed, and they can penetrate into the planetary subsurface by using of the impact driven by penetrator’s internal hammer mechanism. Besides that, a bioinspired penetrator based on the working mechanism of wood wasp ovipositors was proposed for avoiding the needed external force in the space missions [11]. Although these penetrators have advantages of light weight and small dimensions, it is difficult for them to penetrate hard regolith or rocks and thus they are just suitable for subsurface exploration of the shallow depth in relatively loose regolith. Drawing inspiration from nature, several bioinspired excavating robots including IDDS [12], Auto-Gopher [13], and Earthworm-type robot [14] were proposed. The excavating robot can break and remove the regolith for making space and advancement, and it is generally equipped with anchor mechanism used to supply the enough down force when applied on the borehole wall. Although the excavating robot potentially has stronger drilling ability than the traditional drill and the penetrator, it also has the disadvantages in complex operation and structure especially for a robotic mission.Therefore, an Inchworm Boring Robot was proposed for China’s lunar robotic subsurface exploration mission [15]. The IBR has two critical tools of drill bit used for cutting the regolith or rocks and the auger was used to remove the chips. In the case of energy limit, it is necessary to reasonably select operating parameters to reduce working resistance and energy consumption of IBR. Therefore, it is of great significance to study the interaction between tools and lunar regolith for tools design and motion control strategy. The interaction between drill bit and lunar soil or rock had already been analyzed [16, 17], so that this paper mainly focuses on the establishment of auger drilling load model based on the soil mechanics theory. According to the drilling load model, this paper takes the drilling moment and power consumption as the evaluation index and studies the drilling parameters matching which lays the foundation for the motion control strategy of IBR.The remainder of the paper is organized as follows. The IBR and its working principle are introduced in Section2. In Section 3, chips removal in the excavating mode and discharging mode are analyzed. Section 4 gives the establishment of the drilling load model of IBR. In Section 5, the drilling load model was experimentally validated and the effect of drilling parameters on the drilling load is analyzed for the future motion control strategy. Section 6 concludes this paper.


## 2. Working Principle of IBR

Subsurface exploration system shown in Figure1 was proposed to implement scientific investigations of scientific targets such as the physical and mechanical properties and heat flux of lunar regolith. As depicted in Figure 1, the subsurface exploration system is mainly made up of IBR and supporting device. IBR automatically drills into planetary subsurface with the power supply of supporting device according to one tether. In the drilling process, the hard original regolith was broken into loose cuttings, and the cuttings were simultaneously conveyed to chamber at the end of IBR. Once the volume of cuttings accumulated in the chamber reaches the set value, IBR will return back to the surface and discharge the cuttings. In the investigating process, IBR can collect the scientific data by its inner sensors.Figure 1
Subsurface exploration system.The IBR consists of three modules, excavating module, discharging module, and propulsion module, as shown in Figure2(a). Excavating module was equipped with drill head and excavating auger: the drill head was used to break the original regolith or rocks into cuttings and the excavating auger was used to convey the cuttings to the storage room. The discharging module was just equipped with a discharging auger used to convey the cutting to the back of the IBR from storage room, while excavating module and discharging module can be fixed on the borehole wall by excavating anchor and discharging anchor, respectively. Propulsion module can provide linear motion for excavating module and discharging module.Figure 2
Components and drilling process of IBR.
(a)
Components
(b)
Drilling processOne drilling process is composed of four steps as shown in Figure2(b).Step 1.
Discharging anchor engages the borehole wall.Step 2.
Excavating module drills forward with rotating and penetrating motion. At the same time, the excavating auger rotates in the opposite direction.Step 3.
Excavating anchor engages the borehole and discharging anchor disengages the borehole wall.Step 4.
Discharging module drills forward with rotating and penetrating motion.Repeat the steps; IBR realizes the function of continued drilling into the regolith. In Steps2 and 4, the IBR is mainly focused on excavating forward and discharging the cuttings. And thus the two steps can be defined as excavating mode and discharging mode for IBR.


## 3. Chips Removal of IBR

According to the components of IBR, two augers, EA (excavating auger) and DA (discharging auger), were used to remove the cuttings produced by the breaking of regolith or rocks by the DH (drill head). The structure parameters of the EA and DA are shown in Figure3.Figure 3
Structure parameters of EA and DA (r1, r2, and r are the inner radius, outer radius, and middle radius of the screw flight, resp. α is the screw angle. N is the number of the screw flights. L1 and L2 are the lengths of EA and DA, resp. r3 is the inner radius of the storage room; Hc is the maximal height of the storage room. P is the screw pitch. w is the width of the screw flight).According to the working principle of IBR, two working modes of excavating mode and discharging mode can be defined in the whole drilling process as shown in Figure4. In order to analyze the principle of chip removal for the two working modes, the following three assumptions need to be made:(i)
The flow channels (auger groove) of EA and DA are fully filled with the cuttings in the whole drilling process.(ii)
The regolith is relatively compact compared with the cuttings; its bulk density isρ1. The compression among the cuttings on the screw flight is not taken into account, so that the cuttings have a constant bulk density ρ2 in the analysis.(iii)
The cuttings in the storage room are probably compressed when the cuttings are not timely removed by DA, so that the bulk density of the compact cuttings increases and it is noted asρ3.Figure 4
IBR working mode.
(a)
Excavating mode
(b)
Discharging mode


### 3.1. Discharging Mode

In the discharging mode, EA stops working and the DA conveys the compact cuttings to the end of IBR from the storage room. DA rotates and penetrates relative to the borehole; the rotary speed and penetrating velocity areω2 and v2, respectively. For one certain instant, the motion of cuttings on the screw flight is equivalent to a planer motion and the instantaneous velocities are given in Figure 5.Figure 5
Velocities of cuttings on the screw flight.In Figure5, vn represents the peripheral velocity of the auger, and vn=ω2r. vr is the sliding velocity of the cuttings relative to the auger. va is resultant velocity of cuttings relative to the borehole, which has an incline angle β2 and is composed of the velocities vn, v2, and vr. Therefore, from the whole process of conveying, the cuttings are lifted and do upward spiral motion with an opposite direction to the screw flight. As shown in Figure 5, va can be resolved into the useful lifting velocity vf2 and the peripheral velocity vh2 of the cuttings. Hence, the velocity relations of cuttings on the screw flight can be illustrated as follows:(1)vn-vrcos⁡α=vh2vrsin⁡α-v2=vf2vf2=vh2tan⁡β2.Substituting vn=ω2r into (1) and eliminating the velocity vr, the peripheral velocity vh2 and the lifting velocity vf2 of the cuttings can be solved:(2)vh2=ω2rtan⁡α-v2tan⁡α+tan⁡β2(3)vf2=ω2rtan⁡α-v2tan⁡β2tan⁡α+tan⁡β2.In Figure 4(b), Φ2 is the cuttings mass flow rate from the storage room to the flow channel of DA. Φ2 can be given as the reduced cuttings mass flow rate ρ3A3v2 in the storage room and the cuttings mass flow rate ρ2A2vf2+v2 in the flow channel of DA. Therefore, the incline angle β2 can be deduced based on the equation ρ3A3v2=ρ2A2vf2+v2.(4)β2=arctan⁡ρ3A3-ρ2A2v2ρ2A2ω2r-ρ3A3v2cot⁡α,where A2 represents the cross-sectional area of cuttings flow channel in DA or EA and A2=πr12-r22. A3 represents the cross-sectional area of cuttings flow channel in the storage room and A3=πr12-r32.


### 3.2. Excavating Mode

In the excavating mode, DH breaks the original regolith into cuttings and these cuttings are then conveyed to the storage room by EA with the rotary and penetrating motion. The produced cuttings are filled and compressed in the storage room, and some of them are removed with the rotary movement of DA. As shown in Figure4(a), vf11 and vf12 are the vertical upward velocities of cuttings in the EA and DA flow channel. Based on (3), the two velocities can be calculated as follows: (5)vf11=ω11rtan⁡α-v11tan⁡β11tan⁡α+tan⁡β11vf12=ω12rtan⁡αtan⁡β12tan⁡α+tan⁡β12,where ω11 and v11 represent the rotary speed and penetrating velocity of EA, respectively. ω12 represents the rotary speed of DA. β11 and β12 are, respectively, the incline angles of cuttings resultant velocities in the EA and DA. As can be seen in Figure 4(a), Φ11 is the mass flow rate of the chips from the original regolith to the flow channel in EA. Φ11 can be given as the produced cuttings mass flow rate ρ1A1v11 from the original regolith and the cuttings mass flow rate ρ2A2vf11+v11 in the flow channel in EA. In the excavating mode, the mass flow rate Φ11 was divided into two parts: the mass flow rate Φ12 of the flow channel in the DA and the mass flow rate Φ13 in the storage room. Φ12 and Φ13 can be expressed as ρ2A2vf12 and ρ3A3v11, respectively. Therefore, two equations can be obtained as ρ1A1v11=ρ2A2vf11+v11 and Φ11=Φ12+Φ13, and the incline angles β11 and β12 are deduced as shown in the following equation: (6)β11=arctan⁡ρ1A1-ρ2A2v11ρ2A2ω11r-ρ1A1v11cot⁡αβ12=arctan⁡ρ1A1-ρ3A3v11ρ2A2ω12r-ρ1A1-ρ3A3v11cot⁡α,where A1 represents the cross-sectional area of the borehole and A1=πr12.


## 3.1. Discharging Mode

In the discharging mode, EA stops working and the DA conveys the compact cuttings to the end of IBR from the storage room. DA rotates and penetrates relative to the borehole; the rotary speed and penetrating velocity areω2 and v2, respectively. For one certain instant, the motion of cuttings on the screw flight is equivalent to a planer motion and the instantaneous velocities are given in Figure 5.Figure 5
Velocities of cuttings on the screw flight.In Figure5, vn represents the peripheral velocity of the auger, and vn=ω2r. vr is the sliding velocity of the cuttings relative to the auger. va is resultant velocity of cuttings relative to the borehole, which has an incline angle β2 and is composed of the velocities vn, v2, and vr. Therefore, from the whole process of conveying, the cuttings are lifted and do upward spiral motion with an opposite direction to the screw flight. As shown in Figure 5, va can be resolved into the useful lifting velocity vf2 and the peripheral velocity vh2 of the cuttings. Hence, the velocity relations of cuttings on the screw flight can be illustrated as follows:(1)vn-vrcos⁡α=vh2vrsin⁡α-v2=vf2vf2=vh2tan⁡β2.Substituting vn=ω2r into (1) and eliminating the velocity vr, the peripheral velocity vh2 and the lifting velocity vf2 of the cuttings can be solved:(2)vh2=ω2rtan⁡α-v2tan⁡α+tan⁡β2(3)vf2=ω2rtan⁡α-v2tan⁡β2tan⁡α+tan⁡β2.In Figure 4(b), Φ2 is the cuttings mass flow rate from the storage room to the flow channel of DA. Φ2 can be given as the reduced cuttings mass flow rate ρ3A3v2 in the storage room and the cuttings mass flow rate ρ2A2vf2+v2 in the flow channel of DA. Therefore, the incline angle β2 can be deduced based on the equation ρ3A3v2=ρ2A2vf2+v2.(4)β2=arctan⁡ρ3A3-ρ2A2v2ρ2A2ω2r-ρ3A3v2cot⁡α,where A2 represents the cross-sectional area of cuttings flow channel in DA or EA and A2=πr12-r22. A3 represents the cross-sectional area of cuttings flow channel in the storage room and A3=πr12-r32.


## 3.2. Excavating Mode

In the excavating mode, DH breaks the original regolith into cuttings and these cuttings are then conveyed to the storage room by EA with the rotary and penetrating motion. The produced cuttings are filled and compressed in the storage room, and some of them are removed with the rotary movement of DA. As shown in Figure4(a), vf11 and vf12 are the vertical upward velocities of cuttings in the EA and DA flow channel. Based on (3), the two velocities can be calculated as follows: (5)vf11=ω11rtan⁡α-v11tan⁡β11tan⁡α+tan⁡β11vf12=ω12rtan⁡αtan⁡β12tan⁡α+tan⁡β12,where ω11 and v11 represent the rotary speed and penetrating velocity of EA, respectively. ω12 represents the rotary speed of DA. β11 and β12 are, respectively, the incline angles of cuttings resultant velocities in the EA and DA. As can be seen in Figure 4(a), Φ11 is the mass flow rate of the chips from the original regolith to the flow channel in EA. Φ11 can be given as the produced cuttings mass flow rate ρ1A1v11 from the original regolith and the cuttings mass flow rate ρ2A2vf11+v11 in the flow channel in EA. In the excavating mode, the mass flow rate Φ11 was divided into two parts: the mass flow rate Φ12 of the flow channel in the DA and the mass flow rate Φ13 in the storage room. Φ12 and Φ13 can be expressed as ρ2A2vf12 and ρ3A3v11, respectively. Therefore, two equations can be obtained as ρ1A1v11=ρ2A2vf11+v11 and Φ11=Φ12+Φ13, and the incline angles β11 and β12 are deduced as shown in the following equation: (6)β11=arctan⁡ρ1A1-ρ2A2v11ρ2A2ω11r-ρ1A1v11cot⁡αβ12=arctan⁡ρ1A1-ρ3A3v11ρ2A2ω12r-ρ1A1-ρ3A3v11cot⁡α,where A1 represents the cross-sectional area of the borehole and A1=πr12.


## 4. Drilling Load Model of IBR

### 4.1. Soil-Auger Interaction

For obtaining the soil-auger interaction model, a soil element with a small angledθ was taken as the analyzed object on the screw flight as shown in Figure 6(a). In Figure 6(b), the distance from the center of soil element to the central axis of the auger is r. w and H are the height and width of the soil element, respectively. The left lateral surface of the soil element represents the auger stem surface, its area was noted by AL, and AL=Hr2sec⁡αdθ. The right lateral surface of the soil element represents the borehole wall surface, its area was noted by AR, and AR=Hr1sec⁡αdθ. The top and bottom surfaces of the soil element represent the lower and upper surfaces of the screw flight, and the area can be defined as AF: AF=wrsec⁡αdθ. The front and back surfaces representing the contact surface between the soil element and neighboring soil on the screw flight were noted by AC, and AC=Hw. For the soil element, the pressure on the left, top, and right surfaces is, respectively, defined as σl, σu, and σr; the difference pressure acting on the front and back surfaces is dσ.Figure 6
Forces analysis of chips element.
(a)
Soil element
(b)
Forces in space
(c)
Forces on planeThese forces shown in Figure6(b) applied on the soil element can be expressed on the plane as shown in Figure 6(c), and then the static equilibrium equation (7) can be carried out in thex direction (the tangential direction of the screw flight) and the y axial direction (the normal direction of the screw flight).(7)Frcos⁡α+β+Fp-Fl-Fd+Fusin⁡δ-Gsin⁡α=0Fd-Fucos⁡δ-Frsin⁡α+β-Gcos⁡α=0,where Fd is the force of the soil element against the upper surface of the screw flight. Fl is the frictional force of the soil element against the lateral surfaces of auger stem, and Fl=σlAFtan⁡δ. Fu is the force of the soil element against the lower surface of the screw flight, and Fu=σuAFsec⁡δ. Fr is the frictional force of the soil element against the hole wall, and Fr=σrARtan⁡φ. Fp is the resultant force of neighboring soil applied on the soil element, and Fp=dσAC. G is the element gravity, and G=ρ2HAFg. Gw is the centrifugal force of the element, and Gw=ρ2HAFvh2/r. By substituting above forces into (7) and simplifying the equation, (8) can be obtained:(8)dσdθ=Klσl+Kuσu+Krσr+KcKl=r2tan⁡δwcos⁡α,Ku=2rtan⁡δHcos⁡α,Kr=r1cos⁡α+β+δtan⁡φ-wcos⁡δcos⁡α,Kc=ρ2grtan⁡α+tan⁡δ,where δ is the friction angle between soil and metal and φ is the internal friction angle of the soil.The average stressσp caused by the soil gravity on the four lateral surfaces of the soil element can be calculated as σp=ρ2gHK0cos⁡α/2 based on the soil mechanical theory, where K0 is the stress coefficient and K0=1-sin⁡φ [18]. The stress σa caused by the centrifugal force on the left and right lateral surfaces can be calculated as σa=ρ2vh2w/r. According to the compression properties of soil, the stress σ will produce additional compressive stress on the surface of soil element. And the additional compressive stresses on the left, top, and right lateral surfaces are Kσ, where K is the stress transfer coefficient and K=1-sin⁡φ/1+sin⁡φ [18]. Therefore, under the action of its own gravity, centrifugal force, and the additional stress, the stresses applied on the left, top, and right surfaces are deduced as follows:(9)σl=σp-σa+Kσσu=Kσσr=σp+σa+Kσ.Substituting (9) into (8) and solving the differential equation, the explicit expression of the stress σ can be obtained:(10)σ=σ0+Bsexp⁡Asθ-BsAs=KKl+Kr+Ku,Bs=KlσP-σa+KrσP+σa+KcKKl+Kr+Ku,where σ0 represents the preload acting on top of the auger flow channel.


### 4.2. Drilling Moments of Tools

From (12), the stress state of the cuttings on the screw flight is affected by σ0 which is the preload actnig on top of the auger flow channel. Therefore, it is necessary to analyze the stress of the regolith in the storage room and then give the obstructive stress acting on the top of EA flow channel. As shown in Figure 7, in the excavating mode, the cuttings discharged from EA were deposited in the storage and compressed, resulting in compressive stress Pu inside the cuttings. At the same time, the cuttings in the storage room were pushed up by the newly generated cuttings discharged from EA. As a result of the preload Pu and the fact that the frictions between the regolith and walls included borehole wall and the inner wall, the extrusion stress Pd was generated on the bottom of the storage room.Figure 7
Stress of regolith in the storage room.Based on the hyperbolic relation of soil strain and stress assumed in the Duncan-Chang model [19] and the relation of soil strain and void ratio in the condition of confined consolidation test, an e-p compression mode is established as shown in the following equation:(11)e3=e2-1+e2PuAp+BpPu,where e2 and e3 are the void ratios of the cuttings and the compressed cuttings in the storage room and e2=ρs/ρ2-1 and e3=ρs/ρ3-1. ρs is the granular density of regolith. Ap and Bp are the unknown coefficients that need to be determined by the confined compression test. By substituting e2 and e3 into (11), Pu is calculated as follows:(12)Pu=ρ3-ρ2Apρ3-ρ3-ρ2Bp.Based on Janssen’s method [20] and considering the inner wall friction, the stress Pd is calculated by the following equation:(13)Pd=ρ3gEexp⁡HcE-1+Puexp⁡HcEE=2πKr3tan⁡δ+r1tan⁡φA3.In the conveying process of cuttings, the forces ofFl, Fu, and Fd acting on auger will produce the resisting moments which can be, respectively, expressed as Flr2cos⁡α, Fursin⁡δ-α, and Fdrsin⁡δ+α. By integrating the sum of above three resisting moments in the longitudinal direction, the total resisting moment M of auger can be deduced as follows:(14)M=N∫0θmKmlσl+Kmuσu+Kmrσr+KmcdθKml=Hr22tan⁡δ,Kmu=2wr2tan⁡δKmr=Hr1rsin⁡α+βsin⁡α+δtan⁡φsec⁡αsec⁡δKmc=ρ3gwHr2sec⁡δsin⁡α+δ,where θm represents the angle of the screw flight: θm=2πL/P. From the soil-auger interaction analysis, M is the function of the parameters including σ0, ω, v, and β, which can be noted as Mσ0,ω,v,β. In the excavating mode, the drilling moment M1 of EA can be obtained by substituting the parameters Pd, ω11, v11, and β11 into the function of M. In the discharging mode, there is no preload acting on the cuttings output port of the DA, and the drilling moment M2 of EA can also be obtained by substituting the parameters ω2, v2, and β2 into the function of M. Therefore, the drilling moments M1 and M2 can be calculated as follows:(15)M1=MPd,ω11,v11,β11M2=M0,ω2,v2,β2.


## 4.1. Soil-Auger Interaction

For obtaining the soil-auger interaction model, a soil element with a small angledθ was taken as the analyzed object on the screw flight as shown in Figure 6(a). In Figure 6(b), the distance from the center of soil element to the central axis of the auger is r. w and H are the height and width of the soil element, respectively. The left lateral surface of the soil element represents the auger stem surface, its area was noted by AL, and AL=Hr2sec⁡αdθ. The right lateral surface of the soil element represents the borehole wall surface, its area was noted by AR, and AR=Hr1sec⁡αdθ. The top and bottom surfaces of the soil element represent the lower and upper surfaces of the screw flight, and the area can be defined as AF: AF=wrsec⁡αdθ. The front and back surfaces representing the contact surface between the soil element and neighboring soil on the screw flight were noted by AC, and AC=Hw. For the soil element, the pressure on the left, top, and right surfaces is, respectively, defined as σl, σu, and σr; the difference pressure acting on the front and back surfaces is dσ.Figure 6
Forces analysis of chips element.
(a)
Soil element
(b)
Forces in space
(c)
Forces on planeThese forces shown in Figure6(b) applied on the soil element can be expressed on the plane as shown in Figure 6(c), and then the static equilibrium equation (7) can be carried out in thex direction (the tangential direction of the screw flight) and the y axial direction (the normal direction of the screw flight).(7)Frcos⁡α+β+Fp-Fl-Fd+Fusin⁡δ-Gsin⁡α=0Fd-Fucos⁡δ-Frsin⁡α+β-Gcos⁡α=0,where Fd is the force of the soil element against the upper surface of the screw flight. Fl is the frictional force of the soil element against the lateral surfaces of auger stem, and Fl=σlAFtan⁡δ. Fu is the force of the soil element against the lower surface of the screw flight, and Fu=σuAFsec⁡δ. Fr is the frictional force of the soil element against the hole wall, and Fr=σrARtan⁡φ. Fp is the resultant force of neighboring soil applied on the soil element, and Fp=dσAC. G is the element gravity, and G=ρ2HAFg. Gw is the centrifugal force of the element, and Gw=ρ2HAFvh2/r. By substituting above forces into (7) and simplifying the equation, (8) can be obtained:(8)dσdθ=Klσl+Kuσu+Krσr+KcKl=r2tan⁡δwcos⁡α,Ku=2rtan⁡δHcos⁡α,Kr=r1cos⁡α+β+δtan⁡φ-wcos⁡δcos⁡α,Kc=ρ2grtan⁡α+tan⁡δ,where δ is the friction angle between soil and metal and φ is the internal friction angle of the soil.The average stressσp caused by the soil gravity on the four lateral surfaces of the soil element can be calculated as σp=ρ2gHK0cos⁡α/2 based on the soil mechanical theory, where K0 is the stress coefficient and K0=1-sin⁡φ [18]. The stress σa caused by the centrifugal force on the left and right lateral surfaces can be calculated as σa=ρ2vh2w/r. According to the compression properties of soil, the stress σ will produce additional compressive stress on the surface of soil element. And the additional compressive stresses on the left, top, and right lateral surfaces are Kσ, where K is the stress transfer coefficient and K=1-sin⁡φ/1+sin⁡φ [18]. Therefore, under the action of its own gravity, centrifugal force, and the additional stress, the stresses applied on the left, top, and right surfaces are deduced as follows:(9)σl=σp-σa+Kσσu=Kσσr=σp+σa+Kσ.Substituting (9) into (8) and solving the differential equation, the explicit expression of the stress σ can be obtained:(10)σ=σ0+Bsexp⁡Asθ-BsAs=KKl+Kr+Ku,Bs=KlσP-σa+KrσP+σa+KcKKl+Kr+Ku,where σ0 represents the preload acting on top of the auger flow channel.


## 4.2. Drilling Moments of Tools

From (12), the stress state of the cuttings on the screw flight is affected by σ0 which is the preload actnig on top of the auger flow channel. Therefore, it is necessary to analyze the stress of the regolith in the storage room and then give the obstructive stress acting on the top of EA flow channel. As shown in Figure 7, in the excavating mode, the cuttings discharged from EA were deposited in the storage and compressed, resulting in compressive stress Pu inside the cuttings. At the same time, the cuttings in the storage room were pushed up by the newly generated cuttings discharged from EA. As a result of the preload Pu and the fact that the frictions between the regolith and walls included borehole wall and the inner wall, the extrusion stress Pd was generated on the bottom of the storage room.Figure 7
Stress of regolith in the storage room.Based on the hyperbolic relation of soil strain and stress assumed in the Duncan-Chang model [19] and the relation of soil strain and void ratio in the condition of confined consolidation test, an e-p compression mode is established as shown in the following equation:(11)e3=e2-1+e2PuAp+BpPu,where e2 and e3 are the void ratios of the cuttings and the compressed cuttings in the storage room and e2=ρs/ρ2-1 and e3=ρs/ρ3-1. ρs is the granular density of regolith. Ap and Bp are the unknown coefficients that need to be determined by the confined compression test. By substituting e2 and e3 into (11), Pu is calculated as follows:(12)Pu=ρ3-ρ2Apρ3-ρ3-ρ2Bp.Based on Janssen’s method [20] and considering the inner wall friction, the stress Pd is calculated by the following equation:(13)Pd=ρ3gEexp⁡HcE-1+Puexp⁡HcEE=2πKr3tan⁡δ+r1tan⁡φA3.In the conveying process of cuttings, the forces ofFl, Fu, and Fd acting on auger will produce the resisting moments which can be, respectively, expressed as Flr2cos⁡α, Fursin⁡δ-α, and Fdrsin⁡δ+α. By integrating the sum of above three resisting moments in the longitudinal direction, the total resisting moment M of auger can be deduced as follows:(14)M=N∫0θmKmlσl+Kmuσu+Kmrσr+KmcdθKml=Hr22tan⁡δ,Kmu=2wr2tan⁡δKmr=Hr1rsin⁡α+βsin⁡α+δtan⁡φsec⁡αsec⁡δKmc=ρ3gwHr2sec⁡δsin⁡α+δ,where θm represents the angle of the screw flight: θm=2πL/P. From the soil-auger interaction analysis, M is the function of the parameters including σ0, ω, v, and β, which can be noted as Mσ0,ω,v,β. In the excavating mode, the drilling moment M1 of EA can be obtained by substituting the parameters Pd, ω11, v11, and β11 into the function of M. In the discharging mode, there is no preload acting on the cuttings output port of the DA, and the drilling moment M2 of EA can also be obtained by substituting the parameters ω2, v2, and β2 into the function of M. Therefore, the drilling moments M1 and M2 can be calculated as follows:(15)M1=MPd,ω11,v11,β11M2=M0,ω2,v2,β2.


## 5. Experiments and Model Validation

### 5.1. Drilling Test Bed

#### 5.1.1. Mechanical System

For testing the drilling load of EA and DA, a drilling test bed shown in Figure8 was developed. The drilling test bed is composed of the stander, two rotary mechanisms, RA and RB, and two penetrating mechanisms, PA and PB.Figure 8
Drilling test bed.The two rotary mechanisms RA and RB are, respectively, fixed on the two sliding plates. RA consists of rotary motor, torque sensor, and shaft I. Shaft I and the EA are directly driven by the rotary motor for the rotary motion with nominal rotary speed of 300 rpm and nominal moment of 23 Nm. The rotary motor coupled with a reducer with the ratio of 1 : 5 is AC servo motor (MHMJ082) with 750 W power. For moment measurement of shaft I and EA, a torque sensor (HLT-20) which has the range of 0~20 Nm was installed between the rotary motor and shaft I. The rotary mechanism RB consists of rotary motor, torque sensor, gear transmission, and shaft II. Shaft II and the DA are driven by the paralleled rotary motor and a gear transmission mechanism for the rotary motion with nominal rotary speed of 200 rpm and nominal moment of 12 Nm. The rotary motor coupled with a reducer with the ratio of 1 : 10 is AC servo motor (MHMJ042) with 400 W power. For moment measurement of shaft II and DA, a torque sensor (HLT-10) which has the range of 0~10 Nm was installed between the rotary motor and shaft II.Two penetrating mechanisms are arranged in parallel and they are used to provide penetrating motion for EA and DA, respectively. The two penetrating mechanisms have the same features; they consist of penetrating motor, ball-screw mechanism, and sliding plate. The ball-screw mechanism is driven by the penetrating motor and thus the two sliding plates can move linearly on the guide way for penetrating motion with a nominal velocity of 300 mm/min and a nominal force of 500 N. The penetrating motor coupled with a reducer with the ratio of 1 : 5 is also an AC servo motor (MHMJ042) with 100 W power.


#### 5.1.2. Speed Control and Data Acquisition System

The test bed speed control and data acquisition system shown in Figure9 has the function of motion control and signals and data acquisition. The two rotary motors and the two penetrating motors are, respectively, driven by the rotary drivers and penetrating drivers with the closed-loop speed control mode. In this control system, a data acquisition card (PCI 6229) produced by NI company was used to send control instructions to the motor drivers and also collect the signals of torque sensors M1 and M2, rotary speeds n1 and n2, and penetrating velocities v1 and v2, and then these signals can be sent to the PC.Figure 9
Speed control and data acquisition system.


#### 5.1.3. Tools and Simulant

The tools including DH, EA, and DA are shown in Figure10. In the auger EA and DA, the number of screw flights N=3; helix angel α=15.2°. The radii of the augers are r1=37 mm, r2=33 mm, and r3=25 mm, and the lengths of EA and DA are L1=120 mm and L2=150 mm.Figure 10
Tools: DH, EA, and DA.The raw material of the simulant is the Cenozoic alkaline olivine basalt which is dehumidified and crushed into particles in size of 0.1~1 mm. In the process of preparation, the raw material was steeply poured into the container and vibrated for the regolith simulant with consistent mechanical property along the height direction. The bulk densities of the regolith simulant and the cuttings are 2.18 g/cm3 and 1.54 g/cm3, respectively. The internal friction angle of simulant is 26°, the angle between simulant and tools is 17.6°, and the cohesion of the simulant is 0.05 kPa. The coefficients of Ap and Bp are, respectively, 2.2 × 105 and 5 determined by the confined compression test.


### 5.2. Experiments Results

In the drilling experiments,Hc is set to 30 mm, rotary speed n11 is 60 rpm, and penetrating velocities v11 and v12 both are 30 mm/min. In order to investigate the effect of rotary speeds n11 and n12 on the drilling moments, n11 was set to 20 rpm, 40 rpm, and 60 rpm and n12 was set to 5 rpm, 10 rpm, 20 rpm, 30 rpm, and 40 rpm for drilling experiments and each drilling experiment will be repeated three times.


#### 5.2.1. Drilling Experiments

In the drilling test, IBR takes 120 s for one drilling process; the excavating mode and the discharging mode both take 60 s. As shown in Figure11, DH is in contact with the simulant surface at t = 0 s, EA is just fully penetrated into the simulant at t = 540 s, and DA is just fully penetrated into the simulant at t = 1080 s.Figure 11
Inchworm drilling experiments process.The drilling moments of the EA and DA are recorded by two torque sensors with 100 Hz sample rate. Figure12 shows the drilling moments when n11=60 rpm and n12=40 rpm, where the red curve represents the moment M1e of EA in the excavating mode and the blue curve represents the moment M2e of DA in the discharging mode.Figure 12
Drilling moments of EA and DA.From Figure12, the whole drilling test can be divided into three stages: stages I, II, and III. In stage I, drill head breaks the simulant to cuttings; its drilling moment increases as the depth increases and reaches the maximum value M11 at t = 60 s. In stage II, drilling moment of the EA is slowly increasing, while the drilling moment of DA does not increase because it has not interacted with the simulant yet. In stage III, the EA has already drilled into the simulant; thus the storage room is unavoidably filled with cuttings, which will result in a sharp increase in drilling moment of EA. In whole stage III, the drilling moment of EA has reached the maximum value for four times M12, M13, M14, and M15, and this paper selects the maximum value of them as the contrast of theory results. At the same time, the drilling moment of DA is slowly increasing with the drilling depth gradually increasing and reaches the maximum M21 at t = 1080 s. According to the above analysis, the experimental drilling moment M1 of EA and the experimental drilling moment M2 of DA can be noted as follows:(16)M1=max⁡M12,M13,M14,M15-M11M2=M21.


#### 5.2.2. Model Validation

Drilling momentM1 of EA in excavating mode and the drilling moment M2 of DA in discharging mode were calculated based on the drilling load model. Figure 13 gives the comparison between the theory curve and experimental results of the EA drilling moments. From Figure 13, the theoretical curve and the experimental results have the same tendency that the drilling moment of EA decreases with the increase of n11 or n12. There was good consistency between the theoretical model and experimental results with the RMS error of 0.148 Nm, 0.141 Nm, and 0.121 Nm when n11 is 20 rpm, 40 rpm, and 60 rpm, respectively. Figure 14 gives the comparison between the theory and experimental results of the DA drilling moments. From Figure 14, the theoretical curve and the experimental results have the same tendency that the drilling moment of DA decreases with the increase of n2. The theoretical model still has a good agreement with the experimental results with the RMS error of 0.089 Nm.Figure 13
M
1 versus n11 and n12.Figure 14
M
2 versus n2.


### 5.3. Discussion ofK11, K12, and K2

As can be seen from the experimental results, the drilling moments of tools are directly related to the drilling parameters including rotary speeds and penetrating velocities, and reasonable selection of these motion parameters is critical to the subsurface exploration mission. In the theory model, the drilling parameters mainly exist in the form of ratio of rotary speed and penetrating velocity. Therefore, three speed ratiosK11(n11/v11), K12(n12/v11), and K2(n2/v2) are defined for discussing the effect of drilling parameters on the drilling moment requirements and power consumption of EA and DA.According to the theoretical model, the surfaces of drilling moment requirementM1 and power consumption P1 of EA with K11 and K12 in the excavating mode are drawn as shown in Figure 15. As can be seen from Figure 15, when 1<K11<2, the driving moment decreases slowly with the increase of K11, while the driving power consumption increases. And when K11>1, the power consumption decreases while the drilling moment sharply increases with decreasing of K11. Therefore, considering the drilling moment requirement and power consumption of EA, the value of K11 is recommended in the range of 1<K11<4/3. For K12, when K12<1/2, drilling moment requirement and power consumption of EA increase drastically as K12 decreases. Therefore, K12 should satisfy the condition K12<1/2 as far as possible.Figure 15
M
1 and P1 versus K11 and K12.
(a)
M
1
(b)
P
1The theoretical surfaces of drilling momentM2 and power consumption P2 of DA with K2 in the discharging mode are drawn as shown in Figure 16. As can be seen in Figure 16, when K2<1/3, the drilling moment requirement M2 increases drastically with the decrease of K2. And when K2<1/3, the power consumption P2 increases linearly with the increase of K2. Therefore, considering the drilling moment requirement and power consumption of DA, the value of K2 in the discharging mode is recommended in the range of 1/3<K2<1/2.Figure 16
M
2 and P2 versus K2.


## 5.1. Drilling Test Bed

### 5.1.1. Mechanical System

For testing the drilling load of EA and DA, a drilling test bed shown in Figure8 was developed. The drilling test bed is composed of the stander, two rotary mechanisms, RA and RB, and two penetrating mechanisms, PA and PB.Figure 8
Drilling test bed.The two rotary mechanisms RA and RB are, respectively, fixed on the two sliding plates. RA consists of rotary motor, torque sensor, and shaft I. Shaft I and the EA are directly driven by the rotary motor for the rotary motion with nominal rotary speed of 300 rpm and nominal moment of 23 Nm. The rotary motor coupled with a reducer with the ratio of 1 : 5 is AC servo motor (MHMJ082) with 750 W power. For moment measurement of shaft I and EA, a torque sensor (HLT-20) which has the range of 0~20 Nm was installed between the rotary motor and shaft I. The rotary mechanism RB consists of rotary motor, torque sensor, gear transmission, and shaft II. Shaft II and the DA are driven by the paralleled rotary motor and a gear transmission mechanism for the rotary motion with nominal rotary speed of 200 rpm and nominal moment of 12 Nm. The rotary motor coupled with a reducer with the ratio of 1 : 10 is AC servo motor (MHMJ042) with 400 W power. For moment measurement of shaft II and DA, a torque sensor (HLT-10) which has the range of 0~10 Nm was installed between the rotary motor and shaft II.Two penetrating mechanisms are arranged in parallel and they are used to provide penetrating motion for EA and DA, respectively. The two penetrating mechanisms have the same features; they consist of penetrating motor, ball-screw mechanism, and sliding plate. The ball-screw mechanism is driven by the penetrating motor and thus the two sliding plates can move linearly on the guide way for penetrating motion with a nominal velocity of 300 mm/min and a nominal force of 500 N. The penetrating motor coupled with a reducer with the ratio of 1 : 5 is also an AC servo motor (MHMJ042) with 100 W power.


### 5.1.2. Speed Control and Data Acquisition System

The test bed speed control and data acquisition system shown in Figure9 has the function of motion control and signals and data acquisition. The two rotary motors and the two penetrating motors are, respectively, driven by the rotary drivers and penetrating drivers with the closed-loop speed control mode. In this control system, a data acquisition card (PCI 6229) produced by NI company was used to send control instructions to the motor drivers and also collect the signals of torque sensors M1 and M2, rotary speeds n1 and n2, and penetrating velocities v1 and v2, and then these signals can be sent to the PC.Figure 9
Speed control and data acquisition system.


### 5.1.3. Tools and Simulant

The tools including DH, EA, and DA are shown in Figure10. In the auger EA and DA, the number of screw flights N=3; helix angel α=15.2°. The radii of the augers are r1=37 mm, r2=33 mm, and r3=25 mm, and the lengths of EA and DA are L1=120 mm and L2=150 mm.Figure 10
Tools: DH, EA, and DA.The raw material of the simulant is the Cenozoic alkaline olivine basalt which is dehumidified and crushed into particles in size of 0.1~1 mm. In the process of preparation, the raw material was steeply poured into the container and vibrated for the regolith simulant with consistent mechanical property along the height direction. The bulk densities of the regolith simulant and the cuttings are 2.18 g/cm3 and 1.54 g/cm3, respectively. The internal friction angle of simulant is 26°, the angle between simulant and tools is 17.6°, and the cohesion of the simulant is 0.05 kPa. The coefficients of Ap and Bp are, respectively, 2.2 × 105 and 5 determined by the confined compression test.


## 5.1.1. Mechanical System

For testing the drilling load of EA and DA, a drilling test bed shown in Figure8 was developed. The drilling test bed is composed of the stander, two rotary mechanisms, RA and RB, and two penetrating mechanisms, PA and PB.Figure 8
Drilling test bed.The two rotary mechanisms RA and RB are, respectively, fixed on the two sliding plates. RA consists of rotary motor, torque sensor, and shaft I. Shaft I and the EA are directly driven by the rotary motor for the rotary motion with nominal rotary speed of 300 rpm and nominal moment of 23 Nm. The rotary motor coupled with a reducer with the ratio of 1 : 5 is AC servo motor (MHMJ082) with 750 W power. For moment measurement of shaft I and EA, a torque sensor (HLT-20) which has the range of 0~20 Nm was installed between the rotary motor and shaft I. The rotary mechanism RB consists of rotary motor, torque sensor, gear transmission, and shaft II. Shaft II and the DA are driven by the paralleled rotary motor and a gear transmission mechanism for the rotary motion with nominal rotary speed of 200 rpm and nominal moment of 12 Nm. The rotary motor coupled with a reducer with the ratio of 1 : 10 is AC servo motor (MHMJ042) with 400 W power. For moment measurement of shaft II and DA, a torque sensor (HLT-10) which has the range of 0~10 Nm was installed between the rotary motor and shaft II.Two penetrating mechanisms are arranged in parallel and they are used to provide penetrating motion for EA and DA, respectively. The two penetrating mechanisms have the same features; they consist of penetrating motor, ball-screw mechanism, and sliding plate. The ball-screw mechanism is driven by the penetrating motor and thus the two sliding plates can move linearly on the guide way for penetrating motion with a nominal velocity of 300 mm/min and a nominal force of 500 N. The penetrating motor coupled with a reducer with the ratio of 1 : 5 is also an AC servo motor (MHMJ042) with 100 W power.


## 5.1.2. Speed Control and Data Acquisition System

The test bed speed control and data acquisition system shown in Figure9 has the function of motion control and signals and data acquisition. The two rotary motors and the two penetrating motors are, respectively, driven by the rotary drivers and penetrating drivers with the closed-loop speed control mode. In this control system, a data acquisition card (PCI 6229) produced by NI company was used to send control instructions to the motor drivers and also collect the signals of torque sensors M1 and M2, rotary speeds n1 and n2, and penetrating velocities v1 and v2, and then these signals can be sent to the PC.Figure 9
Speed control and data acquisition system.


## 5.1.3. Tools and Simulant

The tools including DH, EA, and DA are shown in Figure10. In the auger EA and DA, the number of screw flights N=3; helix angel α=15.2°. The radii of the augers are r1=37 mm, r2=33 mm, and r3=25 mm, and the lengths of EA and DA are L1=120 mm and L2=150 mm.Figure 10
Tools: DH, EA, and DA.The raw material of the simulant is the Cenozoic alkaline olivine basalt which is dehumidified and crushed into particles in size of 0.1~1 mm. In the process of preparation, the raw material was steeply poured into the container and vibrated for the regolith simulant with consistent mechanical property along the height direction. The bulk densities of the regolith simulant and the cuttings are 2.18 g/cm3 and 1.54 g/cm3, respectively. The internal friction angle of simulant is 26°, the angle between simulant and tools is 17.6°, and the cohesion of the simulant is 0.05 kPa. The coefficients of Ap and Bp are, respectively, 2.2 × 105 and 5 determined by the confined compression test.


## 5.2. Experiments Results

In the drilling experiments,Hc is set to 30 mm, rotary speed n11 is 60 rpm, and penetrating velocities v11 and v12 both are 30 mm/min. In order to investigate the effect of rotary speeds n11 and n12 on the drilling moments, n11 was set to 20 rpm, 40 rpm, and 60 rpm and n12 was set to 5 rpm, 10 rpm, 20 rpm, 30 rpm, and 40 rpm for drilling experiments and each drilling experiment will be repeated three times.


### 5.2.1. Drilling Experiments

In the drilling test, IBR takes 120 s for one drilling process; the excavating mode and the discharging mode both take 60 s. As shown in Figure11, DH is in contact with the simulant surface at t = 0 s, EA is just fully penetrated into the simulant at t = 540 s, and DA is just fully penetrated into the simulant at t = 1080 s.Figure 11
Inchworm drilling experiments process.The drilling moments of the EA and DA are recorded by two torque sensors with 100 Hz sample rate. Figure12 shows the drilling moments when n11=60 rpm and n12=40 rpm, where the red curve represents the moment M1e of EA in the excavating mode and the blue curve represents the moment M2e of DA in the discharging mode.Figure 12
Drilling moments of EA and DA.From Figure12, the whole drilling test can be divided into three stages: stages I, II, and III. In stage I, drill head breaks the simulant to cuttings; its drilling moment increases as the depth increases and reaches the maximum value M11 at t = 60 s. In stage II, drilling moment of the EA is slowly increasing, while the drilling moment of DA does not increase because it has not interacted with the simulant yet. In stage III, the EA has already drilled into the simulant; thus the storage room is unavoidably filled with cuttings, which will result in a sharp increase in drilling moment of EA. In whole stage III, the drilling moment of EA has reached the maximum value for four times M12, M13, M14, and M15, and this paper selects the maximum value of them as the contrast of theory results. At the same time, the drilling moment of DA is slowly increasing with the drilling depth gradually increasing and reaches the maximum M21 at t = 1080 s. According to the above analysis, the experimental drilling moment M1 of EA and the experimental drilling moment M2 of DA can be noted as follows:(16)M1=max⁡M12,M13,M14,M15-M11M2=M21.


### 5.2.2. Model Validation

Drilling momentM1 of EA in excavating mode and the drilling moment M2 of DA in discharging mode were calculated based on the drilling load model. Figure 13 gives the comparison between the theory curve and experimental results of the EA drilling moments. From Figure 13, the theoretical curve and the experimental results have the same tendency that the drilling moment of EA decreases with the increase of n11 or n12. There was good consistency between the theoretical model and experimental results with the RMS error of 0.148 Nm, 0.141 Nm, and 0.121 Nm when n11 is 20 rpm, 40 rpm, and 60 rpm, respectively. Figure 14 gives the comparison between the theory and experimental results of the DA drilling moments. From Figure 14, the theoretical curve and the experimental results have the same tendency that the drilling moment of DA decreases with the increase of n2. The theoretical model still has a good agreement with the experimental results with the RMS error of 0.089 Nm.Figure 13
M
1 versus n11 and n12.Figure 14
M
2 versus n2.


## 5.2.1. Drilling Experiments

In the drilling test, IBR takes 120 s for one drilling process; the excavating mode and the discharging mode both take 60 s. As shown in Figure11, DH is in contact with the simulant surface at t = 0 s, EA is just fully penetrated into the simulant at t = 540 s, and DA is just fully penetrated into the simulant at t = 1080 s.Figure 11
Inchworm drilling experiments process.The drilling moments of the EA and DA are recorded by two torque sensors with 100 Hz sample rate. Figure12 shows the drilling moments when n11=60 rpm and n12=40 rpm, where the red curve represents the moment M1e of EA in the excavating mode and the blue curve represents the moment M2e of DA in the discharging mode.Figure 12
Drilling moments of EA and DA.From Figure12, the whole drilling test can be divided into three stages: stages I, II, and III. In stage I, drill head breaks the simulant to cuttings; its drilling moment increases as the depth increases and reaches the maximum value M11 at t = 60 s. In stage II, drilling moment of the EA is slowly increasing, while the drilling moment of DA does not increase because it has not interacted with the simulant yet. In stage III, the EA has already drilled into the simulant; thus the storage room is unavoidably filled with cuttings, which will result in a sharp increase in drilling moment of EA. In whole stage III, the drilling moment of EA has reached the maximum value for four times M12, M13, M14, and M15, and this paper selects the maximum value of them as the contrast of theory results. At the same time, the drilling moment of DA is slowly increasing with the drilling depth gradually increasing and reaches the maximum M21 at t = 1080 s. According to the above analysis, the experimental drilling moment M1 of EA and the experimental drilling moment M2 of DA can be noted as follows:(16)M1=max⁡M12,M13,M14,M15-M11M2=M21.


## 5.2.2. Model Validation

Drilling momentM1 of EA in excavating mode and the drilling moment M2 of DA in discharging mode were calculated based on the drilling load model. Figure 13 gives the comparison between the theory curve and experimental results of the EA drilling moments. From Figure 13, the theoretical curve and the experimental results have the same tendency that the drilling moment of EA decreases with the increase of n11 or n12. There was good consistency between the theoretical model and experimental results with the RMS error of 0.148 Nm, 0.141 Nm, and 0.121 Nm when n11 is 20 rpm, 40 rpm, and 60 rpm, respectively. Figure 14 gives the comparison between the theory and experimental results of the DA drilling moments. From Figure 14, the theoretical curve and the experimental results have the same tendency that the drilling moment of DA decreases with the increase of n2. The theoretical model still has a good agreement with the experimental results with the RMS error of 0.089 Nm.Figure 13
M
1 versus n11 and n12.Figure 14
M
2 versus n2.


## 5.3. Discussion ofK11, K12, and K2

As can be seen from the experimental results, the drilling moments of tools are directly related to the drilling parameters including rotary speeds and penetrating velocities, and reasonable selection of these motion parameters is critical to the subsurface exploration mission. In the theory model, the drilling parameters mainly exist in the form of ratio of rotary speed and penetrating velocity. Therefore, three speed ratiosK11(n11/v11), K12(n12/v11), and K2(n2/v2) are defined for discussing the effect of drilling parameters on the drilling moment requirements and power consumption of EA and DA.According to the theoretical model, the surfaces of drilling moment requirementM1 and power consumption P1 of EA with K11 and K12 in the excavating mode are drawn as shown in Figure 15. As can be seen from Figure 15, when 1<K11<2, the driving moment decreases slowly with the increase of K11, while the driving power consumption increases. And when K11>1, the power consumption decreases while the drilling moment sharply increases with decreasing of K11. Therefore, considering the drilling moment requirement and power consumption of EA, the value of K11 is recommended in the range of 1<K11<4/3. For K12, when K12<1/2, drilling moment requirement and power consumption of EA increase drastically as K12 decreases. Therefore, K12 should satisfy the condition K12<1/2 as far as possible.Figure 15
M
1 and P1 versus K11 and K12.
(a)
M
1
(b)
P
1The theoretical surfaces of drilling momentM2 and power consumption P2 of DA with K2 in the discharging mode are drawn as shown in Figure 16. As can be seen in Figure 16, when K2<1/3, the drilling moment requirement M2 increases drastically with the decrease of K2. And when K2<1/3, the power consumption P2 increases linearly with the increase of K2. Therefore, considering the drilling moment requirement and power consumption of DA, the value of K2 in the discharging mode is recommended in the range of 1/3<K2<1/2.Figure 16
M
2 and P2 versus K2.


## 6. Conclusions

In this paper, an Inchworm Boring Robot was proposed for lunar subsurface exploration. Two auger tools of EA and DA are utilized to remove chips for IBR. For obtaining drilling characteristics of the two tools, the chips removal principles of IBR in excavating mode and discharging mode are analyzed, and then the relation of tools drilling parameters and the soil flow state in the flow channel of EA and DA are given. Subsequently, the drilling load model of tools is further established based on the soil mechanical theory. Drilling experiments with different drilling parameters had been conducted to test the tools drilling moments, and the proposed theoretical drilling load models agree well with the experimental results within the RMS errors of 0.148 Nm. In addition, according to the theoretical model analysis, the effect of drilling parameters on the tools drilling moments and power consumption was discussed and the recommend value of speed ratios can be given as1<K11<4/3, K12<1/2, and 1/3<K2<1/2. These results can be used for the energy-efficient control strategy for IBR.



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*Source: 1282791-2017-06-01.xml*