WO2013154271A1 - Rotary head of large-diameter drilling machine - Google Patents
Rotary head of large-diameter drilling machine Download PDFInfo
- Publication number
- WO2013154271A1 WO2013154271A1 PCT/KR2013/002082 KR2013002082W WO2013154271A1 WO 2013154271 A1 WO2013154271 A1 WO 2013154271A1 KR 2013002082 W KR2013002082 W KR 2013002082W WO 2013154271 A1 WO2013154271 A1 WO 2013154271A1
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- Prior art keywords
- gear
- gear box
- center shaft
- rotary head
- interlocking
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- 238000005553 drilling Methods 0.000 title claims abstract description 26
- 229920006351 engineering plastic Polymers 0.000 claims abstract description 6
- 230000000149 penetrating effect Effects 0.000 claims abstract description 5
- 239000012634 fragment Substances 0.000 claims description 28
- 230000002093 peripheral effect Effects 0.000 claims description 4
- 238000000034 method Methods 0.000 description 4
- 230000002349 favourable effect Effects 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000001681 protective effect Effects 0.000 description 1
- 230000003014 reinforcing effect Effects 0.000 description 1
- 230000003746 surface roughness Effects 0.000 description 1
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Classifications
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B3/00—Rotary drilling
- E21B3/02—Surface drives for rotary drilling
- E21B3/022—Top drives
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
- E02D17/00—Excavations; Bordering of excavations; Making embankments
Definitions
- the present invention relates to a rotary head for rotating and propelling a rod connected with a cutting device of a large-diameter drilling machine, and more particularly, to a rotary head of a large-diameter drilling machine, which has a simple assembling structure and is favorable to perforate a large-diameter hole because it propels while effectively rotating the rod.
- FIG. 1 illustrates an example of a drilling machine having a hammer as a cutting device.
- the drilling machine includes the hammer which is the cutting device and a rod connected with the cutting device and rotated and propelled by a rotary head. While the rod is rotated and propelled by a rotary driving force of the rotary head, the cutting device cut the ground while being rotated and pressed.
- Such a rotary head adopts a method of rotating the rod through a large-sized interlocking gear driving in interlock with a plurality of driving gears driven by the small-sized motors.
- Korean Patent Laid-open No. 10-2011-0119187 discloses such a rotary head.
- such a rotary head is nothing but propose a way to increase the torque of the interlocking gear through a gear reduction. That is, the rotary head cannot suggest a concrete method to effectively transmit the increased torque to the rod to rotate the rod.
- the conventional rotary head causes an increase of manufacturing costs of the drilling machine due to a complicated assembling structure.
- the present invention has been made in an effort to solve the above-mentioned problems occurring in the prior arts, and it is an object of the present invention to provide a rotary head of a large-diameter drilling machine, which has a simple assembling structure and is favorable to perforate a large-diameter hole because it propels while effectively rotating the rod.
- the present invention provides a rotary head of a large-diameter drilling machine, which rotates a rod connected with a head of the drilling machine, including: a gear box being composed of upper and lower flanges and a side plate and having an inner space of a closed structure; an interlocking gear formed in a shape of an annular ring having teeth formed on inner and outer peripheries thereof, the interlocking gear being mounted in the middle of the inner space of the gear box; a plurality of driving gears being smaller than the interlocking gear and being gear-coupled to the outer periphery of the interlocking gear inside the gear box, the driving gears being driven by receiving a driving power of a motor; a center shaft protruding upwardly and downwardly from the upper and lower flanges of the gear box while passing through the inside of the annular ring of the interlocking gear and penetrating the upper and lower flanges of the gear box, the center shaft being gear-coupled with the inner peripher
- the rotary head of the large-diameter drilling machine according to the present invention can rotate the rod effectively, is favorable to perforate a large-diameter hole, and has a simple assembling structure.
- the rotary head according to the present invention has simple components, and is economical due to a long exchange cycle because the components are usable even though the surfaces of the components are worn out and transformed.
- FIG. 1 is a brief diagram of a drilling machine.
- FIG. 2 is a perspective view of a rotary head of a large-diameter drilling machine according to the present invention.
- FIG. 3 is a sectional view showing an assembled state of the rotary head of FIG. 2.
- FIG. 4 is an exploded perspective view of the rotary head of FIG. 2.
- FIG. 2 is a perspective view of a rotary head 100 of a large-diameter drilling machine according to the present invention
- FIG. 3 is a sectional view showing an assembled state of the rotary head 100 of FIG. 2
- FIG. 4 is an exploded perspective view of the rotary head 100 of FIG. 2.
- the present invention relates to the rotary head 100 for rotating a rod connected with a cutting device, and is characterized by a simple assembly structure of gears and a bearing installation structure for effective rotation of a rod.
- the rotary head 100 of the large-diameter drilling machine includes: a gear box 110 being composed of upper and lower flanges 111 and 112 and a side plate 113, and having an inner space of a closed structure; an interlocking gear 120 formed in a shape of an annular ring having teeth formed on inner and outer peripheries, the interlocking gear 120 being mounted in the middle of the inner space of the gear box 110; a plurality of driving gears 130 being smaller than the interlocking gear 120 and being gear-coupled to the outer periphery of the interlocking gear 120 inside the gear box 110, the driving gears 130 being driven by receiving a driving power of a motor; a center shaft 140 protruding upwardly and downwardly from the upper and lower flanges 111 and 112 of the gear box 110 while passing through the inside of the annular ring of the interlocking gear 120 and penetrating the upper and lower flanges 111 and 112 of the gear box 110, the center shaft 140
- the couplers 151 and 152 and the bearings 161 and 162 are divided into an upper coupler 151 and an upper bearing 161 respectively mounted on the upper flange 111 of the gear box and a lower coupler 152 and a lower bearing 162 respectively mounted beneath the lower flange 112 of the gear box.
- the rotary head 100 according to the present invention can be assembled just by fixing and mounting the couplers 151 and 152 and the center shaft 140 to the upper and lower flanges 111 and 112 of the gear box through the bolt-tightening so as to simply restrict the interlocking gear 120 and the driving gear 130 to the gear box 110. Moreover, because the bearings 161 and 162 are contactingly mounted between the couplers 151 and 152 and the center shaft 140, the torque of the center shaft 140 is transmitted to the rod without any loss to thereby enhance the torque of the rod. Particularly, because the bearings 161 and 162 are made of engineering plastic, the rotary head 100 according to the present invention is economical and has a simple structure.
- FIG. 2 illustrates an example that four driving gears 130 are arranged around the interlocking gear 120 in the rectangular composition.
- four motors (M) and four decelerators (D) for respectively driving the four driving gears 130 are prepared.
- cables for lifting the rotary head 100 may be disposed.
- the motors (M) are track motors. Because the motors (M), the decelerators (D) and the lifting cables (C) are mounted in the same way as the conventional drilling machine, detailed descriptions of them will be omitted.
- FIG. 3 is a sectional view showing an assembled state of the rotary head 100 of FIG. 2, and FIG. 4 is an exploded perspective view of the rotary head 100, and in FIGS. 3 and 4, an assembling structure for simply and stably mounting the couplers 151 and 152 and the bearings 161 and 162 is illustrated.
- the interlocking gear 120 is thinner than the height of the inner space of the gear box 110 and is spaced apart from the upper and lower flanges 111 and 112 of the gear box, and hence, the interlocking gear 120 freely rotates inside the gear box 110.
- the lower bearing 162 is fit between the interlocking gear 120 and the lower flange 112 of the gear box in order to effectively support the rotation of the interlocking gear 120 without any interference.
- Such a lower bearing 162 is located to a position between the center shaft 140 and the lower coupler 152.
- the lower coupler 152 is an annular ring member of a ' ⁇ ' shaped cross section having an outward wing.
- the lower coupler 152 is fit between the lower flange 112 of the gear box and the center shaft 140 and fixed to the lower flange 112 of the gear box by tightening a bolt to the outward wing.
- the lower flange 112 of the gear box, the lower coupler 152, the lower bearing 162 and the center shaft 140 are closely joined in a contact state just by tightening the bolt to the lower flange 112 of the gear box and the lower coupler 152.
- the inner peripheral surface of the lower coupler 152 and the outer peripheral surface of the lower bearing 152 are tapered and contactingly mounted in order to prevent a damage of the bearing due to a stress concentration at an edge.
- the tapered portion (T) of the lower coupler 152 is galvanized, the tapered portion (T) of the lower coupler 152 can more effectively cope with the rotary power of the center shaft 140 together with the lower bearing 162 made of engineering plastic.
- the upper coupler 151 and the upper bearing 161 are mounted above the upper flange 111 of the gear box, and in FIGS. 3 and 4, are mounted conjunctly with the center shaft 140 through the groove-protrusion combination.
- the center shaft 140 has a protrusion band 141 formed at the center of the outer peripheral surface thereof, and the upper coupler 151 and the upper bearing 161 respectively have grooves for receiving the protrusion band 141 of the center shaft to form the groove-protrusion combination.
- the upper coupler 151 has a first fragment 151a and a second fragment 151b for tightening bolts, and it is the result of consideration that it is difficult to batch-install the upper coupler 151 by the protrusion band 141 of the center shaft during the process of assembling and manufacturing the rotary head 100.
- the first fragment 151a is an annular ring member of a ' ⁇ ' shaped cross section having an inward wing and is fit under the protrusion band 141 of the center shaft 140 in such a way as to face the side of the protrusion band 141
- the second fragment 151b is an annular ring member of an 'L' shaped cross section having an outward wing and is mounted in such a way as to face the upper portion of the center shaft 140, which is located above the protrusion band 141, above the first fragment 151a.
- the second fragment 151b is joined to the first fragment 151a by tightening a bolt.
- the upper bearing 161 is mounted between the center shaft 140 and the first and second fragments 151a and 151b of the upper coupler, but in this instance, the upper bearing 161 mounted between the center shaft 140 and the second fragment 151b of the upper coupler is mounted in such a manner that a second fragment 161b being an annular ring member of a ' ⁇ ' shaped cross section having an outward wing is separated from a first fragment 161a of a disc ring as shown in FIG. 3 so as to mount the second fragment 151b of the upper coupler between the first fragment 161a and the second fragment 161b.
- the coupler 151, the lower bearing 162 and the center shaft 140 are closely joined and seated and fixed on the upper flange 111 of the gear box in a state where they are engaged with each other and are in contact with each other just by assembling the second fragment 151b of the upper coupler to the first fragment 151a via a bolt.
- the second fragment 151b of the upper coupler is assembled only to the first fragment 151a via the bolt and the first fragment 151a of the upper coupler is closely fixed to the upper flange 111 of the gear box through the tightening force of the bolt.
- the bolt it is also possible to fasten the bolt to the upper flange 111 of the gear box by penetrating the first fragment 151a of the upper coupler.
- the upper coupler 151 and the upper bearing 161 are tapered and contactingly mounted and the tapered portion (T) of the upper coupler is galvanized, so that an exchange cycle of components can be extended because the surface roughness is moderated.
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Abstract
Disclosed therein is a rotary head of a large-diameter drilling machine, which rotates a rod connected with a head of the drilling machine. The rotary head includes: a gear box being composed of upper and lower flanges and a side plate and having an inner space of a closed structure; an interlocking gear formed in a shape of an annular ring having teeth formed on inner and outer peripheries thereof, the interlocking gear being mounted in the middle of the inner space of the gear box; a plurality of driving gears being smaller than the interlocking gear and being gear-coupled to the outer periphery of the interlocking gear inside the gear box, the driving gears being driven by receiving a driving power of a motor; a center shaft protruding upwardly and downwardly from the upper and lower flanges of the gear box while passing through the inside of the annular ring of the interlocking gear and penetrating the upper and lower flanges of the gear box, the center shaft being gear-coupled with the inner periphery of the interlocking gear and connected with the rod so as to rotate the rod while rotating according to the rotation of the interlocking gear; couplers respectively covering the portions of the center shaft, which respectively protrude upwardly and downwardly from the upper and lower flanges of the gear box, the couplers being fixed to the upper and lower flanges of the gear box through bolt-tightening; and plain bearings made of engineering plastic and contactingly mounted between the center shaft and the couplers.
Description
The present invention relates to a rotary head for rotating and propelling a rod connected with a cutting device of a large-diameter drilling machine, and more particularly, to a rotary head of a large-diameter drilling machine, which has a simple assembling structure and is favorable to perforate a large-diameter hole because it propels while effectively rotating the rod.
In the foundation work for reinforcing the ground or for supporting structures, drilling into the ground must be preceded, and the drilling into the ground is carried out using a drilling machine. FIG. 1 illustrates an example of a drilling machine having a hammer as a cutting device. As shown in FIG. 1, the drilling machine includes the hammer which is the cutting device and a rod connected with the cutting device and rotated and propelled by a rotary head. While the rod is rotated and propelled by a rotary driving force of the rotary head, the cutting device cut the ground while being rotated and pressed.
In the meantime, in order to construct large-diameter mono piles, such as mono piles of the foundation of a off shore wind turbine, large-diameter holes are perforated before the mono pile construction. In order to perforate the large-diameter holes, a drilling machine with a great torque of the rod is needed. Conventionally, in order to increase the torque of the rod, a method of supplying a high power using a rotary head by a large-sized motor is mostly adopted. The large-sized motor makes the size of the drilling machine larger, and hence, it is a factor to decrease workability and economic feasibility. Moreover, there is a limit in application of the large-sized motor because it is produced no more than a predetermined size. In order to solve the above problems, a rotary head using a plurality of small-sized motors has been proposed.
Such a rotary head adopts a method of rotating the rod through a large-sized interlocking gear driving in interlock with a plurality of driving gears driven by the small-sized motors. Korean Patent Laid-open No. 10-2011-0119187 discloses such a rotary head. However, such a rotary head is nothing but propose a way to increase the torque of the interlocking gear through a gear reduction. That is, the rotary head cannot suggest a concrete method to effectively transmit the increased torque to the rod to rotate the rod. Furthermore, the conventional rotary head causes an increase of manufacturing costs of the drilling machine due to a complicated assembling structure.
Accordingly, the present invention has been made in an effort to solve the above-mentioned problems occurring in the prior arts, and it is an object of the present invention to provide a rotary head of a large-diameter drilling machine, which has a simple assembling structure and is favorable to perforate a large-diameter hole because it propels while effectively rotating the rod.
It is another object of the present invention to provide a rotary head of a large-diameter drilling machine, which can prevent a frequent replacement due to brokenness of a bearing when a large-diameter hole is perforated.
To achieve the above objects, the present invention provides a rotary head of a large-diameter drilling machine, which rotates a rod connected with a head of the drilling machine, including: a gear box being composed of upper and lower flanges and a side plate and having an inner space of a closed structure; an interlocking gear formed in a shape of an annular ring having teeth formed on inner and outer peripheries thereof, the interlocking gear being mounted in the middle of the inner space of the gear box; a plurality of driving gears being smaller than the interlocking gear and being gear-coupled to the outer periphery of the interlocking gear inside the gear box, the driving gears being driven by receiving a driving power of a motor; a center shaft protruding upwardly and downwardly from the upper and lower flanges of the gear box while passing through the inside of the annular ring of the interlocking gear and penetrating the upper and lower flanges of the gear box, the center shaft being gear-coupled with the inner periphery of the interlocking gear and connected with the rod so as to rotate the rod while rotating according to the rotation of the interlocking gear; couplers respectively covering the portions of the center shaft, which respectively protrude upwardly and downwardly from the upper and lower flanges of the gear box, the couplers being fixed to the upper and lower flanges of the gear box through bolt-tightening; and plain bearings made of engineering plastic and contactingly mounted between the center shaft and the couplers.
The rotary head of the large-diameter drilling machine according to the present invention can rotate the rod effectively, is favorable to perforate a large-diameter hole, and has a simple assembling structure. Particularly, the rotary head according to the present invention has simple components, and is economical due to a long exchange cycle because the components are usable even though the surfaces of the components are worn out and transformed.
FIG. 1 is a brief diagram of a drilling machine.
FIG. 2 is a perspective view of a rotary head of a large-diameter drilling machine according to the present invention.
FIG. 3 is a sectional view showing an assembled state of the rotary head of FIG. 2.
FIG. 4 is an exploded perspective view of the rotary head of FIG. 2.
(Explanation of essential reference numerals in drawings)
100: rotary head
110: gear box
111: upper flange
112: lower flange
113: side plate
120: interlocking gear
130: driving gear
140: center shaft
141: protrusion band
151: upper coupler
152: lower coupler
161: upper bearing
162: lower bearing
151a, 161a: first fragment
151b, 161b: second fragment
T: tapered portion
M: motor
D: decelerator
C: cable
Reference will be now made in detail to the preferred embodiment of the present invention with reference to the attached drawings.
FIG. 2 is a perspective view of a rotary head 100 of a large-diameter drilling machine according to the present invention, FIG. 3 is a sectional view showing an assembled state of the rotary head 100 of FIG. 2, and FIG. 4 is an exploded perspective view of the rotary head 100 of FIG. 2.
As shown in the drawings, the present invention relates to the rotary head 100 for rotating a rod connected with a cutting device, and is characterized by a simple assembly structure of gears and a bearing installation structure for effective rotation of a rod.
In detail, the rotary head 100 of the large-diameter drilling machine according to the present invention includes: a gear box 110 being composed of upper and lower flanges 111 and 112 and a side plate 113, and having an inner space of a closed structure; an interlocking gear 120 formed in a shape of an annular ring having teeth formed on inner and outer peripheries, the interlocking gear 120 being mounted in the middle of the inner space of the gear box 110; a plurality of driving gears 130 being smaller than the interlocking gear 120 and being gear-coupled to the outer periphery of the interlocking gear 120 inside the gear box 110, the driving gears 130 being driven by receiving a driving power of a motor; a center shaft 140 protruding upwardly and downwardly from the upper and lower flanges 111 and 112 of the gear box 110 while passing through the inside of the annular ring of the interlocking gear 120 and penetrating the upper and lower flanges 111 and 112 of the gear box 110, the center shaft 140 being gear-coupled with the inner periphery of the interlocking gear 120 and connected with the rod so as to rotate the rod while rotating according to the rotation of the interlocking gear 120; couplers 151 and 152 respectively covering the portions of the center shaft 140, which respectively protrude upwardly and downwardly from the upper and lower flanges 111 and 112 of the gear box, the couplers 151 and 152 being fixed to the upper and lower flanges 111 and 112 of the gear box through bolt-tightening; and plain bearings 161 and 162 made of engineering plastic and contactingly mounted between the center shaft 140 and the couplers 151 and 152. Here, because the center shaft 140 protrudes upwardly and downwardly from the upper and lower flanges 111 and 112 of the gear box, the couplers 151 and 152 and the bearings 161 and 162 are divided into an upper coupler 151 and an upper bearing 161 respectively mounted on the upper flange 111 of the gear box and a lower coupler 152 and a lower bearing 162 respectively mounted beneath the lower flange 112 of the gear box.
The rotary head 100 according to the present invention can be assembled just by fixing and mounting the couplers 151 and 152 and the center shaft 140 to the upper and lower flanges 111 and 112 of the gear box through the bolt-tightening so as to simply restrict the interlocking gear 120 and the driving gear 130 to the gear box 110. Moreover, because the bearings 161 and 162 are contactingly mounted between the couplers 151 and 152 and the center shaft 140, the torque of the center shaft 140 is transmitted to the rod without any loss to thereby enhance the torque of the rod. Particularly, because the bearings 161 and 162 are made of engineering plastic, the rotary head 100 according to the present invention is economical and has a simple structure.
FIG. 2 illustrates an example that four driving gears 130 are arranged around the interlocking gear 120 in the rectangular composition. Of course, because there are four driving gears 130 around the interlocking gear 120, four motors (M) and four decelerators (D) for respectively driving the four driving gears 130 are prepared. Additionally, cables for lifting the rotary head 100 may be disposed. Here, it is preferable that the motors (M) are track motors. Because the motors (M), the decelerators (D) and the lifting cables (C) are mounted in the same way as the conventional drilling machine, detailed descriptions of them will be omitted.
FIG. 3 is a sectional view showing an assembled state of the rotary head 100 of FIG. 2, and FIG. 4 is an exploded perspective view of the rotary head 100, and in FIGS. 3 and 4, an assembling structure for simply and stably mounting the couplers 151 and 152 and the bearings 161 and 162 is illustrated.
As shown in the drawings, the interlocking gear 120 is thinner than the height of the inner space of the gear box 110 and is spaced apart from the upper and lower flanges 111 and 112 of the gear box, and hence, the interlocking gear 120 freely rotates inside the gear box 110. The lower bearing 162 is fit between the interlocking gear 120 and the lower flange 112 of the gear box in order to effectively support the rotation of the interlocking gear 120 without any interference. Such a lower bearing 162 is located to a position between the center shaft 140 and the lower coupler 152.
In addition, in FIGS. 3 and 4, the lower coupler 152 is an annular ring member of a 'ㅏ' shaped cross section having an outward wing. The lower coupler 152 is fit between the lower flange 112 of the gear box and the center shaft 140 and fixed to the lower flange 112 of the gear box by tightening a bolt to the outward wing.
Therefore, the lower flange 112 of the gear box, the lower coupler 152, the lower bearing 162 and the center shaft 140 are closely joined in a contact state just by tightening the bolt to the lower flange 112 of the gear box and the lower coupler 152. In this instance, it is preferable that the inner peripheral surface of the lower coupler 152 and the outer peripheral surface of the lower bearing 152 are tapered and contactingly mounted in order to prevent a damage of the bearing due to a stress concentration at an edge. Here, if the tapered portion (T) of the lower coupler 152 is galvanized, the tapered portion (T) of the lower coupler 152 can more effectively cope with the rotary power of the center shaft 140 together with the lower bearing 162 made of engineering plastic.
In the meantime, the upper coupler 151 and the upper bearing 161 are mounted above the upper flange 111 of the gear box, and in FIGS. 3 and 4, are mounted conjunctly with the center shaft 140 through the groove-protrusion combination. The center shaft 140 has a protrusion band 141 formed at the center of the outer peripheral surface thereof, and the upper coupler 151 and the upper bearing 161 respectively have grooves for receiving the protrusion band 141 of the center shaft to form the groove-protrusion combination.
Particularly, the upper coupler 151 has a first fragment 151a and a second fragment 151b for tightening bolts, and it is the result of consideration that it is difficult to batch-install the upper coupler 151 by the protrusion band 141 of the center shaft during the process of assembling and manufacturing the rotary head 100. That is, the first fragment 151a is an annular ring member of a 'ㅏ' shaped cross section having an inward wing and is fit under the protrusion band 141 of the center shaft 140 in such a way as to face the side of the protrusion band 141, and the second fragment 151b is an annular ring member of an 'L' shaped cross section having an outward wing and is mounted in such a way as to face the upper portion of the center shaft 140, which is located above the protrusion band 141, above the first fragment 151a. After that, the second fragment 151b is joined to the first fragment 151a by tightening a bolt.
Of course, the upper bearing 161 is mounted between the center shaft 140 and the first and second fragments 151a and 151b of the upper coupler, but in this instance, the upper bearing 161 mounted between the center shaft 140 and the second fragment 151b of the upper coupler is mounted in such a manner that a second fragment 161b being an annular ring member of a 'ㄱ' shaped cross section having an outward wing is separated from a first fragment 161a of a disc ring as shown in FIG. 3 so as to mount the second fragment 151b of the upper coupler between the first fragment 161a and the second fragment 161b.
Through the above, the coupler 151, the lower bearing 162 and the center shaft 140 are closely joined and seated and fixed on the upper flange 111 of the gear box in a state where they are engaged with each other and are in contact with each other just by assembling the second fragment 151b of the upper coupler to the first fragment 151a via a bolt. Particularly, in FIGS. 3 and 4, the second fragment 151b of the upper coupler is assembled only to the first fragment 151a via the bolt and the first fragment 151a of the upper coupler is closely fixed to the upper flange 111 of the gear box through the tightening force of the bolt. However, it is also possible to fasten the bolt to the upper flange 111 of the gear box by penetrating the first fragment 151a of the upper coupler. Moreover, it is also preferable that the upper coupler 151 and the upper bearing 161 are tapered and contactingly mounted and the tapered portion (T) of the upper coupler is galvanized, so that an exchange cycle of components can be extended because the surface roughness is moderated.
As described above, while the present invention has been particularly shown and described with reference to the example embodiments thereof, it will be understood by those of ordinary skill in the art that the above embodiments of the present invention are all exemplified and various changes, modifications and equivalents may be made therein without departing from the scope of the present invention. Therefore, it would be understood that the technical and protective scope of the present invention shall be defined by the technical idea as defined by the following claims.
Claims (6)
- A rotary head of a large-diameter drilling machine for rotating a rod connected with a head of the drilling machine, the rotary head comprising:a gear box (110) being composed of an upper flange (111), a lower flange (112), and a side plate (113) and having an inner space of a closed structure;an interlocking gear (120) formed in a shape of an annular ring having teeth formed on inner and outer peripheries thereof, the interlocking gear (120) being mounted in the middle of the inner space of the gear box (110);a plurality of driving gears (130) being smaller than the interlocking gear (120) and being gear-coupled to the outer periphery of the interlocking gear (120) inside the gear box (110), the driving gears (130) being driven by receiving a driving power of a motor;a center shaft (140) protruding upwardly and downwardly from the upper and lower flanges (111, 112) of the gear box (110) while passing through the inside of the annular ring of the interlocking gear (120) and penetrating the upper and lower flanges (111, 112) of the gear box (110), the center shaft (140) being gear-coupled with the inner periphery of the interlocking gear (120) and connected with the rod so as to rotate the rod while rotating according to the rotation of the interlocking gear (120);couplers (151, 152) respectively covering the portions of the center shaft (140), which respectively protrude upwardly and downwardly from the upper and lower flanges (111, 112) of the gear box, the couplers (151, 152) being fixed to the upper and lower flanges (111, 112) of the gear box through bolt-tightening; andplain bearings (161, 162) made of engineering plastic and contactingly mounted between the center shaft (140) and the couplers (151, 152).
- The rotary head according to claim 1, wherein the interlocking gear (120) is thinner than the height of the inner space of the gear box (110) and is spaced apart from the lower flange (112) of the gear box,wherein the lower coupler (152) mounted at a lower portion of the center shaft (140) is fit between the lower flange (112) of the gear box and the center shaft (140) and is fixed to the lower flange (112) of the gear box through bolt-tightening,wherein the lower bearing (162) mounted at a lower portion of the center shaft (140) is fit between the lower flange (112) of the gear box and the interlocking gear (120), andwherein the inner periphery of the lower coupler 152 and the outer periphery of the lower bearing (162) are tapered and contactingly mounted.
- The rotary head according to claim 1, wherein the interlocking gear (120) is thinner than the height of the inner space of the gear box (110) and is spaced apart from the upper flange (111) of the gear box,wherein the portion of the center shaft (140), which protrudes upwardly from the upper flange (111) of the gear box has a protrusion band (141) formed at the center of the outer peripheral surface thereof,wherein the upper coupler (151) mounted at the upper portion of the center shaft (140) comprises: a first fragment (151a) fit under the protrusion band (141) of the center shaft (140) in such a way as to face the side of the protrusion band (141); and a second fragment (151b) mounted above the first fragment (151a) in such a way as to face the center shaft (140), which is located above the protrusion band 141, so that the upper coupler (151) is fixed to the upper flange (111) of the gear box through bolt-tightening of the second fragment (151b),wherein the upper bearings (161) mounted at the upper portion of the center shaft (140) are respectively mounted above and beneath the protrusion band (141) of the center shaft, andwherein the inner peripheries of the first fragment (151a) and the second fragment (151b) of the upper coupler and the outer periphery of the upper bearing (161) are tapered and contactingly mounted.
- The rotary head according to claim 2 or 3, wherein the couplers (151, 152) are galvanized at the tapered portions (T)
- The rotary head according to one of claims 1 to 3, wherein the four driving gears (130) are arranged around the outer periphery of the interlocking gear (120) in the rectangular composition.
- The rotary head according to claim 5, wherein the driving gears (130) are driven by track motors.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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KR1020120038538A KR101334298B1 (en) | 2012-04-13 | 2012-04-13 | Rotary Head of Large diameter Drilling Machine |
KR10-2012-0038538 | 2012-04-13 |
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Publication Number | Publication Date |
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WO2013154271A1 true WO2013154271A1 (en) | 2013-10-17 |
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Application Number | Title | Priority Date | Filing Date |
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PCT/KR2013/002082 WO2013154271A1 (en) | 2012-04-13 | 2013-03-15 | Rotary head of large-diameter drilling machine |
Country Status (2)
Country | Link |
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KR (1) | KR101334298B1 (en) |
WO (1) | WO2013154271A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN106223835A (en) * | 2016-04-15 | 2016-12-14 | 陕西太合科技有限公司 | A kind of all hydraulic drive rig power head with independent lubricating system |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
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WO2015080353A1 (en) | 2013-11-26 | 2015-06-04 | 한국지질자원연구원 | High-pressure fluid storage tank and construction method thereof |
WO2015080354A1 (en) | 2013-11-26 | 2015-06-04 | 한국지질자원연구원 | High-pressure fluid storage system and construction method therefor |
CN113863848A (en) * | 2021-10-29 | 2021-12-31 | 浙江金祖环境治理设备股份有限公司 | Top drive mechanism of long spiral drilling machine |
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JP2008267129A (en) * | 2007-04-17 | 2008-11-06 | *** ▲言▼ | Boring drill |
JP4448608B2 (en) * | 2000-09-22 | 2010-04-14 | 日本車輌製造株式会社 | Rotary drive device for tool |
KR100985975B1 (en) * | 2010-08-02 | 2010-10-06 | 박동식 | Auger with 4 stage speed |
KR20100109587A (en) * | 2009-04-01 | 2010-10-11 | 주식회사 대화알로이테크 | Air hammer for digging |
US20100288560A1 (en) * | 2008-09-26 | 2010-11-18 | Longyear Tm, Inc. | Modular rotary drill head |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
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JP3655942B2 (en) * | 1995-02-28 | 2005-06-02 | 株式会社エヌエルシー | Boring chuck device |
-
2012
- 2012-04-13 KR KR1020120038538A patent/KR101334298B1/en active IP Right Grant
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2013
- 2013-03-15 WO PCT/KR2013/002082 patent/WO2013154271A1/en active Application Filing
Patent Citations (5)
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JP4448608B2 (en) * | 2000-09-22 | 2010-04-14 | 日本車輌製造株式会社 | Rotary drive device for tool |
JP2008267129A (en) * | 2007-04-17 | 2008-11-06 | *** ▲言▼ | Boring drill |
US20100288560A1 (en) * | 2008-09-26 | 2010-11-18 | Longyear Tm, Inc. | Modular rotary drill head |
KR20100109587A (en) * | 2009-04-01 | 2010-10-11 | 주식회사 대화알로이테크 | Air hammer for digging |
KR100985975B1 (en) * | 2010-08-02 | 2010-10-06 | 박동식 | Auger with 4 stage speed |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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CN106223835A (en) * | 2016-04-15 | 2016-12-14 | 陕西太合科技有限公司 | A kind of all hydraulic drive rig power head with independent lubricating system |
Also Published As
Publication number | Publication date |
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KR101334298B1 (en) | 2013-11-28 |
KR20130115841A (en) | 2013-10-22 |
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