Device for extracting mineral resources or for driving tunnels

FIELD: device for extracting mineral raw stock or driving mines and tunnels, possible use for extracting solid rock, such as platinum ore.

SUBSTANCE: device contains at least one driven rotary overlapping striking tool, bushing, eccentric shaft, drive, cycloid gearing and safety sleeve for cycloid gearing. Bushing is fastened in the body with possible rotation. Shaft of eccentric is connected by one end to tool and mounted in aperture of eccentric bushing with eccentricity relatively to axis of bushing and with possible rotation around axis of eccentric shaft. Driving shaft of drive is connected to bushing and to device for transferring rotation to shaft of eccentric. Cycloid gearing is positioned outside relatively to bushing and has input and output shafts, formed by eccentric shaft. Disk cam, cycloid on its external periphery, performs circular movement on external ring, having concentrically positioned roller supports. Safety sleeve is connected to external ring or tailing disk, mounted on the shaft of eccentric.

EFFECT: possible achievement of high tool speeds when using one drive in compact structure.

14 cl, 5 dwg

 

The present invention relates to a device intended for the extraction of mineral raw materials or for tunneling or underground workings or galleries.

It is known a device for the extraction of mineral raw materials or for tunneling, tunneling underground workings or galleries and containing at least one driven rotating overlapping impact tool, in particular for the extraction of hard rock, such as platinum ore or copper ore, and for tunneling or excavation, with bushing, mounted rotatably in the housing, the eccentric shaft, one end of which is connected to the instrument, installed in the specified hole bushing eccentrically relative to the axis of the sleeve and rotatably around the axis of the shaft, with a drive device, the drive shaft of which is connected with the sleeve and with a device for transmitting the rotation of the eccentric shaft (see, for example, European patent 1138869).

In this device for mining the eccentric shaft mounted in the sleeve, which can be set in motion with a drive head which carries the tool. The sleeve is balanced in the middle between her legs with opposed whose parameters are calculated for this instrument. To gain sinkovich bearings eccentric shaft in the sleeve, in particular, in relation to overlapping the force of the blow is applied through the eccentric shaft, additional reinforcing bearing housed in a front end protruding part of the sleeve. The transmission of the rotation shaft of the eccentric is carried out by using a separate drive for the eccentric. Have been proposed various designs that connect a single drive shaft with an eccentric.

In one design, the device is provided by reduction gearing, which has the outer crown wheel mounted centrally relative to the drive shaft of the drive in the enclosure that brings eccentric shaft in motion through the internal crown wheel of the hollow wheel attached to the shaft of the eccentric. In this system there are two separate drive for the eccentric shaft and the sleeve and is provided with the ability to control the direction of rotation and speed of rotation of the eccentric shaft.

Alternative design comprises a drive shaft connected to a sleeve capable of transmitting drive force and perceiving the axial pressure, the hydrostatic bearing at the shaft end of the eccentric. When using this construction, the rotation speed of the eccentric shaft are identical due to the eccentricity of the rotation frequency to the rising, and the specified speed can in any case be adjusted within the specified range with hydrostatic bearings. In the third system, the transmission of the rotational shaft eccentric from the outside is carried out using a gimbal mechanism, the driven parts, moving in accordance with the Cam profile, or a pair of toothed wheels.

To enable the notches even hard rocks, such as platinum ore, with a shock of overlapping tools required high circumferential speed of the instruments and, therefore, also relatively high rotation speed of the eccentric shaft. A second separate drive, as in the device in accordance with the prior art, reflects this profile of requirements, however, due to the compactness of the mountain harvester due to the need for more space for the second actuator Assembly. The problem of transmitting rotation of the second actuator to the end of the eccentric shaft, moving eccentrically relative to the body, cannot be solved using the structures described in General terms in the above text, which correspond to the profile of requirements for a high enough speed and enough large transmitted torque.

The purpose of the present invention is to create a device for the extraction of mineral is x raw materials or for tunneling or underground workings, ensuring attainment of the high peripheral speed of the tool when using one drive in a compact design.

This objective is achieved by a device for the extraction of mineral raw materials or for tunneling or underground workings, containing at least one driven rotating overlapping impact tool, in particular, for excavation of hard rock, such as platinum ore, or for tunneling or excavation, sleeve, mounted rotatably in the housing, the eccentric shaft attached at one end to the tool and mounted in the bore of the eccentric sleeve eccentrically relative to the axis of the sleeve and rotatably around the axis of the eccentric shaft, the actuator having a drive shaft connected with the sleeve and with a device for transmitting rotation shaft of the eccentric. According to the invention the device has cycloidal transmission located outside with respect to the sleeve and having input and output shaft, formed by the eccentric shaft, and at least one Cam disk, a cycloidal on its outer periphery and making a circular motion in the outer ring having spaced concentric roller bearing, and a safety clutch associated with the outer ring or madamimadam, mounted on the shaft of the eccentric.

The safety clutch is provided to protect cycloidal transmission and drive overload and possibly to limit the frequency of rotation of the eccentric shaft around its own axis and torque limiting. The safety clutch can be a clutch. Depending on the design cycloidal transmission friction clutch can operate in a radial direction or in an axial direction.

Cyclodina transfer may have at least one Cam disk attached with the possibility of transmission of torque to the shaft of the eccentric.

Cycloidal contour on the outer periphery of the Cam disk enables a separation of the Cam disk on curved areas with cycloalkyl circuit, resulting in each curvilinear section will correspond to the tooth in cycloidal gear engagement. Cam disk rotates concentrically around the axis of the eccentric shaft, while the roller bearing outer ring are concentric around the axis of the sleeve. In the presence of roller supports and cycloidal the geometry of the curved sections of the eccentric is provided "clean" the rolling of the Cam disk in the outer ring without slipping and without noteworthy loss of friction. Rotation of the eccentric disk, OEM home button Flex cable is provided in cycloidal transfer, immediately transmitted to the shaft of the eccentric.

The outer ring can be mounted for concentric rotation about the axis of the sleeve and the protective sleeve may serve as a brake force in the axial direction. In this case, the outer ring may preferably be attached with the possibility of transmission of torque to the supporting element for the spring-loaded friction pads, which can cuddle with adjustable force to the brake disk attached to the chassis with the ability to transfer torque. While not an overload, the outer ring with roller bearings firmly occupies a certain position, and the gear ratio between the rotational speed of the sleeve and the shaft speed of the eccentric determined solely by the number of curved sections. In case of an overload, the outer ring rotates together with the rotating sleeve, so that rotation speed of the eccentric shaft around its own axis may be reduced, possibly to zero.

In another embodiment, cyclodina transfer may have at least one Cam disk mounted rotatably on the shaft of the eccentric and having openings in which are guided the fingers of the slave drive. These notches and fingers can be located concentric with,and/or the rolling body can be fixed on the top surface of the fingers.

Safety clutch may include stretching kit to secure the slave drive on the shaft of the eccentric. Tensile set can be located between the axial protruding part of the slave disk, made in the form of a drum, and the outer surface of the shaft of the eccentric.

The clutch disc can be mounted rotatably on the shaft eccentric and the connecting device can be attached to the end of the eccentric shaft as a safety clutch. The connecting device may have friction pads located on the pressure plate, through which the springs pojate to the slave drive. Spring safety clutch can be a leaf spring, an elastic force which is adjustable by means of clamping screws and disks screed.

Several tools, including chisels, can be mounted on the holder, and placed upon its circumferential periphery, and the holder can be attached with the flexibility to change to another end of the shaft of the eccentric.

Cam disk can have multiple curved sections, the number of rolling elements exceeds the number of curved sections is exactly 1.

Option device for mining operations (mining and quarrying), made in accordance with this image is Itanium, will be described in more detail hereinafter with reference to the accompanying drawings, which depict the following:

figure 1 shows a schematic side view illustrating the functional principle of the extraction of platinum ore by the use of the mountain harvester having overlapping impact tool driven in rotation using cycloidal transfer;

figure 2 shows a schematic side view cycloidal transfer;

figure 3 shows a schematic longitudinal section of the mining machine in accordance with the first embodiment of the present invention;

figure 4 shows a schematic longitudinal section of the mining machine in accordance with the second embodiment of the present invention;

figure 5 shows the cross-section of an alternative implementation of the protection against overload, intended for cycloidal transmission, shown in figure 4.

Figure 1 shows the mountain harvester 10, which breaks up the split rock on the bottom 2 layers 3 platinum ore through overlapping and rotating tool 1 percussion for the extraction of this mineral. Tool 1, which may be in the form of bits, such as roller bit is attached to the holder 5, rotating around the Central axis MEthe shaft 4 of the eccentric, and performs at a rotational motion of the mountain to the of mbina 10 overlapped shock wave motion extraction, which shows the different faces 2, 2', 2", formed during the extraction. Wavy shock overlapped motion sharp ends of the bit 1 is achieved by mounting the shaft 4 of the eccentric in the bore of the sleeve 6, which can be driven with a drive rapid rotation, which will be explained below and which is not shown in figure 1 and 2. Rotation of the sleeve 6 around the Central axis MNsleeve causes rotational movement of the shaft 4 of the eccentric around the Central axis MNsleeve so that the tool 1 is attached to the holder 5 will be impact on the working face 2 and is displaced away from him. In order to combine percussion movement of the tool 1 with the rotational movement, the shaft 4 Cam interacts with the disk Cam 7 cycloidal transmission 20. Figures 1 and 2 clearly shows that the Cam disk 7 has a cycloidal contour on its outer circumferential periphery 8, and zone cycloidal (gear) gear with curved sections 9, 9', 9", 9"' etc. are formed with equal intervals identical to each other. Cam disk 7 is located inside the outer ring 11, which is concentric around the axis MNsleeve and provided with spaced concentric around the axis of the bodies 12 of the rolling elements, which interact with a curved sections 9, 9', 9", 9"'. B is thanks to the circular motion driven in rotation of the sleeve 6 of the Cam disk 7 moves inside the outer ring 11 and the rolling curved sections 9, 9', 9", 9"' on the bodies of 12 rolling. The direction of the circular motion of the Cam disk 7 in the outer ring 11 corresponds to the direction of rotation of the sleeve 6. The diameter of the Cam disk 7 is less than the diameter of the circle formed by the bodies 12 rolling, and in the shown embodiment, Cam disk 7 has a curved section 9, the number of which is one less than the number of roller bearings 12 of the outer ring 11. During each complete revolution of the sleeve 6 in the direction of rotation of the eccentric shaft (4) mounted in the sleeve with eccentricity, similarly makes a full rotation, resulting in curved areas 9, 9', 9", 9"' roll over the bodies of 12 rolling, and thanks to the rolling shaft 4 of the eccentric is shifted by one curvilinear section 9, 9', 9", 9"' against the direction of rotation of the sleeve 6 relative to the original position. This rotation of the Cam disk 7 in the opposite direction, the force caused cycloidal transmission 20 is transmitted to the shaft 4 of the eccentric, which in the result shift when rotating in the direction of the arrow E around the axis MEthe shaft of the eccentric. The rotation shaft 4 of the eccentric in a direction opposite to the direction of rotation of the sleeve 6, occurs with a change in the rotation frequency towards lower values, which is due to a reduction gear, and gear ratio definition what is the number of curved sections 9 of the Cam disk 7. The shaft 4 of the eccentric forms as the input shaft for cycloidal transmission 20, and its output shaft, resulting in the input rotation speed cycloidal transmission corresponds to the eccentric circular movement of the shaft 4 of the eccentric, and the output speed cycloidal transmission 20 corresponds to "own" the rotation shaft 4 of the eccentric relative to the axis MEthe shaft of the eccentric. 1 and 2 make clear that several curved sections 9, 9', 9", 9"' the Cam disk 7 are the bodies 12 of the outer ring raceway 11 in each position, and only a small number of curved sections, such as curvilinear section 9"," not transmit any effort. Therefore, when using cycloidal transmission 20 large torque can be transmitted smoothly, so that the transfer of energy is significantly improved compared to drives with gears even when using one Cam disk. The energy transfer can be improved by using multiple disk Cams, and thereby the load on each Cam disk can be reduced. Characteristics of impact from the side of the tool 1 can be selected in accordance with the listing requirements for mining operations by selecting the diameter and/or eccentricity of the shaft 4 of the eccentric relative to the axis ME

Figure 3 shows a schematic cross section of mountain harvester 10, which is equipped with cycloidal transmission 20 according to the first embodiment, it used the same reference numbers and symbols as in the description of the principles of using figures 1 and 2. Sleeve 6 mounted for rotation in the housing 21 by means of roller bearings 22 located on the side from which the tool is located (with the tool), and spherical roller bearings 23 on the drive side, and the sleeve 6 has a protruding portion 24 of the sleeve from the tool and is connected with the possibility of transmission of torque to the drum 25 in the form of a gear wheel on the drive side. The sleeve 6 is driven by a toothed wheel 17 mounted on the drive shaft 15 of the actuator 16 with great speed, the gear 17 with its outer teeth is engaged with the outer teeth of the drum, made in the form of a gear wheel. When working mountain harvester 10, the sleeve rotates around the axis MNsleeve, which coincides with the axis of the housing 21.

The shaft 4 is installed in the bore of the sleeve 6 with the eccentricity through the set with eccentricity from the tool self-aligning roller bearing 26 located in serving the Asti 24 bushing, and set eccentric self-aligning bearing 27 in the drum 25, is made in the form of a gear wheel. The result of using such a system bearing supports is that the eccentric shaft can rotate around the axis MEthe shaft of the eccentric, while it rotates with the circular movement of the sleeve 6. On the left side of the shaft of the eccentric, as shown in figure 3, by means of screws on the end 28 is fixed to the holder 5 on which tools 1 can be fixed with replacement. Between the end of the housing 21 and the rear side of the holder 5 and between the support ring 29 which serves to seal the protruding part 24 of the sleeve on the end, and the rear side of the holder 5 are sealing strips 30, 31, which provide isolation of the internal space of the housing 21 from the area outside the enclosure. To trim the sleeve 6, the counterweight 34 is attached to the protruding part 24 of the sleeve being provided according to the position of the sleeve hole and the weight of the eccentric shaft, and therefore the counterweight 34 is attached close to the tool 1 and to the front end of the shaft of the eccentric.

At the other end 32 of the shaft Cam inside the housing 21 and the outside relative to the sleeve 6 and the drum 25 is permanently attached to the sleeve, is cyclodina transmission 20 according to the first embodiment. In the embodiment, the wasp is estline according to figure 3 cycloidal transmission 20 includes a Cam disk 7, which is provided with the ability to transmit torque to the protruding part of the end 32 of the shaft of the eccentric and which is made with a cycloidal path or ring gear on the outer circumferential periphery 8. The contour of a cycloidal gear with a cycloidal curve plots 9, for example, can be seen in figures 1 and 2. Cam disk 7 is moving inside the outer ring 11, which is provided with roller bearings 12 serving as bodies which roll curvilinear sections 9, 12 body rolling, as further explained above, are located on a circular rail with a uniform distribution on it. Figure 3 shows that the upper roller bearing 12 is in contact with one of the curved sections the Cam disk 7, while the lower roller bearing 12' is not loaded and is free from contact.

The outer ring 11 bearing roller bearing 12 is concentric about the axis MNsleeve and can be attached to the housing 21 of the machine 10 is able to transmit torque. However, in the shown embodiment, cyclodina transmission 20 has a safety clutch 40, made in the form of axial brake that holds the outer ring 11, which is shown by way rotatably in the housing 21 in this its the position. With this purpose, the safety coupling includes attached to the outer ring 11 is able to transmit torque, for example, attached by screws, having the form of a cap supporting member 41, which has a disc-shaped portion 42, the rear side of which is provided with a friction lining 44 and is shaped drum portion 43, which is a package of 45 Belleville springs, which is pressing the presser plate 47 made with the second friction lining 46, and the brake disc 48. Having the form of a cap brake disc 48 with screws attached to the possibility of transferring torque to the end 33 of housing 21. The elastic force exerted by the package 45, disc spring, acts in the direction of the first friction lining 44, so that the bearing element 41 is held under the action of the applied pressure force, which can be adjusted by means of clamping screws 49 and plate 50 screed and which is transmitted through the friction pads 44, 46 on the brake disc 48, therefore, installed with the possibility of rotation of the outer ring 11 also held the same power and the same brake torque. In that case, if the torque submitted by the shaft 4 of the eccentric on the Cam disk 7 and transferred to the roller bearing 12 of the outer ring 11, exceeds a predefined tor Osney moment bearing element 41 can be displaced relative to the brake disc 48. In the result, the outer ring 11 rotates relative to the housing 21 and the Cam disk 7 in a circular motion, causing the frequency of rotation of the shaft 4 of the eccentric will decrease. In accordance with the same principle of overload coupling 40 can also be adjusted to pre-set the rotation speed of the Cam 4 in the extent regulated by the slippage between the brake disc and the bearing element.

Figure 4 shows a second variant implementation of the mountain harvester 110 cycloidal transmission 120 in accordance with a second embodiment of the design. Identical and similar elements are denoted by reference numbers, increased by 100. Structure for rotation of the sleeve shaft 106 and 104 of the eccentric in the housing 121, identical design in the embodiment according to figure 3, so that it cannot provide any additional re-clarification. The end 132 of the shaft of the eccentric drive side unlike the previous variant implementation, goes almost to the end 133 of the housing 121. The end 132 of the shaft of the eccentric bears in the area beyond the end of the sleeve 106, which is formed by the drum 125, made in the form of a gear wheel, a Cam disk 107, which, through the medium of the ring 113 of the roller bearings installed in the possibility of rotation on the shaft 104 of the eccentric or the end 132 of the shaft of the eccentric. Cam disk 107 also has a cycloidal outer circuit 108 with a cycloidal gear ring formed of curved sections 109, which interact with roller bearings 112, which is supported on the outer ring 111. The outer ring 111 is firmly attached to the housing 121, or it is formed of an annular flange of the housing. Cam disk 107 makes movements, as has already been described with reference to figure 1 and figure 2, in accordance with the circular motion of the shaft 104 of the eccentric in the outer ring 111, and its curved section 109 roll over the bodies 112 rolling. As a result of this Cam disk 107 is driven in the direction against the direction of rotation of the sleeve 106, the direction of rotation which corresponds to the circular motion of the eccentric shaft 104 of the eccentric. Rotation of the Cam disk 107 about the axis MEthe shaft of the eccentric, which is caused by the rolling sections of a cycloidal gear on roller supports 112, is transmitted to the slave disk 114 in cycloidal transmission 120 and is transmitted to the shaft 104 of the eccentric, so that, as was further explained above, there is a forced rotation of the shaft 104 of the eccentric around its axis MEand thus the shaft 104 is driven. To ensure the transmission of torque Cam disk 107 has cutouts 118 under the fingers, the arrangement is installed concentrically around the axis M Ethe shaft of the eccentric, and in these notches 118 includes fingers 119, which is attached to the radial portion 151 of the slave disk 114. On the fingers 119 can be mounted rolling element to reduce friction between the surfaces of the cutouts 118 under the toes and fingers 119. To connect with the shaft 104 of the eccentric with the possibility of transmission of rotation of the driven disk 114 has an axial protruding portion 152 in the form of a drum, which is located over the radial part 151 and which are fixed to the outer side of the end 132 of the shaft of the eccentric by means of "stretching" [spacer] set 153. When using the "stretch" box 153 can be implemented safety clutch in the form of functioning in the radial direction of the brake, because through "stretching" kit 153 maximum torque that can be transferred to the slave disk 114 at the end 132 of the shaft eccentric can be specified in advance. "Tensile" kit 153, for example, may include a cone-shaped "stretching" [spacer] rings 154, 155, the distance between which can be changed by means of screws not shown, and which interact with bushings 156, 157 with cone-shaped holes for installation of the slave disk 114 on the end 132 of the shaft of the eccentric in a state of stress [with "tension"]. In this case, the requirement is s can also be increased by using the friction lining or similar elements.

Figure 5 shows an alternative implementation of the safety clutch 240, which is provided for cycloidal transmission 220, which has a Cam disk 207 mounted on the shaft 204 of the eccentric by means of a ring 213 formed of the pillars, and the outer ring 211 tel 212 rolling and meets design cycledrome the actuator according to figure 4. Cam disk 207 has cutouts 218 under the fingers, which are driven fingers 219 which is fixed concentrically with the ability to transmit torque to the driven disk 214. The clutch disc 214 has a sleeve portion 260 at its inner circumferential periphery, which is installed with a minimum clearance for the protruding part of the end 232 of the shaft of the eccentric. The clutch disc 214 has a disc-shaped part 261, from the front side of which are driven fingers 219 and on the rear side which relies pressure plate 263, made with friction pads 264. Pressure plate 263 pojate to the rear side of the disc-shaped part 261 by means of leaf springs 265, while the elastic force of the plate springs 265 can be adjusted by means of clamping screws 266, plate 268 screed installed with the possibility of displacement in the axial direction, and drive 267 screed, which is provided with the ability to transmit torque to the tapered portion 234 konza eccentric shaft. In this case, the safety clutch 240 also functions as a clutch, and if the torque which can be adjusted through the leaf springs 265, is exceeded, the transfer of energy (power) from the slave drive 214 to the shaft 204 of the eccentric will be interrupted, so that the frequency of rotation of the shaft will fall.

To a person skilled in the art obvious a number of modifications that can be made on the basis of the preceding description and are within the scope of protection defined by the claims. The location and design of safety clutch is provided only as examples, and additional modifications will be obvious to those skilled in the art without further explanation. The figures in each case shows only one Cam disk, however, can also be provided by multiple disk Cams. In addition, other structural variants cyclonic gears can also be within the scope of protection defined by the claims, provided that they use the eccentric shaft as the input shaft and the output shaft, and cycloidal transmission is used in conjunction with overlapping working tools and devices impact. Device, or m the tire according to the invention can also be used for extraction of other mineral raw materials, such as other ore, copper ore, potash or rock salt, as well as for tunneling, underground workings or galleries in the layers of solid rock or other

1. Device for the extraction of mineral raw materials or for tunneling or underground workings, containing at least one driven rotating overlapping impact tool, in particular, for excavation of hard rock, such as platinum ore, or for tunneling or excavation, sleeve, mounted rotatably in the housing, the eccentric shaft attached at one end to the tool and mounted in the bore of the eccentric sleeve eccentrically relative to the axis of the sleeve and rotatably around the axis of the eccentric shaft, the actuator having a drive shaft connected with the sleeve and with device for transmitting the rotation of the eccentric shaft, characterized in that it has cycloidal transmission located outside with respect to the sleeve and having input and output shaft, formed by the eccentric shaft, and at least one Cam disk, a cycloidal on its outer periphery and making a circular motion in the outer ring having spaced concentric roller bearing, and a safety clutch associated with the outer ring or slave drive installed n the shaft of the eccentric.

2. The device according to claim 1, characterized in that the safety clutch is a clutch.

3. The device according to claim 1 or 2, characterized in that the at least one Cam disk attached with the possibility of transmission of torque to the shaft of the eccentric.

4. The device according to claim 3, characterized in that the outer ring mounted for concentric rotation about the axis of the sleeve.

5. The device according to claim 3, characterized in that the outer ring is attached with the possibility of transmission of torque to the supporting element for the spring-loaded friction pads capable of purse with adjustable force to the brake disk attached to the chassis with the possibility of transmission of torque.

6. The device according to claim 1, characterized in that the at least one Cam disk is mounted for rotation on the shaft eccentric and has cutouts are driven toes slave.

7. The device according to claim 6, characterized in that the cutouts and guided the fingers are concentric and/or rolling elements mounted on the upper surface of the fingers.

8. The device according to claim 1, characterized in that the safety coupling includes stretching kit to secure the slave drive on the shaft of the eccentric.

9. The device according to claim 8, characterized in that the tension to which the unit is located between the axial protruding part of the slave disk, made in the form of a drum, and the outer surface of the shaft of the eccentric.

10. The device according to claim 1, characterized in that the clutch disc fixed for rotation on the shaft eccentric and the connecting device is attached to the end of the eccentric shaft as a safety clutch.

11. The device according to claim 10, characterized in that the connecting device has a friction lining located on the pressure plate, through which the springs pojate to the slave disk.

12. The device according to claim 11, characterized in that the spring safety clutch constitute a leaf spring, an elastic force which is adjustable by means of clamping screws and disks screed.

13. The device according to claim 1, characterized in that several tools, in particular, the bit attached to the holder, and placed upon its circumferential periphery, while the holder is attached with the flexibility to change to another end of the shaft of the eccentric.

14. The device according to claim 7, characterized in that the Cam disk has several curved sections, the number of rolling elements exceeds the number of curved sections is exactly 1.

Priority items:

07.02.2002 - claims 1 to 14.



 

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The invention relates to mechanical engineering, in particular to the crankcase gear boxes, angle gear

FIELD: mining industry.

SUBSTANCE: combine has main body, drive, feeding mechanism and executive tool, which is made in form of drum with horizontal rotation axis. It is placed at non-straight angle to longitudinal conveyor axis and is turned in horizontal plane in direction providing for displacement of trajectory of coal output towards conveyor. Drum has cylinder, on outer surface of which in certain order cams with cutters are fixed. Inside the cylinder three or five electric engines are placed. These are inserted in parallel in recesses of fixed body with inner teeth of sun ring of planetary gear, which interact with three satellites. Output shafts of three or five electric engines interact with one common cog-wheel. It is placed coaxially with planetary gear and engaged with it by torsion shaft having two cog tail pieces. One of tail pieces interacts with inner slits of wheel hub, and another interacts with teeth of three satellites of planetary gear. Mechanism for hoisting drum mechanism along bed massive has handle raising jack and handle with horizontal rotation axis placed in horizontal plane at non-straight angle to conveyor axis and turned to direct displacement of executive tool towards pit-face. Shoes of stability mechanism for combine are provided with reverse clamps for shelves on front pit-face and back dump sides of conveyor. Back support of conveyor on soil is placed on dump end of inter-section beams. Combine feeding mechanism has drive for chainless feeding system and leading sprocket. Sprocket interacts with fingers of conveyor rack. Drive is placed beyond handle of executive tool and is made in form of separate electric engine with reducer of self-braking worm type. Engagement of sprocket with fingers is guaranteed by reverse clamp of reducer engaging back planes of conveyor rack carrying these fingers. In method for loading coal on conveyor, drum rotation axis in plane around vertical axis is turned in certain direction to turn trajectory of coal towards conveyor. Movement of mining drum along conveyor is performed first along ceiling, and then along soil along coal output direction while providing for cleaning of soil in direction of frontal movement of conveyor to pit-face.

EFFECT: lesser dimensions, lesser mass, higher quality of operation.

7 dwg

FIELD: mining industry.

SUBSTANCE: combine has main body, drive, feeding mechanism and executive tool, which is made in form of drum with horizontal rotation axis. It is placed at non-straight angle to longitudinal conveyor axis and is turned in horizontal plane in direction providing for displacement of trajectory of coal output towards conveyor. Drum has cylinder, on outer surface of which in certain order cams with cutters are fixed. Inside the cylinder three or five electric engines are placed. These are inserted in parallel in recesses of fixed body with inner teeth of sun ring of planetary gear, which interact with three satellites. Output shafts of three or five electric engines interact with one common cog-wheel. It is placed coaxially with planetary gear and engaged with it by torsion shaft having two cog tail pieces. One of tail pieces interacts with inner slits of wheel hub, and another interacts with teeth of three satellites of planetary gear. Mechanism for hoisting drum mechanism along bed massive has handle raising jack and handle with horizontal rotation axis placed in horizontal plane at non-straight angle to conveyor axis and turned to direct displacement of executive tool towards pit-face. Shoes of stability mechanism for combine are provided with reverse clamps for shelves on front pit-face and back dump sides of conveyor. Back support of conveyor on soil is placed on dump end of inter-section beams. Combine feeding mechanism has drive for chainless feeding system and leading sprocket. Sprocket interacts with fingers of conveyor rack. Drive is placed beyond handle of executive tool and is made in form of separate electric engine with reducer of self-braking worm type. Engagement of sprocket with fingers is guaranteed by reverse clamp of reducer engaging back planes of conveyor rack carrying these fingers. In method for loading coal on conveyor, drum rotation axis in plane around vertical axis is turned in certain direction to turn trajectory of coal towards conveyor. Movement of mining drum along conveyor is performed first along ceiling, and then along soil along coal output direction while providing for cleaning of soil in direction of frontal movement of conveyor to pit-face.

EFFECT: lesser dimensions, lesser mass, higher quality of operation.

7 dwg

Mountain harvester // 2243378
The invention relates to mining equipment

Mountain harvester // 2234600
The invention relates to mining and can be used for extraction of minerals by underground way through treatment uzkozahvatnoj harvesters

The invention relates to mining and can be used in the mining and coal industry

The invention relates to pulsed power systems, and is intended to create drilling rigs, hammers, hammers excavating and cleaning machines used in the mining and coal industry

The invention relates to coal shearers and can be used in the coal industry

Mountain harvester // 2171375
The invention relates to equipment for mechanization of extraction of natural resources in their production treatment faces underground

The invention relates to equipment for mechanization of excavation strong coal and other minerals from thin and very thin layers

The invention relates to equipment for mechanization of excavation strong coal and other minerals from thin and very thin layers

FIELD: mining industry.

SUBSTANCE: combine has main body, drive, feeding mechanism and executive tool, which is made in form of drum with horizontal rotation axis. It is placed at non-straight angle to longitudinal conveyor axis and is turned in horizontal plane in direction providing for displacement of trajectory of coal output towards conveyor. Drum has cylinder, on outer surface of which in certain order cams with cutters are fixed. Inside the cylinder three or five electric engines are placed. These are inserted in parallel in recesses of fixed body with inner teeth of sun ring of planetary gear, which interact with three satellites. Output shafts of three or five electric engines interact with one common cog-wheel. It is placed coaxially with planetary gear and engaged with it by torsion shaft having two cog tail pieces. One of tail pieces interacts with inner slits of wheel hub, and another interacts with teeth of three satellites of planetary gear. Mechanism for hoisting drum mechanism along bed massive has handle raising jack and handle with horizontal rotation axis placed in horizontal plane at non-straight angle to conveyor axis and turned to direct displacement of executive tool towards pit-face. Shoes of stability mechanism for combine are provided with reverse clamps for shelves on front pit-face and back dump sides of conveyor. Back support of conveyor on soil is placed on dump end of inter-section beams. Combine feeding mechanism has drive for chainless feeding system and leading sprocket. Sprocket interacts with fingers of conveyor rack. Drive is placed beyond handle of executive tool and is made in form of separate electric engine with reducer of self-braking worm type. Engagement of sprocket with fingers is guaranteed by reverse clamp of reducer engaging back planes of conveyor rack carrying these fingers. In method for loading coal on conveyor, drum rotation axis in plane around vertical axis is turned in certain direction to turn trajectory of coal towards conveyor. Movement of mining drum along conveyor is performed first along ceiling, and then along soil along coal output direction while providing for cleaning of soil in direction of frontal movement of conveyor to pit-face.

EFFECT: lesser dimensions, lesser mass, higher quality of operation.

7 dwg

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