Extension-type cutter drum for drilling machine

FIELD: mining.

SUBSTANCE: tunnelling machine includes movable frame having the front end section, multiple rotor assemblies containing many working members with rotor cutter, which are located at some distance from each other in the front end section of movable frame, assembly of cutter drum, which is located in the front of the front end section and contains rotation axis located across the section of the front end of movable frame, section of the first end drum, section of the second end drum and section of middle drum. Section of the first end drum includes the following: the first shaft passing along rotation axis and including the first channel passing along rotation axis; the first end drum attached to the first shaft; extension piece of the first end drum, which is located coaxially around rotation axis; the first piston located in the first channel with possibility of rotation relative to it, which is fixed relative to extension piece of the first end drum and offset along rotation axis between extended configuration of extension piece of the first end drum and retracted configuration of extension piece of the first end drum; the first coupling sleeve transmitting the torque moment between the first end drum and extension piece of the first end drum. Section of the second end drum includes the following: the second shaft passing along rotation axis and located at some distance along rotation axis from the first shaft and including the second channel passing along rotation axis; the second end drum attached to the second shaft; extension piece of the second end drum, which is located coaxially around rotation axis; the second piston located in the second channel with possibility of being rotated relative to it, fixed relative to extension piece of the second end drum and offset along the rotation axis between extended configuration of extension piece of the second end drum and retracted configuration of extension piece of the second end drum; the second connecting sleeve transmitting the torque moment between the second end drum and extension piece of the second end drum. Section of middle drum is located concentrically to rotation axis and passes between the first and the second shafts.

EFFECT: development of extension piece of drum of lower layout of cutter drum, which is supported irrespective of the main drum for relative extension and retraction.

22 cl, 63 dwg

 

Description

Background of invention

The technical field of the invention

The present invention relates to the arrangement of the milling drum for use in the tunneling harvester chisel type, in particular to the milling drum having a retractable end drums to increase the width of cut of the milling drum to remove solid material remaining nepogrebennymi working parts of the rotary cutter on the bottom of the roof and working horizon output.

Description of the prior art

Existing drilling tunneling machines for underground work are usually used in parallel alternating working bodies of the rotors with cutting elements performing the shear drift, in General, of oval form in the mine. Chain saws or milling drums continuous use at the levels of the roof and working horizons production to smooth or remove the non-beveled ledges outside the cut path of the working bodies of the rotors. Chain saw or milling drum on the desktop horizon is also used for increasing the width of the undercut in the drift mine.

To facilitate the haulage of the harvester to the front of the bottom of excavation and out of the lower chain saw or milling drum retract, deriving from contact with the side walls of the mine, the raise, putting out of contact with the operating horizon. The upper chain saw or the drum is lowered, deriving from contact with the roof of the output.

Other existing drilling tunneling machines also increase the width of the undercut on the desktop horizon beyond the cut path of the working bodies of the rotors by increasing the width of the lower milling drum after its lowering to the desired position on the desktop horizon on the basis of bottom of excavation, for example, increasing the length composition of the milling drum in the tunneling combines continuous action.

Existing tunneling machines continuous action also have the layout of a milling drum mounted for rotation on an acting forward strelba element. Many cutting teeth protruding from the drum element. Drum element comprises a middle section of the drum and a pair of end sections of the drums. Sections of the middle and end drums mounted telescopically to increase the length of the layout of the drum beyond the width of the harvester. The elongation of the sections end drums is performed by the lateral movement of the boom element having the items holders, bearing rotatably section end drums. Lateral movement perform layout of hydraulic pistons and cylinders, prikladyvaya the lateral pressure on the holders of arrows.

Another existing continuous miner continuous action has protruding forward the layout of the boom, swivel bonded to the frame digging machine. The layout of the boom includes a pair of parallel protruding element holders, swivel connected to the area housing the digging machine. A pair of parallel supporting members movably attached to the corresponding elements of the holders and stands sideways from them. Milling drum rests rotatably on the front end sections of the supporting elements. A couple of layouts actuators bonded to the corresponding elements of the holders and each includes a raised cylindrical rod connected with the supporting member. With the actuation of the layout of the power cylinder section end drums ejected sideways from the middle section of the drum. Section end drums are independently put forward to increase the efficiency of selection.

According to the device of the existing double drilling roadheaders, the bottom layout of the milling drum aligns material at the working horizon, remaining cut the working bodies of the rotors. Usually milling drum includes a Central or middle section of the drum and a pair of end sections drums, otdeleniia the middle section of the drum gears. Gearbox are rotatably appropriate section of the milling drum.

According to one double-rotor arrangement, each transmission is installed under the axis of the rotor and centered on it. With this device, when the end drums put forward to increase the length of the bottom of the milling drum to increase the width of the undercut formed at intervals in the cut path between the extended end drums and working bodies of the rotors. This leaves not cut material or ledges jutting up from the working horizon on the face of excavation.

Normal data existing harvesters includes a section milling drum having a fixed section and the outer raised sections. The outer retractable section is based on the fixed section and telescopically extends from the outer end of the fixed section to increase the width of undercut. However, this places additional loads, such as bending moments on the outer ends of the fixed section. It is believed that the telescopic overlap of the retractable and fixed area needed to carry the additional loads in the extended configuration, is at least 1.5 diameter of the telescopic part. Moreover, the bearings and the design bearing section f is eternulo drum, in General, should be more robust by taking into account these additional loads.

Although the elongation of the composition of the milling drum in the tunneling combine continuous action is accepted, there is a need to create a layout of the proposed milling drum on the tunneling harvester chisel type with the division of effort required for torque transmission and for extension/retraction of the extension of the drum relative to the main drum. In particular, there is a need to create an extension of the drum bottom layout milling drum supported independently of the main drum for relative extension and retraction.

The INVENTION

According to one aspect of a variant embodiment of the invention, created a continuous miner, containing a mobile frame having a front end section. Rotary layout includes many working parts of the rotary cutter mounted for rotation ahead of the front end portion of the frame and passing on the width of the frame under the arrangement of the rotor. The layout of the milling drum includes a middle section of the drum and a pair of end sections of the drums. The driving shaft is mounted for rotation transversely of the front end portion of the eye. The middle section of the drum and a pair of end sections drums are located on the control shaft. The end section of the drum is connected with the possibility of transmission of drive force from the drive shaft to rotation of the drive shaft. Section end drums include a stationary drum and the extension of the drum, movable along the axis on the drive shaft to increase the length composition of the milling drum. Hydraulic device with the piston and cylinder is functionally located between the drive shaft and an extension cord reel for extending and retracting the extension of the drum relative to the fixed drum. The device of the torque transmission is functionally located between the drum and the cord drum for joint rotation.

According to another aspect, the variant embodiment of the invention, the created tunnel harvester comprising a mobile frame having a front end section, a variety of rotor configurations, located at a distance from each other on the front end section of the mobile frame, and the layout of the milling drum, which is located ahead of the front end portion. Many of rotor assemblies includes many working parts of the rotary cutters. The layout of the milling drum includes an axis of rotation that is located across the front end portion of the mobile frame, a section of the first end of the drum, the section of the second end of the second drum and the middle section of the drum, located coaxially with the axis of rotation and passing between the first and second shafts. Section of the first end of the drum includes a first shaft passing along the axis of rotation, the first end of the drum, bonded with the first shaft, the extension of the first end of the drum, located coaxially relative to the axis of rotation, the first piston to move along the axis of rotation between the extended configuration of the extension of the first end of the drum and the involved configuration of extension of the first end of the drum, and the first coupling that transmits torque between the first end drum extension of the first end of the drum. The first shaft includes a first channel passing along the axis of rotation. The first piston is located in the first channel with the possibility of rotation relative to it and is stationary relative to the extension of the first end of the drum. Section of the second end of the drum includes a second shaft passing along the axis of rotation and located at a distance along the axis from the first shaft, the second end of the drum, bonded with the second shaft, the extension of the second end of the drum, located coaxially relative to the axis of rotation, the second piston to move along the axis of rotation between the extended configuration of the extension of the second end of the drum and drawn configurations is her extension of the second end of the drum, and second coupling that transmits torque between the second end drum extension of the second end of the drum. The second shaft includes a second channel passing along the axis of rotation. A second piston located in the second channel with the possibility of rotation relative to it and is stationary relative to the extension of the second end of the drum.

According to an additional aspect of a variant embodiment of the invention, the created method of service composition milling drum digging machine. The layout of the milling drum includes the axis of rotation, the first shaft along the rotation axis, the first end of the drum, bonded with the first shaft, a second shaft passing along the axis of rotation and spaced around the axis with the first shaft, the second end of the drum, bonded with the second shaft, the middle reel, located coaxially with the axis of rotation and passing between the first and second shafts, the first drive unit connecting the first shaft and the average drum capable of transmitting rotation of the second drive unit connecting the second shaft and the average drum capable of transmitting rotation of the first support bearing with the possibility of rotation of the first shaft and located between the first end of the drum and the secondary drum, the second support bearing for rotation of the second shaft and u is defined between the second end of the drum and the secondary drum, and swivel nozzle located slidable between the second support and the second shaft. The method includes disconnecting the many areas of the middle drum, the displacement of each of the specified portions radially from the axis of rotation, disconnecting the first drive unit from the first shaft, disconnecting the second drive unit from the second shaft, the second compartment of the drive unit from the second shaft and the Department of swing pipe from the second shaft. Many sections form the outer peripheral surface located around the axis of rotation. Branch of the first drive unit from the first shaft includes a first offset of the drive unit along the axis of rotation in the direction of the second shaft and then the offset of the first drive unit radially from the axis of rotation. The second compartment of the drive unit from the second shaft includes a second offset of the drive unit along the axis of rotation toward the first shaft and then the offset of the second drive unit radially from the axis of rotation. Department of swing pipe from the second shaft includes an offset rotary nozzle along the axis of rotation to the first shaft and then the offset of the rotary nozzle radially from the axis of rotation.

BRIEF DESCRIPTION of DRAWINGS

The accompanying drawings, forming part of this specification, illustrate preferred is sustained fashion embodiments of the invention and together with the General description, given above and the detailed description below, are intended to explain the features of the invention.

Figure 1 shows a view in plan of the drilling digging machine continuous action set in a drift mine, a couple of working parts of the rotary cutters to remove material from the bottom of the underground workings, when drilling a continuous miner advances in the roadway.

Figure 2 shows a side view of the drilling digging machine shown in figure 1, with one of the working parts of the rotary cutters and the configurations of the upper and lower milling drum, remove material, not remote working parts of the rotary cutter on the roof and working horizon output.

Figure 3 shows the front view of the drilling digging machine 2 with drift oval cut by the combination of a pair of working bodies of the rotary cutters and the upper and lower milling drums.

Figure 4 shows a schematic fragmentary view in plan of the layout of the bottom of the milling drum drilling digging machine figure 1-3, showing the drive drum and swivel installation on the front end of the drilling digging machine.

Figure 5 shows a schematic front view of the gearbox drilling digging machine and the supporting frame for the working parts of the rotary cutters and the upper and lower milling b is Rabanne removed from the working parts of the rotary cutter and the lower cutter drum.

Figure 6 shows a schematic, fragmentary side view of the front end of the drilling digging machine with rotary and the drive connection of the lower drum on the front end of the machine and the drive shaft of the rotary cutters to remove the working parts of the rotary cutter for clarity.

7 shows a schematic, fragmentary side view of the front end of the other side of the chisel digging machine, shown in Fig.6, with the top and bottom of the milling drum and the drive shaft of the working body of the rotary cutter.

On figa and 8b shows an alternative implementation of the drilling digging machine, comprising a lower milling mechanism.

On figa-9l shows an alternative layout of the bottom of the milling drum.

On film-9o shows isometric views of an alternative layout of the bottom of the milling drum figa-9l.

On figa-10l shows a schematic species composition corps gear milling drum figa-9o.

On film shows an isometric view of the layout of the hull gear figa-10l.

On figa-11h shows a schematic species composition of the intermediate shaft layout of the bottom of the milling drum figa-9o.

On figa-12d shows schematic views of an end of the drum layout of the bottom of the milling drum figa-9o.

On figa-13d pok which are schematic views of the extension end of the drum layout of the bottom of the milling drum figa-9o.

On figa-14i shows schematic views of the middle drum layout of the bottom of the milling drum figa-9o.

On fig.14j shows an isometric view of the layout of the drum figa-14i.

DETAILED DESCRIPTION of PREFERRED embodiments of the INVENTION

Figure 1-3 shows the drilling continuous miner 10 continuous steps installed on the roadway 12 mines, formed by side walls 14 and 16, a roof 18 develop and work horizon 20, harvested by the harvester 10. Continuous miner 10 is moving in the roadway 12 to remove solid material from the bottom of excavation (not shown). Material is removed from the bottom of excavation, when the continuous miner 10 is moving in the roadway 12, made in the configuration shown in figure 3, having rounded side walls 14 and 16 and horizontal or flat roof 18 develop and work horizon 20. The extracted material is removed from the bottom of excavation going on the continuous miner 10 and is transported back through the harvester, where it is transmitted to conventional transport equipment for transportation from the mine.

Continuous miner 10 has a housing or frame 22, duly established on tracks 24. Hydraulic motors (not shown) mounted on the frame 22 to move the digging machine 10 during operation of the extraction. Hydraulics is their motors can be controlled by the pump 26 and the block 28 management mounted on the frame 22, as shown in figure 1. The motors can also be used to move the digging machine 10.

Circular conveyor mechanism 30 is installed in the groove 32, passing longitudinally on the frame 22 of the harvester from the front end 34 to the rear swivel section 36 is reset. The rear section 36 of the reset is rotatable on a transverse axis, as shown by broken lines in figure 1. Conveyor section 34 of the front end includes a swivel mounted section 38, shown in Fig.7, passing forward from the front end of the frame 22. Swivel section 38 receives the remote extracted material, overload the working parts of the rotary cutters and the layout of the lower drum section 34 of the front end of the pipeline. The removed material is transported back conveyor mechanism 30 on section 36 of the discharge, where it is transmitted, for example, on a conveyor belt or into a truck for transportation from the mine.

As shown in figure 1, the movable frame 22 of the harvester carries a pair of motors 40 and 42 of the rotor having the drive shafts 44 and 46, passing forward through the main box gear 48 to the front ends of the sections 50 and 52 of the shafts. The sections 50 and 52 of the front ends of the shafts are installed spaced apart parallel to each other, ahead of the movable frame 22. Rotary or drilling cutters 54 and 56 are fixed connected with participants of the AMI 50 and 52.

As can be seen in figure 2 and 3, each rotor 54 and 56 includes many working bodies 58 of the rotor. Each working body 58 of the rotor is telescopic in length, and many cutting teeth (not shown) installed on each working body of the rotor. With this device the torque from the motors 40 and 42 of the rotor is transmitted to drive shafts 44 and 46 on the rotors 54 and 56, rotating in opposite directions. Working bodies 58 of the rotors 54 and 56 rotate in the promotion of the digging machine 10 forward to remove solid material from the bottom of the excavation.

The drilling action of the working bodies 58 of the rotor creates a General semi-circular side walls 14 and 16 on the bottom of excavation with opposite sides of the harvester 10, as seen in figure 3 and 5. Also drilling action formed ledges (not shown), protruding upwards from the working horizon of 20 and protruding down from the roof 18 of manufacture. Layout 60 of the lower drum and layout 62 of the upper drum, shown in figure 2-4 and 7, delete data ledges. Layout milling drums 60, 62 are guided rotatably in a lateral direction at the front end of the movable frame 22, the rear rotors 54 and 56, above and below them.

Link 60 and 62 milling drums are cylindrical in configuration with multiple cutting elements protruding from the surface BA is abanov. Link 60, 62 milling drums can be used to remove ledges protruding from the roof 18 and horizon 20 in the areas of bottom of excavation outside the path of the trajectories of the cutting working bodies 58 of the rotor.

According to the present invention, the bottom layout 60 milling drum is retractable in length. Layout 60 retracts to provide movement of the digging machine 10 in a position opposite the face of excavation, and from this provision. When the opposite face of excavation the ends of the link 60 drum nominated for removal from the working horizon at the base of the bottom of excavation material that is not removed working bodies 58 of the rotor. Arrangement 62 of the upper drum is fixed in length and performs a similar function remove ledges protruding down from the roof framing.

Link 60, 62 of the upper and lower cutting drum 60 are guided rotatably on the main box gear 48 of the frame 22 of the harvester. Link 60, 62 mounted on the front end 64 of the frame 22 of the machine and transversely to the longitudinal axis of the frame 22. As shown in figure 5, the arrangement 62 of the upper drum is a unitary structure supported for rotation with its end sections 66 and 68 to assemblies 70, 72 of the bearings. Btes is key 70, 72 bearing carries the upper end section of the box 48 transmission. In this position arrangement 62 of the upper drum removes material from the bottom of excavation on the roof 18 production outside peripheral trajectories cutting working bodies 58 of the rotor.

The rotation is transmitted to the layout 62 of the upper milling drum from the main box gear 48 through the lower gear 74 7. Reduction gearing 74 is a component box 48 transmission. Frame 76 on the gear box 48 is attached to the upper end of a pair of leveling cylinders 78, shown in figure 5-7. The cylinders 78 are connected by spherical bearings at their lower ends to the frame 22 of the harvester. Extension and retraction of the cylinders 78 vertically moves the front end of the box 48 of the gear relative to the frame 22 of the harvester for removing material when the harvester 10 is rolled on the road with a slope up or down.

Arrangement 62 of the upper drum and the support frame 64 are guided for vertical movement on the front end of the frame 22 of the harvester through a pair of pneumatic cylinders 79, schematically shown in figure 2, 3, 5 and 7. The cylinders of the pneumatic cylinder 79 is mounted on the front face of the main box gear 48. The retractable rod connected with the carrier frame 64. With this device arrangement 62 of the upper drum rises and the op is sketsa relative to the main box gear 48 upon actuation of the pneumatic cylinder 79.

The position of the link 62 milling drum is determined by the diameter of the barrel, cut the rotors 54 and 56. In one embodiment, the digging machine 10 operating parts 58 of the rotors 54 and 56 extended in length for sinking channels of a diameter in the range from 8 to 10 feet (2.4-3.1 m).

As shown in Fig.7, reduction gearing 74 for transmitting the drive to the top of the milling drum 62 includes a slave gear wheel 80, United-slots with the shaft 81 connected by splines with flange 82 with shear pin. The flange 82 is permanently connected by shear pins 83 with the slave flange 84. The flange 84 is permanently connected with the shaft 85 supported rotatably on a box of 48 transmission. The rotation of the wheel 80 and the shaft 85 is transmitted to the propeller shaft (not shown)connected to its end sections of the shaft 85 and the shaft 86.

The shaft 86 is connected with the possibility of transmission of drive force from the bevel gear wheel 87 which engages with the toothed wheel 88, in turn transmitting the rotation of the toothed wheel 90 and 92 on the upper milling drum 62. With this device arrangement 62 of the upper drum transversely installed on the selected mark on the frame 22 of the harvester. The rotation of the milling drum aligns or removes from the roof 18 develop a solid material that is not removed working bodies 58 is otara.

Layout 60 of the lower milling drum serves a similar purpose of removing solid material from the working horizon of 20 production, which is not deleted by the working bodies 58 of the rotor. As can be seen in figure 4 and 6, the arrangement 60 of the lower milling drum rests rotatably on box 94 transmission, swivel-mounted at the bottom of the box 48 transmission. Layout 60 of the lower milling drum includes a section 96 of the middle drum and a pair of raised sections 98, 100 end drums. Section 96 of the middle of the drum, shown in figure 4, has an outer sections 102 and 104 with a circular edge, and sections 98 and 100 end drums have an internal sections 106 and 108 with the annular edge, respectively. Sections 96, 98 and 100 of the drum include many of the cutting elements shown in Fig and 9, projecting from the sections of the drum.

As shown in Fig.6, the arrangement 60 of the lower milling drum rests on box 94 gear for rotary movement in contact with the working horizon of 20 and out of it. Box 94 rotary gear connected to the lower end section of the front end of the main box gear 48. Box 94 transmission comes forward from the box 48 transmission between section 96 of the middle drum sections 98, 100 end drums. The position of the rotation link 60 of the lower milling drum is in contact with the working horizon and it is determined by the diameter of the barrel, cut the rotors 54 and 56.

As can be seen in figure 4, box 94 transmission, which supports rotatably layout 60 of the lower milling drum, includes spaced housings 110 and 112, leaning forward in the gaps separating section 96 of the middle drum sections 98 and 100 end drums. The housings 110 and 112 are held back from sections of the drum to fork holders 114 and 116, a swivel connected to the main transmission gear 48.

Holders 114 and 116 are connected by brackets 118 and 120 extending from the area of the lower end of the box 48 transmission. The inserts 122 are held in the brackets 118 and 120 and placed a finger Assembly, generally indicated by the position 124. The finger 124 Assembly connects the fork holders 114 and 116 with the bracket 118 and 120.

The finger 124 Assembly includes a first pair of short finger 126 installed in the bushings 122. The fingers 126 are end-to-end channel for placing a long finger 128 of the tapered end sections 130. The fingers 128 pass through box 48 transmission. With this device box 94 transmission includes the housings 110 and 112, the bearing arrangement 60 of the lower milling drum set for rotary movement around the finger 124 mounted on the main gear box 48 harvester.

The conveyor 38 is also rotatable connected with elongated fingers 128, as shown in figure 4 and 7. As vidn the figure 4, the conveyor 38 includes a pair of speakers ago brackets 131. The brackets 131 include pass-through channels on the same axis with inserts 122 to accommodate the fingers 128. Support roller 132 at the front end of the conveyor 38 is rotatably one end of the chain conveyor passing along the conveyor tray 32. The chain conveyor is not shown in figure 4.

Preferably, box 94 gear milling drum rotatable connected to the brackets 118 and 120 on the main gear box 48, as shown in figure 4 and 6, to install the link 60 to the bottom of the milling drum in the position desired for the work of the working bodies 58 of the rotor nominated for cutting shafts 9 feet (2.7 m) and 10 ft (3.1 m) in diameter. A common axis of rotation of the gearbox 94 on the main gear box 48 is used for cutting diameters of the working bodies 58 of the rotor for cutting shafts 9 feet (2.7 m)and 10 ft (3.1 m) in diameter.

Working bodies 58 of the rotor can also be used for drilling, for example, a diameter of 8 feet (2.4 m). To adapt to the diameter of 8 feet (2.4 m) box 94 gear moves from the brackets 118 and 120. Then the brackets 118 and 120 is removed from the box 48 transmission and replaced by a second set of brackets 134. The brackets 134 form the axis of rotation on the axis of rotation formed by brackets 118 and 120. One of the brackets 134 shown in broken lines n is 6. The brackets 134 bolted to the bottom of the main box gear 48 of the harvester. Each bracket 134 includes the axis of rotation 136 (shown in Fig.6) to position the finger 124 in the collection, which carries a box of gear 94 to rotate on the gear box 48.

When turning the box gear 94 is rotated layout 60 of the lower milling drum relative to the main box gear 48. The rotation is accomplished by the action of a pair of cylinders 138 Assembly. Only one cylinder 138 Assembly shown in figure 5 and 6, but it should be understood that the cylinder 138 is mounted on each side frame 22 of the harvester.

Each cylinder 138 Assembly includes a cylinder 140, a swivel connected at the base with bracket 142 protruding from the main box gear 48. The retractable rod 144 extends out section 140 of the cylinder and connects the outer end section with bracket 146 mounted on the pressure plate 148 that is installed on the front end section of the box 94 transmission. Push plate 148 is held in its lower end portion, surrounding the layout 60 of the lower milling drum, as shown in Fig.6. In such an arrangement, extension and retraction of the rods 144 relative to the cylinder 140 rotates box 94 around the main gear box gear 48 to raise and lower link 60 of the lower milling drum into engagement with the working horizon of 20 and not the O. The position of the rotation link 60 of the drum for drilling diameters of 8 feet (2.4 m), 9 feet (2.7 m) and 10 ft (3.1 m) is shown in broken lines in figure 6.

Figure 4-6 shows the kinematic connection of the link 60 of the lower drum motor 40 of the rotor. As shown in Fig.6, the block 150 reducer installed on the box 48 transmission of the frame 22 of the harvester. Block 150 reducer is connected with the possibility of transmission of drive force in the usual way with the drive shaft 44 of the motor 40 of the rotor shown in figure 1.

Block 150 reducer includes a slave gear 152, United in the SPL with the shaft 153, which, in turn, is connected to the splined flange 154 on the shear studs. The flange 154 is permanently connected by shear pins 155 slave flange 156. The flange 156 is permanently connected with the shaft 157.

The shaft 157 is fixed rotatably in the gear box 48 and is connected with the possibility of transmission of drive force with a set of 158 bevel gears fixed for rotation in the vertical transfer box 159 fixed on the frame of the harvester main box gear 48. This device is similar to device downshift 74 described above for transmitting drive force to the layout 62 of the upper drum.

From the shaft 157 rotation is transmitted through a set of 158 cone is updateh wheel on a vertical shaft (not shown), fixed rotatably in the gear 159. The centerline 160 of the vertical shaft shown in Fig.6. The second set 162 bevel gear is connected with the lower end of the vertical shaft in the gearbox 159. Drive shaft 164 extends from the kit 162 bevel gears, propeller connected by a hinge (not shown) with the drive shaft 166 kit 168 bevel gears figure 4.

Set 168 bevel gear box carries gear 94 and it is connected with the possibility of transmission of drive force by means of the planetary gear 170 with layout 60 of the drum. Rotation from the planetary gear 170 is transmitted to the pinion gear 172. With pinion 172 rotation is transmitted through the middle gear 174 on the pinion gear 176 drum supported for rotation in a box 94 gear for transmitting rotation to a layout 60 of the lower drum.

On figa-14l shows an alternative implementation of the drilling digging machine 1000 continuous action. Because the overall configuration of an alternative implementation in General similar to those shown in figure 1-7, only the differences should be explained in detail.

On figa and 8b shows an alternative implementation of the drilling digging machine, comprising a kinematic connection, voltage is emer, from the drive shaft 164, shown in Fig.6, through drive shaft 1002, to the layout 1100 milling drum (figa). On fig.8b shows the plot of the right side of the lower beams 1110, the bearing arrangement 1100 of the lower drum on the front end of the movable frame 22.

On figa-9o shows the layout 1100 bottom of the milling drum, which includes the lower beam 1110, right section 1200 of the end drum section 1300 Central or middle drum section 1400 of the left end of the drum. The lower beam 1110 may be adjusted vertically relative to the movable frame 22 hydraulic cylinders 1112 (see fig.8b). The drive unit 1500 and layout 1600 intermediate shaft are sections of the drum for rotation relative to the movable frame 22. The drive unit 1500 is preferably between sections 1400 and 1300 drum, and layout 1600 intermediate shaft preferably is located between the sections 1200 and 1300 of the drum. Also it is shown that the position of the node 1500 and layout 1600 intermediate shaft can be reversed. The extension section 1250 of the right end of the drum is located at the outer end section 1200 and 1450 extension cord section of the left end of the drum is located at the outer end of section 1400.

Lots of cutting elements, such as incisors, teeth, etc. attached to the peripheral surface of each of the sections 1200, 100, 1400 drum extension 1250, 1450 drums and play them out. Cutting elements may be interchangeable. Rotation of the sections 1200, 1300, 1400 drum extension 1250, 1450 drum removes the ledges of solid material at the working horizon of 20 remaining cut the rotors 54, 56. Layout 1100 lower cutting drum cuts work horizon 20 adjacent to the bottom of excavation, forming, in General, a horizontal surface at the working horizon of 20 and forming the vertical sections 17 of the side walls 14, 16, as shown in figure 5.

Extension 1250, 1450 drums can be located on the axis between the involved configuration that is shown in figa-9n, and advanced configuration that is shown in Figo, relatively sections 1200, 1400 drum, respectively. Also on Figo shown hinged door 1004 related to tunneling processor 1000. When opening hydraulic door 1004, that is, pushing the door 1004 from the digging machine 1000 and moving up to him, adjustable protective shield to match the length of the layout 1100 of the lower drum, and thus the agreement forms the side walls 14, 16.

As shown in figa-10m, the drive unit 1500 includes a housing 1510, based on the area of the left side of the lower beam 1110. Torque for the drive unit 1100 lower milling drum lane is given by, for example, the drive shaft 1002, shown in figa, plug 1520 universal joint. As shown, in particular, on figd-10j, fork 1520 shaft connected for rotation with the input shaft 1522, which is based in the case 1510 to the bearings 1524a, 1524b. Kit 1526 gears in the right corner preferably includes a first bevel gear 1526a, United for rotation with the input shaft 1522, and the second bevel gear 1526b, United for rotation with the gear shaft 1528. The pinion shaft 1528 supported by bearings 1530a, 1530b for rotation relative to the housing 1510. Preferably, the pinion shaft 1528 includes a small gear wheel 1528a, mating for transmitting drive force to the intermediate gear wheel 1532, mounted on the intermediate shaft 1534, which is also supported in the housing 1510, for example, bearings 1536a, 1536b. In turn, the intermediate gear wheel 1532 bonded to transmit drive force to the output gear wheel 1538, is fixed to the output shaft 1540, which is also supported in the housing 1510, for example, bearings 1541a, 1541b. Accordingly, the plug 1520 shaft, input shaft 1522, kit 1526 gears right angle, the pinion shaft 1528, the intermediate gear wheel 1532 and the output gear wheel 1538 transmit the driving torque, such as from a drive shaft 1002, the output shaft 1540. Moreover, on the fair system of gears and shafts relies for rotation relative to the housing 1510 bearing which is preferably anti-friction bearings.

The following points explain the three main functions of the output shaft 1540 with specific references to fig.10j. First, the output shaft 1540 shall be capable of transmitting drive force of the drum 1410 left end section 1400. Secondly, the output shaft 1540 delivers drive torque to section 1300, 1200 drum. Thirdly, the output shaft 1540 carries with it the possibility of extension extension section 1450 1400 left end of the drum.

Preferably, the output shaft 1540 configured to mount 1540a, such as the mounting flange, to which is attached the left end of the drum 1410, for example, bolts or other fasteners. Mount 1540a shown in fig.10j near the outer end of the output shaft 1540, but may be located in any suitable position on the output shaft 1540. Accordingly, the drive torque generated on the output shaft 1540 via the output gear wheel 1538, is transmitted to the left end of the drum 1410.

Preferably the drive unit 1542 is located on the inner end of the output shaft 1540. Drive unit 1542 fastened to the output shaft 1540 and creates a docking surface for transferring drive torque to section 1300 of the drum. Preferably, the system 1544 seal is located along the axis between a driving unit 1542 and tubular extension 1545 connected to the housing 510. System 1544 seal, which may include a mechanical face seal, preferably connected directly with the output shaft 1540, for example, instead of connecting with a driving unit 1542. If drive unit 1542 not bonded to the output shaft 1540 and separated from it, can be improved access for inspection, maintenance or replacement of the system 1544 seal.

The third major function of the output shaft 1540, i.e. carrying the extension 1450 left end section of the drum for axial displacement between its extended and drawn configurations, is provided separately from the transmission of the drive torque to the left end of the drum 1410. In the axial channel 1540b in the outer end of the output shaft 1540 is a hydraulic cylinder 1546. Preferably, the hydraulic cylinder 1546 connected to the output shaft 1540 bolts or other fasteners 1546a, and, consequently, the entire hydraulic cylinder 1546 can be replaced as a single unit by removing the bolts 1546a. As easily understood, the hydraulic cylinder 1546 includes the body 1548 cylinder and piston 1550, essentially located in the housing 1548 cylinder rotatably about it. The piston preferably 1550 is connected by a rod 1552 piston also being located in the housing 1548 cylinder for rotation relative to it, with extension 1450 left end of selibaby. As shown in fig.10j, mount 1552a, that is, the mounting flange on the outer end of the rod 1552 piston can be used for fasteners, such as bolts or other fasteners extension 1450 section of the left end of the drum with the rod 1552 piston. The hydraulic fluid required to move the piston 1550 in case 1548 cylinder and thereby extending or retracting the extension 1450 section of the left end of the drum can be fed into the housing 1548 cylinder through pipelines 1554 passing through the output shaft 1540.

As shown in figa-11h, layout 1600 intermediate shaft includes a housing 1610, fixed on the plot right side of the lower beam 1110. In comparison with the case 1510 driving unit 1500, 1610 case does not include the kinematic chain. However, as specifically shown in fig.11d, shaft intermediate shaft 1640 similar output shaft 1540 rests in the housing 1610, for example, bearings 1612a, 1612b. Preferably, the intermediate and output shafts, 1640, 1540 are interchangeable.

Three main functions of the intermediate shaft 1640 described hereinafter with reference to fig.11d. First, the intermediate shaft 1640 shall be capable of transmitting drive force right-hand end drum 1210 section 1200. Secondly, the rotary pipe 1620 interacts with the intermediate shaft 1640 for the supply of hydraulic fluid required DL the work of extension 1250, 1450 drums. Thirdly, the intermediate shaft 1640 carries with it the possibility of extension extension section 1250 1200 right end of the drum.

Preferably, the intermediate shaft 1640 configured to mount 1640a, i.e. the mounting flange, to which is attached the right end drum 1210, for example, bolts or other fasteners. Mount 1640a shown in fig.11d near the outer end of the intermediate shaft 1640, but may be located in any suitable position on the intermediate shaft 1640. Preferably the drive unit 1642 is located on the inner end of the intermediate shaft 1640. Drive unit 1642 bonded with the intermediate shaft 1640 and creates the mating surface so that the drive torque can be transmitted from section 1300 of the middle drum via the intermediate shaft 1640 on the right-hand end drum 1210.

Swivel pipe 1620 includes a fixed section 1622, preferably coupled to the housing 1610, and the sliding section 1624 moved relative to the at least one stationary section 1622 and the intermediate shaft 1640. The sliding section 1624 of swing pipe 1620 may include an annular coil having multiple (two shown) channels 1624a, 1624b hydraulic fluids and many (six shown) o-ring 1626a - 1626f. Preferably, each of the channels 1624a, 1624b gidravlicheskigo includes an internal annular groove, an external annular groove and at least a channel connecting the inner and outer ring grooves. O-ring seals are located between the sliding section 1624, housing 1610, the shaft 1624 intermediate gears to isolate each pair of internal/external annular grooves. Swivel pipe 1620 facilitates the movement of hydraulic fluid between the source of hydraulic fluid under pressure, preferably located on the movable frame 22, the hydraulic cylinders to control the operation of the extension 1250, 1450 drums. Preferably, the system 1644 seal is located in the direction along the axis between a driving unit 1642 and swing pipe 1620. System 1644 seal, which may include a mechanical face seal, preferably connected directly to the intermediate shaft 1640, i.e. opposite to the connection with a driving unit 1642. If drive unit 1642 not bonded to the intermediate shaft 1640 and is separated from it, it is possible to improve access for inspection, maintenance or replacement of the system 1644 seal. If the system 1644 seal is not bonded with the intermediate shaft 1640 and is separated from it, it is possible to improve access for inspection, maintenance or replacement of the swing pipe 1620.

The third main function of the intermediate shaft 1640, i.e. carrying the extension section 1250 of the rights of the th end of the drum for axial displacement between its extended and drawn configurations, is provided separately from the transmission of the drive torque on the right-hand end drum 1210. In the axial channel 1640b in the outer end of the intermediate shaft 1640 posted by hydraulic cylinder 1646. Preferably, the hydraulic cylinder 1646 bonded with the intermediate shaft 1640 bolts or other fasteners 1646a, and, consequently, the entire hydraulic cylinder 1646 can be replaced as a single unit by removing the bolts 1646a. As easily understood, the hydraulic cylinder 1646 includes the body 1648 cylinder and piston 1650 located in the housing 1648 cylinder rotatably about it. The piston 1650 preferably is connected by a rod piston 1652, also located in the housing 1648 cylinder for rotation relative to it, with 1250 elongation of the right end of the drum. As shown in fig.11d, mount 1652a, for example, the mounting flange on the outer end of the piston rod 1652 can be used for fasteners, such as bolts or other fasteners extension 1250 section of the right end of the drum with the rod piston 1652. The hydraulic fluid required to move the piston 1650 in case 1648 cylinder and thereby extending or retracting the extension section 1250 of the right end of the drum can be fed into the housing 1648 cylinder through pipelines 1654, passing through the intermediate shaft 1640 and hydraulically connected with connecting the coupling to the channels 1624a, 1624b hydraulic fluid rotary Union 1620.

With regard to the output shaft and intermediate shaft 1540, 1640, many of their components can be used interchangeably, including drive units 1542, 1642, system 1544, 1644 seal section 1548, 1648 cylinders, pistons 1550, 1650 and the piston rods 1552, 1652. When many components are interchangeable, that is, compliance with them is essentially identical, it is possible to reduce the manufacturing cost and reduce the amount of storage of spare parts, etc.

On figa-12d shows more detail on the right end drum 1210. The main cylindrical housing drum 1210, 1410 can be made essentially identical, but then the orientation and pattern of cutting elements arranged on them consistently distinguish the right-hand end drum 1210 from the left end of the drum 1410. Accordingly, for purposes of the following description, the left end of the drum 1410 may, except as stated, to adopt similar right end drum 1210.

Right-hand end drum 1210 has a ring device located around the axis of rotation R. the Right-hand end drum 1210 includes a cylindrical housing 1212 having an external annular wall 1212a and the inner annular wall 1212b. Cutting elements attached to the outer annular wall 1212a cylindrical body and act on it. Dashed lines the and figs specified circle cutting, formed by the cutting elements during the rotation of the drum 1210 on the axis R of rotation.

As specifically shown in fig.12d, the outer annular wall 1212a preferably has an essentially constant outer diameter, while the inner end 1210a inner annular wall 1212b has a larger inner diameter than the outer end 1210b inner annular wall 1212b. Thus, the radial wall thickness of the end drum 1210 is greater at the outer end 1210b than on the inner end 1210a. Addressed to the axis of the surface 1212c passes radially inside the annular wall 1212b and separates the different wall thickness of the end drum 1210. Surface 1210c exactly Jive with the fastening 1650a on the outer end of the connecting rod 1650, may be bonded with him by bolts or other fasteners.

The end drum 1210 provided with curved sections of the outer end 1210b, it is possible to leave at least one jaw 1214 drum protruding along the axis outward. As shown in figa-12d, two curved jaws 1214a, 1214b drum are arranged symmetrically around the axis R of rotation. The number of circular form (provided there is no cutting), curved length, axial length, at least one jaw 1214 may change if at least one jaw 1214 is suitable for transmission of driving torque to extend the 1250 section of the right end of the drum. Although it is shown that one jaw of the drum may be along the axis outward, should the inclusion of several of the jaws of the drum arranged to create, in General, balanced rotation of the end drum 1210 around the axis R of rotation.

Preferably, the transverse faces 1216a, 1216b each at least one jaw 1214 have a high hardness, for example, created by the hardening or strain hardening. Accordingly, the transverse faces 1216a, 1216b are suitable for power tripping, due to rotation around the axis R of rotation, with the corresponding faces on the extension section 1250 of the right end of the drum.

Described below is shown in figa-13d details of extension section 1250 of the right end of the drum. The main buildings of the extension 1250, 1450 end drums can be made essentially identical, but then the orientation and pattern of cutting elements arranged on them consistently will give the differences between the extension section 1250 of the right end of the drum from 1450 extension cord section of the left end of the drum. Accordingly, for purposes of the following description, the extension section 1450 of the left end of the drum can be considered in other respects similar to the extension section 1250 of the right end of the drum.

The extension section 1250 of the right end of the drum has a circular device, also located around the axis R of rotation. The extension section 1250 of the right end of the drum includes at least one curved section of the cylindrical body 1252, which forms a partial outer annular wall 1252a and partial internal annular wall 1252b.

As specifically shown in fig.13d, partial outer annular wall 1252a preferably has an essentially constant outer diameter, while the inner end 1250a partial inner annular wall 1252b may have a smaller inner diameter than the outer end 1250b partial inner annular wall 1252b. Thus, the radial wall thickness of the extension section 1250 of the right end of the drum may be smaller at the outer end 1250b than on the inner end 1250a. Directed along the axis of the flange 1252c fixed to the inner annular wall 1252b and can divide the different wall thickness of the extension section 1250 of the right end of the drum. Flange 1250c just joined mount 1640a intermediate shaft 1640 and can be bonded with him by bolts or other fasteners.

At least one curved section of the cylindrical housing 1252 creates at least one jaw 1254 extension of the drum, the protruding inward along the axis. As shown in figa-13d, two curved jaws 1254a, 1254b extension drum symmetrically arranged around the axis R of rotation. The number of circular shape (the ri no cutting), the curved length, axial length, at least one jaw 1254 extension of the drum can be changed if at least one jaw 1254 extension cable reel is suitable for receiving drive torque from the right end drum 1210. Although it is shown that one jaw may be along the axis inside, should the inclusion of several jaw extension cable drum arranged to create, in General, balanced rotation of the extension 1250 end of the drum around the axis of rotation R.

Preferably, the transverse faces 1256a, 1256b each at least one jaw 1254 have a high hardness, for example, created by the hardening or strain hardening. Accordingly, the transverse faces 1256a, 1256b are suitable for power tripping, due to rotation around the axis R of rotation, with the lateral edges 1216a, 1216b on the right-hand end drum 1210.

Cutting elements bonded with partial outer annular wall 1252a at least one curved segment of a cylindrical section of the housing and protrude from it and can also be bonded with the flange 1250c and to act on it. Dotted lines on figs show the circumference of the cut formed by the cutting elements when the extension section 1250 of the right end of the drum rotates on the axis R of rotation.

Hydraulic cylinder 646 in the intermediate shaft 1640 shifts the extension 1250 right end of the drum in the axial direction between extended and drawn configurations, that is, so that there is relative axial sliding between the lateral edges 1216a, 1216b, 1256a, 1256b. Right-hand end drum 1210 causes the rotation of the extension 1250 around the axis R of rotation, i.e. due to the force of contact between the lateral edges 1216a, 1216b, 1256a, 1256b. Thus, individual efforts are created for torque transmission and for extension/retraction of the extension relative to the drum.

The following describes the details section 1300 of the drum with links to figa-14j. Section 1300 of the middle drum includes a cylindrical housing formed by many (shows two plots 1310a, 1310b housing middle of the drum. Preferably, the sections 1310a, 1310b bolted in the usual way with one another for the formation of a hollow tube. The number and the length of the arc sections of the housing middle of the drum may change subject to section 1300 of the middle drum suitable for transmission of drive torque from the output shaft 1540 on the intermediate shaft 1640. In addition, it is necessary that the section 1300, as the unit was, in General, is rotationally balanced about the axis of rotation R.

The internal surface of the section 1300 preferably forms a mating surface 1320, 1330 for joint engagement of drive units 1542, 1642, respectively. For example, as shown in fige and 14f, each of the surfaces 1320, 1330 forms a square is twistie, and lots of drive units 1542, 1642 everyone has, in General, a square cross-section (for example, see figa). Also it is shown that the mating surface 1320, 1330 may form apertures of various shapes and drive units 1542, 1642 may have respective cross-sections of various shapes. In addition, small differences (for example, approximately 0,030-0,40 inch(0.8-1.0 mm)hole size relative to the size of the cross section can give admission to nesovpadenija between the drive blocks 1542, 1642.

Cutting elements bonded with section 1300 of the middle drum, and act out of it. In General, the diameter of the cut formed by the cutting elements when the section 1300 is rotated on the axis R of rotation equal to the diameter of the circumference of the cutting sections 1200, 1400 drum.

Section 1300 of the middle drum spaced around the axis with section 1200 of the right reel section of the housing 1510 driving unit 1500. Similarly, section 1300 of the middle drum spaced around the axis with section 1400 of the left drum corps 1610 layout 1600 intermediate gears.

Preferably, replacement hydraulic hoses 1350, 1352 create a hydraulic connection between the channels in 1554 the output shaft 1540 and channels in 1654 intermediate shaft 1640. Hydraulic hoses 1350, 1352, preferably located in a hollow pipe formed in sections 1300, includes a first connecting IUF is s 1350a, 1352a channels 1554 and includes a second coupling 1350b, 1352b channels 1654. Thus, one pair of channels 1624a, 1624b hydraulic fluid in the rotary pipe 1620 can be used to target and simultaneously control the extension or retraction of the extension 1250, 1450, the left and right of the reels. Alternatively, additional channels hydraulic fluid in the rotary pipe 1620 and an additional separate channels in the shafts 1540 intermediate gears can be hydraulically connected by a removable hydraulic hoses 1350, 1352 channels 1554 in the output shaft 1540 with independent means to control the extension or retraction of the extension 1250, 1450, the left and right of the reels. Moreover, additional pivoting nozzle (not shown) can be located in the housing 1510 for hydraulic connection directly with the channels in 1554 the output shaft 1540, thereby eliminating the need for hydraulic hoses 1350, 1352.

If parcels 1310a, 1310b the case of the middle drum to rastrapati, for example Unscrew the bolts, then separate from one another and individually removed, it is possible to improve access to replacement hydraulic hoses 1350, 1352 and the inner ends of the output shaft and intermediate shaft 1540, 1640. Then, as discussed above, optionally, to improve access for inspection, maintenance or replacement of the s swing pipe 1620 and internal systems 1544, 1644 seal.

With links to figd-14i, the following describes a preferred procedure for disassembly of section 1300 of the middle drum.

The first one of the sections 1310a, 1310b housing middle of the drum set so as to be able to reset it down, for example, when splitting a seam between horizontally oriented sections 1310a, 1310b housing middle of the drum (see fig.14h). Then remove the bolts or other fasteners, fastening together the sections 1310a, 1310b housing middle of the drum. If the lower parts 1310a, 1310b the case of the middle drum is not a dive, it is necessary, at least partially re-fasten together parts 1310a, 1310b housing middle of the drum and then turn section 1300 of the middle drum 180 around the axis R of rotation. To carry this out, because the first one of the sections 1310a, 1310b housing middle of the drum is sealed only with the second one of the sections 1310a, 1310b housing middle of the drum, while the second one of the sections 1310a, 1310b housing middle of the drum remains resting on the mounting 1340, 1342 relative to the drive units 1542, 1642, respectively. For example, starting from the middle of the drum 1300 installed, as shown in fig.14h, plot 1310a housing middle of the drum must be separated from section 1310b corps medium drum when lashing bolts connecting sections 1310a, 1310b corps medium is Araban. Then section 1310b housing middle of the drum can be rotated 180 for installation in the position shown in Fig, with stoppers 1340, 1342 supporting section 1310b housing middle of the drum relative to the drive units 1542, 1642. Then latch 1340, 1342, you can release the section 1310b housing middle of the drum, and section 1310b corps medium drum should fall with the drive units 1542, 1642. Reassembly is done in reverse of the above disassembly procedure.

The above-described drilling tunneling machines create a number of advantages. For example, when creating a piston extension/retraction operating in hydraulic cylinders located on the axis of rotation, it becomes possible separation efforts to transfer torque to the extension/retraction of the cords relative to the drum and increase the number of telescopic axial overlap. Accordingly, this creates a more reliable system without the need to have a larger diameter lower the cutting mechanism and without increasing the number of telescopic parts, which must concentrically located around the rotation axis.

There are also a number of modifications. For example, another external source of hydraulic fluid under pressure can alternatively or additionally be used for promotion/utgivare the extension cable drum relative to the drum. An additional source can be connected directly with each of the hydraulic cylinders, for example, through hydraulic couplings through the respective right and left sections of the drum only when you need the extension or retraction when drilling a continuous miner is not working. Such a device may exclude the rotary pipe and pipelines in the output and intermediate shafts or, with a suitable hydraulic circuit, can create backup backup system in case of failure of the rotary nozzle. An additional source may be preferred for a small number of cycles, that is, extensions and retraction of the extension cord reels, or the calibration of the milling drum, such as maintenance, etc.

In another contemplated modification created mechanical stop stop (stops) for fixing the position of the cords of the drum relative to the drum. Mechanical stop stop (stops), for example blocks to support advanced configuration extension of the drum, can be fixed in place by bolts so that the pressure in the hydraulic system, such as hydraulic cylinders, rotary nozzle, etc. could be discharged. At that time, when again you must change the configuration of the extension cord reel, mechanical stopping UE is p (stops) you can detach and delete.

Although the invention is disclosed with reference to some preferred embodiments of numerous modifications, substitutions and changes in the described embodiments are possible without departing from the sphere and scope of the invention defined in the attached claims and their equivalents. Accordingly, it is assumed that the invention is not limited to the described variants of implementation, but has the full scope defined by the language of the following claims.

1. Road header containing the mobile frame having a front end section, a variety of rotor configurations, containing many of the working bodies with rotary cutter located at a distance from each other on the front end section of the mobile frame, the layout of the milling drum, located ahead of the front end portion and containing the axis of rotation, located across the area of the front end of the mobile frame, a section of the first end of the drum, comprising a first shaft passing along the axis of rotation and including a first channel passing along the axis of rotation, the first end of the drum, attached to the first shaft, the extension of the first end of the drum, situated coaxially around the axis of rotation, a first piston located in the first channel rotatably carries the flax him, fixedly mounted relative to the extension of the first end of the drum and to move along the axis of rotation between the extended configuration of the extension of the first end of the drum and the involved configuration of extension of the first end of the drum, the first coupling that transmits torque between the first end drum extension of the first end of the drum, the section of the second end of the drum, comprising a second shaft extending along the axis of rotation and located at a distance along the axis of rotation from the first shaft and including a second channel passing along the axis of rotation, the second end of the drum, attached to the second shaft, the extension of the second end of the drum, located coaxially around the axis of rotation the second piston located in the second channel with the possibility of rotation relative to it, rigidly fixed relative to the extension of the second end of the drum and to move along the axis of rotation between the extended configuration of the extension of the second end of the drum and the involved configuration of extension of the second end of the drum, a second coupling that transmits torque between the second end drum extension of the second end of the drum, and the middle section of the drum, located concentrically with the axis of rotation and passing between the first and second shafts.
2. Continuous miner of claim 1, wherein the first and second couplings, each contains moving along the axis of the coupling having first and second sets of jaws, each of the first sets of jaws is located on a corresponding one of the first and second end drums, and each of the second sets of jaws is located on a respective one of the extensions of the first and second end drums.
3. Continuous miner according to claim 2, in which each moving along the axis of the clutch includes alternating jaw from the first and second sets of jaws which form the peripheral surface located around the rotation axis.
4. Continuous miner according to claim 2, in which the first and second sets of jaws contain having increased hardness of the mating faces.
5. Continuous miner of claim 1, wherein the first channel and the first piston to form a first hydraulic cylinder, and the second channel and the second piston form a second hydraulic cylinder.
6. Continuous miner according to claim 5, in which the first and second hydraulic cylinders are functionally connected so that the extended configuration of the extensions of the first and second end of the drum are provided in response to the first hydraulic signal, and the inverted configuration of the extensions of the first and second end of the drum about especially in response to the second hydraulic signal.
7. Continuous miner according to claim 1, in which the arrangement of the milling drum has a first bearing located between the section of the first end of the drum and the middle section of the drum and containing the first housing, the first bearing shaft made with the possibility of rotation relative to the movable frame, and a drive unit adapted for application of torque to the first shaft and a second bearing located between the section of the second end of the drum and the middle section of the drum and containing a second housing supporting a second shaft configured to rotate relative to the movable frame, and a rotary nozzle adapted to supply hydraulic fluid to the second channel from a source of hydraulic pressure.
8. Continuous miner according to claim 7, in which the drive unit contains a first set of gear wheels comprising a ring gear coaxial with the axis of rotation and attached to the first shaft, and a small toothed wheel that is in working engagement with the annular gear wheel.
9. Continuous miner of claim 8, in which the drive unit includes a second set of gear wheels comprising a first bevel gear fixedly mounted relatively small gear and the second bevel gear wheel that is working is azepine with the first bevel gear wheel and connected with the shaft, capable of transmitting torque to the layout of the milling drum from a source of torque.
10. Continuous miner according to claim 7, in which the rotary nozzle includes a fixed section attached to the second housing, and a sliding section that is moved relative to the at least one stationary section and the second shaft.
11. Continuous miner of claim 10, in which the sliding section of the swivel elbow includes the first channel of the hydraulic fluid that supplies the first hydraulic signal to offset the extension of the second end of the drum is in its extended configuration, and the second channel of the hydraulic fluid, the feed of the second hydraulic signal in the second channel to bias the second piston configuration venutolo extension of the second end of the drum.
12. Continuous miner in claim 11, in which the second shaft includes a first set of channels, creating a hydraulic connection between the first channel hydraulic fluid rotary Union and the first section of the second channel, partially educated first side of the second piston, and a second set of channels, creating a hydraulic connection between the second channel hydraulic fluid swing pipe and the second section of the second channel, partially educated second side of the second piston.
13. Pass the mini-combine harvester according to item 12, in which the first shaft includes a third set of channels, creating a hydraulic connection between the first set of channels and the first sector of the first channel, partially educated first side of the first piston, with the third set of channels capable of feeding the first hydraulic signal to offset the extension of the first end of the drum is in its extended configuration, and a fourth set of channels, creating a hydraulic connection between the second set of channels and the second section of the second channel, partially educated second side of the second piston, while the fourth set of channels capable of feeding the second hydraulic signal to offset the extension of the first end of the drum in vanutau configuration.
14. Continuous miner indicated in paragraph 13 additionally containing the first replacement pipeline connecting the first and third sets of channels, and the second replacement pipeline connecting the second and fourth sets of channels.
15. Continuous miner at 14, in which the middle section of the drum includes a hollow pipe, and first and second removable pipelines pass through the hollow tube.
16. Continuous miner of claim 1, wherein the middle section of the drum is capable of transmitting torque between the first section of the end drum section of the second end of the drum.
17. Prohod the ski harvester according to clause 16, in which section of the middle drum contains many sections forming the outer peripheral surface located around the rotation axis.
18. Continuous miner at 17, further containing a first drive unit located between the first shaft and the middle section of the drum and rotationally connecting them, and the second drive unit, located between the second shaft and the middle section of the drum and rotationally connecting them.
19. Continuous miner according to claim 1, additionally containing at least one door supported on a mobile frame, a pivotable between open and closed positions, located in the open position when extended configuration, at least one first extension and the second end of the drum and located in the closed position when drawn configuration, at least one first extension and the second end of the drum.
20. Method of service composition milling drum digging machine having an axis of rotation, the first shaft along the rotation axis, the first end of the drum, attached to the first shaft, a second shaft passing along the axis of rotation and located at a distance along the axis from the first shaft, the second end of the drum, attached to the second shaft, the middle reel, located coax the material with the axis of rotation, passing between the first and second shafts, the first drive unit that rotationally connecting the first shaft and the average drum, a second drive unit that rotationally connects the second shaft and the middle reel, the first support bearing for rotation relative to the first shaft and located between the first end of the drum and the secondary drum, the second support bearing for rotation relative to a second shaft and located between the second end of the drum and the secondary drum, and the rotary nozzle located slidable between the second support and the second shaft, the method includes the following stages:
disconnecting the many areas of the middle drum, forming an outer peripheral surface located around an axis of rotation; offset of each of the many sections radially from the axis of rotation; disconnecting the first drive unit from the first shaft;
branch of the first drive unit from the first shaft, which includes the offset of the first drive unit along the axis of rotation to the second shaft and then the offset of the first drive unit radially from the axis of rotation;
the second compartment of the drive unit from the second shaft, which includes the offset of the second drive unit along the axis of rotation to the first shaft and then the offset of the second drive unit radially from the axis of the treatment;
Department of swing pipe from the second shaft includes an offset rotary nozzle along the axis of rotation to the first shaft and then the offset of the rotary nozzle radially from the axis of rotation.
21. The method according to claim 20, in which the Department of swing pipe from the second shaft includes: removing the first holder of the seal from the second shaft, disconnecting the second holder seal from the second support and the destruction of the first and second holders seals, which includes the offset of the first and second holders seals along the axis of rotation to the first shaft and then the offset of the first and second holders seals radially from the axis of rotation.
22. The method according to claim 20, further containing service the first end of the drum, attached to the first shaft; the first service support, a carrier rotatably relative to the first shaft, the maintenance of a second end of the drum, attached to the second shaft and the second bearing, the bearing for rotation relative to a second shaft.



 

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FIELD: mining.

SUBSTANCE: invention is related to mining industry and may be used for performance of assembly works in mine openings. Actuator of mining machine comprises boom with crown arranged in it, reducer, reducer drive, mount platform arranged on two front levers and two back levers made in the form of hydraulic cylinders. At the same time levers and their fixation elements make a parallelogram mechanism, device for lifting and moving of mount platform. Device for lifting and moving of mount platform is arranged in the form of one lifting hydraulic cylinder, which is hingedly joined to mount platform, coaxially to hinged joints of front levers connection to mount platform. At the same time lifting hydraulic cylinder is installed at the sharp angle relative to horizontal plane of reducer and is hingedly joined to reducer in zone of back levers connection to mount platform with making of arm relative to hinged joint of front levers installed on reducer.

EFFECT: wider field of mount platform application in various designs of mining machine actuators, and also simplified design of mining machine actuator.

5 dwg

FIELD: mining.

SUBSTANCE: facility for milling and/or drilling rock or similar materials consists of spindle drum assembled on support and intended to rotate around axis; several rotating cutter spindles are installed in drum eccentric to axis of drum. On their ends projecting out of the spindle drum the cutter spindles bear working tools. At least two of cutter spindles are actuated from a common reducing drive, which has driven tooth gears stationary arranged on the cutter spindles and a common drive element interacting with driven tooth gears. Also the drive element and the spindle drum are assembled so as to provide their rotation relative to each other.

EFFECT: processing hard materials at high efficiency of milling, increased operation life of tools, high operational reliability and compactness.

55 cl, 22 dwg

Heading machine // 2328598

FIELD: engines and pumps.

SUBSTANCE: heading machine contains a frame supporting the running gear, an actuator reduction gear. A rotary actuator is fitted on the output shafts of the said reduction gear and consists of a cross-piece with four beams provided with loading scoops, the supplied loading ladles, a borer and starting borer, an electric equipment and hydraulic system. A space with volume not less than that of the bucket is arranged inside every rotary actuator cross-piece beam. All the said spaces communicate, via inlets and outlets, by means of a system of pipes, the inlets and outlets incorporating shut-off valves. The spaces of two adjacent cross-piece beams are filled with high-density a liquid. Note also, that an independent pump with a position pickup is built in the space of every beam, the said pickup being coupled with the cross-piece beam inlet and outlet shut-off valves.

EFFECT: automatic balancing of the rotary actuator cross-piece and ruling out its deviation from rectilinear movement.

5 dwg

Full-face machine // 2324052

FIELD: mining; apparatus for making arched tunnels in underground mining of minerals.

SUBSTANCE: machine includes frame whereon an undercarriage and working element drive gearbox are mounted together with a rotary working head being attached to output shafts of said gearbox. The working head consists of borer, pitching borer, cross element, each end of its arms having a loading bucket with a bottom and sidewalls, and conveyer. The front face bottoms of two loading buckets positioned on opposite arms of said cross element are slopped forward with respect to the machine displacement vector, and those of the other buckets - slopped backward with respect to the same vector.

EFFECT: cleaning-up with the full engagement of the bucket cross-section area; reduction of impact loads for the cross element; reduction of heating and increased wear of the bearings in the working head drive gearbox of the machine.

7 dwg

Full-face machine // 2324051

FIELD: mining; apparatus for making tunnels in underground mining of minerals.

SUBSTANCE: machine includes undercarriage representing a frame whereon caterpillar trucks are attached and trunnion axes of a working head gearbox together with a rotary working head, loading buckets, berm mills, cutting drums, gathering blades, conveyer and protection cowl mounted on supports of said frame. Hydraulic lift cylinders of the working head gearbox are attached to this frame, rods of said cylinders are attached to the working head housing and all rotating parts of said rods are set into bearings equipped with a force lubrication system. The lubrication system includes pump, pressure pipeline, manifolds and system of distribution tubes leading to gear shaft bearings of the gearbox. The undercarriage frame has two tightly closed cavities, wherein a pressure line between the pump and manifolds is positioned being made in the form of coils. Both cavities of the frame are filled with cooling fluid.

EFFECT: cooling of lubricating fluid within the lubrication system; increasing the life of gear shaft bearings of the machine gearbox; decreasing the ambient air temperature; enhancement of working conditions for the operating staff.

4 dwg

FIELD: cutting-loading machines for explosion-free cutting of deposits having complex structures.

SUBSTANCE: mining machine comprises frame with movement mechanism, boom with cutting crown and loading device. Crown has rock-cutting tools. Loading device is made as inclined rotary hoisting table with gathering arms and central drag conveyor. Frame may rotate with loading device installed thereon and with unloading conveyer. Cutting crown may rotate about axis of rotation with respect to longitudinal boom axis through φ angle defined in dependence of rock hardness. Rock-cutting members are made as disc cutters reinforced by hard-alloyed pins and freely rotating in staggered order around replaceable pins.

EFFECT: increased operational efficiency due to extended field of practical usage thereof and increased service life of rock-cutting members.

5 dwg

FIELD: mining.

SUBSTANCE: invention relates to minerals industry, particularly to treating combines for selective concavity of heavy, predominately potassic layers with rock interlayer. Combine for selective concavity of heavy potassic layer with rock interlayer includes casing, on ends of which there are mounted with ability of rotation in vertical plane two handles, each of which is outfitted by integrated rive and screw, and additional cutting block. Additional cutting block contains handle with integrated drive and screw, and is rigidly fixed to casing of combine. Fixed on body basis of cutting block is pivotally connected to carrier and hydro- thruster climbing of handle, which is rigidly connected to slider, installed in guide groove of carrier with ability of displacement with handle to bottom for value not less than width of screw, diametre of which is not more than power of top layer. Additionally end main screws of combine are implemented with diametre of not less than half of power of more heavy layer of stratum.

EFFECT: effectiveness increase of selective concavity of heavy layer with rock interlayer independently from capacity of the latter.

2 dwg

FIELD: mining.

SUBSTANCE: invention relates to mechanisation facilities for underground selective concavity of thin predominately potassic layers by treating combines. Combine for selective concavity of thin layers of minerals includes body, at ends of which there are mounted with ability of rotation in vertical plane two handles, outfitted by agreeably integrated drive and screw with loading shield, and carrier. One of handles allows rigidly fixed on it slider with ability of displacement of it with handle in guide channel of carrier to bottom for value not less than width of screw, diametre of which is not more than output of rock layers of roofing, located at break between bottom and transporter. Screw of other handle is implemented of diametre not less than half of total power of fall rock layers of roofing and mineral.

EFFECT: design simplification of combine, decreasing of its weight and reliability improvement in operation at selective concavity of thin layers with coal-cutting with stone of roofing.

2 dwg

FIELD: mining.

SUBSTANCE: invention concerns engineering and can be applied in mining industry. The combined cutter loader comprises frame, chassis, feeder unit, transporter, and effector, which includes one central and several side cutting drums and cased gears on handles fixed to the cutter loader frame with the help of a horizontal axis and hydraulic cylinders. At each side the central cutting drum is adjoined by two side cutting drums with their axes parallel and displaced against the central cutting drum axis so, that the gear cases are overlapped with the side cutting drums in the pit-face direction.

EFFECT: production of a combined cutter loader with improved performance and wider application range.

3 dwg

The invention relates to the mining industry, in particular to cutting bits for mining machines, and can be used in the design of Executive bodies of mining and mostly roadheaders for the destruction of mineral and synthetic materials in the extraction of minerals and the formation of openings in the soil, as well as in the design of the working bodies of road construction machinery in the construction and repair of roads

Mountain shearer // 2065959

The invention relates to the rock bodies of mining and road-building machines for different purposes

FIELD: mining.

SUBSTANCE: invention concerns engineering and can be applied in mining industry. The combined cutter loader comprises frame, chassis, feeder unit, transporter, and effector, which includes one central and several side cutting drums and cased gears on handles fixed to the cutter loader frame with the help of a horizontal axis and hydraulic cylinders. At each side the central cutting drum is adjoined by two side cutting drums with their axes parallel and displaced against the central cutting drum axis so, that the gear cases are overlapped with the side cutting drums in the pit-face direction.

EFFECT: production of a combined cutter loader with improved performance and wider application range.

3 dwg

FIELD: mining.

SUBSTANCE: invention relates to mechanisation facilities for underground selective concavity of thin predominately potassic layers by treating combines. Combine for selective concavity of thin layers of minerals includes body, at ends of which there are mounted with ability of rotation in vertical plane two handles, outfitted by agreeably integrated drive and screw with loading shield, and carrier. One of handles allows rigidly fixed on it slider with ability of displacement of it with handle in guide channel of carrier to bottom for value not less than width of screw, diametre of which is not more than output of rock layers of roofing, located at break between bottom and transporter. Screw of other handle is implemented of diametre not less than half of total power of fall rock layers of roofing and mineral.

EFFECT: design simplification of combine, decreasing of its weight and reliability improvement in operation at selective concavity of thin layers with coal-cutting with stone of roofing.

2 dwg

FIELD: mining.

SUBSTANCE: invention relates to minerals industry, particularly to treating combines for selective concavity of heavy, predominately potassic layers with rock interlayer. Combine for selective concavity of heavy potassic layer with rock interlayer includes casing, on ends of which there are mounted with ability of rotation in vertical plane two handles, each of which is outfitted by integrated rive and screw, and additional cutting block. Additional cutting block contains handle with integrated drive and screw, and is rigidly fixed to casing of combine. Fixed on body basis of cutting block is pivotally connected to carrier and hydro- thruster climbing of handle, which is rigidly connected to slider, installed in guide groove of carrier with ability of displacement with handle to bottom for value not less than width of screw, diametre of which is not more than power of top layer. Additionally end main screws of combine are implemented with diametre of not less than half of power of more heavy layer of stratum.

EFFECT: effectiveness increase of selective concavity of heavy layer with rock interlayer independently from capacity of the latter.

2 dwg

FIELD: mining.

SUBSTANCE: tunnelling machine includes movable frame having the front end section, multiple rotor assemblies containing many working members with rotor cutter, which are located at some distance from each other in the front end section of movable frame, assembly of cutter drum, which is located in the front of the front end section and contains rotation axis located across the section of the front end of movable frame, section of the first end drum, section of the second end drum and section of middle drum. Section of the first end drum includes the following: the first shaft passing along rotation axis and including the first channel passing along rotation axis; the first end drum attached to the first shaft; extension piece of the first end drum, which is located coaxially around rotation axis; the first piston located in the first channel with possibility of rotation relative to it, which is fixed relative to extension piece of the first end drum and offset along rotation axis between extended configuration of extension piece of the first end drum and retracted configuration of extension piece of the first end drum; the first coupling sleeve transmitting the torque moment between the first end drum and extension piece of the first end drum. Section of the second end drum includes the following: the second shaft passing along rotation axis and located at some distance along rotation axis from the first shaft and including the second channel passing along rotation axis; the second end drum attached to the second shaft; extension piece of the second end drum, which is located coaxially around rotation axis; the second piston located in the second channel with possibility of being rotated relative to it, fixed relative to extension piece of the second end drum and offset along the rotation axis between extended configuration of extension piece of the second end drum and retracted configuration of extension piece of the second end drum; the second connecting sleeve transmitting the torque moment between the second end drum and extension piece of the second end drum. Section of middle drum is located concentrically to rotation axis and passes between the first and the second shafts.

EFFECT: development of extension piece of drum of lower layout of cutter drum, which is supported irrespective of the main drum for relative extension and retraction.

22 cl, 63 dwg

Cutter loader // 2445456

FIELD: machine building.

SUBSTANCE: proposed cutter loader comprises running gear, feeder, conveyor and actuator. Actuator comprises central and peripheral driven cutting drums. Drum drive is fitted on conveyor by means of hydraulic cylinder horizontal axle. Two central cutting drums with parallel rotational axle overlap drum drive on the side of working face and are arranged between aligned peripheral drums.

EFFECT: expanded applications, improved operating performances.

2 dwg

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